KR20010056526A - heat-exechanger is made up of pipe is formed of small diameter - Google Patents

Abstract

PURPOSE: A capillary heat exchanger is provided to promote reduction of pressure loss and to reduce heat exchanging performance by forming a heat exchanger in capillary type including a heat transfer pipe having a pipe diameter of lower than 6mm. CONSTITUTION: A capillary heat exchanger consists of cooling fins(200) having plural groups of slits(220) and heat transfer pipes(100) connected through each connecting hole(210) of the cooling fins. The heat transfer pipe of the capillary heat exchanger has a pipe diameter of 5-6mm smaller than one of the former heat transfer pipe of 9.52mm. The cooling fin has the width(W2) smaller than one of the former cooling fin. Each slit of the cooling fins is arranged in 4 rows of each group. A distance(P1) between the center of a connecting hole and the center of the other connecting hole is about 19-20mm. A distance(P2) between the center of a connecting hole and the center of the other connecting hole on the cooling fin is 10-11mm. Each slit is protruded in the same direction from a side of the cooling fins. Therefore, sudden pressure loss is prevented to the maximum as the distance between the cooling fins is reduced.

Description

Fine-tube heat exchanger {heat-exechanger is made up of pipe is formed of small diameter}

The present invention relates to a fin tube type heat exchanger, and in particular, to reduce the manufacturing cost, the efficiency is increased compared to the conventional heat exchanger, and to reduce the power consumption of the motor due to the pressure loss is small in size It relates to a tubular heat exchanger configured as.

In general, a heat exchanger is a device mainly applied to cooling and heating cycles, and is mainly used for heat exchange between a refrigerant flowing inside and a gas flowing outside thereof.

That is, it is mainly applied to cooling systems, such as an air conditioner and a refrigerator, performing heat transfer between fluids, such as air.

Among these heat exchangers, a fin tube type heat exchanger (Fin-Tube type Heat-Exchanger) is a plurality of plate-like cooling fins 20 on the heat transfer tube 10 through which fluid can flow as shown in FIGS. It is a heat exchanger to maximize heat exchange effect by increasing heat transfer area by fixing.

At this time, the cooling fins 20 are coupled to the heat pipe 10 in a state in which the cooling fins 20 are orthogonal with respect to the direction in which the heat pipe 10 is formed, and are stacked at predetermined intervals.

In addition, a plurality of coupling holes 21 are formed in a zigzag shape while forming a plurality of coupling holes 21 such as an upper end and a lower end of the cooling fin 20 to allow the heat pipe 10 to be inserted into the cooling fin surface. have.

Between the coupling holes 21 formed at the respective stages and the coupling holes 21 formed at the side portions of the same stage, a plurality of protrusion pieces 22a opened along the flow direction of the air are alternated to the front and rear surfaces of the cooling fin ( Iii) the slits 22 are formed in a state where the granular pieces 22b are formed in a mutually integrated state on both sides of each of the protruding pieces while inducing air flows smoothly around the heat exchanger tube on both sides of the protruding pieces. Many are formed.

Accordingly, the coolant flowing from the refrigerant inlet side of the heat transfer tube 10 by the operation of the cooling cycle cools the heat transfer tube 10 while passing through the heat transfer tube, thereby lowering the temperature of the heat transfer tube. The plurality of cooling fins 20 and the slits 22 formed on the cooling fins which are in contact with each other are also lowered in temperature.

In this process, the heat source (air) transmitted from the outside of the heat exchanger passes between the respective cooling fins 20 by the rotation of a fan (not shown) while cooling the heat transfer tube 10 and cooling as described above. The latent heat and heat exchange are performed while contacting the fin 20 and the slit 22.

At this time, the flowing air hits each of the slits while passing through the plurality of slits 22 formed in the cooling fins 20, thereby causing turbulence of the airflow and guiding the flow by the respective granular pieces 22b. By receiving along the circumferential portion of the heat transfer tube 10, the heat exchange effect can be further promoted.

As a result, the air heat-exchanged by the above-described process performs cooling of the room while continuously flowing toward the room.

On the other hand, each of the slits 22 formed in the cooling fins 20 of the fin tube-type heat exchanger having the configuration as described above is formed in the center and the side of the coupling hole 21 formed in any one end of the cooling fins Three rows are formed in a state corresponding to each other along the flow direction of air from the line connecting the center of the other coupling hole 21, and the other end of the cooling fin is also described above. It is formed while forming the same configuration as.

In addition, the slits of the first row formed on the side into which air is introduced and the slits of the last row formed on the opposite side of the six rows of slits 22 formed at each end of the cooling fin 20 are formed of three pieces. In addition, the protrusion height h is formed relatively higher than that of the slits 22 in the other rows, thereby promoting turbulence of the flowing air.

However, in the related art, as described above, the improvement direction of the fin tube type heat exchanger is merely to improve the heat exchange performance by allowing the turbulence to be promoted, which consumes enormous power due to the large pressure loss. Along with this, not only the motor (not shown) causes damage and noise, but also the manufacturing cost is excessively expensive.

In addition, considering that the current general trend is to achieve miniaturization, it is impossible to achieve this with the conventional heat exchanger structure described above, and thus, application to a miniaturized product is not easy.

That is, conventionally, the diameter of the heat exchanger tube 9.52 mm, The width of each cooling fin was set accordingly by using a heat transfer tube made of 7 mm, and the arrangement and shape of each slit formed in each cooling fin was also set accordingly. Even if the heat exchanger is manufactured, the width of each cooling fin ( ) To create a limit.

This is because of the characteristics according to the arrangement and configuration of each slit, when the shape is applied as it is, causing an increase in fan power due to excessive turbulence, which causes a problem of enormous power consumption and damage to the motor. It became.

In addition, considering that the number of heat formed by each slit of the cooling fins as in the prior art is 6, the process for narrowing the width of the cooling fins becomes very difficult, which is directly connected to the productive problem and practically impossible to manufacture.

The present invention has been made to solve the above-mentioned conventional problems, by forming a heat exchanger tube constituting the heat exchanger to a narrow tube having a diameter of 6 mm or less to reduce the pressure loss, and to prevent a decrease in heat exchange performance The purpose is to provide a new type of heat exchanger.

In addition, the capillary heat exchanger provided as described above can achieve the optimum heat exchange efficiency and to achieve a cost reduction for the production, and to respond to the alternative refrigerant.

1 is a sectional view showing main parts of a general fin tube type heat exchanger;

2 is a cross-sectional view taken along line II of FIG. 1.

Figure 3 is a perspective view of the main portion showing the shape of the slit formed on the cooling fin of the general fin tube type heat exchanger

Figure 4 is a sectional view of the main part showing the tubular heat exchanger according to the present invention

5 is a cross-sectional view taken along the line II-II of FIG. 4.

FIG. 6 is an enlarged state diagram of part A of FIG. 5;

Explanation of symbols for main parts of the drawings

100. Heat pipe 200. Cooling fin

210. Mating hole 220. Slit

230. Figurine

According to an aspect of the present invention for achieving the above object is a plurality of stacked at a predetermined interval, the coupling hole formed at a predetermined interval on the surface is arranged to form at least one or more stages on the surface. On the surface of either side between each coupling hole formed in each end is opened in correspondence with the flow direction of air, and the protrusions protruding in the same direction with respect to the surface and both sides of the protrusions The slits made up of granular pieces for guiding the flow are respectively formed to form a group of four rows, and are located in the first and fourth rows based on the flow direction of air among the slits forming the four rows. The slit is divided into two unit slits, and the slits located in the second and third columns are unified Cooling fins made by being configured in each state; It is coupled through the coupling holes of each of the cooling fins, has a tube diameter of about 5 ~ 6mm, the heat exchanger tube is a refrigerant flows along the inside; there is provided a narrow tubular heat exchanger.

Hereinafter, with reference to the accompanying Figures 4 to 6 showing the configuration of the present invention in more detail as follows.

4 is a cross-sectional view illustrating main parts of the tubular heat exchanger according to the present invention, FIG. 5 is a cross-sectional view taken along line II-II of FIG. 4, and FIG. 6 is an enlarged state view of part A of FIG. 5. The configuration of the group is the same as the basic configuration of the conventional heat exchanger.

That is, the plurality of slits 220 are largely composed of a cooling fin 200 formed while forming a group, and a heat transfer tube 100 coupled through the coupling holes 210 formed in the respective cooling fins.

However, the tube diameter of the heat transfer pipe 100 of the narrow-tube heat exchanger according to the present invention ( 5 to 6 mm is the diameter of the heat exchanger tube 10 of the conventional heat exchanger. 99.5 mm, 7 mm) is formed smaller, the width of the cooling fin 200 of the tubular heat exchanger according to the present invention ( ) Is the width of the cooling fins 20 of the conventional heat exchanger ( As it is formed smaller than), the detailed structure is also wrong.

That is, in the present invention, the slits 220 formed while forming groups in each end (upper end and lower end) of the cooling fins 200 are arranged to form four rows for each group, and the cooling is performed. The distance between the center of one coupling hole formed at the same end of each coupling hole 210 formed on the surface of the pin 200 and the center of the other coupling hole formed at its side ( ) Is arranged to form 19mm ~ 20mm, the center of one of the coupling hole formed in the different ends of each coupling hole 210 formed on the surface of the cooling fin 200 and the other coupling hole center formed at the bottom Distance between ) Is arranged to form 10 mm to 11 mm.

This means that if the unidirectional distance and the thermal distance between the coupling hole and the coupling hole are out of the above or below range of the above-mentioned range, a sudden deterioration of heat exchange performance occurs and a sharp increase in the manufacturing cost is caused. Therefore, the configuration as described above is most suitable.

In addition, the configuration as described above is most desirable to achieve the maximum heat exchange effect using a minimum manufacturing cost.

Of the slits 220 forming the group of four rows, the slits positioned in the first row and the fourth row based on the flow direction of air are divided into two unit slits 221a, 221b, 224a, and 224b. Each divided and configured, and the slits 222 and 223 located in the second row and the third row are integrated into a single unit.

Such a configuration is intended to improve heat exchange performance by allowing turbulence of air passing through each slit 220 while allowing smooth air flow.

In addition, each slit 220 having the arrangement as described above is formed to protrude in the same direction as a whole based on any one surface of the cooling fins 200, which is characterized in that between the cooling fins 200 between the characteristics of the tubular heat exchanger This is to prevent the sudden pressure loss that can occur as the gap between them is narrow.

That is, by forming the protrusion pieces 220a constituting each slit 220 to protrude in the same direction with respect to any one surface of both surfaces of the cooling fin 200, the flow of air passing between the cooling fins. This is to make it smooth.

At this time, the protruding distance of each slit is a cooling fin pitch (the spacing between each approximately the same cooling fin 200 as a whole ( By forming a half of), each slit 220 is configured to be in contact with the air smoothly but does not significantly affect the flow of air.

In addition, each of the slits 220 configured as described above is formed to allow the flow of air along the circumference of the heat transfer pipe 100 coupled through each coupling hole 210 of the cooling fin 200 as a whole.

That is, when forming an imaginary circle C along the periphery of the coupling hole 210 formed in the cooling fins 200, each angle formed by each granular piece 220b constituting the slit 220 is an angle slit. An angle formed by a line formed virtually along the direction formed by the rows of 220 and a tangent line (the imaginary line formed toward the center of the virtual circle from both ends of each slit) L ( By forming the same angle or a similar angle) to prevent the stagnation of the air flow that can be made on the downstream side of the heat transfer tube 100 after the passage of air.

The shape of each slit formed by such a granular piece 220b is the same as FIG.

That is, the two unit slits 221a, 221b, 224a, and 224b disposed in the first and fourth rows based on the flow direction of air form a parallelogram inclined inwardly toward the center of each other. Each of the slits 222 and 223 disposed in the second and third columns may have a shape of a trapezoidal shape that gradually decreases on the openings toward each other.

At this time, among the granular pieces 220b constituting both sides of the two unit slits, the granular pieces positioned inside the respective unit slits 221a, 221b, 224a and 224b do not incline as shown in the drawing. Promoting turbulence of the airflow is a more preferred form for improving heat exchange performance.

The process in which the indoor air is heat-exchanged with the refrigerant flowing in the heat transfer pipe 100 by the thin tubular heat exchanger configured as described above will be described in detail later.

First, the coolant flowing from the refrigerant inlet side of the heat transfer tube 100 passes the heat to the heat transfer tube 100 and each cooling fin 200 installed in contact with the heat transfer tube while passing through the heat transfer tube.

At this time, the air flows from the outside of the heat exchanger by the rotation of a fan (not shown) and passes between the respective cooling fins 200 and is arranged in the first row of each slit forming a group of four rows. Pass through the slit.

At this time, the slit of the first row is divided into two unit slits 221a and 221b, and each of the granular pieces 220b is formed to collect the incoming air toward the center side, so that the air passes therethrough. In the process of passing through each unit slit (221a, 221b) is guided by the flow of the flow path by each granular piece (220b) is gathered at the same time, thereby resulting in the turbulence is improved to improve the performance of the heat exchange.

In addition, the air passing through the unit slits 221a and 221b of the first row as described above passes to each granular piece 220b of each slit in the course of passing through the slits 222 and 223 of the second row and the third row. As a result, the flow velocity is guided and uniformity of the flow velocity distribution is achieved.

Thereafter, the air flowing as described above is guided by a flow path by the granular piece 220b of each unit slit in the course of continuously passing the two unit slits 224a and 224b arranged in the fourth row.群) is dispersed toward the rear side of the heat transfer pipe 100 located at each side of each of the slits 220 forming the slit 220 is to perform a continuous heat exchange.

That is, as described above, the air passing through each slit 220 forming one group is guided by the flow by the granular piece 220b constituting each slit, and thus the circumferential direction of the heat pipe 100 is oriented. By flowing along, more smooth heat exchange can be achieved.

In addition, due to the above-described action, the influence of the airflow smoothly extends to the rear side of the heat transfer tube 100, so that the four-area generation of the airflow formed on the rear side of the heat transfer tube 100 can be prevented.

On the other hand, in the present invention as described above, the slits 220 formed while forming a plurality of groups on the cooling fins 200 are formed to form four rows for each group (群), respectively, so that the flow of air is more smooth. It is understood that it is possible to achieve the prevention of pressure loss due to the flow of air between each cooling fin 200.

In addition, as each slit 220 formed in each cooling fin 200 protrudes only in the same direction with respect to one surface of the cooling fin, more smooth air flow is possible.

However, in spite of the above-described operation, the deterioration of the heat exchange performance is not achieved. ) Is not only narrower than in the prior art, but also the distance between the heat pipes and the heat pipes passing through the respective cooling fins 200 ( ) ( This is possible by decreasing).

As described above, the present invention forms a narrower distance between the columns and the distance between the stages of the heat transfer tubes, and reduces the number of columns of each slit formed on each cooling fin, Protruding direction is formed in the same direction, and the direction of the air flow guided therein is configured to flow along the periphery of the heat pipe, thereby enabling the manufacture of a narrow tubular heat exchanger having a tube diameter of 6 mm or less.

That is, it is possible to manufacture a capillary heat exchanger that solves the problem of excessive power consumption due to deterioration of heat exchange performance and promotion of turbulence of air, which has been proposed as a problem for the construction of a small heat exchanger.

In addition, the configuration according to the present invention has the effect that can achieve a cost savings used to manufacture the heat exchanger, after all, the production of a concise heat exchanger is possible, the effect that the application can be made extensively In addition, there is also an effect that the alternative refrigerant can be made.

Claims (3)

Many are stacked at a predetermined interval, Joining holes formed at predetermined intervals on the surface is arranged to form at least one end with respect to the surface, On one side between the respective coupling holes formed in the respective ends on the side of the air in the open state corresponding to the flow direction of the protrusion formed in the same direction relative to the plane and the air forming both sides of the protrusions The slits each composed of granular pieces for guiding the flow of each form a group of four rows. The slits located in the first row and the fourth row are divided into two unit slits based on the flow direction of the air among the slits forming the group of four rows, and the slits located in the second row and the third row are respectively configured in a unified state. Cooling fins made by; Are coupled through the coupling holes of the respective cooling fins, It has a tube diameter of about 5-6 mm or less, A tubular heat exchanger, comprising: a heat transfer tube through which a refrigerant flows. The method of claim 1, The two unit slits located in the first row and the fourth row form the granular pieces inclined at a predetermined angle so as to form a parallelogram shape inclined toward the center side of each other along the air flow direction. The slits located in the second row and the third row correspond to each other, and the tubular heat exchanger is formed by inclining the granular piece at a predetermined angle so as to form a shape of an isometric trapezoid which is reduced in size toward each other. The method of claim 1, The distance between the center of one of the coupling holes formed on the same end of each coupling hole formed on the surface of the cooling fin and the center of the other coupling hole formed on the side thereof is arranged to form 19 mm to 20 mm, Fine diameter, characterized in that the distance between the center of any one of the coupling hole formed in the different ends of the coupling hole formed on the surface of the cooling fin and the center of the other coupling hole formed in the lower end of the coupling hole to form a 10mm ~ 11mm Tubular heat exchanger.