KR20110090750A - High efficiency dehumidifying apparatus with temperature control and the method thereof - Google Patents

Abstract

PURPOSE: A dehumidification device and method by controlling temperature is provided to obtain a target relative humidity by having a delay time until the air of a control space is in thermal equilibrium state. CONSTITUTION: A dehumidification device and method by controlling temperature comprises a step of monitoring the inside temperature and humidity of a control space using each sensors(S112); a step of classifying one or more layers according to the height of the control space based on the measured temperature(S115); a step of establishing a goal humidity of the control space(S117); a step of comparing the average humidity and goal humidity of the humidity measured; a step of discharging the cooled air to the lowest temperature layer and stopping the cooling device for a fixed hour(S118).

Description

Dehumidifier and temperature control method through temperature control {HIGH EFFICIENCY DEHUMIDIFYING APPARATUS WITH TEMPERATURE CONTROL AND THE METHOD THEREOF}

The present invention is to control the humidity of the enclosed space, in detail to control the temperature of the air in order to obtain the target relative humidity in detail high efficiency dehumidification through temperature control to obtain a dehumidification effect and condensation prevention effect An apparatus and a method thereof are provided.

Buildings, structures, or products that occupy some space in the atmosphere contain air inside them unless they are vacuumed. There is air inside the space, and there is moisture in the air. When a change in temperature occurs in such a space, the relative humidity in the interior space changes. Condensation does not occur when the temperature and humidity change while the relative humidity of the internal space does not exceed 100%, but condensation occurs when the relative humidity exceeds 100%. When condensation starts to flow, problems such as corrosion problems, odors, mold growth, electrical leakage or short circuits appear. In consideration of human comfort, it is necessary to keep the relative humidity below 60%, but at least condensation water should be prevented from flowing down.

In order to prevent this condensation and to remove moisture from the air, the most common method is to use a cooling device to make a low temperature object and to contact the surface of this cold object to remove water vapor and to reduce humidity. It is a way.

These basic cooling and dehumidification methods are the same, but slightly depending on whether the purpose of using the device is to lower the temperature only, to remove moisture, or to provide only ventilation while maintaining the temperature of the existing indoor air. Different methods are used. Even for removing moisture, there are some differences in the methods depending on whether the purpose is to lower absolute humidity or to lower relative humidity.

Conventionally, in order to lower the humidity of the air in an enclosed space, an air conditioner, a dehumidifier, or a constant temperature and humidity device is used. In order to obtain the target relative humidity value, the device was forced to circulate air and dehumidified. Air conditioners, dehumidifiers and thermo-hygrostats all use a cooler consisting of a compressor, a condenser, an evaporator and a heat exchanger. The air temperature is lowered or dehumidified through adiabatic compression, cooling, adiabatic expansion and heat exchange. At this time, the method of lowering the temperature or dehumidifying is to make a low-temperature object surface using a cooler, and then contact the high temperature air to change water vapor from the supercooled air by condensation into water and then discharge it.

Looking at the existing cooling method and apparatus in detail, the adiabatic compression process and the cooling process of the cooler in the air conditioner is performed in the outdoor unit, the adiabatic expansion process and heat exchange process is performed in the indoor unit to use the method of releasing heat and moisture out.

In the dehumidifier, all the cooling processes are performed indoors, and the moisture is converted into water and stored in the storage tank of the dehumidifier, but since all processes using electric energy are performed indoors, the dehumidified air is discharged more than the temperature of the air input to the dehumidifier. The temperature is discharged high. Therefore, when the relative humidity is obtained using the dehumidifier and the same relative humidity is obtained using the air conditioner, the absolute humidity is high (because the air temperature is high) when using the dehumidifier.

In case of thermo-hygrostat, it is a device capable of forcibly humidifying and dehumidifying and heating and cooling by additionally using heating heater and humidifier in addition to all devices of air conditioner. Exclude from comparison and do not explain possible comparisons.

 Air density or weight is denser and heavier at lower temperatures, and lower and lighter at higher temperatures. This is expressed as an equation.

ρ _hd is the density of wet air (kg / m³), P _d is the pressure of dry air (Pa), R _d is 287.05 J / (kgK), the specific heat ratio of dry air, T is the absolute temperature (K), P _v Is the pressure (Pa) of wet air, and R _v is 461.495 J / (kgK) which is the specific heat ratio of wet air.

The equation for determining the density of air as a function of the temperature (t: ℃), relative humidity (h:% RH) and pressure (p: mmHg) used in daily life is as follows.

Therefore, the air present in a space has cold air in the low place and hot air in the high place. If this condition is broken, convection occurs and eventually the air moves underneath the low temperature air and up the high temperature air.

In addition, the saturated water vapor pressure (amount of water vapor stored in 1m ³ : g / m ³ ) increases with increasing air temperature and decreases with decreasing temperature. Therefore, in the case of air containing the same amount of water vapor, the relative humidity decreases as the temperature increases, and the relative humidity increases as the temperature decreases. At this time, the absolute humidity is the same.

Due to the density of air described above, there is low temperature air in the low place, high temperature air in the high place, and the relative humidity in the low place becomes high and the relative humidity in the high place in consideration of the change of relative humidity by temperature. Is low.

Therefore, when condensation occurs, condensation occurs from a lower place, and when condensation occurs on the ceiling, relative humidity is 100% or more at all heights. Reflecting this, the temperature distribution and the humidity distribution of a certain space are shown in FIG. 1.

1 is a view showing how the temperature and humidity of the control space 10 is distributed in layers according to the height, the temperature of the bottom air layer is represented by T ₁ , the lowest density because the air with the highest density Location, where the highest density air has the lowest temperature. The humidity of the air layer at the lowest height is denoted by H _{1. At the} same absolute humidity, the lower the temperature, the higher the relative humidity. Therefore, the air layer at the lowest height has the lowest temperature T ₁ and the highest relative humidity H _1. It becomes an air layer which has.

That is, the temperature is T ₁ <T ₂ <T ₃ <T ₄ <T ₅ <T ₆ <T _{7 in} order of T ₇ being the highest, T ₁ being the lowest, and approximately T ₄ being the average temperature. In the case of relative humidity, H ₁ is the highest, H ₇ is the lowest, approximately H ₄ is the average relative humidity, and H ₁ > H ₂ > H ₃ > H ₄ > H ₅ > H ₆ > H ₇ .

The air layer located at the highest point of the control space 10 is the air layer in which the lightest air is the least dense. The least dense air is the hottest air, and at the same absolute humidity, the higher the air temperature, the lower the relative humidity, so the humidity is the lowest. In conclusion, the air layer at the highest position has the highest temperature T ₇ and the lowest relative humidity H ₇ . The air layer at the middle height of the control space 10 has a medium air temperature (average temperature) T ₄ and a medium relative humidity (mean humidity) H ₄ .

In general, in the case of controlling the temperature and humidity of the control space 10, the average temperature and the average humidity are detected and controlled, and the target temperature and the humidity are also mostly evaluated by the average value. However, in the case of precise analysis and precise control, the lowest temperature T ₁ of the control space 10 may be detected and controlled, and the highest temperature T ₇ may be detected and controlled.

In addition, when the air conditioner is installed on the floor and the ceiling, the energy efficiency and the penetration effect are different because the temperature and humidity of the control space 10 are distributed differently according to the height as shown in FIG.

A conventional air conditioner is shown in FIG. 2 to control the temperature and humidity of the air.

2 is a view for explaining in detail the flow and cooling of the cooling air in the control space 10 by the air conditioner using a conventional method, the indoor unit 20 is installed inside the control space as shown , The air passing through the lower grill 21 of the indoor unit 20 is lowered in the heat exchanger 34. The cooled air is discharged to the upper part of the indoor unit by the blowing fan 23 on the upper grill 22 side. At this time, the temperature of the discharged air is discharged at a temperature lower than T ₄ which is the average temperature of most of the room temperature, the humidity is lowered by the dehumidification effect.

In general, in the case of an air conditioner, the indoor unit 20 is installed inside the control space 10, and the indoor unit 20 measures the temperature and humidity inside the control space 10 by installing Hs and a temperature sensor Ts. Accordingly, the operation of the air conditioner is determined. The air conditioner indoor unit 20 sucks air through the lower grill 21 and discharges cooled air through the upper grill 22. At this time, the wind strength of the discharged air is determined by the strength of the blower fan 23.

The air discharged through the upper grill 22 is heavier than the surrounding air because it is cold air. Therefore, the discharged air circulates while being forwarded while drawing forward the trajectory indicated by the dotted arrow in FIG. 2. The height of the indoor unit 20 is manufactured to be almost the same height as the height of the person, and to adjust the horizontal and vertical direction of the wind discharged by using a wing (not shown) installed in the upper grill (22). In the case of such an air conditioner, since the main purpose is to rapidly reduce the average temperature of the internal air by mixing as much as possible with the air inside the control space 10, the air is blown and sent to various spaces as possible. For this purpose, the blade of the upper grill 22 is rotated up and down and left and right, and if necessary, the intensity of the blowing fan 23 may be adjusted. With this equipment to achieve this purpose, the indoor unit 20 becomes more complicated, uses unnecessary energy and generates a lot of noise.

Therefore, in the case of the air conditioner, the air at a position above the height at which the wind intensity by the blower 23 reaches in the upper grill 22 is hardly controlled, and the air conditioner mainly sucks the air inside the trajectory where the cooling air moves. Because it cools and discharges, energy efficiency controlling temperature and humidity using air conditioners is reduced. In addition, in the case of the air conditioner, since the control space 10 tries to maintain a low temperature state by breaking the thermal equilibrium state obtained in the natural state, it is necessary to continuously operate the air conditioner to draw out the heat of the space inside the control space 10 to the outside. From the moment the air conditioner stops operating, the air inside the control space 10 starts to exchange heat with the outside, and eventually the temperature returns to the initial natural thermal equilibrium.

Air conditioners flow from top to bottom because the air discharged from the upper grill is low and heavy. At this time, the air is randomly mixed with the surrounding air to lower the temperature of the air as a whole.

In the case of air conditioners, in order to change the area where air temperature is reduced by mixing with cooling air in the control space, it is obtained by adjusting the rotation speed of the blower fan and the angle of the wing of the upper grill, but the control is not performed because heavy air does not naturally rise upward. There have been many problems in cooling the air in the upper part of the space. In order to solve this problem and increase the cooling efficiency, air conditioners may be installed on the ceiling, but there are disadvantages in that the distance to move the refrigerant increases and the efficiency of circulating the air as a whole is in close proximity to the positions of the inlet and outlet. All of these air conditioners are discharged at a temperature lower than the average temperature of the control space, and the temperature is lowered by randomly mixing the air inside the control space with the cooling air discharged at a lower temperature, and the thermal equilibrium state naturally obtained by the control space. In order to maintain a lower temperature, a large amount of energy had to be used. At this time, since the control space is not completely insulated or sealed from the outside, heat loss continues, and the air conditioner continuously consumes energy.

And the dehumidification process of the conventional dehumidifier is shown in FIG. 3 is a cross-sectional view of the control space showing the flow of cooling air inside the control space when operating the conventional dehumidifier, the entire cooler is contained in the dehumidifier 50 and the dehumidifier 50 is inside the control space. Therefore, the temperature of the air discharged to the upper grill 22 is higher than the air input to the lower grill 21. In the case of dehumidifiers, the air inside the control space is operated without considering the distribution of air temperature and humidity in layers. The dehumidifier 50 has a low height so that the distance between the suction port and the discharge port is short, thereby limiting the range of dehumidification by circulating the air, and without a device for forcibly circulating humid and heavy air at a temperature lower than the temperature of the discharged air, it is wet and heavy. Difficult to move the air The dehumidifier 50 also has low energy efficiency because the dehumidified air and the air requiring dehumidification are randomly mixed and dehumidified, and low temperature humid air, which has to dehumidify moisture, does not move around the dehumidifier. Only air is continuously circulated and dehumidified, resulting in lower energy efficiency.

In addition, when the water vapor in the control space is to be converted into water and stored in the water tank 54, the air in the control space should be cooled. The more the dehumidifier 50 is used, the higher the average air temperature in the control space increases and If the dehumidifier is continuously used in a completely enclosed and completely insulated space, there is a problem that the dehumidification efficiency decreases gradually.

In the case of the dehumidifier 50, the air discharged from the upper grill 22 of the dehumidifier 50 reaches the space where the dehumidification effect is propagated inside the control space 10, and is located in the vicinity of the dehumidifier 50. Only air is dehumidified. Therefore, in the case of a large control space 10, many dehumidifiers 50 are often used. Dehumidifier 50 also does not use the characteristics of the air layer, and the efficiency is inferior because it tries to achieve the effect by mixing randomly controlled air and uncontrolled air, and water that is accumulated in the tank 54 must be treated separately. There was an inconvenience.

In the case of the dehumidifier 50, like the air conditioner, the outside and the control space 10 break the state in which the thermal equilibrium is naturally made and dehumidify by raising the temperature. Therefore, there is a problem that the relative humidity naturally rises when the power is turned off while using the dehumidifier 50.

The present invention solves this problem, provides a high-efficiency dehumidification device and dehumidification method through temperature control that can dehumidify the moisture contained in the air inside the control space in an effective and energy-efficient way and prevent condensation. It aims to do it.

In addition, the present invention is to control the air in the control space by dividing the air layer according to the height, so that the air inside the control space including the air discharged after cooling to have a delay time until the thermal equilibrium state before discharge It is another object of the present invention to provide a high efficiency dehumidification device and a dehumidification method through temperature control to obtain a target relative humidity.

In addition, the present invention is not a method of lowering the average temperature of the air by randomly mixing the air and the cooled air in the control space, the internal air is divided into layers by considering the temperature and humidity distribution according to the height, Another method is to provide a high efficiency dehumidification device and a dehumidification method through temperature control to dehumidify the air inside the control space to increase efficiency by allowing the air layer to sequentially inhale, cool, discharge, propagate and delay air. The purpose.

In addition, the present invention circulates and controls the air in all the spaces of the control space by using the difference in density of the air to circulate the air so as not to mix the dehumidified air with the non-dehumidified air. It is another object of the present invention to provide a high efficiency dehumidifier and a dehumidification method through temperature control.

Dehumidification method using a cooler of the present invention for achieving this purpose, (a) detecting the internal temperature and humidity of the control space to be dehumidified using each sensor, (b) the temperature measured in step (a) Separating the control space to be dehumidified based on the height into one or more layers by temperature, (c) setting the target humidity of the control space, (d) the average of the humidity measured in step (a) Comparing the humidity with the target humidity, and (e) if it is determined that the average humidity is higher than the target humidity, the control unit sucks air in the highest temperature layer of the control space and the sucked air is in the step (b). Driving and cooling the cooler so as to be lower than the lowest temperature sensed by (f), the controller is configured to discharge the cooled air to the lowest temperature layer and to stop the cooler for a predetermined time. Step and (g) the controller may be made to repeat the operation and stop of the cooler until the average humidity reaches the target humidity.

In addition, another dehumidification method using the cooler of the present invention (a) detecting the internal temperature and humidity of the control space to be dehumidified by using each sensor, (b) based on the temperature measured in the step (a) Separating the control space to be dehumidified into one or more layers for each temperature according to the height, (c) setting a target humidity of the control space, (d) the average humidity and the target humidity measured in the step (a) In the step of comparing the humidity, (e) if it is determined that the average humidity is higher than the target humidity in the step (d), the control unit compares the highest temperature in the control space with the outside air temperature to obtain a low temperature air. Inhaling and cooling the sucked air to a lower temperature than the lowest temperature in the control space, and (f) the controller discharges the cooled air to the lowest temperature layer and sets the cooler for a predetermined time. And step (e), the controller of may also be done, including the step of repeating the driving and stopping of the cooler until the average moisture in the target humidity.

The predetermined time for stopping the cooler is a time until the cooling air discharged after the cooling air is discharged to the thermal equilibrium state or a time selected through the selection lever, and the control unit in step (a) The discharge and stop of the cooling air may be repeated by more than the number of separated layers or the discharge and stop of the cooling air may be repeated until the average humidity reaches the target humidity.

The method of cooling the inhaled air below the minimum temperature is to compress and cool the air using a compressor and then adiabatic expansion or to compress and cool the refrigerant by using a compressor and adiabatic expansion to contact the air with a cold heat exchanger. The cooling method can be selected from among the cooling methods.

In addition, the dehumidification apparatus through the temperature control of the present invention is a sensor for measuring the internal temperature and humidity of the control space to be dehumidified, a cooler for cooling the inhaled air and the control space to be dehumidified based on the temperature measured by the sensor. When the target humidity of the control space is set and the target humidity of the control space is set according to the height, the average humidity of the humidity measured in the control space is determined and the target humidity is determined to be higher than the target humidity. When the air is sucked in the highest temperature layer of the control space, the cooler is driven and cooled so as to be lower than the lowest temperature detected in the control space, the cooled air is discharged to the lowest temperature layer, and the cooler is stopped for a predetermined time. Start and stop the cooler until the average humidity reaches the target humidity. It may be configured by a control unit that controls to suit.

On the other hand, another dehumidification apparatus through the temperature control of the present invention is a sensor for measuring the internal temperature and humidity of the control space to be dehumidified, a cooler for cooling the inhaled air and the control space to be dehumidified based on the temperature measured by the sensor Is separated into one or more layers for each temperature according to the height, and if the target humidity of the control space is set, the average humidity of the humidity measured in the control space and the target humidity is compared to determine that the average humidity is higher than the target humidity. If it is determined, the lowest temperature is drawn by comparing the highest temperature in the control space with the outside air temperature, and the cooler is cooled by driving the cooler to be lower than the minimum temperature detected in the control space, and the cooled air is cooled to the lowest temperature. Discharge the bed and stop the cooler for a predetermined time while the average humidity is Until the humidity is constituted by a control unit for controlling so as to repeat starting and stopping of the cooler.

The control unit uses a compressor to compress and cool the air, and then adiabatic expansion or a compressor to compress and cool the refrigerant, and adiabatic expansion to contact the air with a cold heat exchanger to cool the sucked air. It can be cooled to lower than the temperature, the drive of the cooler is stopped until the cooling air discharged after the discharge of the cooling air is in the thermal equilibrium state or the drive of the cooler for a selected time through the selection lever, The desired humidity can be obtained by repeatedly discharging and stopping the cooling air above the number of the separated layers.

Therefore, according to the high-efficiency dehumidification apparatus and dehumidification method through temperature control of the present invention, in the case of a control space where a person lives, the ideal relative humidity for obtaining a comfortable state without changing the temperature of the air inside the control space Control spaces such as warehouses where people who store metals, cements, electronics, etc., do not live, to obtain low relative humidity without considering the comfort index, to prevent corrosion, There is an effect of preventing a failure from occurring.

In addition, according to the present invention, since energy is dehumidified without changing the air temperature inside the control space, energy efficiency is high, and dust is generated less quietly by not circulating the air by the power of the fan, and the temperature inside the control space is forcibly There is no side effect of cooling bottle because it does not lower, and the dehumidified air is automatically propagated to all the positions inside the control space, so the effect range is wide, and it is possible to dehumidify the air at all positions in the control space sequentially so that there is no unnecessary waste of energy. The effect of dehumidification is long lasting due to the use of thermal equilibrium in the present state of the space, and the life of the equipment is prolonged by periodically having a rest period without continuously operating equipment such as a cooler. There is.

1 is a cross-sectional view of a control space showing that it is divided by virtual floors in consideration of the temperature distribution and relative humidity distribution of air according to the height inside the control space,
Figure 2 is a cross-sectional view of the control space showing the flow of cooling air inside the control space when operating the existing air conditioner,
3 is a cross-sectional view of the control space showing the flow of cooling air inside the control space when operating the conventional dehumidifier,
Figure 4 is a block diagram showing the connection of each device showing a case of using a compressor using a refrigerant to obtain cooling air, as an example of installation of a high-efficiency dehumidification apparatus through temperature control according to the present invention,
FIG. 5 is a block diagram illustrating a connection relationship between devices in the case of directly compressing air into a compressor without using a refrigerant to obtain cooling air as an example of installation of a high-efficiency dehumidifying device through temperature control according to the present invention. gram,
6 is a humid air diagram showing an air conditioner, a dehumidifier, and a high-efficiency dehumidifier according to the present invention compared to a humid air diagram;
7 is a flowchart illustrating a control sequence when a compressor using a refrigerant is used to obtain cooling air in the control flowchart of the high efficiency dehumidification apparatus through temperature control according to the present invention.
And,
8 is a flowchart illustrating a control sequence in the case of directly compressing air into a compressor without using a refrigerant to obtain cooling air in the control flowchart of the high efficiency dehumidification apparatus through temperature control according to the present invention.

The terms or words used in this specification and claims are not to be construed as limiting in their usual or dictionary meanings, and the inventors may properly define the concept of terms in order to best explain their invention in the best way possible. It should be interpreted as meaning and concept corresponding to the technical idea of the present invention.

Throughout the specification, when a part is said to "include" a certain component, it means that it can further include other components, without excluding other components unless specifically stated otherwise. In addition, the terms “… unit”, “… unit”, “module”, “device”, and the like described in the specification mean a unit that processes at least one function or operation, which is hardware or software or a combination of hardware and software. It can be implemented as.

Definitions of terms used in the present specification are as follows.

"Control space" means a space to be dehumidified using an air conditioner, a dehumidifier or a heat exchanger, consisting of one or more layers separated by temperature according to the height of the internal air.

"Thermal equilibrium" is the state of thermal equilibrium between layers. That is, it means a state in which the cooled air introduced into each floor of the logically divided control space is returned to the temperature before the moisture is maintained and cooled.

Hereinafter, a high efficiency dehumidification apparatus through temperature control according to an embodiment of the present invention will be described with reference to the drawings.

4 is an embodiment of a high-efficiency dehumidification apparatus through temperature control according to an embodiment of the present invention, and a block diagram showing a connection relationship between devices showing a case of using a compressor using a refrigerant to obtain cooling air. Gram.

Method of using the indoor unit 20 including the outdoor unit 30 and the control unit 70 consisting of the compressor 31, the condenser 32, the evaporator 33 and the heat exchanger 34 as a method of controlling the temperature. to be.

In addition, the indoor unit 20 divides the control space 10 into a plurality of floors, and sensors Hs1 to Hsn and Ts1 to Tsn for measuring humidity and temperature of each floor are electrically connected to the control unit 70.

In an embodiment of the present invention, since the control space 10 is described by dividing it into seven temperature layers, the humidity sensor is described as using Hs1 to Hs7 and the temperature sensor to Ts1 to Ts7.

Since the basic principle of the configuration of the outdoor unit 30, the configuration and operation of the indoor unit 20 is the same as in the prior art, a detailed description thereof will be omitted.

However, the method and principle of controlling the air in the control unit 70 are different, and using the temperature sensor and the humidity sensor at various positions and discharging the cooling air from the lower grill 21 of the indoor unit 20 and suctioning it upwards is as follows. Different. In addition, it is fundamentally different from the conventional air conditioners or dehumidifiers to control and understand deeply that the difference in temperature and humidity according to the height of the air inside the control space 10 forms an air layer with different characteristics.

Specifically, the refrigerant is compressed in the compressor 31 to liquefy and cool in the condenser 32. In addition, since the outdoor unit 30 is installed outside the control space 10, the temperature of the refrigerant is reduced by using external air. At this time, the temperature of the refrigerant inside the condenser 32 to be obtained is controlled in consideration of the degree to which the temperature is lowered when adiabatic expansion in the evaporator 33, and in consideration of the heat loss when transferred to the heat exchanger 34 (10). It is important to lower enough to be lower than T ₁ , the lowest of the internal air temperatures. Although not shown separately, the temperature sensor for detecting the temperature of the refrigerant inside the condenser 32 and the cooling fan of the outdoor unit 30 are electrically connected to the control unit 70 and controlled and controlled.

At this time, the time when the compressor 31 compresses the refrigerant, the time when the refrigerant is cooled in the condenser 32, and the total time used for adiabatic expansion of the refrigerant in the evaporator 33, discharges cooling air into the control space 10. Since it should be shorter than the delay time Dt until the thermal equilibrium, the power of the compressor 31, the cooling fan of the condenser 32, the type of the refrigerant, the size of the evaporator, etc. should be determined.

As described above, when the refrigerant temperature flowing in the heat exchanger 34 is lowered, the surface temperature of the heat exchanger 34 is lowered to the temperature of the refrigerant, and the air input through the suction pipe 26 of the indoor unit 20 receives the heat exchanger 34. The control unit 70 controls the discharge to the control space 10 through the lower grill 21 along the discharge pipe 27 after performing a heat exchange with the surface of the).

In addition, although the heat exchanger 34 is installed in the outdoor unit and the control unit 70 is installed in the indoor unit, the present invention may be installed in the indoor unit or the outdoor unit, respectively.

At this time, the blowing fan 23 to create such a flow of air is slower and weaker than the conventional blowing fan 23, even if rotated to obtain the same or better effect, less noise and high energy efficiency. In addition, the blowing fan 23 may be installed behind the lower grill 21, and the effect is the same even if installed between the heat exchanger 34 and the suction pipe (26).

Looking at the air layer inside the control space 10, the air temperature of the lowest air layer is T ₁ , the humidity is H ₁ , the air temperature of the middle layer is T ₄ , the humidity is H ₄ , and the air of the highest air layer is The temperature is indicated by T ₇ and the humidity by H ₇ .

For example, the air temperature of the lowest air layer is 18 ° C. (T ₁ ) and increases by 1 ° C. per layer to set the control space 10 in which the air temperature of the highest air layer is 24 ° C.

If condensation occurs only in the lowest air layer, the relative humidity (H ₁ ) of this air layer will be 100% (saturated water vapor pressure = 15.366 g / m ³ ), and if all air layers have the same absolute humidity, the intermediate layer will be saturated at 21 ° C. Since the water vapor pressure is 18.323g / m ³ and the highest air layer is 24 ℃, the saturated water vapor pressure is 21.773g / m ³ , so the average (medium) humidity value H ₄ is 83.8%, and the minimum humidity value H ₇ is 70.57%. Becomes

These saturated steam pressures for each temperature are shown in [Table 1].

If the air cooled through the discharge tube 27 discharges air having a relative humidity of 15 ° C. 100% to the lower layer having a temperature of 18 ° C. in the above state, the discharge air having the lowest air temperature has the highest density. Since it is high, it is evenly spread over the entire floor of the control space 10 at the lowest height. The uniform spreading of dense air at the same height is the same phenomenon as flowing water into an enclosed space.

Then, the change in temperature and humidity of each air layer is as shown in [Table 2] below.

The description here as inputting air having 100% relative humidity of 15 ° C. is intended to emphasize the fact that the apparatus and method according to the invention only need to lower the temperature in order to control the humidity.

This is because air at 100 ° C and 15% relative humidity means only lowering the temperature but not controlling the humidity at all.

In the description, the temperature and relative humidity of the control space 10 before the cooling air discharge state are displayed for each air layer, and the height order of the tables and figures is reversed because the first floor is the lowest height and the seventh floor is the highest air layer.

Table 1 is a table illustrating the change in humidity after the first cooling air discharge.

When the primary cooling air is discharged, the heaviest air of 15 ° C. is laid at the lowest position, and the remaining air layer is pushed up one space by buoyancy, and the air at the highest position, which is the seventh floor, is discharged to the outside, or the indoor suction port 24 is provided. After cooling through the heat exchanger 34 through the discharge pipe 27 is input to the lowest end of the control space 10 is circulated. Therefore, the state after discharging the cooling air is momentarily pushed up by one air layer as shown in the center column of [Table 2], and only the lowest air layer is in the state of 15 ° C 100%.

In addition, although the exemplary embodiment of the present invention describes the suction of the air of the highest temperature layer, this may inhale the air of the temperature layer that the user wants to control.

After discharging the cooling air, the controller 70 stops the cooling process and the heat exchange process and waits. How to determine the waiting time (delay time D _t ) will be described below.

After waiting for a predetermined time, the air that is forcedly pushed up by one layer by the contact of the input cooling air with the cooling air and the wall surface, the bottom surface of the control space 10, and the cooling air and the like is thermally equilibrated at a predetermined height again. It is in a state.

At this time, since the air in the air layers except for the bottom has the same absolute humidity as before the cold air is discharged, the relative humidity of each air layer becomes the same as the initial state, but the air of 15 ° C. rises to 18 ° C. Therefore, using natural energy, relative humidity drops to 83.5%. Therefore, condensation is prevented from occurring in the lowest air layer where condensation occurred.

For reference, the relation between relative humidity and water vapor pressure is shown in [Equation 3].

After the discharge of the cooling air, the water vapor pressure of 15 ° C is 12.827 and the thermal equilibrium state is maintained at 18 ° C even though the water vapor pressure is maintained at 12.827, so that the relative humidity is lower than the saturated water vapor pressure of 18 ° C.

That is, when "12.827" is substituted for "current water vapor pressure" and "15.366" is substituted for "saturated steam pressure" in Equation 3, 83.5% is calculated.

In addition, after the thermal equilibrium with the outside is obtained, the control unit 70 again discharges 100% of 15 ° C., which is cooling air, into the control space 10. 18 ° C, 83.5% of the air is pushed up to the second air layer to rise.

[Table 3] is a table illustrating a change in humidity after the discharge of secondary cooling air.

In other words, the temperature and humidity after the thermal equilibrium state obtained in [Table 2] are the temperature and humidity before the discharge of cooling air in [Table 3].

The change in temperature and humidity of the air layer by height after the discharge of the secondary cooling air is shown in a table. The shaded portion in the table represents the humidity of the air layer obtained by entering the cooling air to obtain a dehumidification effect, that is, the humidity after the thermal equilibrium state is obtained.

The first layer is the same as the principle that the primary cooling air is discharged, the state humidity is 83.5%, the second layer is after the cooling air is discharged, the water vapor pressure of the first layer before the discharge of cooling air is 15.836 and the temperature is 18 ℃ When it is pushed out to the second layer and the thermal equilibrium is achieved, the temperature of 18 ° C. is changed to 19 ° C., but the water vapor pressure is constant at 15.836, so that the relative humidity is lowered by the ratio of saturated water vapor pressure at “83.5%”.

In other words, when "15.366" is substituted for "current water vapor pressure" and "15.562" is substituted for "saturated water vapor pressure" in [Equation 3], the relative humidity becomes 98.74%. Therefore, 83.5% of the humidity after cooling air is lowered by 98.74%. 82.43%.

By repeating this process, the change in humidity after the third cooling air discharge is shown in Table 4 below.

When the air layers distributed by height are dehumidified one by one and the dehumidified air layers are pushed up one by one, the dehumidified space is gradually increased. The air layer pushed out of the dehumidified state obtains the thermal equilibrium state at the same humidity state as the first time, and maintains the same humidity value, but the humidity of the air layer pushed up by dehumidification has a lower humidity than the first time.

For reference, Table 5 is a table illustrating a change in humidity after the seventh cooling air discharge by repeating this process.

This is the result after replacing the seven times air with cooling air in the control space 10 divided into seven air layers. The rightmost state of the table represents the temperature and humidity conditions after acquiring thermal equilibrium. The temperature is the same as before the start, but the average humidity has decreased from 83.8% to 70.0%, the highest is 70.57%. 58.9% of the dehumidification was confirmed.

Until now, it was set to discharge the cooling air to the control space 10 with a relative humidity of 100% at a temperature of 15 ℃ arbitrarily. However, when the dehumidification is performed by circulating the air inside the control space 10 once dehumidified as described above, the humidity of the input air is already low so that a lower humidity can be obtained.

At this time, the wet air input to the compressor 31 is already air having a relative humidity of 58.9% at 24 ° C. Cooling the air at 24 ° C. to 15 ° C. results in cooling and dehumidification, thereby lowering the relative humidity. Exactly how much dehumidification effect the 24 ℃, 58.9% of the air on the surface of the heat exchanger 34 of 15 ℃ was not measured, but assume that only about 20% of the water vapor is removed. The amount of saturated steam of the air discharged by cooling at 15 ° C. is 10.26 g / m ³ .

When the air is discharged back to the lowest air layer, the change is as shown in Table 6 below.

In this case, the dehumidified air layer was replaced with a dehumidified 15 ° C. and air of 80.0% while being cooled again. After cooling the air at 24 ° C at the highest height and converting it into cooling air at 15 ° C and entering the control space 10 again, all air layers are pushed up one space again, and the two air layers acquire the dehumidification effect. It will be in the same state as the table.

[Table 7] is a table illustrating the change in humidity after the 9th cooling air discharge.

As shown in the various tables above, the input air layer or the air layer inside the control space 10 does not randomly mix with each other and rises up under buoyancy, thus eliminating unnecessary steps for cooling or dehumidifying the dehumidified or low-temperature air again. Dehumidification is not carried out, and dehumidification is performed first by selecting the air that needs the most dehumidification, and the dehumidifying effect of the cooled air spreads evenly inside all the control spaces 10 to achieve the desired dehumidifying effect. Will be acquired. When this process is repeated to replace the air layer 14 times in total, the result as shown in [Table 8] is obtained.

[Table 8] is a table illustrating the change in humidity after the 14th cooling air discharge.

By sequentially circulating the entire air inside the control space 10 exactly two times (14 times in seven temperature layers), the average humidity is fairly dry, with a relative humidity of 83.8% to 56.0%. The bottom air layer, where condensation occurred, was also reduced from 100% relative humidity to 66.77%, indicating that the environment was suitable for human habitation.

The input suction air is input through the suction pipe 26 to lower the temperature of the air by making contact with the heat exchanger 34. At this time, since it is efficient to input and use air having a low temperature in consideration of the temperature of the air T ₇ located at the highest point of the control space 10 and the temperature of the outside air, the indoor suction port is used to determine and control this. The upper temperature sensor Ts ₇ is installed at the 24 and connected to the control unit 70. The outside temperature sensor Ts _o is installed at the outdoor suction port 25 to compare the temperature of the indoor and outdoor air at a relatively low temperature. Is selected by the selection valve 40 to be sucked. At this time, the characteristics of the present invention determine the intake by setting the temperature of the input air as the main variable, the humidity is hardly considered.

Hereinafter, the case where air is compressed directly by a compressor without using a refrigerant | coolant is demonstrated.

5 is a diagram in which the principles and principles described in FIG. 4 are applied in a similar manner, but the difference is that the method of lowering the temperature of air indirectly by using a refrigerant in FIG. 4 is used. ) And then cooled outside the condenser (32) using the outside air, and adiabatic expansion in the evaporator (33) is the only way to drop the temperature. In this case, the position of the indoor suction port 24 is located at the highest position of the control space 10, and the cooling air is discharged to the lowest height.

6 is a humid air diagram, where the air temperature inside the control space 10 is distributed differently according to the height, and the low place is 20 ° C. and the high place is 27 ° C. FIG. The temperature range inside the control space 10 is indicated by a thick solid line.

The x-axis represents the dry bulb temperature, the y-axis represents the absolute humidity, and the parabolic plot on the XY plane represents the relative humidity.

The original letters ①, ②, and ③ represent the original air condition, ① is the temperature and humidity state of the low temperature part, ② is the average (medium) temperature and humidity state, and ③ is the temperature and humidity state of the high temperature part.

① The relative humidity is over 100%, so the condensation is already occurring in the lower part of this space. ② has a relative humidity of 85% at a temperature of 23.5 ℃, and ③ has a relative humidity of about 70% at 27 ℃.

In the drawing, "A ₁ " represents the air conditioner low temperature and humidity state, "A ₂ " represents the air conditioner average temperature and humidity state, "A ₃ " represents the air conditioner high temperature and humidity state, "C ₁ ~ C ₃ " is the low temperature, average, high temperature of the dehumidifier The temperature and humidity state and "B ₁ ~ B ₃ " is to display the low temperature, average, high temperature temperature and humidity conditions obtained by the high efficiency dehumidification apparatus through the temperature control of the present invention.

The air in the humid and hot control space 10 is changed to the state of A ₁ , A ₂ and A ₃ in the case of air conditioner, A ₁ is about 15.3 ℃, A ₂ is 19 ℃ and relative humidity is and the 60% condition, a ₃ is on the order of about 22.8 ℃.

In case of using dehumidifier, C ₁ , C ₂ and C ₃ are changed to the temperature and humidity state, where C ₁ is about 22.2 ℃, C ₂ is about 25.7 ℃ and the average relative humidity is A ₂ and Equally 60% and C ₃ is about 29.3 ° C.

The temperature and humidity state obtained by the high efficiency dehumidification apparatus through temperature control according to the present invention is represented by B ₁ , B ₂ and B ₃ . The temperature conditions of B ₁ , B ₂ and B ₃ are maintained at 20.0 ° C, 23.5 ° C and 27 ° C as in the original control space 10, and the average relative humidity shows the same 60.0% as the air conditioner or dehumidifier.

In the case of the air conditioner, when cooling and dehumidifying the air inside the control space 10, the characteristics of the air layer by the height of the points ①, ② and ③ are not taken into account, and the cooling air is randomly mixed to cool and dehumidify. In this case, the air that has already been cooled and dehumidified is also unnecessarily cooled and dehumidified, and the air at a height or a position where the cooling air cannot reach remains uncontrolled. In addition, since the temperature and humidity of the space obtained using the air conditioner is A ₁ , A ₂ and A ₃ , the temperature is low overall, and the average temperature is lowered from 23.5 ° C. to 19 ° C. In order to maintain this state of forced thermal equilibrium continuously, the air conditioner must continuously supply the cooling air to the inside of the control space 10 using energy because the air at 19 ° C. must be prevented from returning back to 23.5 ° C. do. In addition, in order to obtain air of about 15.3 ° C, more energy is consumed because the surface temperature of the heat exchanger must be cooled to at least 15.3 ° C or lower.

In the case of the dehumidifier 50, the temperature-humidity state is changed to C ₁ , C _2, and C ₃ , and the average temperature has risen from 23.5 ° C. to 25.7 ° C., and the average relative humidity is 60%, but additional energy is required to make it high. The amount of energy used as a whole increases because the supercooling is performed to dehumidify and the temperature of the cooling air is increased again by using a heater. In addition, when the dehumidifier is turned off, the control space 10 is returned to the thermal equilibrium state with the surroundings, and returns to the original average temperature of 23.5 ° C. which is the most natural state.

Then, the average relative humidity of the control space 10 using the dehumidifier 50 is increased from 60% to about 73% and there is a problem that the dehumidification effect is halved.

However, the high-efficiency dehumidification apparatus through temperature control according to the present invention makes the temperature and humidity of the control space 10 into B ₁ , B ₂ and B ₃ states only by temperature control. In order to convert to this state, the air is cooled, and the lowest temperature is B ₁ , that is, only about 2-3 degrees lower than 20.0 ° C. Therefore, there is no need to overcool the air more than necessary. Since the air is cooled and circulated, it does not require a process of unnecessarily cooling the air once cooled and dehumidified. In addition, once the B ₁ , B ₂ and B ₃ state is acquired, the dehumidification effect is maintained for a long time without serious consideration of heat transfer to the outside because the temperature of the control space 10 naturally obtained in the state of thermal equilibrium. However, in order to prevent the inflow of moisture from the outside, the air inside the control space 10 may be leaked to the outside or humid air may be controlled so that it is much easier and more structurally effective than other methods. Receive less.

Hereinafter, a dehumidifying method of the present invention will be described with reference to the drawings.

7 is a flowchart illustrating the control and operation of the high-efficiency dehumidification apparatus through temperature control according to the present invention. As shown in the drawing, the performance and control of the operation are mainly controlled by the controller 70 in an external temperature and humidity state. Using several temperature sensors and humidity sensors to obtain the.

When the power is turned on first, the controller 70 detects or determines the average humidity Hs _o , the lowest temperature Ts ₁ , the delay time D _t , and the fan operating time F _t in the control space 10 (S110).

There are three ways to determine the delay time D _t . The fundamental principle is that the cooling air discharged into the control space 10 is heated by contact with inner walls, floors and various objects in the control space 10. It is waiting for it to be delivered and restored to its original temperature. The first method is to check the temperature of the discharged cooling air returned to the original temperature with the temperature sensor. The discharge temperature sensor Ts _n initially detects the discharge temperature (eg 15 ° C. in FIG. 4) but over time will become the same as the original lowest temperature T ₁ (eg 18 ° C. in FIG. 4). Therefore, waiting for this time can determine the delay time D _t .

When the delay time is determined using the temperature sensor in this way, Dt is not determined in step S110, but it is included in step S110 to describe all other methods.

The second method is to install a selection lever (not shown) to determine the delay time Dt. In this case, it is correct to determine D _t in step S110.

The third method is to calculate Dt by calculation using heat capacity exchanged with heat exchange of adjacent air layer considering the amount of air discharged and the characteristics of space (area, thermal conductivity of wall surface, etc.). Even in this case, it is better to determine Dt in step S110.

Also, without using a T ₁ in a method for determining the delay time T ₂ Of course, you can use the temperature sensor of any air layer of ~ T ₇ .

Step S111 is a step of determining whether the cooler is operated by comparing the relative humidity (eg, average humidity Hs _a ) to be controlled with the target humidity H _t , and the current humidity (Hs _a ) is the target humidity (H _t). If higher than), dehumidification is required, so switch to step S112 in order to start the cooler, but if the relative humidity is already lower than the target humidity, it is not necessary to start the cooler, so go back to step S110 to detect or determine the humidity and temperature. Do it.

Step S112 initializes the counter of the timer set in the controller 70 and starts time measurement to determine the operating time of the cooler (including the compressor, the condenser, the evaporator, and the heat exchanger of the outdoor unit) and the blower fan 23. It's a step.

Such a blowing fan 23 may not be used if necessary.

When the time meter is initialized in step S112, the controller 70 operates the cooler and the blower fan 23 so that the cooled air is discharged through the lower grill 21 (S113).

Thereafter, in step S114, the discharge temperature is sensed through the discharge temperature sensor Ts _n .

In step S114, the discharge temperature detected by the discharge temperature sensor Ts _n is compared with the value detected by the lower temperature sensor Ts ₁ which detects the lowest height temperature of the control space 10. Is lower than the lowest air temperature in the control space 10, the air is continuously blown without decelerating the speed of the blowing fan 23, and if the temperature of the discharged air is high, the flow is switched to step S117 to determine the speed of the blowing fan 23 By lowering the length of time that the intake air is in contact with the metal surface of the heat exchanger (34) to increase the time to select the step to perform the operation of lowering the temperature.

Here, there are various methods of lowering the temperature of the discharged cooling air, but one method of lowering the speed of the blower fan 23 is a method of determining the cooling temperature using the degree of cooling of the condenser 32 as described above. Can be used.

Step S117 determines the time for discharging the cooling air by operating the blower fan 23. When the elapsed time Timer is greater than the fan operating time F _t , the process goes to step S118 to stop the cooler and the blower fan 23. If the elapsed time (Timer) is still smaller than the fan operating time (F _t ), the step is to check the time while continuing to blow.

In step S118, when it is determined that the elapsed time Timer is greater than the fan operating time F _t in step S117, the cooler and the blowing fan 23 are stopped, and in step S119, the controller 70 resets the time meter. Start the measurement.

Again in the step S120 is again fed back to the step S110 when the time is a delay time _(t D) small, no waiting for a delay time _(t D) is more than repeat the entire procedure.

FIG. 8 is a flowchart illustrating a control sequence in the case of directly compressing air into a compressor without using a refrigerant to obtain cooling air in a control flowchart of a high efficiency dehumidifying apparatus through temperature control according to the present invention. It shows a control flowchart similar to 7, but differs in some ways.

The main difference is that the temperature sensor is used as a method of determining the delay time (D _t ), and the cooler also uses a refrigerant to directly compress and expand the air, rather than using a refrigerant.

Step S130 is the same as that of FIG. 7, but additionally includes calculating and determining a condenser target temperature Tc _r , which is a cooling temperature of the condenser 32.

After performing step S130 as shown in FIG. 7, step S131 detects the temperature of the lowest air in the control space 10 as Ts ₁ and stores the value as the cold storage temperature Ts _1o . The lowest temperature value stored in Ts _1o and stored in this way is to perform the temperature sensor to wait until the discharged cooling air is returned to the original thermal equilibrium state.

Step S131 is the same as step S111 of FIG. 7, and step S133 is a step of operating the compressor 31 to compress the air, and is automatically considered in consideration of the size of the condenser 32 storing the compressed air and the maximum available pressure. It is specified that it is to be stopped.

Step S134 is a step of sensing the internal temperature Tc of the condenser 32 while operating a condenser cooling fan (not shown) to cool the condenser 32, and step S135 is a detected internal temperature of the condenser 32. Comparing the Tc and the calculated condenser target temperature Tc _r , the condenser 32 is continuously cooled to operate the condenser cooling fan to cool the condenser 32.

Step S136 is a step after confirming that the condenser 32 is sufficiently cooled, and stops the condenser cooling fan (not shown) and starts the evaporator fan (not shown).

In step S137, the cooling air stored in the condenser 32 is discharged to the evaporator 33 by using an evaporator fan (not shown) inside the condenser 32. The pressure sensor (not shown) installed in the condenser 32 may be used. By using the step of sending the cooling air to the evaporator until the pressure inside the condenser 32 is equal to the atmospheric pressure.

Step S138 is a step of stopping the evaporator fan to prevent further cooling air discharge, in step S139 detects the temperature value of the lower temperature sensor Ts ₁ for measuring the temperature of the lowest height where the discharged air is located, In step S140, the delay time is determined by comparing with Ts _1o , which is an original temperature value of the control space 10 previously stored. While continuing to wait, if Ts ₁ becomes equal or higher than the original temperature value Ts _1o , the delay ends and the device feeds back to step S131 to repeat the whole process.

As described above, the high efficiency dehumidification apparatus through temperature control according to the present invention is not significantly different from the existing air conditioner or dehumidifier in terms of apparatuses, but the method of controlling the apparatus is different, and the position of the humidity sensor and the temperature sensor to be detected and The number is different, the principle of controlling and circulating the internal air is different and the positions of the inlet and outlet are different. In general, the method of obtaining the target humidity is fundamentally different from the method in which the air inside the control space is maintained without breaking the thermal equilibrium in a given environment and conditions.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is evident that many alternatives, modifications and variations will be apparent to those skilled in the art.

10: control space 20: indoor unit
21: lower grill 22: upper grill
23: blower fan 24: indoor suction
25: outdoor suction port 26: suction pipe
27: discharge tube 30: outdoor unit
31: Compressor 32: Condenser
33: evaporator 34: heat exchanger
40: selector valve 50: dehumidifier
54: tank 70: controller
H1: Level 1 Humidity = Maximum Relative Humidity
H4: Level 4 Humidity = Average Humidity
Hm: m level humidity (m = 1, 2, 3, ,,,, 7)
H7: Level 7 Humidity = Minimum Relative Humidity
Hs: Humidity Sensor Hs1: Lower Humidity Sensor
Hsa: Average humidity sensor Ht: Target humidity value
T1: 1st floor temperature = lowest temperature T4: 4th floor temperature = average temperature
Tn: nth layer temperature (n = 1, 2, 3 ,,, 7)
T7: 7th floor temperature = highest temperature Tc: Condenser internal temperature
Tcr: Condenser Target Temperature Ts: Temperature Sensor
Ts1: Lower temperature sensor Ts1o: Low temperature part storage temperature value
Ts7: Upper temperature sensor Tsn: Discharge temperature sensor
Tso: outside temperature sensor Dt: delay time
Ft: Fan Run Timer: Time Meter

Claims (9)

In the dehumidification method using a cooler,
(a) detecting the internal temperature and humidity of the control space to be dehumidified using each sensor;
(b) separating the control space to be dehumidified into at least one layer for each temperature according to the height based on the temperature measured in step (a);
(c) setting a target humidity of the control space;
(d) comparing the average humidity of the humidity measured in step (a) with the target humidity;
(e) If it is determined that the average humidity is higher than the target humidity, the control unit sucks the air of the highest temperature layer in the control space and the cooler so that the sucked air is lower than the lowest temperature detected in step (b). Driving to cool;
(f) the control unit discharging the cooled air to the lowest temperature layer and stopping the cooler for a predetermined time; and
(g) repeating driving and stopping of the cooler until the average humidity reaches the target humidity;
Dehumidification method through temperature control comprising a.
The method of claim 1,
In step (f)
The predetermined time for stopping the cooler
Dehumidification method by controlling the temperature, characterized in that the time until the discharged cooling air to the thermal equilibrium state after discharging the cooling air.
The method of claim 2,
In step (f)
The control unit is a dehumidification method through temperature control, characterized in that for repeating the discharge and stop of the cooling air more than the number of layers separated in step (a).
In the dehumidification method using a cooler,
(a) detecting the internal temperature and humidity of the control space to be dehumidified using each sensor;
(b) separating the control space to be dehumidified into at least one layer for each temperature according to the height based on the temperature measured in step (a);
(c) setting a target humidity of the control space;
(d) comparing the average humidity of the humidity measured in step (a) with the target humidity;
(e) If it is determined in step (d) that the average humidity is higher than the target humidity, the controller compares the highest temperature in the control space with the outside air temperature and inhales the low temperature air, and the sucked air Cooling the temperature below the lowest temperature in the controlled space;
(f) the control unit discharging the cooled air to the lowest temperature layer and stopping the cooler for a predetermined time; and
(e) the controller repeating driving and stopping of the cooler until the average humidity reaches the target humidity;
Dehumidification method through temperature control comprising a.
The method of claim 4, wherein
In step (f)
The predetermined time for stopping the cooler
Dehumidification method by temperature control, characterized in that the time until the discharged cooling air after the discharged cooling air to the thermal equilibrium state or selected through the selection lever.
6. The method of claim 5,
In step (e)
The control unit is a dehumidification method through temperature control, characterized in that for repeating the discharge and stop of cooling air until the average humidity reaches the target humidity.
The method according to any one of claims 1 to 6,
The compressed air is compressed by using a compressor to cool and then adiabaticly expanded, or the refrigerant is compressed and cooled by using a compressor and then adiabatic to contact air to cool the heat exchanger. Dehumidification method through temperature control, characterized in that the cooling.
A sensor for measuring the internal temperature and humidity of the control space to be dehumidified;
A cooler to cool the sucked air; and
The control space to be dehumidified is divided into one or more layers by temperature based on the temperature measured by the sensor, and when the target humidity of the control space is set, the average humidity and the target humidity of the humidity measured in the control space are set. If it is determined that the average humidity is higher than the target humidity is determined to suck the air of the highest temperature layer of the control space and drive the cooler to cool below the lowest temperature detected in the control space and the cooled air A control unit for discharging the coolant to the lowest temperature layer and then stopping the cooler for a predetermined time and repeating the driving and stopping of the cooler until the average humidity reaches the target humidity;
Dehumidifier through temperature control configured to include.
The method of claim 8,
The control unit
After the cooling air is discharged, the driving of the cooler is stopped until the discharged cooling air is in a thermal equilibrium state, or the driving of the cooler is stopped for a selected time through the selection lever, and the number of the separated layers is equal to or greater than the number of the separated layers. A dehumidifier through temperature control, characterized in that for repeatedly discharging and stopping the cooling air.

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