HK1167840B - Dehumidification device and method for controlling dehumidification device - Google Patents

Description

Dehumidification device and control method of dehumidification device

Technical Field

The present invention relates to operation control of a dehumidifier.

Background

Conventionally, as a technique for controlling the rotor rotation speed or the regeneration temperature of an adsorption rotor type dehumidifier in accordance with a change in dehumidification load or the like, there is a technique of detecting the dew point temperature of supplied air, adjusting the rotor rotation speed and the regeneration temperature so that the detected dew point temperature satisfies a required condition (see patent document 1), and a technique of detecting the humidity of the supplied air by a hygrometer, variably controlling the rotor rotation speed so that the detected humidity matches a set humidity (see patent document 2).

There is also a technique of slowing down the rotation speed of the rotor when the humidity of the air before dehumidification is low, and speeding up the rotation speed of the rotor when the humidity of the air at the inlet of the dehumidification area is high (see patent document 3). There is also a technique of determining whether or not regeneration is nearly complete based on a detection value of a temperature sensor provided in the vicinity of a terminal end of a regeneration region, and adjusting a regeneration air volume (see patent document 4).

Patent document 1: japanese patent laid-open publication No. Hei 6-63344.

Patent document 2: japanese patent laid-open publication No. 2003-21378.

Patent document 3: japanese patent laid-open publication No. Hei 5-200231.

Patent document 4: japanese patent laid-open publication No. 2002-331221.

Conventionally, as a method of energy-saving operation of an adsorption rotor type dry dehumidifier used in a low dew point environment such as a manufacturing environment of a lithium ion battery, there is a method of measuring the humidity of inlet air and outlet air in a dehumidification region by a hygrometer (including a dew point meter) and performing operation control based on a change in the measured value. However, since the moisture meter is affected by dirt or the like in the detection portion, the measurement accuracy is likely to be lowered. Specifically, for example, a capacitance-type or resistance-type hygrometer (dew point meter) is susceptible to measurement errors due to adhesion of solvent vapor and dirt, and has the property that measurement errors increase with time. In addition, the mirror-cooled dew point meter also has a bad influence on the measured value due to the fouling of the mirror surface by contaminants (gas and dust) in the air.

If the measurement error of the hygrometer (dew point meter) increases, improper operation control is performed based on the erroneous measurement value, which may significantly impair dehumidification performance. Therefore, when the dehumidification device is controlled using the hygrometer and the dew-point meter, the dew-point meter and the hygrometer must be periodically maintained (for example, the mirror surface is cleaned) and corrected in order to prevent the stability of the dehumidification performance from being impaired, which makes maintenance troublesome.

Disclosure of Invention

In view of the above problems, the present invention is to solve the problems: provided are a dehumidifying device and a method for controlling the operation of the dehumidifying device, which can simply realize variable control operation with higher stability.

The present invention can easily realize variable control operation with higher stability by estimating the humidity of the air to be dehumidified based on the temperature of the air to be dehumidified and the temperature of the air after dehumidification, and determining the operation condition of the dehumidifier based on the estimated humidity.

More specifically, the present invention provides a dehumidifying apparatus comprising: a dehumidifying unit for dehumidifying the passing air, a dividing member dividing the dehumidifying unit into: a dehumidification region for passing air to be dehumidified, dehumidifying the passed air, and setting a dew point of the passed air within a predetermined range; a regeneration area for regenerating a dehumidification capacity of the dehumidification unit by passing air after temperature adjustment; and a purge (パージ) area for dissipating heat from the dehumidification unit with passing air; a zone changing unit configured to repeatedly allocate the dehumidification units in the order of the dehumidification zone, the regeneration zone, and the purge zone; a temperature obtaining unit that obtains a temperature of the air to be dehumidified; and using the temperature of the air dehumidified by the dehumidification region; an estimated humidity obtaining unit configured to obtain an estimated humidity of the air to be dehumidified corresponding to the temperature obtained by the temperature obtaining unit, based on a correspondence relationship between the temperature of the air to be dehumidified and the temperature of the air after dehumidification, which is prepared in advance, and the humidity of the air to be dehumidified; and an appropriate operating condition obtaining unit configured to obtain the appropriate operating condition corresponding to the estimated humidity obtained by the estimated humidity obtaining unit, based on appropriate operating condition information prepared in advance and indicating a relationship between the appropriate operating condition and the humidity of the air to be dehumidified, wherein the appropriate operating condition minimizes an amount of heat required for regeneration by the dehumidifying unit while maintaining a dew point of the dehumidified air within the predetermined range, and the dehumidifying device is controlled in accordance with the appropriate operating condition.

The present invention is suitable for a dehumidifier that dehumidifies air to be dehumidified while regenerating the dehumidification capability of a dehumidification unit by repeating dehumidification, regeneration, and purge in the dehumidification unit. The dehumidification units are distributed by the zone changing means so that three zones, i.e., a dehumidification zone, a regeneration zone, and a purge zone, are formed in the dehumidification units, and the dehumidification units are continuously or intermittently switched to these zones. In the dehumidification region of such a dehumidification device, the temperature of the air after passing through the dehumidification region is higher than the temperature of the air before dehumidification due to the influence of the heat of adsorption of the water vapor. The lower the air humidity before dehumidification, the smaller the temperature rise, and the higher the air humidity before dehumidification, the larger the temperature rise. The present invention previously studies the relationship between the temperature of the air before and after dehumidification and the humidity of the air to be dehumidified by experiments, simulations, and the like, and estimates the humidity of the air to be dehumidified from the temperature of the air before and after dehumidification.

The estimated humidity may be used as a material for determining the operating condition of the dehumidifying apparatus. For example, the change speed of the dehumidification unit assigned by the zone changing means and the adjustment target value of the temperature of the air used for regeneration may be determined based on the estimated humidity. That is, conventionally, control is performed based on humidity and dew point obtained by a hygrometer (dew point meter), but in the present invention, by performing control based on estimated humidity, problems such as erroneous measurement and maintenance trouble due to the hygrometer (dew point meter) do not occur, and variable control operation with high stability can be easily realized.

The operating conditions used for controlling the dehumidifier include, for example, the rotor rotation speed of the desiccant rotor type dehumidifier and the regeneration temperature which is a temperature adjustment target value for heating the regeneration air by the regeneration heater. In general, as the rotor rotation speed (or regeneration temperature) is lower, the amount of heat required for heating regeneration is smaller, and energy saving is possible, but the dew point of the supply air (dehumidified air) is increased. In addition, when compared with the same rotor rotation speed (or regeneration temperature), the lower the absolute humidity at the inlet of the dehumidification region, the lower the dew point of the supplied air tends to be. The "suitable" operation condition in the present invention means an operation condition that can minimize the amount of heat required for regeneration of the dehumidifying unit in a state where the dew point of the supply air satisfies a predetermined range (a range of a set value or a target value), and particularly, a great effect is produced in partial load operation in which the dehumidifying load is small, such as in winter.

In the present invention, the dehumidifying unit is a dehumidifying rotor that is repeatedly assigned in the order of the dehumidifying area, the regenerating area, and the purge area by rotating the dehumidifying rotor at a set number of revolutions per unit time, the suitable operating condition obtaining means obtains the suitable rotor speed corresponding to the estimated humidity from the suitable operating condition information of the dehumidifying apparatus indicating a relationship between a suitable rotor speed and the humidity of the air to be dehumidified, the suitable rotor speed minimizes the amount of heat required for regenerating the dehumidifying rotor in a state where the dew point of the dehumidified air is maintained within the predetermined range, and the area changing means rotates the dehumidifying rotor at the obtained suitable rotor speed to change the amount of heat required for regenerating the dehumidifying rotor in the dehumidifying area, The regeneration zone and the purge zone are sequentially and repeatedly assigned to the desiccant rotor.

More specifically, when the humidity of the air to be dehumidified is low, it is sufficient to use a relatively small dehumidification capacity, and therefore the rotor speed is reduced, and when the humidity is high, a large dehumidification capacity is required, and therefore the rotor speed is increased, and the above-described method is adopted to cope with this. In addition, an appropriate rotor rotation speed that minimizes the amount of heat required for regeneration of the desiccant rotor in a state where the dew point of the dehumidified air satisfies a predetermined range (a range of a set value or a target value) has a fixed relationship with the humidity of the air to be dehumidified. Therefore, in the present invention, the relationship between the humidity of the air to be dehumidified by the dehumidifier and the rotor speed suitable for energy consumption is studied in advance through simulation, experiment, and the like, and the rotor speed is determined based on the estimated humidity according to the relationship. The present invention can be used for a dry dehumidifier of a so-called adsorption rotor system, for example. Further, the number of revolutions per unit time may be set by the number of revolutions per se (e.g., the number of revolutions per minute, etc.), or may be set by the rotational speed (e.g., the rotational angle per second, the rotational distance, etc.).

In the present invention, the purge air volume, which is the air volume of the air introduced into the purge region, is controlled to vary in proportion to the rotation speed of the rotor.

Particularly, when the air volume (regeneration air volume) used for regeneration is controlled in accordance with the outlet temperature of the purge region, it is preferable that: the temperature distribution at the outlet of the purge zone remains constant even with varying rotor speed. Therefore, the total purge air volume (purge air volume × purge time) must be constant. Further, since the purge time is inversely proportional to the rotor speed, it is preferable that the purge air volume is proportional to the rotor speed in order to keep the total purge air volume constant.

For example, when the rotor rotation speed is reduced, since the retention time of the desiccant rotor in the purge region is increased, the desiccant rotor can be cooled with a smaller purge air volume. In particular, in a dehumidifier of a system in which a part of dehumidified air is used for purging under a normal design condition in which a supply air volume of dehumidified air to a load is constant, since the dehumidification air volume is inevitably reduced if the purge air volume is reduced, it is preferable that: the amount of purge air is controlled to be proportional to the rotor speed.

In the present invention, the suitable operating condition obtaining means obtains the suitable operating condition corresponding to the estimated humidity and the dehumidification air volume obtained by the estimated humidity obtaining means, based on suitable operating condition information that is prepared in advance and that indicates a relationship between the suitable operating condition, the humidity of the air to be dehumidified, and the dehumidification air volume that is the air volume of the air introduced into the dehumidification region.

That is, in the present invention, the relationship between the humidity and the dehumidification air volume of the air to be dehumidified and the appropriate operating condition (for example, the rotor speed) in terms of energy consumption is examined in advance through simulation, experiment, or the like, and the appropriate operating condition can be determined according to the relationship. As information for obtaining the appropriate operating condition, in addition to the estimation of the humidity, the appropriate operating condition with higher accuracy can be obtained by using the dehumidification air volume.

Further, the dehumidifying apparatus of the present invention further comprises: a differential pressure obtaining part obtaining a differential pressure between air before being introduced into the dehumidifying area and air after passing through the dehumidifying area; and an estimated airflow rate obtaining unit that obtains an estimated dehumidification airflow rate of air introduced into the dehumidification region corresponding to the differential pressure obtained by the differential pressure obtaining unit, based on a correspondence relationship between the differential pressure and the dehumidification airflow rate that is prepared in advance, wherein the appropriate operation condition obtaining unit obtains the appropriate operation condition corresponding to the estimated humidity obtained by the estimated humidity obtaining unit and the estimated dehumidification airflow rate obtained by the estimated airflow rate obtaining unit.

The dehumidifying apparatus of the present invention further comprises: a differential pressure obtaining part for obtaining the differential pressure between the air before being introduced into the purging area and the air after passing through the purging area; and an estimated air volume obtaining unit that obtains an estimated purge air volume of the air introduced into the purge region corresponding to the differential pressure obtained by the differential pressure obtaining unit, based on a correspondence relationship between the differential pressure and the purge air volume that is prepared in advance, and controls the estimated purge air volume to change in proportion to the rotor rotation speed.

In order to obtain the air volume, an air volume meter may be used, but as described above, the air volume may be estimated from the differential pressure. Since the air volume meter has problems such as erroneous measurement and troublesome maintenance as in the case of a hygrometer, accurate control can be easily performed by obtaining the air volume by estimation.

Further, in the present invention, the temperature of the air introduced into the regeneration area is adjusted by a regeneration heater so that the temperature of the air introduced into the regeneration area becomes a set regeneration temperature, the suitable operation condition obtaining means obtains the suitable regeneration temperature corresponding to the estimated humidity based on the suitable operation condition information of the dehumidifying apparatus indicating a relationship between a suitable regeneration temperature and the humidity of the air to be dehumidified, the suitable regeneration temperature minimizes the amount of heat required for regeneration by the dehumidifying unit while maintaining the dew point of the dehumidified air within the predetermined range, and the regeneration heater adjusts the temperature of the air introduced into the regeneration area so that the temperature of the air introduced into the regeneration area becomes the suitable regeneration temperature.

More specifically, when the air humidity to be dehumidified is low, it is sufficient to use a small dehumidification capacity, and therefore, the regeneration temperature is decreased to cope therewith, and when the air humidity to be dehumidified is high, a large dehumidification capacity is required to cope therewith, so that the regeneration temperature is increased to cope therewith. In addition, an appropriate regeneration temperature that minimizes the amount of heat required for temperature adjustment of air used for regeneration in a state where the dew point of the dehumidified air satisfies a predetermined range (a range of a set value or a target value) has a fixed relationship with the humidity of the air to be dehumidified. Therefore, in the present invention, the relationship between the humidity of the air to be dehumidified in the dehumidifier and the regeneration temperature suitable for energy consumption is studied in advance by simulation, experiment, or the like, and the regeneration temperature is determined based on the estimated humidity according to the relationship.

Further, in the present invention, the temperature obtaining means obtains the temperature of the air as the dehumidification target; and a temperature of the dehumidified air in a dehumidification region near the regeneration region, among the dehumidified air.

If the operation is performed stably or in a transient state with a small purge air volume, the dehumidification unit may move to the dehumidification region in a state where the cooling in the purge region is insufficient. When the cooling in the purge region is sufficient, the temperature difference hardly occurs in the temperature distribution on the air-discharge side of the dehumidification region, but when the cooling in the purge region is insufficient, heat is transferred from the purge region to the dehumidification region due to the heat capacity of the dehumidification unit, and the temperature of the air near the purge region on the air-discharge side of the dehumidification region is relatively high. Therefore, in the present invention, by using the temperature of the dehumidified air in the dehumidification region near the regeneration region as the temperature of the dehumidified air, it is possible to prevent deterioration of the estimation accuracy of the air humidity to be dehumidified due to the influence of the transfer of heat from the purge region to the dehumidification region.

Further, the present invention provides a control method of a dehumidifying apparatus, comprising: a dividing member dividing a dehumidifying rotor for dehumidifying passing air into: a dehumidification region for passing air to be dehumidified, dehumidifying the passed air, and setting a dew point of the passed air within a predetermined range; a regeneration region for regenerating a dehumidifying capacity of the dehumidifying rotor by passing the temperature-adjusted air; and a purge region for dissipating heat of the dehumidifying rotor using passing air; and a zone changing unit configured to repeatedly allocate the desiccant rotors in the order of the dehumidification zone, the regeneration zone, and the purge zone by rotating the desiccant rotors at a set number of revolutions per unit time, wherein the method of controlling the dehumidifier includes: a temperature obtaining step of obtaining a temperature of the air as the dehumidification target; and using the temperature of the air dehumidified by the dehumidification region; an estimated humidity obtaining step of obtaining an estimated humidity of the air to be dehumidified corresponding to the temperature obtained in the temperature obtaining step, based on a correspondence relationship between the temperature of the air to be dehumidified and the temperature of the air after dehumidification, which is prepared in advance, and the humidity of the air to be dehumidified; an appropriate operating condition obtaining step of obtaining, based on appropriate operating condition information prepared in advance and indicating a relationship between an appropriate operating condition for minimizing the amount of heat required for regeneration of the dehumidifying rotor and the estimated humidity obtained in the estimated humidity obtaining step, the appropriate operating condition corresponding to the estimated humidity obtained in the estimated humidity obtaining step, the appropriate operating condition being maintained in a state in which the dew point of the dehumidified air is maintained within the predetermined range; and a control step of controlling at least one of the rotation speed of a dehumidifying rotor of the dehumidifier and the temperature of the regeneration air in accordance with the appropriate operating condition.

According to the present invention, it is possible to provide a method for variably controlling the rotor speed and the regeneration temperature of a dehumidifier, which can easily realize a variable control operation with higher stability.

Drawings

Fig. 1 is a diagram showing a system configuration for supplying low dew point air, which includes a dry dehumidifier according to an embodiment.

Fig. 2 is a perspective view showing a desiccant rotor and a cross-sectional partition box according to the embodiment.

Fig. 3 is a diagram showing the position of a temperature sensor provided for detecting the outlet temperature at a position close to the regeneration region in the purge region in the embodiment.

Fig. 4A is a diagram showing a relationship between a position angle of the rotor in the rotation direction and outlet temperatures of the regeneration region and the purge region in the dehumidification device according to the embodiment.

Fig. 4B is a graph showing the outlet air temperature at the coordinates (position angle) in the rotational direction of the regeneration region and the purge region for each regeneration air volume ratio.

Fig. 4C is a graph showing a correlation between the regeneration air volume ratio shown in fig. 4B and the temperature of the purged air that has no temperature distribution and is uniform.

Fig. 5 is a diagram showing a relationship between absolute humidity of air at an inlet of a dehumidification region and an air temperature difference at an inlet and an outlet of the dehumidification region in the dry dehumidification device according to the embodiment.

Fig. 6 is a graph showing a relationship between an appropriate rotor rotation speed and the absolute humidity of the inlet air of the dehumidification region in the embodiment.

Fig. 7 is a graph showing a relationship between an appropriate regeneration temperature and the absolute humidity of the inlet air of the dehumidification region in the embodiment.

Fig. 8 is a diagram illustrating a relationship between the dew-point temperature of the air at the outlet of the dehumidification region and the rotor speed when the surface wind speed passing through the dehumidification region is 2.0 m/s.

Fig. 9 is a graph illustrating a relationship between the dew-point temperature of the air at the outlet of the dehumidification region and the regeneration temperature when the surface wind speed passing through the dehumidification region is 2.0 m/s.

Fig. 10A is a diagram a showing the energy saving effect obtained by the control of the embodiment.

Fig. 10B is a diagram B showing the energy saving effect obtained by the control of the embodiment.

Fig. 11 is a diagram showing an air temperature distribution on the outlet side of the dehumidification region in the embodiment.

Fig. 12 is a diagram showing an example (1) of the installation position of the temperature sensor for detecting the temperature of the air after dehumidification.

Fig. 13 is a diagram showing an example (2) of the installation position of the temperature sensor for detecting the temperature of the dehumidified air.

Fig. 14 is a diagram showing an example of detection positions of differential pressure and temperature in the case where the regional ventilation air volume is calculated by estimation from the differential pressure and the temperature.

Fig. 15 is a diagram showing an example of a temperature measurement position in the case where the present invention is used in a two-stage processing system.

Fig. 16 is a diagram showing a change in the process flow of the dehumidification system according to the present invention.

Fig. 17 is a diagram showing a change in the temperature of the exhaust air in the conventional dehumidifying apparatus.

Description of the reference numerals

1 Dry dehumidification device

11 dehumidifying rotor

11a dehumidification region

11b regeneration zone

11c purge zone

12. 13 section division box

42. 43, 44 temperature sensor

23. 46 air gauge

Detailed Description

Embodiments of the dehumidifying apparatus of the present invention will be described below with reference to the drawings. In the present embodiment, the case where the present invention is applied to the adsorption rotor type dry dehumidifier is described, but the present invention is not limited to the adsorption rotor type dry dehumidifier, and the present invention may be applied to any dehumidifier as long as it performs regeneration of dehumidification capability by a cycle of dehumidification, regeneration, and purge. For example, the present invention may also be applied to a shuttle type dehumidifying apparatus of the type: a regeneration air duct inserted from an open end of the dehumidification unit is disposed in the rectangular dehumidification unit having the desiccant disposed therein, and the regeneration air duct reciprocates with respect to the dehumidification unit (actually, the regeneration air duct may be moved by driving a motor or the like, or the dehumidification unit may be used). The present invention is applicable regardless of the area division ratio of the desiccant rotor and the size of the desiccant rotor. The present invention is also applicable to a dehumidifying apparatus having a multistage dehumidifying rotor.

Fig. 1 is a diagram showing a system configuration for supplying low dew point air to a low dew point space such as a low dew point chamber, which includes the dry dehumidifier of the present embodiment. Fig. 2 is a perspective view showing the desiccant rotor and the cross-sectional division box according to the present embodiment. The dry dehumidifier 1 includes a desiccant rotor 11, and dehumidifies air passing through the interior of the desiccant rotor 11 by disposing a base material containing a moisture absorbent such as synthetic zeolite, silica gel, and lithium chloride inside the desiccant rotor 11. On both end surfaces of the desiccant rotor 11, the cross-sectional boxes 12 and 13 are arranged, and air is introduced into the desiccant rotor 11 and discharged from the desiccant rotor 11 through the cross-sectional boxes 12 and 13. The desiccant rotor 11 corresponds to a desiccant unit of the present invention, and the cross-sectional cassettes 12 and 13 correspond to a partition member of the present invention.

The inside of each of the cross-sectional boxes 12, 13 is divided to divide the desiccant rotor 11 into a desiccant region 11a, a regeneration region 11b, and a purge region 11 c. The section dividing box 12 is provided with: a dehumidification region inlet 12a for introducing air to be dehumidified into the dehumidification region 11 a; a regeneration-zone outlet 12b for discharging air used in regenerating the dehumidification capability from the regeneration zone 11 b; and a purge zone outlet 12c for discharging purge air from the purge zone 11 c. The section dividing box 13 is provided with: a dehumidification-area outlet 13a for discharging dehumidified air from the dehumidification area 11 a; a regeneration-zone inlet 13b for introducing air used in regeneration into the regeneration zone 11 b; and a purge zone inlet 13c for introducing purge air into the purge zone 11 c.

The desiccant rotor 11 is driven to rotate by the gear motor 72 in a state where the above-described split boxes 12, 13 are attached to both ends. As described above, the inside of the cross-sectional boxes 12 and 13 is divided to divide the desiccant rotor 11 into the desiccant region 11a, the regeneration region 11b, and the purge region 11c in this order in the rotation direction of the desiccant rotor 11. Therefore, the air passage area of the desiccant rotor 11 is divided into three parts (the desiccant area 11a, the regeneration area 11b, and the purge area 11c in this order in the rotation direction of the desiccant rotor 11), and the respective parts of the desiccant rotor 11 correspond to the desiccant area 11a, the regeneration area 11b, and the purge area 11c in this order with the rotation of the desiccant rotor 11. Therefore, the dehumidification by the desiccant rotor 11, the regeneration of the dehumidification capability of the desiccant rotor 11, and the purge of the desiccant rotor 11 that becomes a high temperature due to the regeneration are repeated, and the dehumidification performance of the dry dehumidification device is maintained. The gear motor 72 is controlled by a control arithmetic unit CU. That is, the gear motor 72 and the control arithmetic unit CU for controlling the same correspond to the zone changing means of the present invention.

The dehumidification region 11a, the regeneration region 11b, and the purge region 11c are each divided into radial regions centered on the rotation axis of the dehumidification rotor 11 (see fig. 2). If the size of the area occupied by each zone in the entire cross-sectional box is represented by an angle centered on the rotation axis of the desiccant rotor 11, the desiccant zone 11a is 270 degrees, the regeneration zone 11b is 60 degrees, and the purge zone 11c is 30 degrees in the present embodiment (see fig. 3). Further, a duct is connected to each of the ports provided in the sectioning boxes 12 and 13.

A dehumidification duct 22 for obtaining air to be dehumidified is connected to the dehumidification-area inlet 12a of the cross-sectional box 12. A fan 21 is provided in the dehumidification duct 22, and air to be dehumidified is obtained by operation of the fan 21.

A supply duct 24 for supplying the dehumidified low dew point air to the low dew point space is connected to the dehumidification region outlet 13a of the cross-sectional box 13. The air obtained from the dehumidifying duct 22 is dehumidified by the action of the moisture absorbent or the like in the dehumidifying rotor 11, and is discharged from the dry dehumidifying apparatus through the supply duct 24. In addition, a set dew point as a target value is set in the dry dehumidifier, and when the dry dehumidifier operates as desired, the air to be dehumidified obtained from the dehumidification duct 22 is dehumidified to below the set dew point and then discharged to the supply duct 24.

A purge introduction line 25 for introducing air for reducing the temperature of the moisture absorbent or the like regenerated in the regeneration region 11b is connected to the purge region inlet 13c of the cross-sectional box 13. The supply line 24 is connected to a purge introduction line 25 for introducing air into the purge region 11c, in addition to the low dew point space, and a part of the air discharged to the supply line 24 is supplied to the low dew point space and a part is guided to the purge region 11c through the purge introduction line 25. Further, the supply amount to the low dew point space and the introduction amount to the purge region 11c are adjusted by controlling the supply damper provided in the supply line 24 and the purge introduction damper provided in the purge introduction line 25.

A purge exhaust line 26 for exhausting air used in purging is connected to the purge zone outlet 12c of the sectioning box 12. A regeneration exhaust duct 27 for exhausting air used for regenerating the desiccant for dehumidification is connected to the regeneration area outlet 12b of the cross-sectional box 12. The purge exhaust duct 26 merges with the regeneration exhaust duct 27 in the vicinity of the upstream of the regeneration fan 31. Therefore, the purge used air and the regeneration used air are sucked by the regeneration fan 31, and a part of the purge used air is discharged to the outside of the system.

A regeneration introduction duct 32 for introducing air used for regenerating the moisture absorbent for dehumidification is connected to the regeneration area inlet 13b of the cross-sectional box 13. Further, a regeneration introduction line 32 is connected to the regeneration exhaust line 27, and a regeneration heater 33 is equipped in the middle of the regeneration introduction line 32. Therefore, after the purge used air and the regeneration used air are sucked by the regeneration fan 31, a part of the purge used air is discharged to the outside of the system, and a part of the purge used air is sent to the regeneration introduction duct 32. The exhaust damper provided in the regeneration exhaust duct 27 and the circulation damper provided in the regeneration introduction duct 32 are controlled to adjust the amount of exhaust gas to the outside of the system and the amount of exhaust gas to be introduced into the regeneration introduction duct 32.

The air sent to the regeneration introduction duct 32 is heated by the regeneration heater 33 and then introduced into the regeneration region 11 b. The temperature regulator 45 obtains the detection result of the temperature sensor 44 provided between the regenerative heater 33 and the regeneration-zone inlet 13b, and controls the regenerative heater 33 by the temperature regulator 45 to regulate the temperature of the regeneration air introduced into the regeneration zone 11b to a set regeneration temperature. The dehumidifying capacity of the part of the dehumidifying rotor 11 located at the position corresponding to the regeneration area 11b is regenerated by the regeneration air, and thereafter the part is reused for dehumidification by moving to the position corresponding to the dehumidifying area 11 a.

Control of regenerative air volume

In the dehumidifier of the present embodiment, the regeneration air volume is controlled before (or at the same time as) the process of estimating the absolute humidity of the inlet air of the dehumidification region and controlling the rotor rotation speed and/or the regeneration temperature according to the present invention. The regeneration air volume is an air volume of air (here, air heated to a high temperature) introduced into the regeneration zone 11b to regenerate the dehumidification capability of the desiccant rotor 11. The regeneration fan 31 provided in the regeneration introduction duct 32 is controlled so that the air volume detected by the air volume meter 46 provided downstream of the regeneration fan 31 becomes the set target regeneration air volume (in the present embodiment, an appropriate regeneration air volume determined by the method described below is set as the target regeneration air volume). However, according to the embodiment, the regeneration air volume may be controlled by another method. Depending on the embodiment, the control of the regeneration air volume described later may be omitted.

Fig. 17 shows a change in the temperature of the exhaust air in the conventional dehumidifying apparatus. From the temperature change shown in fig. 17, it was confirmed that: conventionally, regeneration is completely completed in the regeneration zone 11b, and only the rotor is cooled in the purge zone 11 c. The heat of the regeneration air first increases the temperature of the rotor (a to d in the figure), and thereafter is used as the desorption heat of moisture (d to e in the figure). Then, the temperature rises again (e to f in the figure) after the moisture desorption is completed. Conventionally, a temperature sensor is provided in the regeneration zone 11b at a position close to the purge zone 11c, and the regeneration air volume is controlled so that the temperature sensor detects the regeneration completion temperature. Therefore, in the related art, the heat applied to the rotor after the water desorption ends reduces the treatment efficiency of the regeneration and purge. Here, the regeneration completion temperature is a temperature for determining whether or not regeneration of the rotor is completed based on the temperature of the air passing through the rotor, and is set to 100 degrees celsius, for example.

In contrast, in the present embodiment, in the control of the regeneration air volume, attention is paid to the fact that even if the regeneration is not completely completed in the regeneration zone 11b, the dehumidification capability is regenerated by heating the purge air by the stored heat of the rotor in the purge zone 11c, and the regeneration is completed in the purge zone 11 c. That is, the regeneration air volume is controlled so that the outlet temperature at the position near the regeneration region 11b in the purge region 11c is higher than the outlet temperature at the position closest to the purge region 11c in the regeneration region 11b, and the outlet temperature at the position near the regeneration region 11b in the purge region 11c is equal to or higher than the regeneration completion temperature.

Fig. 3 is a diagram showing the position of the temperature sensor 41 provided for detecting the outlet temperature at a position close to the regeneration region 11b in the purge region 11c in the present embodiment. The regeneration air volume is controlled so that the regeneration completion temperature is detected by the temperature sensor 41 provided at the position shown in the figure, and the regeneration air volume is: the regeneration is not completely completed in the regeneration region 11b, and the regeneration is completed in the purge region 11c by purge air heated by the stored heat of the rotor, thereby improving the efficiency of the apparatus. The position of the purge region 11c close to the regeneration region 11b means a position closer to the regeneration region 11b than the center of the purge region 11 c.

Fig. 4A is a diagram showing a relationship between the position angle θ of the rotor in the rotation direction of the dehumidifying apparatus of the present embodiment and the outlet temperatures of the regeneration zone 11b and the purge zone 11 c. In fig. a to E, the heat of the regeneration air is first used to raise the temperature of the rotor (fig. a to D), and is thereafter used as the desorption heat of the adsorbed moisture (fig. D to E). In the present embodiment, the regeneration air volume is controlled so that the regeneration completion temperature is detected by the temperature sensor 41 shown in fig. 3, and therefore the rotor is shifted to the purge region 11c immediately before the rotor regeneration is completed. In the figure, most of the region of the rotor in the state E except the vicinity of the outlet reaches around 140 ℃. Further, since the heat capacity per unit volume of the rotor is much larger than that of air, the rotor in the E state is in a high-temperature heat storage state. If low-temperature purge air flows through the rotor, the temperature of the purge air is rapidly increased to about 140 degrees centigrade, and the moisture absorbent that has not been regenerated is regenerated (F to G). According to the above-described processing, the dehumidifier of the present embodiment can save energy required for regeneration compared to the conventional dehumidifier.

Further, according to the study of the present inventors and the like, it was clarified that: in a state where the purge air volume is constant, the temperature of the purged air (that is, the average temperature of the outlet air of the purge zone 11c) in a state where there is no temperature distribution after passing through the purge zone 11c (that is, the temperature of the purged air is uniform by mixing the purged air) has a correlation with the distribution of the outlet temperatures of the regeneration zone 11b and the purge zone 11c, accompanying the change in the regeneration air volume ratio (i.e., the regeneration air volume/the dehumidification air volume). The regeneration air volume ratio is a ratio of the regeneration air volume to the air volume passing through the dehumidification region (the processing air volume of the dehumidification device).

Fig. 4B is a graph showing the outlet air temperature at the coordinates (position angles) of the regeneration region 11B and the purge region 11c in the rotational direction for each regeneration air volume ratio. In the example shown in fig. 4B, it can be confirmed that: if the regeneration air volume is decreased (the value of the regeneration air volume ratio α is decreased), the distribution curve of the outlet air temperature moves to the right in the figure, and there is a regeneration air volume ratio in which the outlet temperature at any position in the purge region 11c close to the regeneration region is higher than the outlet temperature at the position in the regeneration region 11b closest to the purge region 11c, and the outlet temperature at any position in the purge region 11c close to the regeneration region is equal to or higher than the regeneration end temperature.

Fig. 4C is a graph showing a correlation between the regeneration air volume ratio shown in fig. 4B and the temperature of the purged air which has no temperature distribution and is uniform. From fig. 4C it can be confirmed that: there is a correlation between the regeneration air volume ratio and the temperature of the purged air that has no temperature distribution and is uniform. Therefore, in the control of the regeneration air volume described above, as shown in fig. 3, a method is employed in which: instead of directly measuring the outlet temperature of the purge zone 11c at a position close to the regeneration zone 11b by the temperature sensor 41 and determining the regeneration air volume based on the measured temperature, the following method may be employed: the temperature of the purged air having no temperature distribution and being uniform is measured by using a temperature sensor (not shown) provided in the purge exhaust duct 26, and the regeneration air volume is determined based on the measured temperature. Even with such a method, the regeneration air volume can be controlled so that the outlet temperature at the position in the purge zone 11c close to the regeneration zone 11b is higher than the outlet temperature at the position in the regeneration zone 11b closest to the purge zone 11c, and the outlet temperature at the position in the purge zone 11c close to the regeneration zone 11b is equal to or higher than the regeneration completion temperature.

Control by temperature at inlet and outlet of dehumidification area

The dry-type dehumidification device of the present embodiment controls the rotor rotation speed and the regeneration temperature by the control arithmetic device CU, thereby achieving efficient operation. In the present embodiment, the appropriate rotor speed or the appropriate regeneration temperature is estimated from the air temperatures at the dehumidification-area inlet 12a and the dehumidification-area outlet 13 a.

A temperature sensor 42 for detecting the temperature of the air to be dehumidified is provided near the dehumidification-area inlet 12a of the dehumidification duct 22, and a temperature sensor 43 for detecting the temperature of the supply air after dehumidification is provided near the dehumidification-area outlet 13a of the supply duct 24. The temperature sensors 42, 43 detect the temperature of the air (inlet air temperature T) entering the dry type dehumidification device through the dehumidification duct 22_A) And the temperature of the air (outlet air temperature TB) sent to the low dew-point space or the purge introduction duct 25 through the supply duct 24, and the detected temperature T is sent to the control arithmetic unit CU_AAnd temperature T_B. Further, an air gauge 23 is provided in the dehumidification duct 22. The air volume meter 23 detects the air volume of the air entering the dry dehumidifier through the dehumidification duct 22, and sends an air volume signal to the control arithmetic unit CU. The control arithmetic unit CU calculates the surface wind speed v of the dehumidification region according to the input air volume signal_pro。

FIG. 5 shows the absolute humidity x of the air at the inlet of the dehumidification region in the dry dehumidification apparatus according to the present embodiment_AAir temperature difference Δ T between the dehumidification-area inlet 12a and the dehumidification-area outlet 13a_pro＝T_B-T_AA graph of the relationship of (1). In the dehumidification region 11a, the outlet air temperature T is affected by the heat of adsorption of water vapor_BSpecific inlet air temperature T_AHigh. Absolute humidity x of inlet air of dehumidification region_AThe lower the temperature rise Δ T_proThe smaller, the absolute humidity x of the inlet air of the dehumidification region_AThe higher the temperature rise Δ T_proThe larger. The air temperature difference Δ T between the dehumidification-area inlet 12a and the dehumidification-area outlet 13a is previously examined through experiments, simulations, and the like_proAbsolute humidity x of inlet air of dehumidification area_AThe relationship (c) is stored as estimated humidity information in the storage device of the control arithmetic unit CU in the form of a relational expression (for example, expression (1) shown below) or a map for humidity estimation processing. The control arithmetic unit CU receives the air temperature T at the dehumidification region inlet 12a and the dehumidification region outlet 13a_A、T_BAfter the measurement of (2), calculation is performed or humidity is referred to by using the relational expressionAn estimation processing chart for estimating the absolute humidity x of the inlet air of the dehumidification region_A. The absolute humidity x of the inlet air of the dehumidification region is sufficiently cooled in the purge region 11c and the heat is not transferred from the purge region 11c to the dehumidification region 11a_AAccording to inlet air temperature T_AAnd outlet air temperature T_BThe control arithmetic unit CU determines the temperature T of the air at the dehumidification region inlet 12a and the dehumidification region outlet 13a by using the following formula (1)_A、T_BSubstituting into formula (1) to calculate absolute humidity x of inlet air of dehumidification region, regardless of rotor rotation speed, regeneration temperature, dehumidification air volume, etc_A。

x_A＝f(T_A,T_B) … formula (1)

The control arithmetic unit CU uses the absolute humidity x of the inlet air of the dehumidification region_AThe variable control is performed such that the rotor speed is reduced (or the regeneration temperature is reduced) when the humidity is low, and the rotor speed is increased (or the regeneration temperature is increased) when the humidity is high.

Fig. 6 shows a suitable rotor rotation speed ω according to the present embodiment_optAbsolute humidity x of inlet air of dehumidification area_AA graph of the relationship of (1). FIG. 7 shows a suitable regeneration temperature T in the present embodiment_reg,optAbsolute humidity x of inlet air of dehumidification area_AA graph of the relationship of (1). The relationship is examined in advance through experiments, simulations, and the like, and is stored as appropriate operation condition information in a storage device of the control arithmetic device CU in the form of a relational expression (see the following expressions (2) and (3)), a map for controlling the rotor rotational speed (see fig. 6), a map for controlling the regeneration temperature (see fig. 7), and the like.

ω_opt＝f(v_pro,x_A,T_reg,T_A) … formula (2)

T_reg,_opt＝f(v_pro,x_A,ω,T_A) … formula (3)

Lower pairThe entire flow of the process of determining the operating conditions based on the air temperatures at the dehumidification-area inlet 12a and the dehumidification-area outlet 13a will be described. First, the control arithmetic unit CU calculates the absolute humidity x of the inlet air of the dehumidification region by referring to the humidity estimation processing map based on the temperature signals input from the temperature sensors 42 and 43_A(using equation (1)). The control arithmetic unit CU calculates the surface wind speed v of the dehumidification region based on the air volume signal input from the air volume meter 23_pro. However, the air volume passing through each region such as the dehumidification region may be obtained by an estimation process using the formula (4) described later, without being detected by an air volume meter. Next, the control arithmetic unit CU performs any of the previously determined "control of the rotation speed", "control of the regeneration temperature", and "control of the rotation speed and the regeneration temperature".

When the rotational speed is controlled, the control arithmetic unit CU controls the surface wind speed v of the dehumidification region_proAbsolute humidity x of inlet air of dehumidification area_ARegeneration temperature T_regInlet air temperature T_ASubstituting into formula (2), or referring to rotor speed control chart, calculating appropriate rotation speed ω_opt. The rotation speed of the motor for driving the desiccant rotor 11 is adjusted using the appropriate rotation speed as a target value.

When controlling the regeneration temperature, the control arithmetic unit CU adjusts the surface wind speed v of the dehumidification region_proAbsolute humidity x of inlet air of dehumidification area_ARotor speed omega, inlet air temperature T_ASubstituting into equation (3), or referring to the regeneration temperature control map, to calculate the appropriate regeneration temperature T_reg,opt. The output of the regenerative heater is adjusted with the appropriate regeneration temperature as a target value.

When controlling both the rotational speed and the regeneration temperature, the control arithmetic unit CU controls the surface wind speed v according to the dehumidification region_proAbsolute humidity x of inlet air of dehumidification area_AAnd inlet air temperature T_ACalculation formula of combination of suitable rotation speed and regeneration temperature, or map for controlling rotation speed and regeneration temperature of rotorAnd the like are stored in a storage device, and an appropriate combination of the rotor rotational speed and the regeneration temperature is calculated by performing calculation using the calculation formula or referring to the rotor rotational speed and the regeneration temperature control map. The rotation speed of the motor for driving the desiccant rotor 11 and the output of the regenerative heater are adjusted by using the appropriate rotation speed and the appropriate regeneration temperature as target values.

Effect

FIG. 8 is a graph showing the surface wind velocity v passing through the dehumidification region_proAt 2.0 m/s, the dew point temperature T of the air at the outlet of the dehumidification region_d,BA graph showing an example of the relationship with the rotor speed ω. When the rotor speed is constant, the absolute humidity x of the inlet air of the dehumidification area is determined_A[g/kg(DA)]The lower, the dehumidification region outlet air dew point temperature T_d,BThe lower, the more dehumidification becomes necessary. According to the control of the rotor speed of the present embodiment, the absolute humidity x of the inlet air in the dehumidification region_AIn the low case, since the control is: since the rotor rotation speed ω is reduced within a range in which the supply air dew point satisfies the design specification, the residence time of the desiccant rotor 11 in the regeneration region 11b becomes longer, and regeneration can be performed with a smaller amount of regeneration heat (with a smaller amount of regeneration air).

FIG. 9 is a graph showing the surface wind velocity v in the dehumidification region_proAt 2.0 m/s, the dew point temperature T of the air at the outlet of the dehumidification region_d,BAnd regeneration temperature T_regA diagram of an example of the relationship of (1). At the regeneration temperature T_regIn certain cases, due to the absolute humidity x of the inlet air of the dehumidification region_AThe lower, the dehumidification region outlet air dew point temperature T_d,BThe lower, the more dehumidification becomes necessary. According to the regeneration temperature control of the present embodiment, the absolute humidity x of the inlet air in the dehumidification region_AIn the low case, since the control is: reducing the regeneration temperature T within a range in which the dew point of the supply air satisfies the design specification_regTherefore, the temperature of the desiccant rotor 11 in the regeneration region 11b increases less, and the amount of heat required for heating regeneration is reduced.

Fig. 10A and 10B are graphs showing the energy saving effect (the ratio of the amount of heat regenerated when the amount of heat regenerated at the rated operation is 100%) obtained by the control according to the present embodiment. Let the surface wind speed passing through the dehumidification region be v_pro2.0 m/s (nominal) and v_proTwo cases of 1.0 m/s. The blowing surface air speed is determined by the formula (4), and the regeneration air quantity is controlled by the processing.

From the results shown in fig. 10A and 10B, it can be confirmed that: at x_AAt a part load of 0.5g/kg (da), the "control of the rotational speed" can reduce the amount of regenerative heat by about 27% at v of 2.0 m/s, about 58% at v of 1.0 m/s, and about 22% at v of 1.0 m/s, compared to the case of operating at the rated rotational speed, and the "control of the regenerative temperature" can reduce the amount of regenerative heat by about 10% at v of 2.0 m/s, compared to the case of operating at the rated regenerative temperature. In order to obtain such an energy saving effect, the conventional technique requires the use of a hygrometer and a dew point meter, but according to the dry type dehumidification device of the present embodiment, the same energy saving effect as when the hygrometer and the dew point meter are used can be obtained without using the hygrometer and the dew point meter. Compared with the prior art, the invention can improve the stability of dehumidification performance, does not need to regularly correct the hygrometer and the dew point meter, and is easy to maintain.

Modification example: measurement position of dehumidification area outlet air temperature

Fig. 11 is a diagram showing the air temperature distribution on the outlet side of the dehumidification region in the present embodiment. If the operation is performed in a stable or transient state with a small purge air volume, the desiccant rotor 11 may move to the desiccant region 11a in a state where the cooling in the purge region 11c is insufficient. As shown in fig. 11, when the cooling in the purge region 11c is sufficient, the temperature distribution hardly occurs on the outlet side of the dehumidification region, but when the cooling in the purge region 11c is insufficient, the heat is transferred from the purge region 11c to the dehumidification region 11a by the heat capacity of the dehumidification rotor 11, and the outlet side of the dehumidification region is close to the purge regionThe temperature of the air of the domain 11c is relatively high. In this case, the difference Δ T in air temperature between the dehumidification-area inlet 12a and the dehumidification-area outlet 13a is caused by a factor other than the heat of adsorption_proBecomes larger, so if the absolute humidity x of the inlet air of the dehumidification region is estimated from the air temperature in the duct on the outlet side of the dehumidification region_AThe absolute humidity x of the inlet air of the dehumidification area is adjusted_AIt is inferred to be too large. Therefore, a temperature sensor for detecting the temperature of the air after dehumidification is provided at a position (not shown) near the regeneration area 11b on the dehumidification area outlet side of the cross-sectional box 13, and the humidity can be estimated using the temperature detected at this position.

Fig. 12 is a diagram showing an example (1) of the installation position of the temperature sensor for detecting the temperature of the air after dehumidification. If the temperature difference Δ T of the air at the inlet 12a and the outlet 13a of the dehumidification region is calculated_proThe temperature at the time of dehumidification region outlet can be eliminated by using the indicated value of the temperature sensor inserted into the cassette portion of the regeneration region 11b on the dehumidification region outlet side as shown in fig. 12, instead of using the indicated value of the temperature sensor of the duct portion of the dehumidification region outlet 13 a. In fig. 11, the temperature closest to the regeneration area 11b is high because of the influence of radiant heat from the partition plate between the dehumidification area 11a and the regeneration area 11 b. It is preferable that a certain distance is provided between the partition plate and the temperature sensor (for example, a linear distance between the temperature sensor and the partition plate is about 20cm or more).

Fig. 13 is a diagram showing an example (2) of the installation position of the temperature sensor for detecting the temperature of the dehumidified air. As shown in fig. 13, by dividing the dehumidification region 11a into two and detecting the temperature of the outlet-side duct portion of the dehumidification region 11a2 on the side away from the purge region 11c, even when the cooling in the purge region 11c is insufficient, the influence of the heat transfer from the purge region 11c can be eliminated, and the absolute humidity x of the inlet air of the dehumidification region can be prevented from being changed_AIt is inferred to be too large.

Modification example: air volume measuring method

Fig. 14 is a diagram showing an example of detecting the positions of the differential pressure and the temperature when the regional ventilation air volume is calculated by estimating the differential pressure and the temperature. As shown in fig. 14, if the temperature sensor and the differential pressure gauge dP are provided in each region to measure, the ventilation air volume in each region can be obtained by the following equation without using an air volume meter. Since the air gauge has a problem of erroneous measurement and maintenance trouble like a hygrometer, a more desirable result may be obtained by an estimation method from the viewpoint of stability of dehumidification performance. In addition, in the case of estimating the air volume from the differential pressure and the temperature, the following formula (4) may be used.

Area ventilation air volume (area before area) x area inlet/outlet pressure difference/(coefficient a x area inlet/outlet average temperature + coefficient b)

… formula (4)

For the measurement of the air temperature at the outlet of the zone required for the calculation of the formula (4), it is necessary to measure the air temperature at the outlet of the zone in which there is no temperature distribution, but since the temperature distribution at the outlet of the desiccant rotor is large particularly in the purge zone 11c and the regeneration zone 11b, it is difficult to mix, and the outlet temperature may not be measured accurately. This temperature distribution naturally disappears as the duct flow path is longer, but if the duct flow path is longer, the outlet temperature that is originally to be measured may not be accurately measured due to heat loss caused by heat release from the duct. Therefore, for example, the zone outlet air may be stirred, and the temperature of the stirred air may be measured as the zone outlet air. Such stirring can be performed by a damper, a propeller, a deflector, an elbow, or the like provided in the air flow path on the outlet side of the region. Alternatively, a plurality of temperature sensors may be inserted into the cassette part on the outlet side of the zone at regular intervals (in the angular direction) without stirring, and the average of the measured temperatures may be used as the outlet air temperature of the zone.

Modification example: temperature measurement location for two-stage processing system

Fig. 15 is a diagram showing an example of a temperature measurement position in a case where the present invention is applied to a two-stage processing system. In the example shown in fig. 15, the dehumidification region is divided into a first dehumidification region 11a1 and a second dehumidification region 11a2, and the air to be dehumidified once passes through the first dehumidification region 11a1 and then passes through the second dehumidification region 11a 2. That is, in the example shown in fig. 15, the air to be dehumidified passes through the dehumidification region twice. In the case where the first method is used in the two-stage treatment system shown in fig. 15, the control can be performed by estimating the inlet humidity of the first dehumidification region 11a1 from the inlet-outlet temperature difference of the first dehumidification region 11a1, and estimating the inlet humidity of the second dehumidification region 11a2 from the inlet-outlet temperature difference of the second dehumidification region 11a 2. In the case where the outlet air temperature of the first dehumidification region 11a1 and the inlet air temperature of the second dehumidification region 11a2 are substantially equal, either one of the temperature sensors may be omitted.

Modification example: control of purge air volume

When the rotation speed of the desiccant rotor 11 is reduced, the time during which the desiccant rotor 11 stays in the purge region 11c becomes long, and therefore the desiccant rotor 11 can be cooled with a smaller purge air volume. In particular, in a system of a type using a part of the dehumidification air flow rate for the purge air flow rate, since the dehumidification air flow rate is inevitably reduced if the purge air flow rate is reduced, it is preferable that: the regeneration fan rotation speed (controlled by the inverter control (インバータ)) and the opening degree of the damper provided in the purge flow path are controlled so that the purge air volume is proportional to the rotor rotation speed. The appropriate swept face wind speed corresponding to the appropriate rotor speed is calculated by equation (5) shown below.

Appropriate blowing surface wind speed is rated blowing surface wind speed multiplied by appropriate rotor speed/rated rotor speed

… formula (5)

Fig. 16 is a diagram showing a change in the process flow of the dehumidification system according to the present invention. In the table shown in fig. 16, the dehumidifying device shown in column a is configured such that the flow direction of the purge air is the same as the flow direction of the dehumidifying air in the dehumidifying rotor 11, but the flow direction of the regeneration air is opposite to the flow direction, and the dehumidifying device shown in column B is configured such that the flow directions of the regeneration air and the purge air are opposite to the flow direction of the dehumidifying air in the dehumidifying rotor 11. The dehumidifier indicated in line 1 is where the air used in purging is merged with the air used in regeneration upstream of the regeneration fan 31 for regeneration. The dehumidification device indicated by row 2 is such that the air used in purging and the air used in regeneration are merged downstream of the regeneration fan 31 for regeneration. The dehumidification plant, line 3, is such that the air used in the purge is not used after it has been used in the regeneration. The dehumidifier shown in row 4 is used in regeneration after the air used in the purge is merged with the air obtained from the outside. However, the dehumidifier and the method for controlling the dehumidifier of the present invention may be applied to a dehumidifier having a process flow not shown in fig. 16.

Claims (8)

1. A dehumidifying device characterized by comprising:

a dehumidifying unit for dehumidifying the passing air,

a dividing part dividing the dehumidifying unit into: a dehumidification region for passing air to be dehumidified, dehumidifying the passed air, and setting a dew point of the passed air within a predetermined range; a regeneration area for regenerating a dehumidification capacity of the dehumidification unit by passing air after temperature adjustment; and a purge region for dissipating heat of the dehumidification unit using the passing air;

a zone changing unit configured to repeatedly allocate the dehumidification units in the order of the dehumidification zone, the regeneration zone, and the purge zone;

a temperature obtaining unit that obtains a temperature of the air to be dehumidified; and using the temperature of the air dehumidified by the dehumidification region;

an estimated humidity obtaining unit configured to obtain an estimated humidity of the air to be dehumidified corresponding to the temperature obtained by the temperature obtaining unit, based on a correspondence relationship between the temperature of the air to be dehumidified and the temperature of the air after dehumidification, which is prepared in advance, and the humidity of the air to be dehumidified; and

suitable operating condition obtaining means for obtaining the suitable operating condition corresponding to the estimated humidity obtained by the estimated humidity obtaining means, based on suitable operating condition information prepared in advance and indicating a relationship between a suitable operating condition for minimizing the amount of heat required for regeneration by the dehumidifying means while maintaining the dew point of the dehumidified air within the predetermined range,

controlling said dehumidifying means according to said suitable operating conditions.

2. A dehumidifying device as claimed in claim 1,

the dehumidifying unit is a dehumidifying rotor which is repeatedly distributed in the order of the dehumidifying zone, the regenerating zone and the purging zone by rotating the dehumidifying rotor at a set number of revolutions per unit time,

the appropriate operating condition obtaining means obtains the appropriate rotor rotational speed corresponding to the estimated humidity from the appropriate operating condition information indicating the relationship between the appropriate rotor rotational speed and the humidity of the air to be dehumidified of the dehumidifying apparatus, the appropriate rotor rotational speed minimizing the amount of heat required for regeneration of the dehumidifying rotor in a state where the dew point of the dehumidified air is maintained within the predetermined range,

the region changing means repeatedly allocates the desiccant rotors in the order of the desiccant region, the regeneration region, and the purge region by rotating the desiccant rotors at the obtained appropriate rotor rotation speed.

3. The dehumidifier according to claim 2, wherein a purge air volume as an air volume of the air introduced into the purge region is controlled to vary in proportion to the rotation speed of the rotor.

4. The dehumidifier according to any one of claims 1 to 3, wherein the suitable operating condition obtaining means obtains the suitable operating condition corresponding to the estimated humidity and the dehumidification air volume obtained by the estimated humidity obtaining means, based on suitable operating condition information prepared in advance and indicating a relationship among the suitable operating condition, the humidity of the air to be dehumidified, and the dehumidification air volume that is the air volume of the air introduced into the dehumidification region.

5. The dehumidifying device according to claim 4, further comprising:

a differential pressure obtaining part obtaining a differential pressure between air before being introduced into the dehumidifying area and air after passing through the dehumidifying area; and

an estimated airflow rate obtaining unit configured to obtain an estimated dehumidification airflow rate of the air introduced into the dehumidification region corresponding to the differential pressure obtained by the differential pressure obtaining unit, based on a correspondence relationship between the differential pressure and the dehumidification airflow rate prepared in advance,

the appropriate operating condition obtaining means obtains the appropriate operating condition corresponding to the estimated humidity obtained by the estimated humidity obtaining means and the estimated dehumidification air volume obtained by the estimated air volume obtaining means.

6. A dehumidifying device as claimed in any one of claims 1 to 3,

adjusting the temperature of the air introduced into the regeneration zone using a regeneration heater so that the temperature of the air introduced into the regeneration zone becomes a set regeneration temperature,

the appropriate operating condition obtaining means obtains the appropriate regeneration temperature corresponding to the estimated humidity based on the appropriate operating condition information indicating the relationship between an appropriate regeneration temperature for minimizing the amount of heat required for regeneration by the dehumidifying means while maintaining the dew point of the dehumidified air within the predetermined range of temperature, and the humidity of the air to be dehumidified,

the regeneration heater adjusts the temperature of the air introduced into the regeneration zone such that the temperature of the air introduced into the regeneration zone is the appropriate regeneration temperature.

7. The dehumidifying device according to any one of claims 1 to 3, wherein the temperature obtaining means obtains the temperature of the air as the dehumidifying object; and a temperature of the dehumidified air in a dehumidification region near the regeneration region, among the dehumidified air.

8. A control method of a dehumidifying device is characterized in that,

the dehumidifying apparatus includes: a dividing member dividing a dehumidifying rotor for dehumidifying passing air into: a dehumidification region for passing air to be dehumidified, dehumidifying the passed air, and setting a dew point of the passed air within a predetermined range; a regeneration region for regenerating a dehumidifying capacity of the dehumidifying rotor by passing the temperature-adjusted air; and a purge region for dissipating heat of the dehumidifying rotor using passing air; and a zone changing means for repeatedly distributing the desiccant rotor in the order of the desiccant zone, the regeneration zone, and the purge zone by rotating the desiccant rotor at a set number of revolutions per unit time,

the control method of the dehumidifying device executes the following steps:

a temperature obtaining step of obtaining a temperature of the air as the dehumidification target; and using the temperature of the air dehumidified by the dehumidification region;

an estimated humidity obtaining step of obtaining an estimated humidity of the air to be dehumidified corresponding to the temperature obtained in the temperature obtaining step, based on a correspondence relationship between the temperature of the air to be dehumidified and the temperature of the air after dehumidification, which is prepared in advance, and the humidity of the air to be dehumidified;

an appropriate operating condition obtaining step of obtaining, based on appropriate operating condition information prepared in advance and indicating a relationship between an appropriate operating condition for minimizing the amount of heat required for regeneration of the dehumidifying rotor and the estimated humidity obtained in the estimated humidity obtaining step, the appropriate operating condition corresponding to the estimated humidity obtained in the estimated humidity obtaining step, the appropriate operating condition being maintained in a state in which the dew point of the dehumidified air is maintained within the predetermined range; and

and a control step of controlling at least one of the rotation speed of the dehumidifying rotor of the dehumidifier and the temperature of the regeneration air in accordance with the appropriate operating condition.