JP2011208891A - Precision air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a precision air conditioner capable of providing precision air at an adjusted temperature and humidity, and reducing power consumption.SOLUTION: The precision air conditioner includes a first path 10 with a first condenser 11 and a first evaporator 13 composing a cooler 13A disposed in a serial loop, a second path 20 with a second condenser 21 and a second evaporator 23 disposed in parallel with the first condenser 11 and the first evaporator 13, a third path 30 disposed in parallel with the first condenser 11, first, second and third flow control valves V1-V3 disposed in the first, second and third paths 10-30, and a control means 50 for controlling a flow rate of a refrigerant to be introduced into the first evaporator 13 and first and second condensers 21, 31 through the flow control valves V1-V3 so as to obtain air at a predetermined temperature and humidity.

Description

  The present invention relates to a precision air conditioner mainly used for industrial use.

Conventionally, an air conditioner that performs dehumidification only by a refrigeration cycle is known (see Patent Document 1).
However, in the case of this type of air conditioner, if the set temperature of the evaporator is lowered in order to increase the dehumidifying capacity, the evaporator is frozen and the dehumidifying capacity is significantly reduced. For this reason, the temperature of the evaporator cannot be lowered, and the dehumidifying ability cannot be further improved.

  Then, the precision air conditioner which can improve a dehumidification capability, without freezing an evaporator is proposed (patent document 2). The precision air conditioner dehumidifies the air blown by the fan after being cooled by the evaporator and then heated to a predetermined temperature by the heater.

  On the other hand, a precision air conditioner that supplies desired humidified air has been proposed (see Patent Document 3). Such a precision air conditioner obtains humidified air by evaporating water using a heater.

JP-A-5-99514 (abstract) JP2009-198050 (abstract) JP-A-5-223296 (abstract)

  However, since the conventional apparatus uses a heater for dehumidification and humidification, power consumption increases. Also from the ecological point of view, it is important to reduce power consumption.

  Therefore, an object of the present invention is to provide a precision air conditioner that can obtain precision air with adjusted temperature and humidity and that consumes less power.

  In order to achieve the above object, a precision air conditioner according to an aspect of the present invention includes a cooler 13A that cools the taken-in air A0 and a preheater for humidifying the air A1 that is cooled by the cooler 13A. 1 heater 21 </ b> A, a humidifier 1 that retains moisture and humidifies the air A <b> 2 so that the heated air A <b> 2 passes through a predetermined first humidity, and the humidified air The second heater 31A for heating the air A3 to obtain the air A4 having a predetermined temperature and the second humidity, and the air in the order of the cooler 13A, the first heater 21A, the humidifier 1 and the second heater 31A. In a precision air conditioner including a fan F that sends air A1 to A4 so as to pass through, a compressor CP that pumps refrigerant to the cooler 13A, the first and second heaters 21A, 31A, and the compressor CP Pumped from A first condenser 11 that condenses the refrigerant to cool it by heat exchange and a first evaporator 13 that constitutes the cooler 13A that cools the surrounding air A0 with the refrigerant from the first condenser 11 are connected in series. The first path 10 disposed in the loop, the second condenser 21 that condenses the refrigerant pumped from the compressor CP and constitutes the first heater 21A, and heats the refrigerant from the second condenser 21. The second evaporator 23 for raising the temperature by replacement is arranged in parallel with the first condenser 11 and the first evaporator 13, and the refrigerant pumped from the compressor CP is condensed. In order to pump the refrigerant from the third condenser 31 constituting the second heater 31A to the first evaporator 13, the third condenser 31 is in series with the first evaporator 13, and Arranged in parallel to the first condenser 11 Three paths 30, first, second and third flow control valves V1 to V3 arranged in the first, second and third paths 10 to 30, and air A4 having the predetermined temperature and second humidity. Control means 50 for controlling the flow rate of the refrigerant introduced into the first evaporator 13, the second and third condensers 21 and 31 by the flow rate control valves V 1 to V 3 is obtained.

Here, in the present invention, the principle of obtaining precise air with desired temperature and humidity will be briefly described.
First, when the target temperature and target humidity of the air A4 to be supplied are set, the amount of moisture per unit volume contained in the air A4 is known. On the other hand, the amount of heat to be cooled by the cooler and the amount of heat to be heated by the first and second heaters are known from the suction temperature and the temperature of the target temperature.
An air conditioner using such a principle is well known, and the detailed principle is disclosed in Japanese Patent Laid-Open No. 7-174360.

According to the present invention, since heating for humidification is performed by the first heater before humidification by the humidifier, the moisture content of the air that has passed through the humidifier can be set to a desired moisture content. Then, since it heats with a 2nd heater, the air of desired temperature and humidity is obtained.
Here, since the first and second heaters are not electric heaters but are each constituted by a condenser, the exhaust heat of energy generated by the compressor can be used. Consumption can be as high as 30% of the conventional one.
In addition, only the humidification can be controlled by using only the second path 20.
Furthermore, by using (operating) only the third path 30, it is possible to perform full heating while performing full dehumidification.
Therefore, the control range temperature and humidity can be dramatically expanded.

FIG. 1 is a schematic configuration diagram showing a precision air conditioner according to an embodiment of the present invention. It is a schematic block diagram which shows the 1st cycle of the same precision air conditioner. It is a schematic block diagram which shows the 2nd cycle of the precision air conditioner. It is a schematic block diagram which shows the 3rd cycle of the precision air conditioner. It is a schematic perspective view which shows a humidifier and a water supply nozzle. It is a schematic block diagram which shows the operation example of a precision air conditioner. It is a schematic block diagram which shows the operation example of a precision air conditioner. It is a schematic block diagram which shows the operation example of a precision air conditioner. It is a schematic block diagram which shows the operation example of a precision air conditioner. It is a schematic block diagram which shows the operation example of a precision air conditioner. It is a schematic block diagram which shows the operation example of a precision air conditioner.

  In a preferred aspect of the present invention, the water supply nozzle 1n for supplying water to the humidifier 1 by dropping or flowing down, and a water control valve WV for controlling the amount of water supplied from the water supply nozzle 1n are further provided. When the opening degree of the second flow rate control valve V2 that controls the flow rate of the refrigerant introduced into the second condenser 21 that is the first heater 21A is increased, the opening degree of the water control valve WV increases. And when the opening degree of the said 2nd flow control valve V2 is made small, the said control means 50 performs control so that the opening degree of the said water control valve WV becomes small.

  According to this aspect, the amount of water necessary for humidification is supplied to the humidifier, so that the supply of water to the humidifier can be minimized, and the drainage equipment can also be miniaturized.

In a preferred aspect of the present invention, the second heat exchanger 42 that raises the temperature of the refrigerant in the second evaporator 23 raises the temperature of the cold refrigerant in the second evaporator 23 with water.
According to this aspect, the temperature of cooling water falls by introduce | transducing the industrial water as cooling water of a factory in the 2nd heat exchanger 42, and the energy which cools the cooling water of a factory is reduced.

In a preferred aspect of the present invention, the first heat exchanger 41 that cools the refrigerant in the first condenser 11 has a first water passage W1 through which water for cooling the heated refrigerant in the first condenser 11 flows. The first water passage W1 is disposed upstream of the second water passage W2 through which the water flows in the second heat exchanger 42 that raises the temperature of the refrigerant in the second evaporator 23.
According to this aspect, the first heat exchanger is water-cooled, and the temperature of the water increases here. As a result, the temperature of the water introduced into the second water channel of the second heat exchanger at the subsequent stage becomes high, so that the refrigerant in the second evaporator of the second heat exchanger is efficiently heated.

  According to a preferred aspect of the present invention, the first expansion valve means 12 comprising an electronic expansion valve is provided downstream of the first and third condensers 11 and 31 and upstream of the first evaporator 13. The second expansion valve means 22 is disposed downstream of the second condenser 21 and upstream of the second evaporator 23.

  In a preferred embodiment of the present invention, the amount of water per unit contained in the air A4 to be supplied is determined from the target temperature and target humidity of the air A4 to be supplied, and the predetermined first humidity ( A calculation unit 51 for obtaining a primary temperature of the air A2 humidified to a substantially constant relative humidity) and obtaining a primary humidity of the air A2 humidified to the predetermined first humidity by the humidifier 1 from the moisture amount; The first to third flow control valves so that the air A2 passing through the first heater 21A approaches the primary temperature and the air A4 heated by the second heater 31A approaches the target temperature. The control means 50 includes a control unit 52 that controls the flow rate of the refrigerant flowing through the cooler 13A and the first and second heaters 21A and 31A by controlling V1 to V3.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
overall structure:
As shown in FIG. 1, this precision air conditioner includes a humidifier 1, a first condenser 11, a first evaporator 13, a second condenser 21, a second evaporator 23, a third condenser 31, and a check valve. 61, fan F, compressor CP, and a number of pipes.
A first flow rate control valve V1, a second flow rate control valve V2, and a third flow rate control valve V3 are provided upstream of the first evaporator 13, the second condenser 21, and the third condenser 31, respectively. .
A first expansion valve means 12 comprising an electronic expansion valve is provided downstream of the first and third condensers 11 and 31 and upstream of the first evaporator 13.
Downstream of the second condenser 21 and upstream of the second evaporator 23, for example, second expansion valve means 22 composed of an electronic expansion valve is provided.

Circulation cycle:
First, the refrigerant circulation cycle and the air flow will be described. This system has the following three types of refrigerant circulation cycles. The following circulation cycles are used in combination as will be described later.

In the schematic configuration diagram of the precision air conditioner shown below, the thick line indicates the circulation path through which the refrigerant passes, and the closed states of the flow control valves V1 to V3 are shown by filling the valve symbols.
Moreover, in the following description and FIGS. 2-11, description and illustration about the hot gas bypass HG for preventing freezing of the 1st evaporator 13 are abbreviate | omitted for easy understanding.

First cycle:
As shown in FIG. 2, in the first cycle, the first flow control valve V1 is opened, and the second flow control valve V2 and the third flow control valve V3 are closed.
As shown by the thick line in FIG. 2, the compressor CP circulates the refrigerant in the order of the first condenser 11, the first expansion valve means 12, the first evaporator 13, and the first path 10.
A check valve 61 is provided between the first expansion valve means 12 and the first evaporator 13. An accumulator 63 is provided downstream of the compressor CP.

  The vaporized refrigerant pumped from the compressor CP is gradually liquefied in the first condenser 11 and the first expansion valve means 12. At this time, the refrigerant is condensed in the first condenser 11 upstream of the first expansion valve means 12. Thereafter, the refrigerant exits from the first expansion valve means 12, becomes a low pressure in a relatively thick pipe in the first evaporator 13, and vaporizes again, thereby taking away the heat around the first evaporator 13. 1 The ambient temperature of the evaporator 13 is lowered.

First heat exchanger 41:
The first heat exchanger 41 has a first water channel W1. For example, factory water flows through the first water channel W1. In the first heat exchanger 41, the hot refrigerant in the first condenser 11 is cooled by the water flowing through the first water channel W1. The water flowing through the first water channel W1 is heated by heat exchange with the refrigerant in the first condenser 11 and introduced into the downstream second water channel W2.

Air flow in the first cycle:
Air A0 sucked by the fan F is introduced into the first evaporator 13. As described above, the first evaporator 13 takes away the ambient heat and lowers the ambient temperature due to the vaporization of the refrigerant in the first evaporator 13. Therefore, the air A0 introduced into the first evaporator 13 is cooled by passing through the first evaporator 13. Accordingly, the first evaporator 13 constitutes a cooler 13A for cooling the air A0.
The air A1 cooled through the cooler 13A is discharged downstream.

Second cycle:
As shown in FIG. 3, in the second cycle, the second flow rate control valve V2 is opened, and the first flow rate control valve V1 and the third flow rate control valve V3 are closed.
As shown by the thick line in FIG. 3, the compressor CP circulates the refrigerant in the order of the second path 20, the second condenser 21, the second expansion valve means 22, and the second evaporator 23.

  The vaporized refrigerant pumped from the compressor CP is sent to the second condenser 21 and the second expansion valve means 22 via the second path 20, and gradually in the second condenser 21 and the second expansion valve means 22. Liquefied. The refrigerant is condensed in the second condenser 21 upstream of the second expansion valve means 22. Thereafter, the refrigerant exits from the second expansion valve means 22, becomes a low pressure in the relatively thick pipe of the second evaporator 23, and vaporizes again, thereby taking away the heat around the second evaporator 23, and the second The ambient temperature of the evaporator 23 is lowered.

Second heat exchanger 42:
The second heat exchanger 42 has the second water channel W2. In the second heat exchanger 42, the cold refrigerant in the second evaporator 23 is warmed by the water flowing through the second water passage W2 introduced from the first water passage W1.
Here, since the refrigerant in the second evaporator 23 has a very low temperature, if the water flowing through the second water channel W2 is 5 ° C. or higher, heat is exchanged to warm the refrigerant in the second evaporator 23. It is done.
As described above, in the first heat exchanger 41, the water flowing through the first water channel W1 is warmed by heat exchange with the hot refrigerant in the first condenser 11, so that the second evaporator is more effectively performed. The refrigerant in 23 can be warmed.
Industrial water is mainly used as the water in the second water channel W2.

Humidifier 1:
As shown in FIG. 5, the humidifier 1 is formed by laminating materials having water absorption. The humidifier 1 is made of a hydrophilic polymer fiber made of, for example, a polyester material, and includes the above-described mixed material 1D as a material having a certain degree of hardness and high water absorption. The shape of the mixed material 1D is a structure in which slate is laminated, and efficient vaporization is realized by a certain degree of ventilation resistance so that the relative humidity becomes constant regardless of the temperature of the supply air.
In addition, as the humidifier 1, for example, a dripping pervaporation type humidifier manufactured by Wetmaster Co. can be employed.

A large number of water supply nozzles 1n for dropping water are provided on the upper portion of the humidifier 1, and the amount of water dripping from the water supply nozzle 1n is determined by opening and closing a water control valve WV including a proportional control electromagnetic valve, for example. Be controlled.
The water control valve WV is linked to the second flow control valve V2, and is set so that the opening of the water control valve WV changes according to the opening of the second flow control valve V2.
When the mixed material 1D is wet with water dropped from the water supply nozzle 1n and the air A2 is introduced into the humidifier 1 by the fan F (FIG. 3), the wet state in the humidifier 1 When the air A2 passes between the mixed materials 1D, the air A2 is humidified, and is exhausted from the humidifier 1 as the humidified air A3 as indicated by the halftone dots.

Air flow in the second cycle:
As shown in FIG. 3, the air A <b> 1 that has passed through the cooler 13 </ b> A (first evaporator 13) is introduced into the second heater 21 by the fan F. As described above, the refrigerant in the second condenser 21 is heated by the compressor. Therefore, the air A <b> 1 introduced into the second condenser 21 is heated by passing through the second condenser 21. Accordingly, the second condenser 21 constitutes a first heater 21A for heating the air A1.
On the other hand, the humidifier 1 is in a wet state by the water dropped from the water supply nozzle 1n, and the air A2 blown by the fan F is humidified by passing through the humidifier 1 to become high-humidity air A3. To be discharged.

Third cycle:
As shown in FIG. 4, in the third cycle, the third flow control valve V3 is opened, and the first flow control valve V1 and the second flow control valve V2 are closed.
As shown by the thick line in FIG. 4, the compressor CP circulates the refrigerant in the order of the third path 30, the third condenser 31, the first expansion valve means 12, the first evaporator 13, and the first path 10.

The vaporized refrigerant pumped from the compressor CP is sent to the third condenser 31 via the third path 30 and gradually liquefied in the third condenser 31 and the first expansion valve means 12. The refrigerant is condensed in the third condenser 31 upstream of the first expansion valve means 12. Thereafter, the refrigerant leaves the first expansion valve means 12 and is sent to the first evaporator 13.
As described above, the refrigerant sent to the first evaporator 13 becomes a low pressure in a relatively thick pipe in the first evaporator 13 and is vaporized again to thereby reduce the heat around the first evaporator 13. The temperature around the first evaporator 13 is lowered.

Air flow in the third cycle:
The air A0 sucked by the fan F is introduced into the cooler 13A, and the air A1 cooled by the first evaporator 13 is discharged as described above. The air A1 passes through the first heater 21A and the humidifier 1 and is introduced into the third condenser 31 as air A3.
On the other hand, the refrigerant in the third condenser 31 is heated by the compressor CP. Therefore, the air A <b> 3 introduced into the third condenser 31 is heated by passing through the third condenser 31. Therefore, the third condenser 31 constitutes a second heater 31A for heating the air A3.

Control configuration:
As shown in FIG. 1, a temperature sensor T and a humidity sensor H are provided on the downstream side of the third condenser. The temperature sensor T and the humidity sensor H are connected to the control means 50.

The control means 50 includes a calculation unit 51 and a control unit 52.
The control unit 52 controls the first, second, and third flow rate control valves V1 to V3 in accordance with inputs from the temperature sensor T and the humidity sensor H, and feedback-controls the refrigerant flow rate.

  The calculating part 51 calculates | requires the moisture content per unit (volume) contained in the air which should be supplied from the target temperature and the target humidity of the air which should be supplied input from the setting part which is not shown in figure. The calculation unit 51 obtains a primary temperature of the air humidified to a predetermined first humidity by the humidifier 1 based on the moisture amount, and further humidified to the predetermined first humidity by the humidifier 1 from the moisture amount. Find the primary humidity of the air. The calculation unit 51 causes the control unit 52 to control the first, second, and third flow control valves V1 to V3 based on the primary temperature and the primary humidity.

The control unit 52 performs first to third so that the air A2 that has passed through the first heater 21A approaches the primary temperature, and the air heated by the second heater 31A approaches the target temperature. The flow rate control valves V1 to V3 are controlled to control the flow rate of the refrigerant flowing through the cooler 13A and the first and second heaters 21A and 31A.
As described above, the opening degree of the water control valve (proportional control electromagnetic valve) WV changes according to the opening degree of the second flow control valve V2. That is, when the opening degree of the second flow rate control valve V2 increases, the opening degree of the water control valve WV increases. On the other hand, when the opening degree of the second flow rate control valve V2 decreases, the opening degree of the water control valve WV decreases.

Opening degree of each flow control valve V1-V3:
Therefore, in order to control to approach the target temperature / humidity, the opening degree of each flow control valve V1 to V3 is set as follows.
When lowering the temperature of the air A4: The opening degree of the first flow control valve V1 is increased, and the opening degree of the third flow control valve V3 is reduced.
When raising the temperature of the air A4: The opening degree of the first flow control valve V1 is reduced, and the opening degree of the third flow control valve V3 is increased.
When increasing the humidity of the air A4: Increase the opening of the second flow control valve V2.
When reducing the humidity of the air A4: The opening degree of the second flow control valve V2 is reduced.
The flow control valves V1 to V3 are controlled so as to approach a desired temperature and second humidity by adjusting the opening degree as described above.
The opening / closing control of the flow control valves V1 to V3 is performed based on the principle for obtaining the desired temperature and humidity described above.

Control method of flow control valve:
The flow control valves V1 to V3 and the water control valve WV are controlled in various ways depending on the set temperature and humidity. A typical control method will be described below.
When the precision air conditioner is started, the control unit 50 operates the compressor CP and, based on the temperature and humidity set by the operator by a setting unit (not shown), the flow control valves V1 to V1 through the control unit 52. Controls opening and closing of V3 and the water control valve WV.
In addition, the set temperature / humidity described below does not necessarily match the temperature / humidity blown out from the third condenser 31.

1. For cooling and dehumidification MAX;
For example, when the temperature and humidity sucked into the first evaporator 13 is 25 ° C./50% and the temperature and humidity blown from the third condenser 31 are set to 0 ° C./0%, the precision air conditioner is always cooled / Dehumidifying MAX. In such a case, as shown in FIG. 6, the first flow control valve V1 is opened, and the second flow control valve V2 and the third flow control valve V3 are closed. Therefore, 100% refrigerant flows through the first evaporator 13 and is neither heated nor humidified.
On the other hand, the refrigerant of the first condenser 11 pumped from the compressor CP is cooled by the water flowing through the first water passage W1 of the first heat exchanger 41.

Accordingly, the air A0 is cooled by passing through the cooler 13A, and moisture in the air A0 is condensed and dehumidified as the temperature of the air A0 decreases.
The condensed water is collected and discharged in a drain pan (not shown) provided in the lower part of the first evaporator 13.

2. For heating / dehumidifying MAX;
For example, when the temperature and humidity sucked into the first evaporator 13 is set to 25 ° C./50% and the temperature and humidity blown from the third condenser 31 are set to 40 ° C./0%, the precision air conditioner is always heated / Dehumidifying MAX. In such a case, as shown in FIG. 7, the first flow control valve V1 and the second flow control valve V2 are closed, the water control valve WV is closed, and the third flow control valve V3 is opened. Is done. Therefore, 100% of the refrigerant flows through the third condenser 31 and is heated and dehumidified (= cooled), and is not humidified.
Accordingly, the air A3 dehumidified (= cooled) by the first evaporator 13 is heated by the second heater 31A and the temperature rises, and the relative humidity of the air A3 further decreases due to the temperature rise of the air A3. . Therefore, the heated and dehumidified air A4 is discharged from the second heater 31A.
In this way, by supplying the refrigerant only to the second heater 31A and the cooler 13A of the third path 30, heating and dehumidification that could not be performed conventionally can be performed in the MAX.

3. For heating and humidification MAX;
For example, when the temperature and humidity sucked into the first evaporator 13 is 25 ° C./50% and the temperature and humidity blown out from the third condenser 31 are set to 40 ° C./60%, the precision air conditioner is always heated.・ It becomes humidification MAX. In such a case, as shown in FIG. 8, the first flow control valve V1 is closed and the second flow control valve V2 and the third flow control valve V3 are opened. Therefore, 50% of the refrigerant flows through the second path 20 and the third path 30. 50% refrigerant flows through the first evaporator 13 and is operated with a cooling capacity of 50%.

As described above, since the water control valve WV is interlocked with the second flow rate control valve V2, water is dropped from the water supply nozzle 1n to the humidifier 1.
The air A1 cooled by the cooler 13A is heated by the first heater 21A, then becomes air A3 humidified by the humidifier 1, and the air A4 heated by the second heater 31A is discharged.
On the other hand, the refrigerant pumped from the second expansion valve means 22 to the second evaporator 23 is heated by the water flowing through the second water passage W2 of the second heat exchanger 42.

  Therefore, after the air A0 becomes the air A1 cooled by the cooler 13A, it is heated by the first heater 21A and humidified by the humidifier 1. Thereafter, the air A3 humidified by the humidifier 1 is heated by the third condenser 31, and the heated and humidified air A4 is discharged.

4). When heating / humidification does not become MAX;
For example, in the case where the temperature and humidity sucked into the first evaporator 13 is 25 ° C./50%, and the temperature and humidity blown out from the third condenser 31 are set to 31 ° C./55%, as a precision air conditioner, Humidification does not become MAX.
In such a case, as shown in FIG. 9, the first flow control valve V1 is closed, and the second flow control valve V2 and the third flow control valve V3 are opened to a predetermined opening. When the second flow rate control valve V2 and the third flow rate control valve V3 are opened at a predetermined angle, 25% of the refrigerant flows into the second condenser 21 and flows into the third condenser 31 and the first evaporator 13. 75% refrigerant flows.
In the water control valve WV, water is dropped from the water supply nozzle 1n to the humidifier 1 in conjunction with the second flow rate control valve V2.
On the other hand, the refrigerant pumped from the second expansion valve means 22 to the second evaporator 23 is heated by the water flowing through the second water passage W2 of the second heat exchanger 42.

The air A1 cooled by the cooler 13A is heated by the first heater 21A, then becomes air A3 humidified by the humidifier 1, and the air A4 heated by the second heater 31A is discharged.
Therefore, 25% of the refrigerant flows through the first evaporator 13, and after the air A0 is cooled by the cooler 13A with a cooling capacity of 25%, heating and humidification are performed with the set capacity, and finally the air A4 Is operated at a temperature / humidity of about 25 ° / 55%.

5. For humidified MAX;
For example, when the temperature and humidity sucked into the first evaporator 13 are set to 25 ° C./50%, and the temperature and humidity blown from the third condenser 31 are set to 25 ° C./80%, as shown in FIG. The first flow control valve V1 and the third flow control valve V3 are closed, and the second flow control valve V2 is opened. Therefore, the refrigerant does not flow to the first evaporator 13, and the air A0 is not cooled and only humidification is performed.
On the other hand, the refrigerant pumped from the second expansion valve means 22 to the second evaporator 23 is heated by the water flowing through the second water passage W2 of the second heat exchanger 42.
Therefore, in such a case, the refrigerant is operated in the second cycle (FIG. 3) passing through the second condenser 21.
In this way, by supplying the refrigerant only to the first heater 21A and the second evaporator 23 in the second path 20, it is possible to perform the operation of the humidification MAX that could not be performed conventionally.

6). When cooling / humidification does not become MAX;
For example, in the case where the temperature and humidity sucked into the first evaporator 13 is set to 26 ° C./51% with respect to the temperature / humidity of 25 ° C./50%, the precision air conditioner is Humidification does not become MAX. In such a case, the first flow control valve V1 shown in FIG. 9 is opened, and the second flow control valve V2 and the third flow control valve V3 are closed and started. Thereafter, the opening and closing of the second and third flow rate control valves V2, V3 are controlled toward the set temperature / humidity of 26 ° C./51%.
On the other hand, the refrigerant of the first condenser 11 pumped from the compressor CP is cooled by the water flowing through the first water passage W1 of the first heat exchanger 41.

The air A1 cooled by the cooler 13A passes through the first heater 21A and the humidifier 1, and the air A4 heated by the second heater 31A is discharged.
Here, after the air A0 is cooled, it is heated and humidified with the set capacity, and finally the air A4 is operated at a temperature and humidity of about 26 ° / 51%.

  The present invention can be used for industrial precision air conditioners.

DESCRIPTION OF SYMBOLS 1: Humidifier 1n: Water supply nozzle 10: 1st path | route 11: 1st condenser 12: 1st expansion valve means 13: 1st evaporator 13A: Cooler 20: 2nd path | route 21: 2nd condenser 22: 2nd 2 expansion valve means 23: 2nd evaporator 30: 3rd path 31: 3rd condenser 31A: 2nd heater 41: 1st heat exchanger 50: control means 51: calculating part 52: control part A0-A4: Air CP: Compressor F: Fan V1: First flow control valve V2: Second flow control valve V3: Third flow control valve W1: First water channel W2: Second water channel WV: Water control valve (proportional control solenoid valve)

Claims (5)

A cooler 13A for cooling the taken-in air A0;
A first heater 21A for preheating to humidify the air A1 cooled by the cooler 13A;
A humidifier 1 that retains moisture and humidifies the air A2 so that the heated air A2 passes through the air A2 having a predetermined first humidity;
A second heater 31A for heating the humidified air A3 to obtain air A4 having a predetermined temperature and a second humidity;
In a precision air conditioner comprising a fan F that sends air A1 to A4 so that the air passes in the order of the cooler 13A, the first heater 21A, the humidifier 1 and the second heater 31A,
A compressor CP for pumping refrigerant to the cooler 13A, the first and second heaters 21A, 31A;
The 1st condenser 11 which condenses in order to cool the refrigerant | coolant pumped from the said compressor CP by heat exchange, and the said cooler 13A which cools the surrounding air A0 with the refrigerant | coolant from the said 1st condenser 11 are comprised. A first path 10 for arranging the first evaporator 13 in a series loop;
A second condenser 21 that condenses the refrigerant pumped from the compressor CP and constitutes the first heater 21A, and a second evaporator for raising the temperature of the refrigerant from the second condenser 21 by heat exchange. 23 in parallel with the first condenser 11 and the first evaporator 13;
In order to condense the refrigerant pumped from the compressor CP and pump the refrigerant from the third condenser 31 constituting the second heater 31A to the first evaporator 13, the third condenser 31 is A third path 30 arranged in series with the first evaporator 13 and in parallel with the first condenser 11;
First, second and third flow control valves V1 to V3 disposed in the first, second and third paths 10 to 30, respectively;
The flow rate of the refrigerant introduced into the first evaporator 13, the second and third condensers 21, 31 is controlled by the flow rate control valves V1 to V3 so that the air A4 having the predetermined temperature and the second humidity is obtained. A precision air conditioner provided with a control means 50. The water supply nozzle 1n according to claim 1, wherein water is supplied to the humidifier 1 by dropping or flowing down.
A water control valve WV for controlling the amount of water supplied from the water supply nozzle 1n;
When the opening degree of the second flow rate control valve V2 that controls the flow rate of the refrigerant introduced into the second condenser 21 that is the first heater 21A is increased, the opening degree of the water control valve WV increases. And the precision air conditioner which the said control means 50 performs control so that the opening degree of the said water control valve WV may become small when reducing the opening degree of the said 2nd flow control valve V2.   The precision air conditioner according to claim 2, wherein the second heat exchanger (42) for raising the temperature of the refrigerant in the second evaporator (23) raises the temperature of the cold refrigerant in the second evaporator (23) with water.   In Claim 3, the 1st heat exchanger 41 which cools the refrigerant | coolant in the said 1st condenser 11 has the 1st water path W1 through which the water which cools the temperature-warmed refrigerant | coolant in the said 1st condenser 11 flows. The precision air conditioner in which the first water channel W1 is disposed upstream of the second water channel W2 through which the water flows in the second heat exchanger 42 that raises the temperature of the refrigerant in the second evaporator 23.   The first expansion valve means 12 comprising an electronic expansion valve is provided downstream of the first and third condensers 11 and 31 and upstream of the first evaporator 13 according to claim 4, wherein the first 2 A precision air conditioner in which a second expansion valve means 22 is arranged downstream of the condenser 21 and upstream of the second evaporator 23.

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