JPH03117860A - Condenser - Google Patents

Abstract

PURPOSE:To improve heat exchanging performance, to reduce the size and to save the refrigerant by connecting a refrigerant passage tube through a connector, and arranging the passage tube having small refrigerant passage sectional area from a refrigerant inlet side to an outlet side. CONSTITUTION:Refrigerant flowing from a refrigerant inlet tube 10 is heat exchanged in a refrigerant passage tube 1 of an inlet zigzag passage A, and fed into a connector 7. Refrigerant is fed into a refrigerant passage tube 2 of an intermediate zigzag passage B, heat exchanged, fed to a connector 8 and a refrigerant passage tube 3 of a zigzag passage C, thence fed through a refrigerant outlet tube 11 out of a condenser. The refrigerant in the passage A is in a gaseous state, the sectional area of a refrigerant passage 14 of the tube 1 is large, and the refrigerant is efficiently condensed. The passage B is in gas and liquid mixture state, the sectional area of the passage 14 is smaller than that of the tube 1, and the refrigerant is efficiently condensed. In the passage C, the refrigerant is completely liquefied, the sectional area of the passage 14 is smaller than that of the tube 2, no wasteful space exists in the passage of the liquid refrigerant, and a refrigerant flowing speed is accelerated. Accordingly, its condensing capacity is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a condenser used in air conditioners and refrigerators to condense a refrigerant from gas to liquid.

[Conventional technology]

A condenser condenses and liquefies a refrigerant that has been converted into a high-temperature, high-pressure gas by a compressor by cooling it by exchanging heat with a condensing medium whose temperature is lower than the condensing temperature of the refrigerant.

At this time, the refrigerant passage within the condenser is roughly divided into a gasification section near the inlet, a gas-liquid two-phase section near the intermediate condensation section, and a condensed liquid section near the outlet. In order to improve the heat exchange efficiency of such a condenser, the efficiency of the intermediate condensing section is a problem, and it is necessary to ensure a large heat transfer area, that is, a large cross-sectional area of the refrigerant passage.

However, in the condensate part near the outlet where supercooling occurs, if the cross-sectional area of the refrigerant passage is as large as in the condensing part, the refrigerant flow rate decreases, the refrigerant flow rate decreases, and the amount of heat dissipated ultimately decreases. Therefore, in the condensed liquid section near the outlet, which is supercooled, the cross-sectional area of the refrigerant passage does not need to be as large as the gasification section near the inlet or the intermediate condensation section.

In conventional condensers, the cross-sectional area of the refrigerant passage is constant from the inlet to the outlet, and few have taken the above points into consideration. A proposal that takes this point into consideration is JP-A-63-3
A proposal described in Japanese Patent No. 4466 is known. The condenser proposed by this proposal has multiple refrigerant passage pipes connected perpendicularly to the header and parallel to each other between two vertical headers on the left and right, and a partition plate is provided in the header to allow the refrigerant to flow simultaneously. By reducing the number of passage pipes, the refrigerant passage cross-sectional area is reduced from the inlet side to the outlet side.6 [Problems to be Solved by the Invention] However, the prior art described in the above publication does not This invention relates to a condenser having a structure in which a plurality of horizontal refrigerant passage pipes are connected in parallel between two left and right vertical headers, and is not applicable to condensers having a generally used structure.

On the other hand, in a conventional condenser consisting of a single meandering refrigerant passage pipe, the passage cross-sectional area is constant because the refrigerant passage pipe is formed of a flat extruded tube, and the size of this passage cross-sectional area If it is adjusted to the condensing part, the result will be too large in the condensate part near the outlet, as described above. As a result, there will be areas with high condensation ability and areas with low condensation ability,
Furthermore, this results in an increase in the size of the condenser and an increase in the amount of refrigerant charged. However, there is a limit to the size of the condenser, and there is a limit to improving the condensing performance without increasing the size of the condenser. Further, there is also a problem in that gradually changing the passage cross-sectional area of the flat extruded refrigerant passage pipe is extremely complicated.

The present invention has been made in view of the above circumstances, and aims to provide a condenser that uses a meandering refrigerant passage pipe to improve heat exchange performance, downsize, and save refrigerant. purpose.

[Means to solve the problem]

To achieve the above object, the present invention provides a refrigerant passage having at least two types of refrigerant passage cross-sectional areas in a condenser formed by meanderingly stacked refrigerant passage pipes and having fins joined between adjacent refrigerant passage pipes. The pipes are connected through at least one connector, and a refrigerant passage pipe with a small refrigerant passage cross-sectional area is arranged from the refrigerant inlet side to the refrigerant outlet side.

[Effect]

According to the above configuration, in a condenser having a meandering refrigerant passage pipe, the passage cross-sectional area can be changed. As a result, the appropriate heat transfer area, that is, the cross-sectional area of the refrigerant passage, can be selected in each of the gasification section near the refrigerant inlet, the intermediate condensation section, and the condensate section near the outlet, so that the entire condenser can generate heat. It is possible to maintain high exchange performance and improve condensation capacity. Furthermore, since there are fewer wasteful parts compared to conventional condensers, the condenser can be made smaller and lighter, and furthermore, the reduction in the internal volume of the condenser facilitates the use of less refrigerant.

〔Example〕

Hereinafter, one embodiment of the present invention will be described with reference to the drawings.

An embodiment of the present invention is shown in FIGS. 1 to 3.

In the figure, three refrigerant passage pipes 1, 2.3 having at least two types of refrigerant passage cross-sections are stacked in a meandering manner by porous flat tubes whose interiors are partitioned into a plurality of passages.

Bent portions on both sides of corrugated fins 4, 5, 6 are joined between adjacent flat side surfaces of these refrigerant passage pipes 1, 2.degree. 3 by brazing, soldering, or the like.

Further, as shown in FIG. 2, the refrigerant passage pipes 1, 2, and 3 have the same height and the depths become gradually shorter.

The refrigerant passage pipes 1 and 2 having different refrigerant passage cross-sectional areas are connected via at least one hollow tubular connector 7 whose both ends are closed with a lid 9, as shown in FIG. One ends of the refrigerant passage pipes 1 and 2 are inserted into the insertion ports L5 and 16 formed in the refrigerant passage pipes 1 and 2, and are firmly joined by brazing. Similarly, the refrigerant passage pipes 2 and 3 are also connected to the connector 8. Furthermore, a refrigerant inlet pipe 1 is provided at each end of the refrigerant passage pipes 1 and 3 that is not connected to the connector 7.8.
0 and a refrigerant outlet pipe 11 are joined and connected by brazing. In addition, the corrugated fins 4, 5.6 joined between the respective refrigerant passage pipes 1, 2.3 have the same size as the heat transfer area of each refrigerant passage pipe 1, 2.3, as shown in Fig. 2. It is adjusted to

In this embodiment, as shown in FIG. 1, all the refrigerant passages are divided into three groups: an inlet meandering passage A, an outlet meandering passage C, and an intermediate meandering passage B existing between them.
As shown in the figure, the middle part meandering passage B is the entrance part meandering passage A.
The refrigerant passage cross-sectional area is smaller than that of the outlet meandering passage C, and the refrigerant passage cross-sectional area of the intermediate meandering passage B is smaller. As a result, the cross-sectional area of the refrigerant passage is reduced from the inlet to the outlet, and the fins interposed between the refrigerant passages also form a condenser that is matched to the heat transfer area of each refrigerant passage pipe.

Note that reference numerals 12 and 13 shown in FIG. 1 are side plates provided above and below the condenser, and reference numerals 14 and 13 shown in FIG.
is the refrigerant passage.

Next, the operation of this embodiment will be explained. The refrigerant flowing from the refrigerant inlet pipe 10 in the upper part of the condenser passes through the refrigerant passage pipe 1 of the entrance meandering passage A while exchanging heat, and flows into the connector 7.

The refrigerant that has flowed into the connector 7 then flows into the refrigerant passage pipe 2 of the intermediate meandering passage B connected to the connector 7, passes therethrough while exchanging heat, and flows into the connector 8. Thereafter, the refrigerant similarly flows into the refrigerant passage pipe 3 of the outlet meandering passage C, passes through this, and then flows out of the refrigerant outlet pipe 11 to the outside of the condenser.

The refrigerant in the inlet meandering passage A is in a gasified state with a large volume. However, since the cross-sectional area of the refrigerant passage 14 of the refrigerant passage pipe 1 is set large, the heat transfer area is also large, and efficient refrigerant condensation is performed. Next intermediate meandering passage B
is a gas-liquid two-phase state in which a condensed and liquefied part of the refrigerant and an uncondensed gas part coexist. Therefore, the heat transfer area may be smaller than that of the inlet meandering passage A, and accordingly, the cross-sectional area of the refrigerant passage 14 of the intermediate meandering passage B is set smaller than that of the refrigerant passage pipe 1.

Therefore, condensation is efficiently carried out here as well.

Furthermore, since the refrigerant is completely liquefied in the outlet meandering passage C, the volume is small, and the cross-sectional area of the passage may be small. In accordance with this, the cross-sectional area of the refrigerant passage 14 of the outlet meandering passage C is set smaller than that of the refrigerant passage pipe 2, so there is no wasted space for the liquid refrigerant to pass through, and the amount of liquid refrigerant is reduced. Less is needed. Furthermore, since the refrigerant flow rate is also accelerated, the condensing ability is also improved.

According to this embodiment, as the refrigerant flows into the inlet meandering passage A, the intermediate meandering passage B, and the outlet meandering passage C of the supercooling section, the refrigerant gradually adjusts to the respective refrigerant conditions. Refrigerant passage pipes 1 and 2 with reduced refrigerant passage cross-sectional area
．． At the same time, we installed fins 4,5°6 that match the heat transfer area of the refrigerant pipes, making it possible to obtain an optimal condensation state, improving the heat dissipation performance of the entire condenser, and improving heat exchange performance. can be kept high. Furthermore, since there is no wasted space in the refrigerant passage, the use of refrigerant is promoted, and at the same time, the condenser can be made smaller and lighter.

In the above embodiment, the height of the refrigerant passage pipes 1, 2.3 is constant and the depth length is gradually shortened.
As shown in the figure, the depth and length of the refrigerant passage pipes 17, 18, and 19 may be constant, and the heights may be gradually decreased. In this case, the depths of the fins 20, 21 and 22 are also constant. Furthermore, although not shown, both the height and depth of the refrigerant passage pipe may be changed. Note that numerals 23 and 24 are side plates.

Furthermore, in each of the above embodiments, a case has been described in which connectors 7.8 for connecting refrigerant passage pipes having two different cross-sectional areas of refrigerant passages are arranged at the ends of each meandering passage. Connectors 28, 29 may be placed at appropriate positions in the refrigerant passages 25° 26, 27. In this case, the length of the refrigerant passage pipe can be set to suit the state of the refrigerant within the passage pipe. In addition, the code|symbol 30 is a fin.

The same effects as in the first embodiment can also be obtained by each of the embodiments described above.

In each of the above embodiments, three types of refrigerant passage pipes are used, but the number of types of refrigerant passage pipes is three.
The refrigerant passage pipes are not limited to the type, and an optimal condensing capacity can be achieved by using multiple types of refrigerant passage pipes depending on the purpose and combining them with fins that are compatible with the refrigerant passage pipes.

Further, the refrigerant passage tube is not limited to a porous flat tube divided into a plurality of passages, but may be a single flat tube.

〔Effect of the invention〕

As explained above, according to the present invention, the meandering refrigerant passage pipes provided in the condenser are configured in a plurality of types so that the refrigerant passage cross-sectional area sequentially decreases from the inlet side to the outlet side, Since they are connected through sequential connectors, an optimal condensation state can be obtained, radiation performance can be improved, and heat exchange performance can be maintained at a high level. Furthermore, since there is no wasted space in the refrigerant passage, the use of refrigerant is promoted, and at the same time, the condenser can be made smaller and lighter.

[Brief explanation of the drawing]

FIG. 1 is a front view showing one embodiment of the present invention, and FIG. 2 is a front view showing one embodiment of the present invention.
3 is a perspective view showing a separated state of the connector and refrigerant passage pipe in FIG. 1, FIG. 4 is a longitudinal sectional view showing another embodiment of the present invention, and FIG. The figure is a front view showing still another embodiment of the present invention. 1.2,3,17,18,19,25,26゜27...
・Refrigerant passage pipe, 4, 5, 6, 20, 21゜22.30・
...Fin, 7, 8, 28, 29... Connector. Kaguo Diagram J 4 - Linghai Meng f6a Men Helian 3 Diagram 3

Claims (1)

[Claims] 1. In a condenser formed by meanderingly stacked refrigerant passage pipes with fins joined between adjacent refrigerant passage pipes, the refrigerant passage pipes having at least two types of refrigerant passage cross-sectional areas are connected via at least one connector. A condenser characterized in that the refrigerant passage pipe is connected to the refrigerant passage and has a small cross-sectional area from the refrigerant inlet side toward the refrigerant outlet side.