KR19980042618A - Heat exchange coil - Google Patents

Abstract

Heat exchange coils having fin groups consisting of a number of opposing parallel plate fins are arranged at specific intervals in the ventilation direction, and the pipes transferring the heat medium penetrate into the plurality of plate fins several times in the ventilation direction, thereby transferring heat. Increases capacity and heat exchange efficiency and prevents drain from dispersing.

Description

Heat exchange coil

The present invention relates to a heat exchange coil used in a heat exchanger in which air is forcibly sent, such as an air conditioner.

A conventional heat exchange coil used in an air conditioner is constructed as shown in FIG. The coil 21 is constructed by inserting a pipe 24 which directs the heat medium to a plurality of plate fins 23 arranged in parallel and facing each other in the ventilation direction. Arrow A in this figure indicates the ventilation direction. In large articles such as air handling units, the wind speed is limited to 2.5 to 3.0 meters per second, and in small articles such as fan coils the wind speed is limited to 1.5 to 2.0 meters per second. This is because if the wind speed exceeds the speed limit (e.g. 4.5 to 5.0 m per second for larger items or 3.0 m per second for smaller items), the heat transfer capacity will decrease or air resistance will increase. In cooling or drying, the drain is dispersed in the wind through the fins where water leaks out of the air conditioner. In the coil 21 constructed as shown in FIG. 1, such a problem is difficult to solve. In addition, air conditioners increase in size due to wind speed limitations, thus raising the price.

In heating, in addition to the coil 21, as shown in Figure 1, it is necessary to install various types of humidity controller 22, such as evaporation type, steam type, fan type, water particle spray type. Such a hygrostat 22 is, however, very expensive and similar or more expensive than a coil in terms of price. Moreover, for example, in the humidity control method of the evaporator type humidity regulator, since the steam with air contact is used, an effective transfer showing how much the water particle transfer to the humidity controller has actually been added to the passing air. The water particle utilization efficiency (effective amount of humidification / conveyed water) is low, and the water not used for humidity control is directly discarded, which is very uneconomical.

The present invention has been invented to solve the above problems, and a main object thereof is to provide a heat exchange coil having a high capability in high speed ventilation operation and preventing the drain from dispersing.

The heat exchange coil of the present invention consists of a plurality of fin groups spaced at appropriate intervals in the ventilation direction, and each fin group includes a plurality of plate fins arranged in parallel to each other. In such a plurality of plate pins, a plurality of pipes for delivering the fruit medium are fitted so as to be perpendicular to the ventilation direction, and each pipe is fitted to the plate pin several times in the ventilation direction. Therefore, the air guided to the coil contacts the end of the fin group several times, so that the front end efficiency is high, thus increasing the heat transfer capacity and the heat exchange efficiency. The drain from heat exchange falls in the gap between the fin groups. Therefore, even when cooling or drying proceeds at high speed, it is possible to prevent the drain from dispersing out.

Here, most of the wind pitch pin pitch (pin spacing) is pressed toward the wind wind when less than the pin pitch of the wind wind. As a result, the air passing through the coil does not directly pass through the fin group on the windward side, but is dispersed to be in sufficient contact with it, thereby increasing heat transfer efficiency and heat exchange efficiency. Moreover, by setting more wind pin pitches than preset valves, pressure loss can be prevented. In this configuration, since most of the windward fin groups serve as heat exchangers and eliminators, there is no need to install a separate eliminator. Therefore, the size of the air conditioner is smaller and the price is lowered. In addition, by transferring the heat medium from the wind direction to the windward in the pipe, the heat transfer of the wind direction fin group with a small pin pitch is improved. At least when the wind end of the plate fin is zigzag, the contact area with the air increases, and thus the heat exchange efficiency becomes high.

Still another object of the present invention is to provide a heat exchange coil that functions as a moisture controller.

The heat exchange coil of the present invention includes a means for transferring the water particles to the fin group in the wind direction among a plurality of fin groups arranged at predetermined intervals in the ventilation direction. Therefore, it is possible to use the coil itself as a humidity controller regardless of high speed or low speed. In the fin group to which the water particles are fed, the moisture of the water particles is in contact with the coils that exchange air for heat, and the heat is also exchanged with the pipes and fins through which heat of the heat medium is transferred, so that the water particles are likely to evaporate. Therefore, compared with commercial evaporative humidity controllers, the transport water particle utilization efficiency is high, water is saved, and operating cost is reduced. In addition, when heating, the fin group to which water particles are supplied can be used as a hygrostat, and when cooling, the fin group can be used as a heat exchanger and a remover. Therefore, there is no need to install such expensive appliances, and the air conditioner is made smaller and lower in price.

When the cross section of the pipe is elliptical or circular, and its long diameter direction becomes almost the same as the ventilation direction, the air resistance in the coil can be reduced, and the rise of the required power can be prevented. Alternatively, the drain can be led into the gap in that direction by tilting the direction of the ellipse or the circular long side downward so as to face the gap between the groups of fins. By varying the direction of the diameter in all longitudinal, all transverse, or individually longer lengths, the generation of turbulence in the coil increases the heat exchange efficiency, the water particle retention time, and therefore the transport water particle utilization efficiency Lose.

Optionally, slits are formed to corrugate the plate fins, the direction of the slit of the fin group to which no water particles are supplied is substantially orthogonal to the ventilation direction, and the direction of the slit of the fin group to which the water particles are supplied is ventilated. It is almost equal to or inclined to the direction. As a result, heat exchange of the fin group to which the water particles are not supplied and humidification of the fin group to which the water particles are supplied can be most efficiently performed.

In addition, in most groups of fins in the wind direction, when the pipe penetrates in one or two rows in a direction orthogonal to the ventilation direction, drain dispersion is more securely prevented when it is equal to or wider than the fin width per line of the other fin groups. In addition, the heat transfer and humidity control of most of the wind direction fin groups is further improved.

The above objects and features of the present invention will become more apparent from the detailed description taken in conjunction with the following drawings.

1 is a longitudinal sectional view showing a conventional heat exchange coil.

Figure 2 is a schematic perspective view showing the main part of an air conditioner with a heat exchange coil according to the present invention.

3 is a perspective view of the heat exchange coil of FIG.

4 is a longitudinal sectional view of the IV-IV line of FIG. 3;

5 is a longitudinal sectional view showing another heat exchange coil.

6 is a side cross-sectional view of the V-V line of FIG.

7 is a longitudinal sectional view of the heat exchange coil according to FIG. 2;

8 is a longitudinal sectional view of the heat exchange coil according to FIG. 3;

9 is a longitudinal sectional view of the heat exchange coil according to FIG. 4;

10 is a longitudinal sectional view of the heat exchange coil according to FIG. 5;

FIG. 11 is a longitudinal sectional view of the heat exchange coil according to FIG. 6. FIG.

12 is a longitudinal sectional view of the heat exchange coil according to FIG. 7;

FIG. 13 is a longitudinal sectional view showing the heat exchange coil according to FIG. 8. FIG.

14 is a longitudinal sectional view of the heat exchange coil according to FIG. 9;

FIG. 15 is a modified illustration of the wind direction portion shown in FIG. 7. FIG.

FIG. 16 is a front view of the heat exchange coil according to FIG. 10. FIG.

FIG. 17 is a front view of the heat exchange coil according to FIG. 11. FIG.

18A shows the shape of the gap of the plate pin according to FIG. 12.

FIG. 18B is a sectional view of the plate pin of the B-B line of FIG. 18A. FIG.

19 shows another slit configuration of plate pins.

20 shows another slit configuration of plate pins.

FIG. 21 is a sectional view of the plate pin of the X-X line of FIG. 18A; FIG.

Referring to the drawings, specific points of the present invention will be described in detail below.

Example 1

Figure 2 is a schematic perspective view showing the main part of an air conditioner with a heat exchange coil according to the present invention. 3 is a perspective view showing a heat exchange coil. In the figure, arrow A indicates the ventilation direction. The heat exchange coil has a plurality of plate fins 1 facing each other and parallel to each other, a U-shaped bent pipe 2 inserted into a plurality of plate fins 1 in a plurality of side and vertical rows, and a plurality of plates. Header 15 at the inlet and outlet of the fruit piece connecting both ends of each pipe 2, with pins 1 having an upper end and a lower end supported by the upper frame 3 and the lower frame 4, respectively. It consists of (See Figure 4)

4 is a longitudinal cross-sectional view of the IV-IV line of FIG. 3 of the heat exchange coil of Example 1. FIG. FIG. 6 is a side cross-sectional view of the V-V line of FIG. 4. FIG. The heat exchange coil is divided into a blow part 5 (pin group) and a wind direction part 6 (pin group), which is a predetermined distance L to form a drain cut gap 7. It is arranged. This interval L is appropriately set according to the ventilation speed, the drying amount, etc. in order to prevent the drain generated in the wind blowing portion 5 from penetrating into the wind direction portion 6. For example, this interval is set to 5 to 20 mm, not too thick in the ventilation direction A. The drain discharge hole 8 is formed in the lower frame 4 which contacts the drain cut gap 7. A drain pan 9 is provided below the lower frame 4.

As shown in FIG. 4, the thin fins 1 of the wind direction part 6 have a row (or two lines as shown in FIG. 5) in a direction perpendicular to the direction perpendicular to the ventilation direction. Is inserted. In order to minimize the pressure loss of the wind blowing part 5, to induce pressurization more safely, to improve the heat transfer capacity and the heat exchange efficiency to the best, and to hold the drain in the wind direction part 6 most safely, the wind direction part 6 ), The pin pitch (pin spacing) E is preferably as small as possible, for example, set to 1.8 to 2.2 mm. The pin pitch P of the wind portion 5 must be equal to or greater than the pin pitch E of the wind direction portion 6, and this relationship is preferably E P 2E as shown in FIG. 6.

The heat medium passing through the pipe 2, such as cold or hot water, is supplied from a header 15 which is connected to the side end of the wind direction part 6 and is connected to the side end of the wind part 5. Is discarded and continues to flow from the wind direction part 6 to the windward part 5.

A water particle transport device 11 for transporting water particles to the wind direction part 6 is provided above the wind direction 6. The water particle transport apparatus 11 is composed of water treatment means 12, such as a water purifier or a filter, and a penetrating material 13 adapted to the upper frame 3 on the wind direction part 6. The tap water sent from the water feeder is treated to be water particles such as purified water from which bleach powder or other impurities are removed to prevent sticking of hard deposits from the water treatment means 12 and is supplied to the penetrating material 13. The water particles supplied to the penetrating material 13 are filtered and delivered to the fin 1 and the pipe 2 through the water particles passing through the holes provided in the upper frame 3 in the wind direction 6.

When cooling or drying is performed at a high speed, for example, 3 m per second by using such a coil, the drain generated in the wind blowing portion 5 is drained through the drain cut gap 7 and the drain discharge hole 8. Abandoned by the fan (9). At this time, also in the wind direction part 6, the air cools and a drain occurs. However, the amount is small so that, through an act of eliminator of the wind direction part 6, the drain is held between the adjacent pins 1 of the wind direction part 6 by surface tension and is detained. Therefore, even when the wind speed is high speed, in the wind direction part 6, the drain is not dispersed in the wind direction from the (drain fan 9), but falls to the drain pan 9 through the wind direction part 6.

Here, in order to minimize the amount of drain occurring in the wind direction part 6, the number of rows of pipes 2 in the wind direction part 6 is preferably one or two, and if more than two, the wind direction part Drain generation increases at (6), which is undesirable.

In the meantime, the air passing through the coil has a low resistance at the wind blowing portion 5 because of the large pin pitch, and the pressure loss is caused by the pressurization of the wind direction portion 6 having a smaller pin pitch than the wind blowing portion 5. During dispersion, pressure loss is prevented. Therefore, without directly passing through the wind blowing portion 5, the air is sufficiently in contact with the fin 1 of the wind blowing portion 5, and heat is transferred (ie the bypass element is small). Moreover, the wind direction part 6 is the side inlet of the heat medium and has a small fin pitch, thus increasing the heat transfer rate. In addition, the air contacts the end 5b of the windward side of the windward part 5 and the end 6a of the windward side of the windward part 6 twice, and the end effect doubles, thus The heat transfer capacity and heat exchange efficiency are increased as compared to the coil which is not divided as shown in FIG. Thus, heat is effectively exchanged with air in both the wind portion 5 and the wind direction portion 6.

When the pin pitch E of the wind direction part 6 is smaller than 1.8 mm, the air resistance increases in the wind direction part 6, which is undesirable. Alternatively, when the pin pitch E exceeds 2.2 mm, the pressing force drops, the bypass air is increased in the air blowing portion 5, and the drain is not safely held between the pins of the wind direction portion 6, but it is In (1), it is easily placed and scattered by wind pressure, which is undesirable. However, when the pin pitch P of the air blowing portion 5 is more than twice the pin pitch E of the wind direction portion 6, the heat transfer area and the contact air are reduced, and the heat transfer capacity and heat exchange efficiency are lowered. This is not desirable. Alternatively, when the pin pitch P of the wind blowing portion 5 is not larger than the pin pitch E of the wind direction portion 6, this is not preferable because the pressure loss is large.

In the case of heating by using this coil and heating the air, when water particles are supplied to the wind direction part 6 through the water particle transport device 11, moisture passes air to exchange heat for evaporative heat of heat. Contact with the coil. In addition, heat is exchanged with the pipes 2 and fins 1 through which the heat medium is transferred. Therefore, compared to the evaporation by the air-liquid contact network, the water particles evaporate faster, thus moistening the coils through which the air passes. Therefore, the humidification capacity and the efficiency of using the conveyed particles are increased, and there is no waste of water. Even better, the water particle transfer device 11 can be easily made at a low price by using a water purifier, a penetrating material or the like.

Incidentally, when water particles enter the undivided coil as shown in Fig. 1, the heat exchange capacity becomes low, which is not suitable for practical use. However, in the present invention, since the wind blowing portion 5 and the wind direction portion 6 are completely divided, heat and water particles do not interfere with each other. Therefore, the air blowing portion 6 plays the role of a heat exchanger, and the wind direction portion 6 performs the role of a humidity controller independently. In addition, since the heating load is generally less than the cooling load, the heating load can only be accommodated by the wind blowing section 5, and the wind direction section 6 having one or two lines of pipes 2 can be used as a humidity controller. Can be. Therefore, a practical heat exchange coil can be obtained. When this coil is also used as a humidity controller, it can be used regardless of the wind speed.

Example 2

FIG. 7 is an embodiment where the fin width T of the wind direction portion 6 is about twice the fin width S of the wind portion 5. The other configuration is the same as that shown in Fig. 4, the same numbers are given, and the description is omitted. In this configuration, the heat transfer area of the wind direction part 6 is increased, and thus the coil capacity and the humidification capacity are increased. In particular, since the heat medium, cold or hot water, flows from the wind direction part 6 to the wind part part 5 side, the heat transfer capacity is increased, the heat transfer efficiency is improved, and thus the coil capacity and the humidification capacity can be further improved. will be.

Example 3

In FIG. 7, the pipes 2 of the wind direction part 6 are arranged in one row, which is arranged in the middle of the fin width T, while in FIG. 8, this row is winded in the middle. It is arranged toward.

In Embodiment 3, the heat medium flows through the pipe 2 installed on the windward side of the wind direction part 6, and the heat medium is not supplied toward the wind direction. Thus, the windward side of the wind direction part 6 functions as a heat exchanger, a remover and a humidity regulator, while the windward side functions as a remover and a humidity regulator. As a result, the capacity to catch and hold the drain and the humidification capacity are increased.

The row of pipes 2 may be biased towards the wind direction (FIG. 15).

Example 4

In FIG. 9, two rows of holes for passing the pipe 2 of the wind direction portion 6 are provided, the pipe 2 is installed in the wind row, and the wind row pipe

(2) Reduce the holes not installed. In this embodiment, the wind direction pin 1 is made by cutting a plate made in the same way as the wind direction pin, thereby reducing the cost.

Example 5

In Examples 1 to 4, the cross section of the pipe 2 is circular, but it may be elliptical as shown in FIG. The longer diameter direction of the ellipse in cross section is the same as the ventilation direction (A). The other configuration is the same as that of the first embodiment as shown in Fig. 4, the same numbers are given, and the description is omitted. In this configuration, even if air flows at a high speed, the resistance is not large, and an increase in required power is prevented.

Example 6

In Fig. 11, similarly to the fifth embodiment, the cross section of the pipe 2 is elliptical, but in the wind portion 5, the long diameter direction is inclined toward the drain cut gap 7 in the wind direction. In this way, the air drawn into the coil flows along a parabolic line with a low point (bottom) in the drain cut gap 7 due to the shape of the pipe 2 almost, which causes the drain to flow into the drain cut gap 7. Let it be. As a result, drain discharge of the drain cut gap 7 and prevention of drain dispersion of the wind direction part 6 can be executed more safely. In addition, the wind direction of the wind direction portion 6 becomes a direction for catching the drop of water particles during humidity control. As a result, the time for detaining the water particles is long, and the humidification capacity and the use of the conveyed material particles are high.

Example 7

As shown in Fig. 12, when the long radial direction of the cross section of the pipe 2 is arbitrary and irregular in the wind portion 5 and the wind portion 6, the air flows violently, and the heat exchange efficiency is increased. . Upon humidification, the water particles are guided by the pipe 2 and fall into a zigzag. Therefore, the water particle retention time is long, and the humidification capacity and the transport particle particle utilization efficiency are increased efficiently. If the absolute value of the crossing angle between the long radial direction and the ventilation direction A is, for example, 45 degrees or less, the pressure loss is prevented.

The long radial direction of the pipe 2 is different in every longitudinal direction, in addition to the zigzag arrangement of FIG. 12, can be different in all longitudinal and all transverse directions, and can be free in the arrangement.

Example 8

FIG. 13 shows the end portions (winding ends of the winding portions 5) of both sides of the drain cut gap 7 of a wave shape (or zigzag non-uniform shape) in the wind portion 5 and the wind portion 6. 5a) and the fin 1 facing the wind end 6a of the wind direction part 6. As a result, the end effect is further increased, and the heat exchange effect is increased. This configuration can be applied to all embodiments.

Example 9

FIG. 14 shows an embodiment in which the plate fin 1 is divided into three to form the intermediate part 10 between the winder part 5 and the wind direction part 6. A drain cut gap 7 is formed between the wind portion 5 and the middle portion 10, between the middle portion 10 and the wind portion 6, and the drain discharge hole 8 is formed at each drain cut gap. It is supplied to the lower frame 4 corresponding to (7). In addition, the water particle transport apparatus 11 is supplied to transport the water particles to the wind direction part 6. Other configurations are the same as in FIG.

In this configuration, since the coil passing through the air sequentially contacts the ends of the air blowing portion 5, the middle portion 10, and the wind direction portion 6, the end effect is increased and the heat exchange efficiency is further increased. In addition, the intermediate portion can be divided into a plurality of portions in the ventilation direction A, and a drain cut gap 7 can be provided between the portions. In this case, corresponding to each drain cut gap 7, a drain discharge hole 8 may be provided in the lower frame 4. In addition, in response to the heat load and the amount of humidification, the water particle transport apparatus 11 may be provided to supply water particles to both the wind direction part 6 and the middle part 10.

In the embodiment shown in FIG. 14, the wind direction part 6 has one or two rows of pipes 2 and a pin pitch E of at least (preferably 1.8 to 2.2 mm). The pin pitch P of the wind portion 5 and the middle portion 10 is equal to or greater than the pin pitch of the wind direction portion 6 (E P 2E is preferred). Thus, the wind direction part 6 can be used as a heat exchanger, a remover, a humidity controller, and drain dispersion can be safely prevented, whereby it is possible to effectively humidify.

The fin width T of the wind direction portion 6 is preferably equal to or greater than the fin width S of the intermediate portion 1 and the wind-up portion 5. In this case, the row of pipes 2 may be located in the middle as in FIG. 7 or may be positioned towards the windward side as in FIG. 8 (or as in FIG. 15). In addition, as shown in FIG. 9, the holes may be formed in two rows, and the pipe 2 may be installed in the row of the wind-slot holes to pass the heat medium. The winder side can thereby function as a heat exchanger, eliminator, and humidity controller, and the winder side can function as a eliminator and a humidity controller. Moreover, the cross section of the pipe 2 may be elliptical as in FIGS. 10 and 12, and the end of the pin 1 is not flat as in FIG. 13.

Example 10

The water particle transport device 11 includes a heater 14 for heating the water particles, as shown in FIG. In this case, evaporation of the water particles is further promoted.

Example 11

As shown in FIG. 17, instead of the configuration including the heater 14, the water transport pipe 17 of the water particle transport device 11 is preferably configured to wind around the header 15. The water particle temperature is raised, for example, by contacting the header when transferring heat.

Example 12

The plate fin 1 is configured as shown in Fig. 18A, in which the slits 16 and the step portions 18, which are raised in the form of a plurality of bridges, are formed to be corrugated. FIG. 18B is a cross sectional view along line B-B in FIG. 18A; FIG. FIG. 19 is a cross sectional view along line X-X in FIG. 18A; The step portion 18 has a concave portion on one surface of the pin and a convex portion on the other surface. The step portion 18 is configured perpendicular to the ventilation direction A in the longitudinal direction to prevent water from flowing in the wind direction (water stop effect) and to lead the water downward (drain effect). In this way, the step portion 18 serves as a discharge passage, and the drain is thus smoothly discharged, effectively preventing drain dispersion.

Preferably, a plurality of step portions are arranged at intervals in the ventilation direction A. FIG. The depth (height) H of the step part 18 should not be smaller than the maximum value of the depth T of water, and HT is preferable.

The maximum effect of water stop and water drainage can be obtained when the step portion 18 is constantly formed in a straight line between the upper and lower portions of the fin 1. It may be formed zigzag or winding discontinuously, corresponding to the desired degree of effect. The cross-sectional view of the step portion 18 is not limited to a trapezoid as shown in FIG. 19, but may be in various forms such as semicircles, squares, and the like. Moreover, it varies depending on the number, location, and depth (H).

The direction of the slit 16 can be freely placed, it may be perpendicular to the ventilation direction (A) as shown in Figure 18A, or may be in the lateral direction such as the ventilation direction (A), as shown in Figure 19, As shown in FIG. 20, the direction may be oblique to the ventilation direction A. FIG. Because of the plate fin 1 shown in Fig. 18A, the end effect is increased, thus increasing the heat transfer capacity and the heat exchange efficiency. Because of the plate fin 1 shown in Fig. 19, the water particles stay in the fin 1, so that the water particles hardly flow straight down. Due to the plate pin 1 shown in FIG. 20, the water particles are zigzag and almost do not flow straight down.

In particular, in the wind blowing portion 5 to which no water particles are supplied, the direction is orthogonal to the ventilation direction A as shown in Fig. 18A, and in the wind direction portion 6 to which the water particles are supplied, the direction is the ventilation direction. It is the same direction as (A) or as shown in FIG. 20, and it is oblique direction. Thereby, the heat transfer effect is increased in the portion where water particles are not supplied, while the decrease in heat transfer capacity and pressure loss are suppressed in the portion where water particles are supplied, and the drop distance and time of the water particles are increased to the maximum, and thus the transport is performed. Water particle utilization efficiency is higher. The width and shape of the raised slit 18 are not limited to the embodiment. Alternatively, only the raised portion (slit 16) may be formed by omitting the recessed portion 18.

Moreover, for the purpose of giving hydrophilicity, a hydrophilic coating film 31 is formed on the surface of the plate fin 1. The connection angle of the plate pin 1 and water is 30 degrees, and 15 degrees is preferable. The film 31 causes the water to be confined with the cold condensate by the fins 1. Thus, water receives a smaller air pressure. As a result, water hardly flows in the wind direction with the high-speed coil through which air passes, and easily flows downward, whereby the drain dispersion preventing effect is further increased. In addition to this, the contact area between the water and the fin 1 becomes larger, and thus, the wet heat transfer surface, the wet surface coefficient and the heat transfer coefficient become larger, thereby increasing the cooling capacity of the coil through which the air passes. When the water particle transport means is supplied, the minimum of the contact area increases the heat transfer efficiency. Since the maximum area of the water thickness T is reduced, the depth (height) H of the step portion 18 can be designed small as shown in FIG.

The structure of the hydrophilic coating film can be applied to all embodiments. This means of giving hydrophilicity is not limited to coating films only.

In this embodiment, it is free to change the pin pitch of the coil portion and the number of strings of the coil portion as required. In addition, it can pass in the opposite direction of the heat medium, ie from the windward side toward the wind direction. For example, by omitting water treatment means 12 such as a water purifier and a filter, it is also free to change the structure of the water particle transfer device 11, and tap water can also be directly supplied to the humidity control water. In this case, by passing the water particles (by appropriately increasing the flow rate) at a predetermined time interval after the ventilation stops, the fin 1 can be cleaned, and the accumulation of dust and coagulum can be prevented.

The heat exchange coil of the present invention can be used in a small air conditioner such as a fan coil or a large air conditioner such as an air handling unit.

Since the present invention has been practiced in various forms without departing from the essential features thereof, the present invention is therefore not intended to be explanatory or limited, and the scope of the present invention is defined by the appended claims rather than the foregoing description, All changes in borders, or equivalents of borders of a claim, are therefore included in the claims.

Claims (9)

A plurality of pin groups placed at specific intervals in the ventilation direction, the plurality of pin groups including a plurality of plate pins placed parallel to each other; And a pipe penetrating the plate fin to pass through the heat medium. The heat exchange coil according to claim 1, wherein the spacing of the fins in the wind direction is smaller than the pitch of the fins in the wind direction. The heat exchange coil according to claim 1 or 2, further comprising water particle conveying means for conveying the water particles to the fin group in the wind direction. 3. The heat exchange coil according to claim 1 or 2, wherein the pipe cross section is an ellipse, and the long diameter direction of the ellipse is almost the same as the ventilation direction. The heat exchanger according to claim 1 or 2, wherein a plurality of cross sections of the elliptical pipe are placed in the longitudinal direction and the transverse direction, and the long radial direction of the ellipse is configured in the longitudinal direction, the transverse direction, and differently. coil. The direction of each plate fin of the fin group to which no water particles are supplied is substantially orthogonal to the ventilation direction, and the direction of each plate fin of the fin group to which the water particles are supplied is substantially the same as the ventilation direction. And a water particle conveying means for conveying the water particles to a group of wind-side fins in which slits raised from each of the same or inclined plate fins are supplied to form a corrugation. 3. A pipe according to claim 1 or 2, wherein the pipe penetrates into a group of fins in the wind direction in one or two rows in a direction orthogonal to the ventilation direction, wherein the plate fins of this fin group are fins for each row of plate fins of another fin group Heat exchanger coil equal or wider than width. The heat exchange coil according to claim 1 or 2, wherein in the plate fin, a step portion is formed so as to prevent water solidified by heat exchange toward the wind direction. The heat exchange coil according to claim 1 or 2, wherein the surface of the plate fin is treated to be hydrophilic.