KR20170106748A

KR20170106748A - Cooling dehumidifier using heatpipe

Info

Publication number: KR20170106748A
Application number: KR1020160030231A
Authority: KR
Inventors: 윤 식 변; 양권옥
Original assignee: 윤 식 변; 양권옥
Priority date: 2016-03-14
Filing date: 2016-03-14
Publication date: 2017-09-22

Abstract

The present invention relates to a heat exchange line in which a working fluid flows into the inside and heat exchange with outside air is performed, and an anti-corrosive coating layer is formed on an outer periphery; One or more pipes for cooling the air introduced from the front end of the heat exchange line by heat exchange of the working fluid contained in the shape of wrapping the front end and the rear end of the heat exchange line and for heating the air passing through the heat exchange line at the rear end of the heat exchange line A heat pipe heat exchanger including a body; And a blower fan for allowing air to pass through the heat exchange line and the heat pipe heat exchanger and exhausting the air.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a cooling dehumidifier using a heat pipe,

According to the present invention, a dehumidifying heat pipe is used to pre-cool the passing air in a pre-cooling heat pipe heat exchanger provided at the front end of the cooling coil to increase the amount of dehumidification of the cooling coil and also to use low temperature and high humidity air after passing through the cooling coil To a cooling dehumidifier capable of simultaneously lowering the absolute humidity and the relative humidity by reducing the relative humidity by reheating the heat by the precooled heat quantity.

Generally, the cooling dehumidifier is installed in the space where the humidity should be kept low, such as manufacturing and storage of semiconductors, communication devices, electric and electronic parts, foods, pharmaceuticals and precision machines, and various test rooms. Or less.

However, in the conventional cooling and dehumidifying apparatus, as shown in FIG. 1, in order to adjust the humidity, the air introduced into the apparatus is cooled and humidified and reheated to operate the system in such a manner that the temperature and humidity reach the set value. It was an inefficient method.

That is, in the conventional cooling dehumidifier, when the temperature reaches the set value, when the humidity is high, the pass air is subcooled in the evaporator in order to decrease the humidity, and then the absolute humidity is lowered. There is a problem in that the system is inefficiently operated such that a large amount of energy is consumed and a separate cooling means and reheating means are required to perform cooling and reheating.

Korean Patent No. 0917835

Accordingly, an object of the present invention is to pre-cool air introduced into a cooling coil (evaporator) without using any separate power for dehumidification to increase the dehumidifying amount of the cooling coil (evaporator) And to provide a cooling dehumidifier in which the temperature is maintained at a predetermined value and the relative humidity is lowered by reheating the high-humidity air as preheated.

In order to accomplish the above object, the present invention provides a cooling and dehumidifying device comprising: a heat exchange line having a working fluid flowing into the inside thereof to perform heat exchange with outside air and having an anti-corrosive coating layer formed on an outer periphery thereof; One or more pipes for cooling the air introduced from the front end of the heat exchange line by heat exchange of the working fluid contained in the shape of wrapping the front end and the rear end of the heat exchange line and for heating the air passing through the heat exchange line at the rear end of the heat exchange line A heat pipe heat exchanger including a body; And a blowing fan for allowing air to pass through the heat exchanging line and the heat pipe heat exchanger and exhausting the air.

As an example, the corrosion-inhibiting coating layer may comprise 10 to 20 parts by weight of a cericite powder, 1 to 5 parts by weight of manganese oxide, 0.5 to 3 parts by weight of cellulose acetate, and 1 to 5 parts by weight of calcium nitrite, based on 100 parts by weight of the polyacrylic acid resin .

As one example, the heat pipe heat exchanger has a U-shaped housing space to allow the pipe body to be disposed in the accommodation space, and both side portions opposed to the front end and the rear end of the heat exchange line are opened Shaped casing is further constituted.

For example, the casing may have a heat insulating plate at a portion connecting the side portion and at a portion facing the heat exchange line.

As one example, the heat insulating plate is characterized in that it comprises 30 to 50 parts by weight of expanded vermiculite, 5 to 10 parts by weight of aluminum hydroxide and an alumina mixture, and 1 to 3 parts by weight of biochar to 100 parts by weight of polyacrylic acid resin.

The cooling dehumidifier of the present invention is advantageous in that energy consumption can be reduced by providing a heat pipe heat exchanger to accommodate the front and rear ends of the heat exchange line, and precooling and reheating the passing air without dehumidifying power.

Further, the cooling dehumidifier of the present invention is advantageous in that a heat insulating plate or the like is provided to prevent performance deterioration of the heat pipe heat exchanger, thereby increasing preheating and reheat efficiency and doubling the dehumidification efficiency.

1 is a schematic view for explaining a conventional cooling dehumidifier;
2 is a schematic view for explaining the cooling dehumidifier of the present invention.
3 is a schematic view for explaining an operating state of the cooling dehumidifier according to the present invention.
4 is a cross-sectional view and a longitudinal sectional view showing a pipe body of a heat pipe heat exchanger which is an embodiment of the present invention.
5A and 5B are perspective views showing an embodiment of the angle of the pipe body groove.
6A-6B are cross-sectional views illustrating embodiments of pipe body groove formation.
7 is a perspective view showing an embodiment of the cooling dehumidifier of the present invention.

Hereinafter, a cooling dehumidifier according to the present invention will be described in detail with reference to the accompanying drawings.

The present invention relates to a cooling and dehumidifying device for reducing energy by having a heat pipe heat exchanger (50) configured to surround a front end and a rear end of a heat exchange line. 2, the air passing through the front end of the heat exchange line is precooled by the heat pipe heat exchanger 50 to reduce the cooling load and the temperature of the heat exchange line to increase the amount of dehumidification, The heat pipe heat exchanger 50 reheats the heat exchanger 50 without using any other energy at the rear end of the heat exchanger line.

In the present invention, the term " front end of the heat exchange line " refers to a side to which the air is introduced based on a direction in which the air introduced from the outside flows through the heat exchange line, and the rear end of the heat exchange line refers to the heat exchange line Means the side through which it passes.

Here, the heat exchange line cools the air flowing in accordance with the heat exchange between the charged working fluid and the inflow air, thereby providing the cooled and humidified air into the space requiring substantial humidity control. The heat exchanging line may be an evaporator in a general cooling and dehumidifying device including a condenser, a compressor, and an evaporator. In the case of a cooling dehumidifier using a cold water or a brine manufactured by an external refrigerator as a heat source, have.

Hereinafter, an evaporator in a general cooling dehumidifier will be described as an example of a heat exchange line. However, in the present invention, the heat exchange line is not limited to the evaporator, but it is natural that a cooling coil that performs a cooling operation by using cold water or brine as a heat source as described above is also applicable.

3, the compressor 10, the condenser 20, the expansion valve 400, and the evaporator 40 are connected to each other, And they are composed of a structure in which vaporization and liquefaction are repeated with mutual circulation as they perform a heat exchange process.

The compressor 10 is for compressing a refrigerant (hereinafter, referred to as 'working fluid'). The compressor 10 compresses a low-pressure working fluid in a gaseous state moving from the evaporator 40 and converts it into a high- , And discharges the high-pressure working fluid to the condenser (20).

The condenser 20 cools the high-temperature and high-pressure working fluid discharged from the compressor 10 to thereby condense heat to condense and liquefy the fluid, thereby allowing the gaseous working fluid to be liquefied.

In the present invention, as shown in FIG. 3, the cooling fan 200 and the fluid of the condenser 20 can be cooled in a variety of ways through a known technique such as water cooling or air cooling. And a cooling fin (210) for cooling the fluid tube due to the cooling air of the cooling fan (200). The cooling fan (200) and the cooling fin (210) The cooling method is presented as an example.

Then, the working fluid liquefied in the condenser 20 is moved to the receiver 30 and temporarily stored. The receiver 30 is installed between the condenser 20 and the evaporator 40 and absorbs a change in the amount of the operating fluid due to a load variation of the evaporator 40 to be described below, It is a matter of course that such a receiver 30 can be selectively applied.

The evaporator 40 changes the working fluid of high temperature and high pressure liquefied in the condenser 20 to the low-temperature and low-pressure working fluid while passing through the expansion valve 400 installed in the evaporator 40, The working fluid evaporates and absorbs the heat of the object to be cooled, thereby performing a cooling sensation (or dehumidification) action.

The air cooled by the heat exchange due to evaporation of the working fluid is discharged to a space requiring cooling by using a blowing means such as a blower. The evaporator 40 has a plurality of fin structures surrounding the tube It is preferable to facilitate the heat transfer to the outside air passing through the evaporator 40 so as to cool the air introduced in a short time.

Here, the working fluid may be various heat transfer fluids suitable for the use temperature, and finally the temperature depending on the heat exchange action may be determined according to the increase or decrease of the type of the working fluid and the amount of the working fluid heat exchanged in the evaporator.

As described above, the present invention further includes a heat pipe heat exchanger (50) for reducing energy unnecessarily used in dehumidification or dehumidification and configured to surround the front end and the rear end of the evaporator (40) It is characterized by being configured.

In the conventional cooling and dehumidifying device, in order to lower the relative humidity of the blowing air, the cooling coil is excessively cooled in advance to increase the dehumidifying amount, and then the excessively cooled temperature is set to the set temperature and the relative humidity is decreased There has been a problem in that a large amount of energy is consumed due to a vicious circle of such a process. That is, in the case of the existing cooling dehumidifier, a separate preheating means and a reheating means were required to perform the preheating and the reheating.

Accordingly, in the present invention, the heat pipe heat exchanger 50 performing the pre-cooling and reheating functions by heat exchange itself without external power is disposed at the front end and the rear end of the evaporator 40, thereby maximizing the energy saving.

Specifically, the present invention accommodates the outside of the evaporator (40) and cools the air flowing into the evaporator (40) by heat exchange of the internal working fluid, and also heats the air passing through the evaporator (40) A heat pipe heat exchanger 50 and a blowing fan 60 for allowing air to pass through the evaporator 40 and the heat pipe heat exchanger 50 and to discharge the air to a required space.

As shown in FIG. 3, the heat pipe heat exchanger 50 is formed by arranging a plurality of U-shaped pipe main bodies 510, and the pipe main body 510 is preferably made of aluminum or copper having a good heat transfer coefficient And a groove 511 for guiding the flow of the working fluid 520 liquefied by heat exchange in the longitudinal direction is formed on the inner surface as shown in FIG.

The groove 511 is provided in the circulation process of the working fluid 520 and has a capillary structure to return the working fluid 520 in the liquid state from the condensing portion to the evaporator portion. That is, the groove 511 feeds back the liquefied working fluid 520 using the capillary phenomenon due to the surface tension of the liquid and the gravity. Such a groove 511 will be described in detail below.

The working fluid 520 is filled in the pipe main body 510 and serves to transfer heat by phase change of gas and liquid. The working fluid 520 is suited to the operating temperature like the working fluid circulating through the evaporator 40 A variety of heat transfer fluids may be used.

3, one end of the heat pipe heat exchanger 50 is a portion facing the front end of the evaporator 40 and is referred to as an evaporator 50A. The other end of the heat pipe heat exchanger 50 is connected to the evaporator 40, (40), and this portion is referred to as a condensing portion (50B).

4, the working fluid 520 of the heat pipe heat exchanger 50 is connected to the working fluid 520A in the gaseous state having a pressure corresponding to a constant temperature and the working fluid 520A in the extra liquid state Fluid 520B and this extra liquid working fluid 520B are present in groove 511 of pipe body 510.

In view of the operation of the heat pipe heat exchanger 50, the air introduced from the outside by the blowing fan 60 passes through the evaporator 50A of the heat pipe heat exchanger 50, The working fluids 520A and 520B existing in the pipe body 510 corresponding to the evaporator 50A are heated by the heat of vaporization due to the heat being higher than the outlet temperature of the evaporator 40, The gas pressure in the evaporator 50A increases to generate a pressure difference with the condenser 50B and the evaporated gaseous working fluid 520A moves to the condenser 50B.

In the evaporator 50A of the heat pipe heat exchanger 50, the liquid working fluid 520B existing in the groove 511 absorbs heat from the air passing through the evaporator 50A, As the fluid absorbs heat during the phase change to the fluid 520A, precooling of the passing air is performed.

Further, the heat energy due to the phase change in the evaporator 50A is moved to the condenser 50B as described above.

On the other hand, the working fluid 520A in the gaseous state moved to the condenser 50B of the heat pipe heat exchanger 50 is heat-exchanged with the air cooled in the evaporator 40 to heat the heat energy absorbed from the evaporator 50A The heat is transferred from the main body 510 itself to the rear end side of the evaporator 40 in contact with the condensing portion 50B so that the air that has passed through the rear end of the evaporator 40 is reheated.

The working fluid 520A that has released heat in the condensing section 50B is again liquefied by the working fluid 520B in the liquid state and is returned to the evaporation section 50A through the groove 511 of the pipe body 510 And the preheating and reheating processes described above can be repeatedly performed.

As described above, according to the present invention, precooling and reheating are performed at the front end and the rear end of the evaporator 40 through heat transfer and circulation processes according to a phase change of vaporization and liquefaction using the heat pipe heat exchanger 50, No separate power source, pre-cooling means or reheat means is required in the control process, so that the consumption of energy can be reduced and high-efficiency operation is possible.

On the other hand, in the evaporator 40, scale may be deposited due to excessive condensation during the heat exchange process, and the heat exchange efficiency may be reduced due to such a cause.

In the present invention, as shown in FIG. 3, an example is shown in which the anti-corrosion coating layer 41 is applied to the outer periphery of the evaporator 40.

The anti-corrosive coating layer (41) comprises 10 to 20 parts by weight of cericite powder, 1 to 5 parts by weight of manganese oxide, 0.5 to 3 parts by weight of cellulose acetate, and 1 to 5 parts by weight of calcium nitrite, based on 100 parts by weight of polyacrylic acid resin .

A polyacrylic resin is used as a base material. This is to make the condensation (anti-corrosion) coating layer 41 as a water-soluble binder add water to prevent condensation.

The sericite is intended to reinforce the strength of the dew condensation preventing coating layer 41 as a filler, and in particular, to prevent condensation of the dew condensation preventing coating layer 41 as a hydrophilic mineral.

In addition, cellulose acetate is added to the anti-corrosion coating layer 41, and the cellulose acetate is added as a hydrophilizing agent to control the generation of scale by the oil component contained in the condensation by hydrophilization.

On the other hand, even if hydrophilic property is imparted by adding cellulose acetate to the polymer, the scale due to other foreign substances contained in the condensation can not be controlled. Generally, colloidal materials such as EPS, protein, and the like are weakly negatively charged due to the selective adsorption of anions, especially hydroxide ions, in the medium. Thus, manganese oxide is further added to the anti-corrosion coating layer 41. The manganese oxide exhibits a negative charge at pH 6 to 8 to generate sludge and repulsive force, so that the generation of scale by sludge can be controlled.

The calcium nitrite is intended to improve the anti-rust property and prevent the scale from depositing on the outer periphery of the evaporator 40 due to corrosion. Preventing coating layer 41 and preventing corrosion of the groove 511 of the iron material even if a relatively small amount of the corrosion inhibiting coating material is used.

This small nitrite ion (NO2-) of the calcium nitrite reacts with the iron ion (Fe ++) eluted from iron (Fe) to prevent the formation of ferric hydroxide [Fe (OH) 3] The compound Fe2O3 is produced. The resulting Fe2O3 forms a film at the corrosion point formed on the iron surface and closes it, thereby preventing corrosion of iron.

7, a heat pipe heat exchanger 50 according to an embodiment of the present invention includes a groove 501 in a U-shape, A plurality of pipe bodies 510 disposed along the housing space 502 of the casing 500 and heat exchange with air flowing through the pipe body 510 And a working fluid 520 to be performed.

The casing 500 is formed in an upright shape by a combination of horizontal or vertical frames, and each side is opened so that air introduced from the outside can pass through. A housing space is provided in a U shape so that the pipe body 510 is disposed in the accommodation space 502 and the evaporator 40 is disposed in the groove 501, Side portions (portions A in Fig. 3) facing the front end and the rear end of the front end portion 40 are open.

In order to allow the casing 500 to be opened only at both side portions (A portion in FIG. 3) facing the front end and the rear end of the evaporator 40, The portion connecting the both side portions, that is, the portion B in FIG. 3, is formed to form a closed end, thereby preventing the efficiency of the working fluid flowing in the pipe body 510 from deteriorating as the heat exchange is performed in the portion B.

7, a heat insulating plate 503 is formed at a portion of the casing 500 facing the evaporator 40 as a portion connecting the side portions (portion B), so that heat exchange is performed only at the portion A And the heat exchange is blocked in the portion B and the efficiency is doubled.

Accordingly, in the present invention, an example of the heat insulating arm 503 for preventing the heat exchange and doubling the efficiency is presented in the part B.

The heat insulating plate 503 of the present embodiment is characterized in that it comprises 30 to 50 parts by weight of expanded vermiculite, 5 to 10 parts by weight of aluminum hydroxide and an alumina mixture, and 1 to 3 parts by weight of biochar to 100 parts by weight of polyacrylic acid resin.

First, the heat insulating plate 503 is also made of a polyacrylic resin as a main component, which is added with water as a water-soluble binder to prevent excessive condensation.

The expanded vermiculite is excellent in anti-corrosive properties, and is particularly intended to block the transmission of heat to the inside and the outside of the heat insulating plate 503 due to the porous material (the heat insulating plate is made of an iron plate.

Further, 5 to 10 parts by weight of a mixture of aluminum hydroxide and alumina is further mixed with the heat insulating plate 503 to control temperature cracks due to curing heat generated during the manufacturing process. In the case where microcracks are generated by curing heat in the process of manufacturing the heat insulating plate 503, such microcracks act as a point of heat transfer, and as a result, they act as a factor to lower the heat exchange efficiency. So that the aluminum hydroxide and alumina mixture are further blended with the composition of the heat insulating plate 503.

The aluminum hydroxide absorbs heat generated in the curing reaction process and decomposes into aluminum trioxide and water. That is, it is possible to control the temperature crack by reducing the hardening heat.

However, when aluminum hydroxide alone is added, as described above, it is decomposed into aluminum trioxide and water in the endothermic reaction process. As such a by-product, water may cause the strength of the paste to be lowered and the capillary phenomenon may be promoted, Which is the cause of the problem. Alumina is used as a mixture of aluminum hydroxide and alumina. The alumina is porous and absorbs the generated water to remove water as a by-product.

It is preferable that aluminum hydroxide and alumina have a weight ratio of 7: 3 to 8: 2. If the addition amount of alumina is less than the above range, the water absorption function of the by-product is insufficient. There is a problem that workability and the like are lowered.

Particularly, the insulating plate 503 is characterized in that it contains biochar. The biochar is a porous high carbon material obtained by pyrolyzing biomass and waste resources under anaerobic or hypoxic conditions. First, the amount of generated carbon dioxide is reduced through carbon absorption .

That is, in a closed space where dehumidification is required, a large amount of carbon dioxide is generated due to respiration of a person, etc., and the occurrence of such excessive carbon dioxide may act as a factor to lower the heat exchange efficiency. As a result, the amount of carbon dioxide which reduces the heat exchange efficiency by containing biochar is reduced, and it is advantageous in terms of environment by reducing the amount of generated carbon dioxide.

The pipe body 510 is installed along the longitudinal direction of the casing 500 in the accommodating space 502 of the casing 500 as described above and includes a U- Structure. The pipe main body 510 has a structure in which the working fluid 520 is received therein and the working fluid 520 can flow and circulate from one end to the other end or from one end to the other end according to heat exchange .

The pipe main body 510 has a plurality of pipe main bodies 510. The pipe main bodies 510 are spaced apart from each other by a predetermined distance and are disposed side by side in the housing space 502 of the casing 500. One end of the pipe main body 510 is connected to the front end of the evaporator 40 And the other end thereof is provided so as to face the rear end of the evaporator 40.

The gudge part 511 formed in the pipe body 510 is for flowing the working fluid in the liquid state from the condensing part to the evaporating part in the phase change of the working fluid 520 as described above, The capillary pressure acts as a driving force for returning the liquid working fluid 520 from the condensing portion 50B to the evaporating portion 50A.

5A, the groove 511 of the pipe body 510 is formed on the inner circumferential surface of the pipe body 510 of the cylindrical body such that the angle in the longitudinal direction of the pipe body 510, that is, And a groove 511 parallel to the longitudinal direction of the pipe body 510 is continuously formed.

5B, the groove 511 may be formed on the inner circumferential surface of the pipe body 510 so that the angle in the longitudinal direction of the pipe body 510, that is, the inclination angle is in the range of 0 deg to 90 deg The grooves can be continuously formed in parallel with the longitudinal direction of the pipe body 510 or with a turning angle between 0 and 90 degrees.

6A, the groove 511 according to an embodiment of the present invention has an upper width D1, which is an opening toward the central point of the pipe body 510 in the pipe body 510, ), And the cross-sectional area of the inside increases.

Here, the groove 511 of this embodiment can be formed by rounding both corners of the lower width D2 as shown in FIG. 6B, so that the friction of the liquid flow path can be reduced with the increase of the cross-sectional area.

The reason why the bottom width D2 of the groove 512 is larger than the top width D1 is that it is transmitted from one end (vaporizing portion) 50A to the other end (condensing portion) 50B of the heat pipe heat exchanger 50 When the heat load to be performed is large, the liquid evaporation amount per unit time in the evaporator 50A increases, so that the liquid is quickly recirculated from the condenser 50B to the evaporator 50A to ensure continuous heat transfer Since the circulation of the working fluid 520 is made by the pressure difference, the structurally induced capillary pressure? Pcap is proportional to the pressure loss? P1 and? Pv in the liquid flow path and the gas flow path, The groove 511 is formed sufficiently to compensate for the pressure gradient? Pg of the liquid by the difference in relative height between the evaporator 50A and the condenser 50B in the gravitational field.

Considering the above factors, the pressure relationship for operation of the normal heat pipe heat exchanger 50 is as follows.

? Pcap??? P1 +? Pv +? Pph +? Pg

Therefore, the present invention proposes a shape of the groove 511 in which the above-mentioned? Pcap is made larger and the above-mentioned? P1 is made smaller in order to achieve a higher efficiency of the heat pipe heat exchanger 50. [

Therefore, in order to maximize the return force from the other end (condensing portion) 50B of the heat pipe heat exchanger 50 to the one end (vaporizing portion) 50A, the capillary pressure [Delta] Pcap is maximized, The pressure loss DELTA P1 in the liquid flow path is reduced by reducing the friction of the flow and by increasing the cross sectional area of the groove 512 to increase the heat transfer area in the condensing portion 50B and the evaporation portion 50A, The efficiency can be increased.

It will be apparent to those skilled in the art that various modifications and variations can be made in the present invention without departing from the spirit or scope of the invention. Therefore, the technical scope of the present invention should not be limited to the contents described in the detailed description of the specification, but should be defined by the claims.

10: compressor 20: condenser
30: Receiving machine 40: Evaporator
50: heat pipe heat exchanger 60: blowing fan
500: casing 510: pipe body
520: working fluid

Claims

A heat exchange line in which a working fluid flows into the inside and heat exchange with outside air is performed, and a corrosion prevention coating layer is formed on an outer periphery;
One or more pipes for cooling the air introduced from the front end of the heat exchange line by heat exchange of the working fluid contained in the shape of wrapping the front end and the rear end of the heat exchange line and for heating the air passing through the heat exchange line at the rear end of the heat exchange line A heat pipe heat exchanger including a body; And
And a blowing fan for allowing air to pass through the heat exchanging line and the heat pipe heat exchanger and exhausting the air.

The method according to claim 1,
The corrosion-
10. The cooling dehumidifier according to claim 1, wherein the polytetrafluoroethylene resin comprises 10 to 20 parts by weight of a cericite powder, 1 to 5 parts by weight of manganese oxide, 0.5 to 3 parts by weight of cellulose acetate and 1 to 5 parts by weight of calcium nitrite, based on 100 parts by weight of the polyacrylic acid resin.

The method according to claim 1,
The heat pipe heat exchanger
And a casing having a shape of 'U' shaped so that both sides of the heat exchanging line opposed to the front and rear ends of the heat exchanging line are opened, wherein the casing body is accommodated in the accommodating space. Cooling dehumidifier.

The method of claim 3,
Wherein a heat insulating plate is formed at a portion of the casing that connects the side portion and opposes the heat exchange line.

5. The method of claim 4,
Wherein the heat insulating plate comprises 30 to 50 parts by weight of expanded vermiculite, 5 to 10 parts by weight of an aluminum hydroxide and alumina mixture, and 1 to 3 parts by weight of a biochip, based on 100 parts by weight of the polyacrylic acid resin.