KR100366451B1 - Evaporator combined with dual-tube and fins for refrigerator - Google Patents

Abstract

The present invention relates to an evaporator of a refrigerator, and more particularly, to an integrated dual tube evaporator in which a pair of refrigerant tubes and fins are integrally formed to improve heat exchange and flowability of cold air.

The integrated dual tube evaporator structure according to the present invention includes a pair of refrigerant pipes 52 and louver fins 30 formed therebetween, and a plurality of stages 58 formed of the refrigerant pipes 52 and louver fins 30. It is formed. The structural feature of the present invention is that no defrost pipe is provided between the pair of refrigerant pipes 52. Therefore, according to the above configuration, the amount of cold air flowing between the pair of refrigerant pipes 52 and the louver fins 30 can be increased, and the defrost heater 64 for the defrosting operation is provided separately from the evaporator 51. By installing in the lower portion of the effect of increasing the efficiency of the defrosting action.

Description

Evaporator combined with dual-tube and fins for refrigerator

The present invention relates to an evaporator of a refrigerator, and more particularly, to an integrated dual tube evaporator in which a pair of refrigerant tubes and fins are integrally formed to improve heat exchange and flowability of cold air.

First, referring to FIG. 1, the heat exchange between the refrigerant in the refrigerator and the cold air is as follows.

The refrigerant flows into the evaporator 4 located behind the freezer compartment 2 via a compressor (not shown), a condenser (not shown), and a capillary tube (not shown). The refrigerant circulates in the refrigerator in the evaporator 4 and performs heat exchange with the warmed cold air f1. In addition, the cold air f2 cooled by the heat exchange is introduced into the freezing chamber 2 by the blowing fan 6 again. This operation is repeatedly performed, and the inside of the refrigerator is kept at a low temperature.

At this time, the cold air circulated in the freezer compartment (2) and the refrigerating compartment (8) is introduced into the lower portion of the evaporator (4) through the return duct 10 in a state containing the moisture in the high-temperature, contained in the cold air (f1) As the moisture comes into contact with the low temperature evaporator 4 surface, it forms on the surface of the evaporator 4.

If this action is repeated, the frost formed on the surface of the evaporator 4 forms a thick layer, which in turn causes a decrease in the heat exchange performance of the evaporator 4. Therefore, the frost formed on the surface of the evaporator 4 is removed through the defrost heater (not shown) at regular intervals. This is called defrosting.

In addition, an evaporator mainly used in recent years for improving the efficiency of the heat exchange and defrosting is an integrated tritube evaporator.

Hereinafter, the configuration and operation of the conventional integrated tritube evaporator will be described in detail with reference to the accompanying drawings.

Figure 2 shows a longitudinal section of a conventional integrated tritube evaporator. According to this, a pair of refrigerant pipes 22 are located on the left and right sides, and the defrost pipe 24 is located at the center thereof. A refrigerant flows inside the refrigerant pipe 22, and a heating wire 26 is provided inside the defrost pipe 24. Defrosting is performed by the hot wire 26.

The pair of refrigerant pipes 22 and the defrost pipes 24 therebetween are connected by a flat fin-forming portion 28. The tritube evaporator is formed integrally, and the material is mainly used aluminum having excellent thermal conductivity. On the other hand, the plate-shaped fin forming portion 28 is formed into a louver fin (Louver fin) 30 to pass through the cold air (f1) flowing into the evaporator (4). This is illustrated in FIGS. 3 and 4.

3 shows a cross-sectional view of an integrated tritube evaporator. According to this, the louver fin 30 is formed between the pair of refrigerant pipes 22 and the defrost pipe 24. As described above, the louver pin 30 is formed from the fin forming portion 28. That is, the pin-shaped portion 28 on the plate is cut from the top to the bottom of the drawing, and to form the louver pin 30 by twisting the cut pieces so that the space of the cut portion at regular intervals. The cold air f1 flows through the spaced space.

4 is a longitudinal cross-sectional view of the line AA ′ of FIG. 3. According to this, it turns out that the angle | corner of the said louver pin surface 30a is 45 degrees. In addition, it can be seen that the cold air f1 flows through the spaced spaces between the louver pins 30.

As a result, the cold air f1 flows in the spaced space between the louver fins 30 and comes into contact with the surface of the louver fin 30 and also with the surface of the refrigerant pipe 22. Then, heat exchange is performed through the contact. In addition, the moisture contained in the cold air (f1) is formed on the surface of the louver pin 30, which is due to the operation of the heating wire 26 in the defrost pipe 24 located between the pair of refrigerant pipes (22). It will be removed at regular intervals.

However, the conventional integrated tritube evaporator presents the following problems.

First, since the defrosting tube 24 is formed between the pair of refrigerant pipes 22, the length between the refrigerant pipe 22 and the defrosting tube 24 is short, so that the fin forming portion 28 is a louver pin 30. Bits in the process formed by) have a limitation in the process. That is, according to FIG. 4, about 45 degree is suitable for the said twist angle. Thus, as shown in the figure, the louver fin 30 is in a form lying obliquely across the flow direction of the cold air (f1), which prevents the flow of the cold air (f1) heat exchange of the evaporator (4) There is a problem of lowering the efficiency.

Second, the gap between the refrigerant pipe 22 and the defrost pipe 24 is small, the twist angle of the louver pin 30 is formed as small as described above, the louver pin 30 and the louver pin 30 The space between is formed small. Therefore, the space between the louver fins 30 may be easily closed due to the frost formed on the surface of the refrigerant pipe 22 and the louver fins 30. This reduces the heat efficiency of the evaporator 4 by blocking the flow of cold air f1.

Third, the frosting takes place mainly at the bottom of the evaporator 4. This is because the cold air f1 contains a large amount of moisture at the inlet of the evaporator 4 into which the cold air f1 flows. However, according to the above, since the defrost pipe 24 is evenly distributed on the upper part of the evaporator 4, which does not need a defrosting operation, there is a problem that the efficiency of the defrosting operation is lowered.

Fourth, since the defrost pipe 24 is formed integrally with the pair of refrigerant pipes 22, it is difficult to insert the heating wire 26 into the defrost pipe 24, and both ends of the defrost pipe 24 are bent. The problem is that the handling of the losing part is very difficult.

Accordingly, an object of the present invention is to provide an evaporator having excellent heat exchange between air and a refrigerant and fluidity of the air by expanding a cold air passage.

Another object of the present invention is to provide an evaporator which can perform defrosting efficiently and has improved workability with respect to installation of the defrosting pipe.

1 is a side sectional view of a refrigerator showing a circulation structure of cold air;

Figure 2 is a cross-sectional view showing the extrusion shape of a conventional integrated tritube evaporator.

Figure 3 is a cross-sectional view of a conventional integrated tritube evaporator structure.

4 is a cross-sectional view taken along line AA ′ of FIG. 3.

Figure 5 is a longitudinal sectional view showing a preferred embodiment of the extrusion configuration of the integrated dual tube evaporator according to the present invention.

Figure 6 is a cross-sectional view showing a preferred embodiment of the integrated dual tube evaporator structure according to the present invention.

7 is a longitudinal cross-sectional view taken along a line A′-A ′ of FIG. 6.

Figure 8 is a longitudinal cross-sectional view showing a state in which the defrost heater is further mounted in the integrated dual tube evaporator according to the present invention.

Explanation of symbols on the main parts of the drawings

52 ....... Refrigerant pipe 54 ....... Fining part

56 ....... Loop pin 56a ...... Lubber pin face

58 ....... But 60 ....... Bending

62 ....... Holder 64 ....... Defrost Heater

66 ....... Support

A feature of the present invention for achieving the above object is, a plurality of louver fins are formed integrally formed between a pair of refrigerant pipes and a pair of refrigerant pipes through which the refrigerant flows, and the pair of refrigerant pipes and the louver fins It consists of being bent and molded in this multistage.

The surface of the louver pin is installed parallel to the flow of air flowing into the evaporator, it is preferable to further install a heater for defrosting at the lower end of the plurality of stages.

According to the present invention as described above, the space in which cold air flows between the louver fins formed between the pair of refrigerant pipes is widened, so that the heat exchange efficiency can be increased. Further, by separately installing the defrost heater under the evaporator, the efficiency of the defrosting operation is also increased, and since the defrosting pipe is not installed between the pair of refrigerant pipes, the manufacturing work of the evaporator is simplified.

Hereinafter, the configuration of the integrated dual tube evaporator according to the present invention will be described in detail with reference to the preferred embodiment shown in the drawings.

Figure 5 shows a longitudinal section of the integrated dual tube evaporator of the present invention. According to this, a pair of refrigerant pipes 52 are formed on both left and right sides. The pair of refrigerant pipes 52 are connected by a fin forming portion 54. In addition, the fin forming portion 54 is cut at right angles to the longitudinal direction of the refrigerant pipe 52, and twists the surface formed by the cutting to form a louver pin 56.

Therefore, the feature of the evaporator according to the present invention is that no defrost pipe is installed between the pair of refrigerant pipes 52. By doing so, the distance between the pair of refrigerant pipes 52 is formed to be long, and the length of the louver fins 56 formed between the pair of refrigerant pipes 52 can be formed to be long. In addition, since the defrosting pipe is not formed integrally with the refrigerant pipe 52, the troublesome work of installing the heating wire in the defrosting pipe is omitted.

Meanwhile, a state in which the louver fins 56 are formed between the pair of refrigerant pipes 52 is illustrated in detail in FIGS. 6 and 7.

6 shows a cross-sectional view of an integrated dual tube evaporator according to the present invention. FIG. 7 is a longitudinal cross-sectional view taken along line BB ′ of FIG. 6. Accordingly, it can be seen that the surface 56a of the louver fin 56 formed between the pair of refrigerant pipes 52 is formed in parallel with the cold air f1 flow path. That is, the angle of twisting the louver pin surface 56a is 90 degrees. Therefore, as shown in the figure, the cold air passing between the refrigerant pipes 52 may flow without being affected by the louver fin surface 56a, thereby increasing the heat exchange efficiency of the evaporator.

However, in the case of the integrated dual tube evaporator, since the defrost pipe is not installed between the pair of refrigerant pipes 52, it is necessary to install the defrost heater separately. This will be described with reference to FIG. 8.

8 shows a longitudinal cross-sectional view of the evaporator 51, showing a state in which a defrost heater 64 for defrosting is mounted. According to this, it can be seen that the evaporator 51 has a multi-stage stage 58 formed of a pair of refrigerant tubes and louver pins formed integrally with the pair of refrigerant tubes. The end 58 and the end 58 are connected by a bent part 60 in which the end of the end 58 is curved. The evaporator 51 is provided with holders 62 on both left and right sides thereof to support the multi-stage.

In addition, according to the figure, the defrost heater 64 is provided separately in the lower part of the evaporator 51. As shown in FIG. That is, the defrost heater 64 supported by the support parts 66 connected to one side of the left and right holder 62 is installed below the evaporator 51. Therefore, since the frost concentrated on the lower part of the evaporator 51 is effectively removed, it is possible to increase the efficiency of the defrosting work.

However, the method of installing the defrost heater 64 is not limited to that shown in the drawing. For example, the defrost heater 64 may be provided to overlap the lower portion of the evaporator 51, and the support 66 may be provided at the lowermost end of the evaporator 51.

Within the technical scope of the present invention, of course, many other modifications are possible to those skilled in the art.

Therefore, according to the integrated dual tube evaporator of the present invention, the following effects are expected.

First, since the plate surface of the louver fin formed between the pair of refrigerant pipes is installed in parallel with the cold air flow path, the flow of cold air is not disturbed by the plate surface of the louver fin. Therefore, the supply of cold air increases in the refrigerator and at the same time, the supply speed of the cold air is increased, thereby increasing heat exchange efficiency.

Second, since the defrosting pipe is not installed between the pair of refrigerant pipes, the space formed between the pair of refrigerant pipes and the louver fins is increased, thereby increasing the flow path of the cold air.

Third, as the space formed by the pair of refrigerant tubes and louver fins becomes larger, the closing of the cold air flow path due to the conception generated on the surfaces of the refrigerant tubes and louver fins is delayed.

Fourth, by installing the defrost pipe at the bottom of the evaporator without installing a defrost pipe between the pair of refrigerant pipes can effectively remove the frost that is concentrated in the lower portion of the evaporator can maximize the defrosting effect.

Fifth, the manufacturing process of the evaporator is simplified by not installing the defrost pipe between the pair of refrigerant pipes.

Claims (3)

A plurality of louver fins formed between the pair of refrigerant pipes and the pair of refrigerant tubes through which the refrigerant flows are integrally formed, and the pair of refrigerant tubes and the louver pins are bent in multiple stages of the refrigerator. Dual tube evaporator. The integrated dual tube evaporator of claim 1, wherein the surface of the louver fin is installed in parallel to the flow of air introduced into the evaporator. The integrated dual tube evaporator of claim 1 or 2, further comprising a heater for a defrosting operation installed at a lower end of the plurality of stages.