KR20030056379A - Small bore tube heat exchanger - Google Patents

Abstract

PURPOSE: A small bore tube heat exchanger is provided to improve dehumidifying performance. CONSTITUTION: A small bore tube heat exchanger includes a refrigerant tube(10) formed with a circular tube successively bent, and having a diameter(D) smaller than 5.5mm; and a plurality of heat transfer fins(12) arranged in parallel at regular intervals, fixed on the refrigerant tube by welding, and mounted to cross the bent refrigerant tube. The heat transfer fin is divided into a front part(121); and a rear part(122) contacting with flowing air after the front part. Width(W1) of the front part is 10-11mm, and width(W2) of the rear part is 12-15mm. An interval(RP) between the refrigerant tube penetrating the front part of the heat transfer fin and a refrigerant tube(10') penetrating the rear part of the heat transfer fin is 10-11mm. An interval between refrigerant tubes in each of the front part and the rear part of the heat transfer fin is 19-20mm. Humidify of air introduced through the front part of the heat transfer fin is reduced as passing the rear part of the heat transfer fin.

Description

Small bore tube heat exchanger

The present invention relates to a heat exchanger, and more particularly to a tubular heat exchanger is configured in which the heat transfer fin is asymmetrical.

In general, a fin tube type heat exchanger used in an air conditioner or the like has a circular tube having a predetermined length as shown in FIG. 'Bending in the form of a continuous (bending) a kind of a multi-layered refrigerant tube 10, and a plurality of parallel arrangements at regular intervals are attached to the refrigerant tube 10 by welding, apparently bent refrigerant tube It consists of the thin-panel heat-transfer fins 12 mounted in the form which crosses (10).

As shown in FIG. 2, the refrigerant tube 10 is generally double-passed through a single heating fin 12 in the width direction, and is alternately arranged. The center line between the front and rear refrigerant tubes 10 and 10 ′ (imaginary line on the drawing) is shown. When the heat transfer fin 12 is divided into two parts, the first contact portion 121 is first contacted with the flowing air (when thick arrows in the drawing) and the second contact portion 122 is later contacted with the first half 121. The width W1 and the width W2 of the second half portion 122 are configured to be the same.

In addition, the louver 12a is formed in the heat transfer fin 12 to improve heat exchange efficiency. The louver 12a is made by partially cutting the heat transfer fin 12 and bending the louver 12a. Since it is made in a manner, a slit (not shown) having the same area as the louver 12a is formed at one side thereof.

According to the conventional fin tube type heat exchanger, the refrigerant acts as an evaporator or a condenser by exchanging heat with outside air in the process of flowing through the refrigerant tube 10, and the heat transfer area of the refrigerant tube 10 is transferred by the heat transfer fins 12. Since the air passing through each of the heat transfer fins 12 is curved and flows by the louver 12a, the contact length between the air and the heat transfer fins 12 is longer than that of the flat heat transfer fins, thereby increasing the heat transfer efficiency of the heat exchanger. Is improved.

On the other hand, the general fin tube type heat exchanger has a diameter (D) of the refrigerant tube 10 is 7mm or more, it requires a relatively large amount of refrigerant loading, the overall volume can be seen as a large, the recent heat exchanger to compensate for this disadvantage The diameter D of the refrigerant tube 10 is a trend of being composed of a so-called narrow tube type of 5 mm.

The tubular heat exchanger has a structure in which the size of the heat transfer fins 12 is also reduced in order to prevent the efficiency of the heat transfer fins 12 from decreasing as the diameter D of the refrigerant tube 10 decreases.

When such a tubular heat exchanger is used as a condenser, there is no difference in performance from the existing heat exchanger because the heat transfer coefficient of the air is increased due to the heat transfer effect due to the temperature difference.

However, when used as an evaporator, the heat transfer action is performed by the temperature difference and the humidity difference, and the heat transfer fin 12 is also reduced in proportion to the diameter decrease of the refrigerant tube 10, so that the heat transfer fin 12 and the contact area of the air are reduced. This decreases and the wettability is lowered.

Therefore, when comparing the difference between the conventional heat exchanger and the capillary heat exchanger alone, it can be seen as the difference in the material transfer coefficient as shown in FIG. 3, and in the heat exchanger system to which the heat exchanger is applied, it can be understood as the dehumidification capacity as shown in FIG. 4. Can be.

In addition, the difference between the conventional heat exchanger and the tubular heat exchanger is as follows through the air diagram as shown in FIG.

First, in the existing heat exchanger, the air contacting the heating fins passes through the first half and the temperature is lowered without changing humidity (①-> ②), while the temperature and humidity are drastically lowered at the same time while passing through the second half (②-> ③). ), In the tubular heat exchanger, it can be seen that the humidity change (②-> ③ ') in the latter part of the heat transfer fin is far less than that of the existing heat exchanger.

Therefore, according to the conventional tubular heat exchanger as described above, since the dehumidification is performed in comparison with the conventional heat exchanger, a problem arises that the performance of the heat exchange system is lowered as a result.

The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a tubular heat exchanger having a dehumidification function by being made of an asymmetrical structure having different widths in the first half and the second half of the heating fin.

1 is a perspective view showing the structure of a general heat exchanger.

2 is a cross-sectional view showing the structure of a general heat exchanger.

3 is a graph illustrating a comparison of the mass transfer coefficients between the general heat exchanger and the tubular heat exchanger.

Figure 4 is a graph showing a comparison of the dehumidification capacity of the general heat exchanger and the tubular heat exchanger.

Figure 5 is an air line diagram showing a comparison between the general heat exchanger and the tubular heat exchanger.

6 is a cross-sectional view showing the structure of a capillary heat exchanger according to an embodiment of the present invention.

<Explanation of symbols for the main parts of the drawings>

10: refrigerant tube 12: heating fin

121: first half 122: second half

12a: louver

In order to achieve the above object, the tubular heat exchanger includes a refrigerant tube having a diameter of 5.5 mm or less formed in a multi-ply shape in which a circular tube of a predetermined length is continuously bent, and a plurality of refrigerant tubes are arranged in parallel at regular intervals to form a refrigerant by welding. It is attached to the tube and is mounted in the form of a thin panel that crosses the seemingly bent refrigerant tube, and includes a heating fin divided into a first half contacting the air flowing first and a second half touching later based on the centerline between the front and rear refrigerant tubes. In addition, the heat transfer fin is characterized in that the asymmetrical shape of the width of the second half larger than the first half.

Here, the heat transfer fin has a width of 10-11 mm in the first half and a width of 12-15 mm in the second half, and a gap between the coolant tube passing through the first half of the heat transfer fin and the coolant tube passing through the second half is 10-11 mm.

Hereinafter, embodiments of the present invention will be described in detail with reference to FIG. 6.

The tubular heat exchanger according to the embodiment of the present invention has a multi-layered shape in which a circular tube of a predetermined length is continuously bent as shown in the drawing and has a diameter (D) of 5.5 mm or less with the refrigerant tube 10 at regular intervals. A plurality of heat transfer fins 12 are arranged in parallel and attached to the refrigerant tube 10 by welding, and are formed in a thin panel form mounted in a form that crosses the apparently bent refrigerant tube 10.

Here, the heat transfer fin 12 is divided into a first half portion 121 that comes into contact with air flowing first and a second half portion 122 that comes into contact with air flowing on the basis of the center line between the front and rear refrigerant tubes 10, and the width W1 of the first half portion 121. The width (W2) of the second half 122 is made of a larger asymmetric shape, specifically, the width (W1) of the first half 121 is composed of 10 ~ 11mm, the width (W2) of the second half 122 is composed of 12 ~ 15mm. do.

In addition, the interval RP between the refrigerant tube 10 penetrating the first half 121 of the heat transfer fin 12 and the refrigerant tube 10 'penetrating the second half 122 is 10 to 11 mm, and each half The spacing SP between the coolant tube 10 and the coolant tube 10 in the 121 and 122 is preferably maintained at 19 to 20 mm.

According to the tubular heat exchanger according to the embodiment of the present invention configured as described above, the air introduced through the first half portion 121 of the heat transfer fin 12 is lowered while passing through the second half portion 122, and the second half portion 122. Since the width (W2) of the () is longer than in the prior art, the wettability is increased, and the amount of humidity drop is larger than in the related art.

Therefore, when the cooling action is performed by the heat exchanger system to which the heat exchanger is applied according to the present embodiment and the heat exchanger is used as the evaporator, the dehumidification action is effectively performed as well as the cooling action.

As described above, the tubular heat exchanger according to the present invention has a smaller diameter than the conventional heat exchanger due to the structure of the refrigerant tube with a small diameter, and the dehumidification capacity is not reduced due to the asymmetrical structure of the heat transfer fin having a wider second half than the first half. Applied to the system has excellent merchandise, has the advantage of performing the cooling and dehumidification function effectively.

Claims (3)

A refrigerant tube made of a multi-ply shape by continuously bending a circular tube of a predetermined length; A plurality of panels are arranged in parallel at regular intervals and are attached to the refrigerant tube by welding, and are thin panels that are mounted in a form that crosses the seemingly bent refrigerant tube. Heat transfer fins are divided into the first half, the second half to contact later, In the tubular heat exchanger having a diameter of the refrigerant tube of less than 5.5mm; The heat exchange fin is a narrow tube heat exchanger, characterized in that the width of the rear portion is made larger than the first half. The method of claim 1, wherein the heat transfer fin A tubular heat exchanger having a width of 10 to 11 mm in the first half and a width of 12 to 15 mm in the second half. The method of claim 1, The tubular heat exchanger characterized in that the interval between the refrigerant tube penetrating the first half of the heat transfer fin and the refrigerant tube penetrating the second half is 10 ~ 11mm.