KR101601085B1 - evaporator - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an evaporator, and more particularly, to an evaporator that facilitates discharge of condensed water generated during heat exchange by forming a louver of a fin from a side of an air inlet port to a straight or straight louver.

The evaporator of the present invention includes an upper header tank (10) and a lower header tank (20), which are spaced apart from each other by a predetermined distance. Tubes (31) and (32) having both ends thereof fixed to the header tanks (10) and (20) to form a heat exchange medium flow path and having a first row and a second row; The evaporator (100) includes a fin (50) interposed between the first heat tube (31) and the second heat tube (32) and forming a louver (40) And a front region (35) in which the louver (40) is not formed from the end of the first heat tube (31), which is a point where the first heat tube (31) do.

The evaporator of the present invention having the above-described structure effectively discharges or removes condensed water generated during heat exchange, thereby preventing heat exchange performance deterioration due to a decrease in flow rate, thereby enhancing heat exchange efficiency and inducing quick drying of the core in the evaporator It is possible to reduce the odor due to mold generation.

Heat exchanger, evaporator, pin, louver, condensate

Description

Evaporator {Evaporator}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an evaporator used in an air conditioner for an automobile, and more particularly, to an evaporator for facilitating the discharge of condensate generated during heat exchange by forming a louver of a fin part from a side of an air inlet port to a straight- will be.

Various heat exchangers are used for the purpose of reusing heat energy or for using the temperature lower or higher according to the application, and various heat exchangers are also provided in automobiles. The evaporator is a kind of heat exchanger, and is a component provided inside the air conditioner of the automobile, and is a cooling device for exchanging heat with the outside air to supply cold air to the automobile room.

FIG. 1 is a perspective view showing a conventional evaporator, FIG. 2 (a) is a partial plan view showing a conventional evaporator, and FIG. 2 (b) is a sectional view taken along the line AA 'shown in FIG. FIG. 3 is a perspective view showing the shape of a louver, FIG. 4 is a partial cross-sectional view showing a conventional evaporator, and FIG. 5 is a partial cross-sectional view showing a flow of a condensate of a conventional evaporator.

The conventional evaporator E includes an upper header tank 1 and a lower header tank 2, which are spaced apart from each other by a predetermined distance as shown in FIG. A tube (3) having both ends fixed to the upper header tank (1) and the lower header tank (2) to form a heat exchange medium flow path; A pin (5) interposed between the tubes (3); And a control unit.

The evaporator E having the above configuration is a cooling device in which a low-temperature heat exchange medium is circulated and the heat exchange medium is heat-exchanged with the outside air passing through the evaporator to allow cold air to flow into the automobile , The temperature of the inside and the surface of the evaporator becomes lower than the ambient temperature, and condensed water is present on the surface of the evaporator. However, when the condensed water remains on the surface of the evaporator, the condensed water not only acts as an obstacle to the flow of air but also degrades the heat exchange performance between the evaporator and the air.

1 and 2 show a conventional evaporator for a heat exchanger for a vehicle. As shown in FIG. 2, between the tubes 3 forming the circulating fluid flow path in the heat exchanger for exchanging the inside circulating fluid and the outside air such as the evaporator, the condenser or the radiator of the automobile air conditioner, ) Is enlarged so as to increase the heat exchange efficiency between the two fluids.

The fin 5 is in contact with the tube 3 through which the circulating fluid flows and exchanges heat with the tube 3 and also with the air in contact with the surface of the tube 3 so that the heat exchange rate between the circulating fluid and the air in the tube 3 The higher the thermal conductivity and the larger the specific surface area (specific surface area), the higher the heat exchange rate.

Accordingly, the fins 5 are generally made of a metal material having a high thermal conductivity and easy to be formed, such as aluminum, and in particular, a thin plate structure having a waveform capable of maximizing the specific surface area without causing resistance to fluid flow.

As shown in FIGS. 2 and 3, a portion of the incised portion is bent obliquely with respect to the direction of the air flow so that air entering the fin 5 Shaped louvers 4 are formed so as to be arranged at equal intervals along the air flow direction.

As shown in FIG. 4, the conventional louvers 4 of a conventional evaporator are symmetrically formed in a substantially V-shape at the center, and flow air flows through the shape of the louver group 4 through the V- To improve the heat exchange performance.

Referring to FIG. 5, a large amount of condensed water is generated on the inlet side where hot and humid air suddenly reaches the surface of the evaporator below the dew point. At this time, the group of louvers 4 having the existing V-shaped path has a disadvantage in that it can not easily discharge the condensed water 6 as shown in Fig. Of course, although the condensed water 6 is discharged through the cleaved gap, the discharge of the condensed water 6 is often delayed at the inlet side of the evaporator where a large amount of condensed water 6 is generated. Also, as shown in FIG. 3, the lobes 4, which are torn on both sides, block the flow of smooth condensate and the condensate drops increase the flow of air, making it difficult to discharge the condensate.

When the discharge of the condensed water is delayed, the condensed water enters the evaporator and blocks the air flowing into the evaporator. As a result, the pressure drop on the air side is increased, the flow rate is reduced, and the cooling performance is lowered. Thereby causing odor induction.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a method and an apparatus for reducing the pressure drop on the air side and a flow rate drop due to condensed water by facilitating the discharge of condensed water between the spaces between the first and second heat tubes And an area of direct contact with air of the heat exchanger due to condensed water is reduced, thereby eliminating the cause of deteriorating the heat exchange performance.

The evaporator of the present invention includes an upper header tank (10) and a lower header tank (20), which are spaced apart from each other by a predetermined distance. Tubes (31) (32) having first and second rows, both ends of which are fixed to the header tanks (10) (20) to form a heat exchange medium flow path; The evaporator (100) includes a fin (50) interposed between the first heat tube (31) and the second heat tube (32) and forming a louver (40) And a front region (35) in which the louver (40) is not formed from the end of the first heat tube (31), which is a point where the first heat tube (31) do.

The evaporator 100 may further include the louver 40 or the slit formed in the front region 35 in parallel with the air flow direction.

Also, the front region 35, the louver 40, or the slit may be formed in a range from a minimum of 20% to a maximum of 80% of the width of the first heat tube 31.

In the evaporator 100, the louver 40 formed on the fin 50 interposed on the first heat tube 31 in addition to the front region 35 may be provided at one side And the other side is formed in a downward direction.

The evaporator of the present invention having the above-described structure effectively discharges or removes condensed water generated during heat exchange, thereby preventing heat exchange performance deterioration due to a decrease in flow rate, thereby enhancing heat exchange efficiency and inducing quick drying of the core in the evaporator It is possible to reduce the odor due to mold generation.

Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

FIG. 6 is a perspective view showing the evaporator of the present invention, and FIG. 7 is a partial perspective view showing the evaporator of the present invention. FIG. 8A is a partial plan view showing the evaporator of the present invention, FIG. 8B is a sectional view of BB 'shown in FIG. 7A, and FIG. 9 is a partial sectional view showing a louver of the present invention. FIG. 10 is a partial cross-sectional view of the evaporator of the present invention, and FIG. 11 is a partial cross-sectional view of a condensed water flow of the evaporator of the present invention. FIG. 12A is a partial plan view showing an evaporator of another embodiment of the present invention, and FIG. 12B is a partial perspective view showing an evaporator according to another embodiment of the present invention.

6 and 7, the present invention includes an upper header tank 10 and a lower header tank 20, which are spaced apart from each other by a predetermined distance. Tubes (31) and (32) having both ends thereof fixed to the header tanks (10) and (20) to form a heat exchange medium flow path and having a first row and a second row; The evaporator (100) includes a fin (50) interposed between the first heat tube (31) and the second heat tube (32) and forming a louver (40) So that the louver 40 is not formed in the predetermined front area 35 of the first column tube 31 located, thereby facilitating the discharge of the condensed water.

8, the evaporator pin 50 and the louver 40 include a first heat tube 31 for forming a flow path of the circulating fluid of the evaporator to increase the heat exchange area with the outside air, And is interposed between the two row tubes 32.

The fin 50 is formed by folding a plurality of louvers 40, which are in the form of scales, at a predetermined angle of inclination by using a flat plate, and then bending to form a waveform.

7, the corrugated fins 50 provided between the first heat tube 31 and the second heat tube 32 are formed in a zigzag manner And the first and second heat tubes 31 and 32 are brought into contact with the upper and lower sides of the corrugated fin 50, So that the self heat of the two-row tubes 31 and 32 is radiated naturally and the heat exchange efficiency is increased by using the widened specific surface area. The fins 50 having a corrugated shape are formed in a state in which a plurality of louvers 40 are inclined at a predetermined inclination angle on an inclined plane.

Referring to FIGS. 8 and 10, the louver group 40 has a symmetrical structure at the center and forms a V-shape. And the louvers 40 are formed in a V shape so as to increase the heat exchange path through the long contact area of the V shape to improve the heat exchange performance. The pin 50 interposed on the first column tube 31 forms a louver 40 having a diagonal line shape with one side facing upward and the other facing downward and a pin 50 Form a louver 40 having a diagonal shape with one side facing down and the other facing upward.

At this time, the fins (50) interposed on the first heat tube (31) move from the end of the first heat tube (31), which is the point where the air meets the air in the width direction of the first heat tube The louver 40 is not formed in the front region 35 from the minimum 20% to the maximum 80% of the width of the heat tube 31. This is because a large amount of condensed water is generated due to the introduction of hot and humid air into one side of the first row tube 31 which is the first inlet of the air. However, the louver 40 is not formed in the front region 35, As shown, the condensate 60 is slidably moved in the direction of the arrow without being subjected to the resistance of the louver to facilitate the quick discharge of the condensate.

In the case of an evaporator having a large amount of condensed water, it is possible to smoothly discharge the condensed water by designating the front region 35 to 80%, and in the case of the evaporator having a small amount of condensed water, the front region 35 can be reduced by 20% It is possible to prevent the heat loss due to the reduced specific surface area of the louver 40 from being formed.

The pins 50 positioned in the same direction in the longitudinal direction of the header tanks 10 and 20 are arranged in the entire area of the first and second heat tubes 31 and 32, As shown in FIG. The front region 35 of the first heat tube 31 has a starting point where it meets the air with respect to the entire area of the first heat tube 31 (including the thickness of the tube).

That is, as shown in FIG. 8, the reference point S means 0%, and the reference point E means 100%.

9, in order to discharge the condensed water 60 flowing along the front region 35 of the first heat tube 31 between the first heat tube 31 and the second heat tube 32, The shape of the louver 40 remaining on the heat tube 31 is a diagonal shape in which one side is upward and the other side is downward. 10, the shape of the louver 40 induces the flow direction of the air in the direction of the gravity so that the condensed water 60 generated in the fin 50 is rapidly discharged to the first heat tube (31) and the second row tube (32). This makes it possible to suppress the propagation of bacteria such as fungus caused by the condensed water that has not been drained, and it is possible to prevent odors caused by such bacteria.

12, the fins 50 of the front region 35 interposed on the first heat tube 31 may be provided with louvers 40 or slits (not shown) formed horizontally along the flow direction of air, Slit may be formed. This is to increase the heat exchange specific surface area and to facilitate discharge of condensed water. The slit is formed by partially cutting the fin 50 and deforming it upwardly or downwardly. As with the louver 40, the slit is used as a means for improving the heat exchange efficiency and discharging the condensed water.

Although four louvers 40 formed in the horizontal direction are shown in FIG. 12, one or more louvers 40 may be formed.

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

Referring to FIGS. 10 and 11, the temperature of the inside and the surface of the evaporator is lower than the ambient temperature, and the condensed water 60 is present on the surface of the evaporator. The condensed water 60 is also generated in the fins 50 provided between the first heat tube 31 and the second heat tube 32 in order to increase the thermal efficiency. The louver 40 is not formed or formed in the horizontal direction along the air flow direction to smooth the discharge of the condensed water and the flow of the air to the remaining part fins 50 of the first heat tube 31 in the gravity direction The louver 40 is formed to allow the condensed water to be discharged between the first heat tube 31 and the second heat tube 32, as shown in FIG.

The rapid discharge of condensed water not only enhances the cooling performance by smoothly flowing the air, but also inhibits the generation of mold caused by the condensed water, thereby preventing bacterial contamination and odor.

It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims.

1 is a perspective view showing a conventional evaporator;

FIG. 2A is a partial plan view showing a conventional evaporator

2B is a cross-sectional view taken along line AA 'shown in FIG. 3A

3 is a perspective view showing the shape of a louver

4 is a partial sectional view showing a conventional evaporator

5 is a partial cross-sectional view showing the flow of condensate in a conventional evaporator

6 is a perspective view showing the evaporator of the present invention

7 is a partial perspective view of the evaporator of the present invention

8A is a partial plan view showing the evaporator of the present invention

8B is a sectional view of BB 'shown in FIG. 7A

9 is a partial cross-sectional view showing the louver of the present invention

10 is a partial cross-sectional view showing the evaporator of the present invention

11 is a partial cross-sectional view of the condensate flow of the evaporator of the present invention

12A is a partial plan view showing an evaporator of another embodiment of the present invention

12B is a partial perspective view of an evaporator according to another embodiment of the present invention.

Description of the Related Art

100: Evaporator

10: upper header tank 20: lower header tank

30: tube 31: first row tube

32: second row tube 35: front region

40: louver 50: pin

Claims (4)

An upper header tank 10 and a lower header tank 20 which are spaced apart from each other by a predetermined distance; Tubes (31) and (32) having both ends thereof fixed to the header tanks (10) and (20) to form a heat exchange medium flow path and having a first row and a second row; And a fin 50 interposed between the first heat tube 31 and the second heat tube 32 to form the louver 40. In the evaporator 100, The evaporator (100) A front region 35 formed rearward from an end portion of the first heat tube 31 which is a point where air coincides with the air in the width direction of the first heat tube 31 located on the first inlet side of air on the fin 50 ), The louver 40 formed on the fin 50 interposed on the first heat tube 31 except for the front region 35 conveys the air to the upper side of the louver 40, Side is a diagonal structure formed downward, Wherein the louver (40) or slit is formed in the front region (35) parallel to the air flow direction without blocking in the air flow direction. delete The method according to claim 1, Wherein the front region (35), the louver (40) or the slit is formed in a range from a minimum of 20% to a maximum of 80% of the width of the first heat tube (31). delete

Images