KR20200112034A - Apparatus and controll method for constant temperature and humidity - Google Patents

Abstract

The present invention relates to a thermo-hygrostat capable of improving energy efficiency by removing ice that may be generated during low temperature operation of the thermo-hygrostat, and a thermo-hygrostat control method using the same. The thermo-hygrostat according to the present invention includes: a first chamber maintaining a constant temperature and humidity state; a temperature sensor measuring a temperature in the first chamber; a humidity sensor measuring a humidity in the first chamber; a heater that increases the temperature of the surrounding air by generating heat according to control; a humidifier that increases the humidity of the surrounding air by generating moisture according to control; a cooling device that absorbs heat according to control and adjusts the temperature and humidity of the surrounding air; a blower that moves air of which the temperature and humidity are controlled by the heater, humidifier or cooling device to the first chamber; a second chamber in which the heater, humidifier, cooling device and blower are located; and a controller that controls the operation of the heater, humidifier, cooling device, and blower based on values measured by the temperature sensor and humidity sensor.

Description

Thermo-hygrostat and control method of thermo-hygrostat using the same {APPARATUS AND CONTROLL METHOD FOR CONSTANT TEMPERATURE AND HUMIDITY}

The present invention relates to a thermo-hygrostat and a thermo-hygrostat control method using the same, and more particularly, by applying an inverter to a cooling device, it is possible to increase energy efficiency and reduce noise that may occur during the operation of the thermo-hygrostat. The present invention relates to a thermo-hygrostat and a thermo-hygrostat control method using the same.

In general, a thermo-hygrostat maintains the temperature and humidity of a room or a chamber in a state set according to the purpose of use of the place. The constant temperature and humidity device includes a heater, a humidifier, a cooling device, etc. to maintain a room or a space within a chamber at a desired temperature and humidity. Depending on how a heater, a humidifier, and a cooling device are operated in combination, how precisely the temperature and humidity in the room or in the chamber can be precisely controlled by the thermo-hygrostat and operating costs vary.

There are various types of thermo-hygrostats according to their configuration. For example, there are air-cooled thermo-hygrostat and water-cooled thermo-hygrostat according to the type of cooling device, and electric heater-type thermo-hygrostat and hot water coil-type thermo-hygrostat depending on the type of heater. In addition, according to the humidifier type, there are an electric heating type constant temperature and humidity device and a steam type constant temperature and humidity device.

The cooling device basically consists of a compressor, a condenser, an expander (or expansion valve), and an evaporator, and controls the temperature according to the cooling cycle. In the case of a constant temperature and humidity system, the capacity of the heater must be set in proportion to the capacity of the cooling system. That is, when the capacity of the cooling device increases, the capacity of the compressor increases proportionally, and thus the capacity of the heater must be proportionally increased. When the capacity of the heater and the compressor increases, there is a high possibility that unnecessary electricity is used to operate the heater and the compressor, which leads to a decrease in energy efficiency of the thermo-hygrostat.

In addition, as the compressor capacity increases, the noise generated also increases, making the equipment use environment difficult, as well as incurring additional costs for reducing the noise of the thermo-hygrostat.

Republic of Korea Patent Publication 10-1866424 (2018.6.4), pages 1 to 6

The present invention was devised to improve the conventional method as described above, and by applying an inverter to the cooling device, even if the capacity of the cooling device increases, energy efficiency can be improved and noise that may occur during operation is reduced. It provides a thermo-hygrostat and a thermo-hygrostat control method using the same.

The present invention provides a thermo-hygrostat capable of improving energy efficiency by removing ice that may be generated during low temperature operation of a thermo-hygrostat, and a thermo-hygrostat control method using the same.

The present invention provides a thermo-hygrostat and a thermo-hygrostat control method using the same, which can remove ice without additional cost during operation, so that maintenance/management is easy and maintenance/management cost can be saved.

The thermo-hygrostat according to the present invention includes a first chamber maintaining a constant temperature and humidity state, a temperature sensor measuring the temperature in the first chamber, a humidity sensor measuring the humidity in the first chamber, and generating heat according to the control A heater that increases the temperature of the air, a humidifier that increases the humidity of the surrounding air by generating moisture under control, a cooling device that absorbs heat and adjusts the temperature and humidity of the surrounding air according to the control, the heater, a humidifier, or a cooling device A blower for moving air whose temperature and humidity is controlled by the first chamber, a second chamber in which the heater, a humidifier, a cooling device, and a blower are located, and the heater based on values measured by the temperature sensor and the humidity sensor It characterized in that it comprises a controller for controlling the operation of the humidifier, the cooling device and the blower.

In one embodiment, the cooling device includes a compressor that compresses a phase change refrigerant, a condenser that heat exchanges and liquefies the refrigerant compressed through the compressor, an expander that expands the liquefied refrigerant through the condenser, and the refrigerant expanded through the expander. It characterized in that it comprises an evaporator for vaporizing by heat exchange.

In one embodiment, the thermo-hygrostat further comprises an inverter controlling the speed of the driving motor of the compressor, an inverter controller controlling the operation of the inverter, and a speed sensor measuring the speed of the driving motor of the compressor, the controller Is characterized in that controlling the inverter controller based on the values measured by the temperature sensor and the humidity sensor and the speed of the driving motor measured by the speed sensor.

In one embodiment, the thermo-hygrostat includes an atmospheric pressure sensor that measures the atmospheric pressure in the first chamber, a first valve that diverges and flows the refrigerant compressed through the compressor according to control, and a high-temperature flow rate introduced through the first valve. It characterized in that it further comprises a heating pipe for heating the evaporator by flowing a refrigerant.

In one embodiment, the thermo-hygrostat further comprises an evaporator temperature sensor for measuring a surface temperature of the evaporator.

In an embodiment, when the following Equation 1 is satisfied, the controller performs an ice removal operation of the evaporator through Equation 2 below.

[Equation 1]

Here, T _current,eva is the evaporator surface temperature measured by the evaporator temperature sensor, T _f (P) is the freezing point temperature according to the measured atmospheric pressure of the first chamber, and P is the measurement of the first chamber measured by the barometric pressure sensor. atmospheric pressure

[Equation 2]

Here, H _current is the current humidity in the first chamber, H _saturated (T _current ) is the saturated humidity at the current temperature in the first chamber, T _current is the current temperature in the first chamber, t _{(Tcurrent,eva ≤ Tf(P ))} is the time when the evaporator surface temperature is lower than the freezing point temperature of the first chamber, t _current is the current time, α is the first correction factor, β is the second correction factor, and I _th is the preset threshold of the I value.

In one embodiment, when the above equation (2) is satisfied, the controller controls the inverter to lower the current temperature of the first chamber by a compensation temperature, and controls the first valve to control the high temperature. The refrigerant is flowed through the heating pipe for a predetermined time to perform an ice removal operation.

In one embodiment, when the Equation 1 is satisfied, the controller calculates Equation 3 below and performs an ice removal operation of the evaporator when the constant temperature and humidity mode operation is terminated.

[Equation 3]

Here, T _end is the time when the operation of the thermo-hygrostat is terminated.

In one embodiment, the controller controls the first valve for a time calculated by Equation 4 below to flow the high-temperature refrigerant through the heating pipe to perform an ice removal operation.

[Equation 4]

Where γ is the third correction factor

In one embodiment, the cooling device includes a compressor for compressing a phase change refrigerant, a second valve for branching and flowing the refrigerant compressed through the compressor, a first condenser for exchanging heat and liquefying the refrigerant introduced through the first valve, A second condenser that heats and liquefies the refrigerant introduced through the first valve, a third valve that merges and flows the liquefied refrigerant through the first condenser and the second condenser, and expands the refrigerant introduced through the second valve. It characterized in that it comprises an expander and an evaporator for vaporizing by heat exchange of the refrigerant expanded through the expander.

In one embodiment, the second valve is characterized in that the refrigerant flows to the first condenser, but when the flow rate of the refrigerant exceeds a preset value, the refrigerant flows to the first condenser and the second condenser at the same time.

In the method for controlling a thermo-hygrostat according to the present invention, a temperature sensor measuring a temperature in a first chamber, a humidity sensor measuring a humidity in the first chamber, and an atmospheric pressure sensor measuring an atmospheric pressure in the first chamber. , The evaporator temperature sensor measuring the surface temperature of the evaporator, and the controller performing an ice removal operation of the evaporator based on the measured temperature, humidity, atmospheric pressure, and the surface temperature of the evaporator in the first chamber. To do.

In one embodiment, the performing of the ice removal operation of the evaporator comprises the step of, when the following Equation 1 is satisfied, the controller performing the ice removal operation of the evaporator through Equation 2 below. do.

[Equation 1]

Here, T _current,eva is the evaporator surface temperature measured by the evaporator temperature sensor, T _f (P) is the freezing point temperature according to the measured atmospheric pressure of the first chamber, and P is the measurement of the first chamber measured by the barometric pressure sensor. atmospheric pressure

[Equation 2]

Here, H _current is the current humidity in the first chamber, H _saturated (T _current ) is the saturated humidity at the current temperature in the first chamber, T _current is the current temperature in the first chamber, t _{(Tcurrent,eva ≤ Tf(P ))} is the time when the evaporator surface temperature is lower than the freezing point temperature of the first chamber, t _current is the current time, α is the first correction factor, β is the second correction factor, and I _th is the preset threshold of the I value.

In one embodiment, in the performing of the ice removal operation of the evaporator, when the Equation 2 is satisfied, the controller controls the inverter through the inverter controller to increase the current temperature of the first chamber by a compensation temperature. And performing an ice removal operation by lowering and controlling the first valve by the controller to flow the high-temperature refrigerant through the heating pipe for a predetermined time.

As described above, the thermo-hygrostat and the thermo-hygrostat control method using the same according to the present invention can improve energy efficiency even when the capacity of the cooling device increases and reduce noise that may occur during operation.

The thermo-hygrostat according to the present invention and the thermo-hygrostat control method using the same can improve energy efficiency by removing ice that may be generated during low-temperature operation.

The thermo-hygrostat according to the present invention and the thermo-hygrostat control method using the same can remove ice without additional cost during operation, so that maintenance/management is easy and maintenance/management cost can be saved.

1 is a block diagram showing a schematic configuration of a thermo-hygrostat according to an embodiment of the present invention
Figure 2 is a block diagram showing a schematic configuration of the thermo-hygrostat of Figure 1
3 is a diagram showing a process of controlling the temperature in a chamber using a cooling device to which an inverter is applied
Figure 4 is a block diagram showing another embodiment of the cooling device of Figure 1
5 is a block diagram showing another embodiment of the cooling device of FIG. 1
6 is a block diagram showing a schematic configuration of an evaporator
7 is a block diagram showing a schematic configuration of a thermo-hygrostat according to another embodiment of the present invention
8 is a block diagram showing a schematic configuration of the thermo-hygrostat of FIG. 7
9 is a flowchart illustrating a control method of a thermo-hygrostat according to an embodiment of the present invention

Hereinafter, specific details for implementing the thermo-hygrostat according to the present invention and the thermo-hygrostat control method using the same will be described as follows.

1 is a block diagram showing a schematic configuration of a thermo-hygrostat according to an embodiment of the present invention.

Referring to FIG. 1, the thermo-hygrostat 100 includes a first chamber 104, a separation wall 106, a second chamber 108, a temperature sensor 110, a humidity sensor 112, and a blower ( 114), a heater 116, a humidifier 118, and a cooling device 120, and the cooling device 120 includes a compressor 122, a condenser 124, an expander 126, and an evaporator 128. .

The constant temperature and humidity device may be a device provided in the computer room to protect the computer equipment, or may be a test device for reliability testing of industrial products. Hereinafter, for convenience of explanation, a constant temperature and humidity device for testing the reliability of an object to be tested such as an electronic device and a battery will be described.

The first chamber 104 is a space that maintains a constant temperature and humidity state set as a space separated from the second chamber 108 through the separation wall 106. In an embodiment, the object to be tested 102 may be located in the first chamber 104. For example, the object to be tested may be an electronic device or a battery.

The second chamber 108 includes a heater 116, a humidifier 118, a cooling device 120, and a blower 114. The first chamber 104 and the second chamber 108 are not respectively sealed chambers, and air in the first chamber 104 and the second chamber 108 may circulate.

The temperature sensor 110 measures the temperature in the first chamber 104, and the humidity sensor 112 measures the humidity in the first chamber 106. The positions of the temperature sensor 110 and the humidity sensor 112 in the first chamber 104 may vary according to implementation examples.

The heater 116 generates heat according to the control to increase the temperature of the surrounding air, and the humidifier 118 generates moisture according to the control to increase the humidity of the surrounding air. For example, when using the electric heating type humidifier 118, the humidifier 118 may be composed of a water tank in which water is accommodated and a humidifying heater disposed inside the water tank.

The cooling device 120 adjusts the temperature and humidity of the surrounding air by absorbing heat according to the control. The cooling device 120 controls temperature and humidity according to the cooling cycle. The compressor 122 compresses the high-temperature and low-pressure phase-change refrigerant gas through the evaporator 128 into high-pressure gas, and the condenser 124 converts the heat of the refrigerant into the heat of condensation while converting the high-temperature and high-pressure refrigerant gas into a high-pressure liquid. Discharge (heat exchange) into furnace. The expander 126 expands the high-pressure liquid refrigerant through the evaporator 128 into a low-pressure liquid, and the evaporator 128 absorbs the heat of vaporization of the refrigerant from outside air while changing the low-pressure refrigerant liquid into a high-temperature and low-pressure gas (heat exchange). )do. The evaporator 128 is located in the second chamber 108 and absorbs heat in the second chamber 108 to lower the temperature in the second chamber 108. In addition, the evaporator 128 may lower the ambient temperature to condense moisture, thereby lowering the humidity in the second chamber 108.

That is, the thermo-hygrostat can increase or decrease the temperature of the first chamber 104 by using the heater 116 and the cooling device 120, and can be removed by using the humidifier 118 and the cooling device 120. 1 The humidity of the chamber 104 can be increased or decreased.

The blower 114 moves air from the second chamber 108 whose temperature and humidity are controlled by the heater 116, the humidifier 118, and the cooling device 120 to the first chamber 104.

2 is a block diagram showing a schematic configuration of the thermo-hygrostat of FIG. 1.

2, the constant temperature and humidity device includes a temperature sensor 110, a humidity sensor 112, a blower 114, a heater 116, a humidifier 118, a cooling device 120, an AC power supply 202, and a rectifier. 204, an inverter controller 206, an inverter 208, a controller 210, a speed sensor 212, and the cooling device 120 includes a compressor 122, a condenser 124, an expander 126 and It includes an evaporator (128).

Hereinafter, for convenience of description, a description will be given focusing on configurations not described in FIG. 1. The rectifier 204 rectifies the alternating current (AC) received from the alternating current power source 202 into direct current (DC). The DC power rectified by the rectifier 204 is used as power to drive the internal components of the thermo-hygrostat.

The controller 210 controls the operation of the heater 116, the humidifier 118, the cooling device 120, and the blower 114 based on values measured by the temperature sensor 110 and the humidity sensor 112.

The inverter controller 206 controls the operation of the inverter 208 under the control of the controller 210. The inverter 208 controls the speed of the drive motor of the compressor 122 provided in the cooling device 120. The speed sensor 212 measures the speed of the drive motor of the compressor 122.

In one embodiment, the controller 210 controls the inverter controller 206 based on the values measured by the temperature sensor 110 and the humidity sensor 112 and the speed of the driving motor measured by the speed sensor 212, The inverter controller 206 can control the operation of the inverter 208.

3 is a diagram illustrating a process of controlling a temperature in a chamber using a cooling device to which an inverter is applied.

Referring to FIG. 3, the inverter 208 controls the speed of the driving motor of the compressor 122 to continuously operate the compressor 122 until the temperature in the chamber reaches the _target temperature T _target . In one embodiment, the drive motor may be configured as a BLDC motor.

The method of controlling the temperature in the chamber while using the inverter 208 to control the operating speed of the compressor 122 can increase energy efficiency of the thermo-hygrostat by reducing energy waste compared to a method not using the inverter 208 . As the inverter 208 modifies the operating speed of the compressor 122 so that the temperature in the chamber approaches the _target temperature T _target as shown in FIG. 3, less energy is consumed as the temperature in the chamber approaches the _target temperature T _target do.

When the inverter 208 is not used, the thermo-hygrostat lowers the temperature of the chamber by driving the cooling device 120 when the temperature in the chamber reaches the upper limit temperature (T2), and the temperature in the chamber reaches the lower limit temperature (T1). When it reaches, the operation of the cooling device 120 is stopped. When the temperature in the chamber reaches the lower limit temperature T1, the thermo-hygrostat drives the heater 116 so that the temperature in the chamber reaches the _target temperature T _target . A target temperature (T _target) since the inverter 208 if it is not user-based cooling device 120 according to the set upper limit temperature (T2) and a lower limit temperature (T1) and the heater 116 is on / off as the Consistently consumes the same driving energy regardless of proximity. As the capacity of the cooling device 120 increases, the difference in energy efficiency between the use of the inverter 208 and the case of not using the inverter 208 may increase.

In addition, in the case of controlling the operating speed of the compressor 122 through the inverter 208, as the temperature in the chamber approaches the _target temperature T _target , the speed of the compressor 122 driving motor can be driven with a smaller load. Noise that may occur due to the operation of the drive motor can be reduced. When the inverter 208 is not used, the cooling device 120 and the heater 116 are turned on/off regardless of whether the _target temperature T _target is close to each other, so the drive motor of the compressor 122 continuously operates with the same load. It is driven and the noise is continuously generated. As the capacity of the cooling device 120 increases, the load of the driving motor of the compressor 122 increases, and thus the difference in noise between the inverter 208 and not in use may increase.

4 is a configuration diagram showing another embodiment of the cooling device of FIG. 1.

The larger the space or chamber to maintain the constant temperature and humidity, the larger the capacity of the cooling device of the constant temperature and humidity system. In addition, as the capacity of the cooling device increases, the thermo-hygrostat can have rapid temperature and humidity control capabilities. In the case of a thermo-hygrostat, as the capacity of the cooling device increases, the compressor capacity increases proportionally, and thus the capacity of the heater must increase proportionally. 4 is a block diagram showing an embodiment of a cooling device with increased capacity.

4, the cooling device 120 includes a compressor 410, a first valve 420, a first condenser 430, a second condenser 440, a second valve 450, an expander 460, and It includes an evaporator 470. Hereinafter, for convenience of explanation, a description will be made focusing on a configuration different from that of the cooling device 120 described in FIG. 1.

The refrigerant compressed by the compressor 410 is branched through the first valve 420 and flows to the first condenser 430 and the second condenser 440. In an embodiment, the controller 120 may control the first valve 420 according to the amount of refrigerant introduced from the compressor 410 to flow the refrigerant to the first condenser 430 and the second condenser 440. . For example, when the refrigerant introduced from the compressor 410 is less than a preset amount, the controller 120 flows the refrigerant to the first condenser 430, and when a refrigerant exceeding the preset amount is introduced, the controller 120 May flow the refrigerant introduced beyond the set amount to the second condenser 440. Alternatively, the controller 120 controls the first valve 420 to flow the refrigerant into the first condenser 430, but when the flow rate of the refrigerant exceeds a preset value, the first condenser 430 and the second condenser ( Refrigerant may be flowed to 440 at the same time.

In another embodiment, the controller 120 may control the first valve 420 according to the flow rate of the refrigerant introduced from the compressor 410 to flow the refrigerant to the first condenser 430 and the second condenser 440. . For example, when the refrigerant is introduced at a flow rate that is slower than a preset speed, the controller 120 flows the refrigerant to the first condenser 430, and when the refrigerant flows at a flow rate faster than a preset speed, the controller 120 is May be distributed to the first condenser 430 and the second condenser 440 to flow.

The second valve 450 merges the refrigerant condensed in the first condenser 430 and the second condenser 440 and flows it to the expander 460. The second valve 450 may flow refrigerant from the first condenser 430 and the second condenser 440 according to control by the controller 120.

When the refrigerant is condensed using the first condenser 430 and the second condenser 440 as described above, the capacity of the condenser may be increased, and as a result, the capacity of the cooling device 120 may be increased. In addition, energy unnecessarily consumed by the cooling device 120 may be reduced by selectively driving the first condenser 430 and the second condenser 440 according to circumstances.

5 is a block diagram showing another embodiment of the cooling device of FIG. 1.

5 is an example of a case in which the cooling device 120 is configured by connecting a plurality of (n>2) cooling devices in parallel. Referring to FIG. 5, the cooling device 120 includes a first cooling device and a second cooling device, and the first cooling device is a first compressor 510, a first condenser 512, and a first expander 514. , And a first evaporator 516. The second cooling device includes a second compressor 520, a second condenser 522, a second expander 524, and a second evaporator 526. Hereinafter, for convenience of explanation, a description will be made focusing on a configuration different from that of the cooling device 120 described in FIG. 1.

The cooling device 120 includes a first cooling device and a second cooling device, and the controller 120 may simultaneously drive or selectively drive the first cooling device and the second cooling device depending on the situation. For example, when the current temperature in the first chamber is higher than a predetermined value or higher than the _target temperature (T _target ), or when the temperature in the first chamber is set to rapidly decrease, the controller 120 may be configured with a first cooling device and a second cooling device. Can be driven simultaneously.

When the first cooling device and the second cooling device are provided as described above, the capacity of the cooling device 120 can be increased. In addition, energy unnecessarily consumed by the cooling device 120 may be reduced by selectively driving the first cooling device and the second cooling device according to the situation.

6 is a block diagram showing a schematic configuration of an evaporator.

Referring to FIG. 6, the evaporator 128 includes a refrigerant pipe 610 and a heat exchange fin 620. The refrigerant pipe 610 flows a low-pressure phase change refrigerant. A low-pressure liquid refrigerant flows into the refrigerant pipe 610 of the evaporator 128, and the refrigerant that has been converted into a gaseous state by absorbing heat through heat exchange flows out. The heat exchange fins 620 are physically connected to the refrigerant pipe 610 and allow the refrigerant flowing through the refrigerant pipe 610 to exchange heat with the surrounding air easily. In one embodiment, the heat exchange fins 620 may be formed of a conductor plate having high thermal conductivity.

7 is a block diagram showing a schematic configuration of a thermo-hygrostat according to another embodiment of the present invention, and FIG. 8 is a block diagram showing a schematic configuration of the thermo-hygrostat of FIG. 7.

Referring to FIG. 7, the thermo-hygrostat 700 includes a first chamber 704, a separation wall 706, a second chamber 708, a temperature sensor 710, a humidity sensor 712, and an atmospheric pressure sensor. 714, a blower 716, a heater 718, a humidifier 720 and a cooling device 722, and the cooling device 722 is a compressor 724, a condenser 726, an expander 728, an evaporator 730, an evaporator temperature sensor 732, a heating pipe 734, and a third valve 736.

8, the constant temperature and humidity device includes a temperature sensor 710, a humidity sensor 712, an atmospheric pressure sensor 714, a blower 116, a heater 718, a humidifier 720, a cooling device 722, and an AC The power supply 802, the rectifier 804, the inverter controller 806, the inverter 808, the controller 910, and a speed sensor 812, the cooling device 722 is a compressor 724, a condenser 726 , An expander 728, an evaporator 730, an evaporator temperature sensor 732, a heating pipe 734, and a third valve 736.

Hereinafter, for convenience of explanation, a description will be made focusing on a configuration different from that of the thermo-hygrostat 100 of FIGS. 1 and 2.

The atmospheric pressure sensor 714 measures the atmospheric pressure in the first chamber 704. The measured air pressure can be used to calculate a freezing point temperature in the first chamber 704.

In one embodiment, the third valve 736 branches the high-temperature refrigerant compressed through the compressor 724 under control of the controller 810 and flows it into the heating pipe 734. The heating pipe 734 heats the evaporator 730 by flowing the high-temperature refrigerant introduced through the third valve 736. For example, when ice (or frost) occurs in the evaporator 730, the controller 810 heats the evaporator 730 by flowing a high-temperature refrigerant through the heating pipe 734 and performs the ice removal operation of the evaporator 730. Can be done.

When the constant temperature and humidity device 700 maintains the low temperature operation mode below the freezing point for a long period, the temperature in the first chamber 704 may decrease below the freezing point, and ice may be generated in the evaporator 730 when moisture is supplied. have. Ice generated in the evaporator 730 may lower the cooling efficiency of the cooling device 722 and, as a result, the energy efficiency of the thermo-hygrostat 700 may be lowered.

Hereinafter, a process in which the thermo-hygrostat 700 performs an ice removal operation of the evaporator 730 will be described in detail.

The controller 810 measures the surface temperature of the evaporator 730 through the evaporator temperature sensor 732 and monitors whether the following Equation 1 is satisfied.

[Equation 1]

Here, T _current,eva represents the evaporator surface temperature measured through the evaporator temperature sensor 732, and T _f (P) represents the freezing point temperature according to the measured atmospheric pressure of the first chamber 704. P denotes the measured atmospheric pressure of the first chamber 704 measured through the atmospheric pressure sensor 714. In the case of 1 atm, the freezing point is 0 degrees, but when the air pressure in the chamber varies depending on the test environment, the freezing point temperature may also change. The freezing point according to the air pressure can be measured and stored in the past.

When the evaporator surface temperature is lower than the freezing point temperature of the first chamber 704, moisture in the first chamber 704 condenses on the surface of the evaporator 730, and ice may be generated in the evaporator 730.

When Equation 1 is satisfied, the controller 810 performs an ice removal operation of the evaporator 730 through Equation 2 below.

[Equation 2]

Here, H _current is the current humidity in the first chamber 704, H _saturated (T _current ) is the saturated humidity at the current temperature in the first chamber 704, and T _current is the current temperature in the first chamber 704. Where t _{(Tcurrent,eva ≤ Tf(P))} is a time when the evaporator surface temperature is lower than or equal to the freezing point temperature of the first chamber 704, and t _current is a current time. α represents a first correction factor, β represents a second correction factor, and I _th represents a preset threshold of an I value. The first correction factor and the second correction factor may vary depending on the implementation example. For example, the first correction coefficient and the second correction coefficient may be set in advance through specific experiments.

The controller 810 calculates an I(t) value through Equation 2, and when the I(t) value exceeds a preset threshold value I _th , performs an ice removal operation of the evaporator 730.

In one embodiment, the controller 810 controls the inverter 808 through the inverter controller 806 to lower the current temperature of the first chamber 704 by a compensation temperature (T _current -T _{lower_compensat} ), and the third valve By controlling 736, a high-temperature refrigerant flows through the heating pipe 734 for a preset time (t). The heating pipe 734 heats the evaporator 730 for a predetermined time t to perform an ice removal operation. In one embodiment, when there are a plurality of evaporators in the cooling device 722 as shown in FIG. 5, a heating pipe 734 may be provided for each evaporator to independently perform an ice removal operation on each evaporator.

In another embodiment, the controller 810 may perform an ice removal operation after the operation is terminated instead of during the operation of the thermo-hygrostat. For example, when the ice removal function is activated after the operation is terminated, the controller 810 may perform an ice removal operation after the thermo-hygrostat operation is terminated.

In one embodiment, when the operation of the thermo-hygrostat in the low-temperature mode is terminated, the controller 810 may perform an ice removal operation. For example, when Equation 1 is satisfied, the controller 810 calculates Equation 3 below until the operation is terminated.

[Equation 3]

Here, T _end represents the time at which the operation of the thermo-hygrostat is ended.

When the operation of the constant temperature and humidity device is terminated, the controller 810 performs the ice removal operation of the evaporator 730 for the time calculated by Equation 4 below based on the I(t) value calculated through Equation 3 do.

[Equation 4]

Here, γ represents a third correction factor, and the third correction factor may be set in advance through a specific experiment. []intger represents the function that calculates the largest integer.

The controller 810 controls the third valve 736 to flow high-temperature refrigerant through the heating pipe 734 to perform an ice removal operation. In one embodiment, when there are a plurality of evaporators in the cooling device 722 as shown in FIG. 5, a heating pipe 734 may be provided for each evaporator to independently perform an ice removal operation on each evaporator.

9 is a flowchart illustrating a control method of a thermo-hygrostat according to an embodiment of the present invention.

Referring to FIG. 9, the temperature sensor 710 measures the temperature in the first chamber 704 (step S910), and the humidity sensor 712 measures the humidity in the first chamber 704 (step S920). The atmospheric pressure sensor 714 measures the atmospheric pressure in the first chamber 704 (step S930), and the evaporator temperature sensor 732 measures the surface temperature of the evaporator 730 (step S940).

The controller 810 performs an ice removal operation of the evaporator 730 based on the measured temperature, humidity, air pressure, and surface temperature of the evaporator in the first chamber (step S950).

The controller 810 measures the surface temperature of the evaporator 730 through the evaporator temperature sensor 732 and monitors whether the following Equation 1 is satisfied.

[Equation 1]

When Equation 1 is satisfied, the controller 810 performs an ice removal operation of the evaporator 730 through Equation 2 below.

[Equation 2]

The controller 810 calculates an I(t) value through Equation 2, and when the I(t) value exceeds a preset threshold value I _th , performs an ice removal operation of the evaporator 730.

In one embodiment, the controller 810 controls the inverter 808 through the inverter controller 806 to lower the current temperature of the first chamber 704 by a compensation temperature (T _current -T _{lower_compensat} ), and the third valve By controlling 736, a high-temperature refrigerant flows through the heating pipe 734 for a preset time (t). The heating pipe 734 heats the evaporator 730 for a predetermined time t to perform an ice removal operation.

In another embodiment, the controller 810 may perform an ice removal operation after the operation is terminated instead of during the operation of the thermo-hygrostat. For example, when the ice removal function is activated after the operation is terminated, the controller 810 may perform an ice removal operation after the thermo-hygrostat operation is terminated.

For example, when Equation 1 is satisfied, the controller 810 calculates Equation 3 until the operation is terminated. When the operation of the constant temperature and humidity device is terminated, the controller 810 performs the ice removal operation of the evaporator 730 for the time calculated by Equation 4 based on the I(t) value calculated through Equation 3 can do.

The control power supply method using the hybrid control power supply device described with reference to FIG. 9 may also be implemented in the form of a recording medium including instructions executable by a computer such as an application or module executed by a computer.

Computer-readable media can be any available media that can be accessed by a computer, and includes both volatile and nonvolatile media, removable and non-removable media. Further, the computer-readable medium may include both computer storage media and communication media. Computer storage media includes both volatile and nonvolatile, removable and non-removable media implemented in any method or technology for storage of information such as computer readable instructions, data structures, modules or other data. Communication media typically includes computer readable instructions, data structures, program modules, or other data in a modulated data signal such as a carrier wave, or other transmission mechanism, and includes any information delivery medium.

The term module may mean hardware capable of performing functions and operations according to the respective names described in the specification, and may also mean computer program code capable of performing specific functions and operations, In addition, it may refer to an electronic recording medium, such as a processor, on which a computer program code capable of performing a specific function and operation is mounted.

Although described above as an embodiment of the present invention, the technical idea of the present invention is not limited to the above embodiment, and a hybrid control power supply device using various spatial recognition and control power supply using the same within the scope not departing from the technical idea of the present invention It can be implemented in this way

100: constant temperature and humidity device
104: first chamber
106: separation wall
108: second chamber
110:, temperature sensor
112: humidity sensor
114: blower
116: heater
118: humidifier
120: cooling device

Claims (14)

A first chamber maintaining a constant temperature and humidity state;
A temperature sensor measuring a temperature in the first chamber;
A humidity sensor measuring humidity in the first chamber;
A heater for increasing the temperature of the surrounding air by generating heat according to the control;
A humidifier for increasing the humidity of the surrounding air by generating moisture under control;
A cooling device that absorbs heat according to control to adjust the temperature and humidity of the surrounding air;
A blower for moving air whose temperature and humidity are controlled by the heater, humidifier, or cooling device to the first chamber;
A second chamber in which the heater, humidifier, cooling device, and blower are located; And
Thermo-hygrostat including a controller for controlling the operation of the heater, humidifier, cooling device, and blower based on values measured by the temperature sensor and the humidity sensor. The method of claim 1, wherein the cooling device
A compressor for compressing a phase change refrigerant;
A condenser for exchanging heat and liquefying the refrigerant compressed through the compressor;
An expander for expanding the liquefied refrigerant through the condenser; And
Thermo-hygrostat including an evaporator that heats and vaporizes the refrigerant expanded through the expander. The method of claim 2, wherein the constant temperature and humidity device
An inverter controlling the speed of the driving motor of the compressor;
An inverter controller controlling the operation of the inverter; And
Further comprising a speed sensor for measuring the speed of the drive motor of the compressor,
The controller controls the inverter controller based on values measured by the temperature sensor and humidity sensor and the speed of the driving motor measured by the speed sensor. The method of claim 2, wherein the constant temperature and humidity device
An atmospheric pressure sensor measuring the atmospheric pressure in the first chamber;
A first valve branching and flowing the refrigerant compressed through the compressor according to control; And
A thermo-hygrostat, further comprising a heating pipe for heating the evaporator by flowing a high-temperature refrigerant introduced through the first valve. The method of claim 4, wherein the constant temperature and humidity device
Thermo-hygrostat further comprising an evaporator temperature sensor measuring the surface temperature of the evaporator. The method of claim 5,
When the controller satisfies the following Equation 1, the constant temperature and humidity device performs an ice removal operation of the evaporator through Equation 2 below.
[Equation 1]

Here, T _current,eva is the evaporator surface temperature measured by the evaporator temperature sensor, T _f (P) is the freezing point temperature according to the measured atmospheric pressure of the first chamber, and P is the measurement of the first chamber measured by the barometric pressure sensor. atmospheric pressure
[Equation 2]

Here, H _current is the current humidity in the first chamber, H _saturated (T _current ) is the saturated humidity at the current temperature in the first chamber, T _current is the current temperature in the first chamber, t _{(Tcurrent,eva ≤ Tf(P ))} is the time when the evaporator surface temperature is lower than the freezing point temperature of the first chamber, t _current is the current time, α is the first correction factor, β is the second correction factor, and I _th is the preset threshold of the I value. The method of claim 6,
When the controller satisfies Equation 2,
By controlling the inverter through the inverter controller to lower the current temperature of the first chamber by a compensation temperature,
A thermo-hygrostat for removing ice by controlling the first valve to flow the high-temperature refrigerant through the heating pipe for a predetermined time. The method of claim 5,
When the controller satisfies Equation 1, the controller calculates Equation 3 below and performs an ice removal operation of the evaporator when the constant temperature and humidity mode operation is terminated.
[Equation 3]

Here, T _end is the time when the operation of the thermo-hygrostat is terminated. The method of claim 8,
The controller controls the first valve for a time calculated by the following equation (4) to flow the high-temperature refrigerant through the heating pipe to perform an ice removal operation.
[Equation 4]

Where γ is the third correction factor The method of claim 1, wherein the cooling device
A compressor for compressing a phase change refrigerant;
A second valve branching and flowing the refrigerant compressed through the compressor;
A first condenser for liquefying the refrigerant introduced through the first valve by heat exchange;
A second condenser that heat-exchanges the refrigerant introduced through the first valve to liquefy;
A third valve that merges and flows the liquefied refrigerant through the first condenser and the second condenser;
An expander that expands the refrigerant introduced through the second valve; And
Thermo-hygrostat including an evaporator that heats and vaporizes the refrigerant expanded through the expander. The method of claim 10,
The second valve flows the refrigerant to the first condenser, and when the flow rate of the refrigerant exceeds a preset value, the second valve simultaneously flows the refrigerant to the first condenser and the second condenser. In the thermo-hygrostat control method using the thermo-hygrostat,
A temperature sensor measuring a temperature in the first chamber;
A humidity sensor measuring humidity in the first chamber;
An atmospheric pressure sensor measuring the atmospheric pressure in the first chamber;
Measuring, by the evaporator temperature sensor, a surface temperature of the evaporator; And
And performing an ice removal operation of the evaporator based on the measured temperature, humidity, atmospheric pressure, and surface temperature of the evaporator in the first chamber. The method of claim 12, wherein performing the ice removal operation of the evaporator
When the following Equation 1 is satisfied, the controller performs an ice removal operation of the evaporator through Equation 2 below. The method of claim 13, wherein performing the ice removal operation of the evaporator
When the equation (2) is satisfied, the controller controlling the inverter through the inverter controller to lower the current temperature of the first chamber by a compensation temperature; And
And performing an ice removal operation by controlling the first valve by the controller to flow the high-temperature refrigerant through the heating pipe for a predetermined time.

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