JPH11523A - Operating method of dry dehumidifier and dry dehumidifier - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable to dehumidify a larger volume of wind than heretofore even with a same sized rotor and to save energy by setting a ratio of a passing wind volume through a regeneration region against a dehumidifying area at a specific ratio and operating the device. SOLUTION: Air dehumidified at a dehumidifying region 5a of a first stage dry type dehumidifier 5, is further cooled and dehumidified at a pre-cooler 8, then being more dehumidified at a dehumidifying region 11a of a second stage dry type dehumidifier 10, and then the temperature is adjusted with a heater 21 and an after-cooler 22 to be fed to a low dew point space R. Ventilated air RA2 from the space R is introduced into a purge region 11C of a rotor 11 of the dry type dehumidifier 10, and on the other hand, the air heated with a regeneration heater 28 is introduced into the regeneration region 11b of the rotor 11. In this case, a ratio of the dehumidified region 11a positioned at the edge surface of the rotor 11 against the regeneration region 11b is 9:2, thus a passing volume of the regeneration air passing through the regeneration region 11b is 2/9 of the dehumidified air, namely 0.22 time.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for operating a dry dehumidifier and a dry dehumidifier characterized by a ratio of an area of an air passage area located on an end face of a rotor.

[0002]

2. Description of the Related Art There is a cooling and dehumidifying method as a commonly used method for dehumidifying air. In the cooling and dehumidifying method, the dew point is -5.degree.
Only the above air can be formed, and it cannot cope with a low dew point (−50 ° C. or less). Therefore, a dry dehumidifier using a rotary rotor is used as an air conditioner for supplying such low dew point air. The dry dehumidifier has a honeycomb-shaped rotor impregnated with an absorbing liquid such as lithium chloride or calcium chloride, or a rotor composed of an adsorbent such as silica gel or zeolite, and the air passage area located on the end face of the rotor. Is divided into a dehumidifying area and a regenerating area, and while processing air is passed through the dehumidifying area while rotating the rotor to produce dry air, and high-temperature regenerating air is passed through the regenerating area, the absorption liquid and the adsorbent are absorbed. It is configured so that the moisture in the material is evaporated into the regeneration air to perform the dehumidification process continuously.

In this case, if the rotor moves to the dehumidification zone while the temperature is high, the dew point rises because the processing air passes through the rotor without dehumidification. A purge area for cooling the rotor by passing air through the air may be set between the regeneration area and the dehumidification area. In particular, a two-stage dry dehumidifier system is connected in series, and the air dehumidified by the first stage dehumidifier is further dehumidified by the second stage dehumidifier. Such a purge zone is often set on the rotor end face of the second-stage dry dehumidifier in the dehumidification system.

The rotor used in this type of conventional dry dehumidifier will be described with reference to the drawings. As shown in FIGS.
Chambers 102 and 103 are arranged on both end surfaces of the first chamber 1. The end face of the rotor 101 is radially divided into three air passage areas of a dehumidification area 101a, a regeneration area 101b, and a purge area 101c in the order of rotation of the rotor 101 shown by the arrow in FIG. Further, a dehumidification inlet 102a, a regeneration outlet 102b, and a purge outlet 102c for connecting to a duct or the like are formed on the outer end surface of the chamber 102 corresponding to each of these sections. The chamber 10
A dehumidification outlet, a regeneration inlet, and a purge inlet are also formed on the outer end face of each of the three sections corresponding to the three sections (all are not shown).

[0005] The division ratio of the dehumidifying zone 101a, the regeneration zone 101b, and the purge zone 101c, which are the three passing zones of the rotor 101, is represented by the central angle θ when radially formed. Central angle θ1 of 101a
Is 225 °, the central angle θ2 of the reproduction area 101b is 90 °,
The central angle θ3 of the purge section 101c was set at 45 °. Further, the ratio of the amount of air passing through each zone is proportional to the area of the passing zone. The regeneration zone 101b is 0.4 times the dehumidification zone 101a, and the purge zone 101c is 0.2 times the half of the dehumidification zone 101a. Was. Such division ratios and air flow ratios are not determined on the basis of exceptional grounds, but are empirically set up until now.

[0006]

The dry dehumidifying apparatus 100 having such a configuration has a superior dehumidifying ability as compared with a general cooling and dehumidifying method, but is disadvantageous in that it consumes a lot of energy. . Such a dry dehumidifier is used, for example, in a low dew point space in a lithium-ion battery manufacturing plant. As is well known, this type of manufacturing plant operates for 24 hours. In fact, there is a strong demand for a reduction in energy.

[0007] The present invention has been made in view of such a point, the amount of heat required for the regeneration of the rotor, the amount of air passing through the regeneration area,
A dry type dehumidifier capable of reducing the amount of air passing through the purge area and consequently increasing the amount of processing in the dehumidifying area, so that even with a rotor of the same size, more air can be dehumidified than before. It is an object of the present invention to provide an operation method and a dry dehumidifier to respond to the above demand for energy saving.

[0008]

According to one aspect of the present invention, there is provided an apparatus for passing process air through a rotatable rotor to dehumidify the process air.
The air passage area located at the end face of the rotor is divided into a dehumidification area, a regeneration area, and a purge area so that the purge area is located before the transition from the regeneration area to the dehumidification area by rotation of the rotor. In the two-stage dry dehumidification system in which each of these zones is arranged, when the ratio Z of the flow rate of the passing air in the regeneration zone to the dehumidification zone is set to 1 in the dehumidification zone,
An operation method of a dry-type dehumidifier is provided, wherein the operation is performed so that 0.2 ≦ Z <0.4.

According to the inventor, the air volume of the regeneration zone with respect to the dehumidification zone is increased by a factor of 0.2 to less than 0.4 (preferably 0.2 to 0.4).
(0.25 times), it was found that the dehumidifying ability did not change at all. The air volume in the regeneration area is 0.2 times to 0.
To operate with a setting of less than four times means to reduce the regeneration air volume as compared with the conventional one, and at the same time, it is possible to increase the dehumidification processing air volume as compared to the conventional one. In other words, when performing the same amount of dehumidification processing as before, a more compact system is sufficient, and the energy required for regeneration and purging, the fan, and the processing in the first-stage dehumidifier when connected in multiple stages are required. The required energy is reduced, and a large energy saving effect is obtained as a whole.

According to a second aspect of the present invention, there is provided an apparatus for passing processing air through a rotatable rotor to dehumidify the processing air, wherein the passage area of the air located on the end face side of the rotor is reduced. A dry dehumidifier, which is divided into a wet section, a regeneration section, and a purge section, and wherein the respective sections are arranged such that the purge section is located before the transition from the regeneration section to the dehumidification section by rotation of the rotor, A method for operating a dry dehumidifier is provided, wherein the flow rate of the regeneration air is controlled so that the outlet temperature of the regeneration zone near the purge zone approaches a predetermined value.

In this case, when controlling the amount of the regenerated air, the blower for blowing air to the regenerated area is controlled by an inverter as described in claim 3, or connected to the regenerated area as described in claim 4. Such control can be easily performed by adjusting the opening degree of the damper interposed in the regeneration system to be performed.

Here, the predetermined temperature for approaching the outlet temperature near the purge section in the regeneration section, that is, the target temperature, is such that the flow rate of the regeneration air when the flow rate of the dehumidification section is 1 is 0.2 to 0 times. Less than 0.4 times (preferably 0.2 to 0.
25 times). Therefore, if the temperature is determined in advance and the regenerative air volume is controlled so as to approach the temperature, the regenerative air volume can be reduced as compared with the conventional case, as in the case of claim 1. , The energy required for processing by the fan and the first-stage dehumidifier can be reduced. Moreover, since the control is performed based on the temperature, there is no need to sequentially calculate the air volume ratio, and the control is easy.

According to a fifth aspect of the present invention, there is provided an apparatus for passing processing air through a rotatable rotor to dehumidify the processing air, wherein the passage area of the air located on the end face side of the rotor is reduced. A dry dehumidifier, which is divided into a wet section, a regeneration section, and a purge section, and wherein the respective sections are arranged such that the purge section is located before the transition from the regeneration section to the dehumidification section by rotation of the rotor, An operation of the dry dehumidifier, wherein the ratio Z of the flow rate of air in the purge zone to the dehumidification zone is set to 0.1 ≦ Z <0.2 when the dehumidification zone is set to 1. A method is provided.

Conventionally, the dehumidification air volume is 1, the regeneration air volume is 0.4
On the other hand, the purge air volume is set to 0.2, but the purge air volume is reduced with the reduction of the regeneration air volume. That is, since the purging is performed to cool the rotor heated in the regeneration, the purge air volume can be reduced as the regeneration air volume decreases. Since the purge air volume is used only for cooling the rotor, the purge air volume can be smaller than the regeneration air volume. This is because regeneration uses heat for both heating the rotor and evaporating moisture. Therefore, as the air volume ratio, a purge air volume of 1/2 of the regeneration air volume is sufficient. Therefore, the purge air volume can be reduced along with the reduction of the regeneration air volume, and as a result, the energy saving effect can be improved as compared with the conventional case.

According to a sixth aspect of the present invention, there is provided an apparatus for passing processing air through a rotatable rotor to dehumidify the processing air, wherein the passage area of the air located on the end face side of the rotor is reduced. A dry dehumidifier, which is divided into a wet section, a regeneration section, and a purge section, and wherein the respective sections are arranged such that the purge section is located before the transition from the regeneration section to the dehumidification section by rotation of the rotor, An operation method of a dry dehumidifier is provided, wherein the flow rate of the purge air is controlled so that the outlet temperature of the purge zone near the dehumidification zone approaches a predetermined value. The predetermined temperature in such an operation method means that the flow rate of the purge air when the flow rate in the dehumidification zone is 1 is 0.1 to less than 0.2 times (preferably 0.1 to 0.15 times). ). Therefore, also in this case, the temperature is determined in advance,
Thereafter, if the regenerated air volume is controlled so as to approach this temperature, the required energy can be reduced. Moreover, since the control is performed based on the temperature, there is no need to sequentially calculate the air volume ratio, and the control is easy.

In controlling the amount of purge air, the blower for blowing air to the purge area is controlled by an inverter as described in claim 7, or the purge air connected to the purge area is controlled as described in claim 8. It can be proposed to adjust the opening of a damper interposed in the system.

According to a ninth aspect of the present invention, there is provided an apparatus for passing process air through a rotatable rotor to dehumidify the process air, wherein a passage area of the air located at an end face of the rotor is:
In a dry dehumidifier, which is divided into a dehumidification section, a regeneration section, and a purge section, and these sections are arranged so that the purge section is located before the transition from the regeneration section to the dehumidification section by rotation of the rotor, A dry dehumidification apparatus is provided, wherein the ratio of the area of the dehumidification zone located on the end face side of the rotor to the other zone (regeneration zone + purge zone) is 3: 1.

Since the area ratio between the dehumidifying zone and the other zone (regeneration zone + purge zone) is changed as described above, more dehumidifying processes can be performed than in a conventional dry dehumidifier of the same type. Therefore, to dehumidify the same amount of air as before,
As a result, a more compact system is sufficient and the energy required for regeneration and purging can be saved, and the rating of the fan and the first-stage dehumidifier can be smaller than before.
A large energy saving effect is obtained as a whole.

The ratio between the area of the regeneration zone and the area of the purge zone may be set to 2: 1 as described in claim 10, and if the ratio is set to 1: 1 as described in claim 11, lower rotation speed is obtained. It is possible to deal with the use in.

[0020]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 schematically shows a system of a two-stage dry dehumidification system using the dry dehumidifier according to the present embodiment. The two-stage dry dehumidification system includes a low dew point air in a low dew point space R. It is configured as a system for supplying.

The introduced outside air OA is guided by the outside air intake duct 1 and cooled and dehumidified by the outside air processing cooler 2. The cooled and dehumidified air is then mixed with the regeneration surplus air cooled by the regeneration surplus air cooling cooler 3 and introduced into the dehumidification area 5a of the first-stage dry dehumidifier 5 by the outside air processing fan 4, For example, the humidity is reduced to a dew point temperature of −10 ° C. Since the rotor (not shown) in the first-stage dry dehumidifier 5 has a high dew point temperature for processing, the passage area of the air divided into the dehumidifying section 5a and the regeneration section 5b is divided by the rotor end face. This is the type that you have on the side. The thickness of the rotor is 200 mm, and the dehumidification area 5a and the regeneration area 5b
Is 3: 1.

After that, the air that has passed through the dehumidifying section 5a of the first-stage dry dehumidifier 5 and has been treated with the outside air is supplied to the low dew point space R
Return air RA1 returned from the air return duct 6
And sent to the precooler 8 by the processing fan 7. After the processing air is cooled by the precooler 8, the second-stage dry dehumidifier 10 according to the present embodiment is cooled.
Is introduced into the dehumidification area 11a of the rotor 11 for dehumidification processing.

The second-stage dry dehumidifier 10 is shown in FIGS.
As shown in (1), the rotating rotor 11 has a configuration in which chambers 12 and 13 are arranged on both end faces. Rotor 1
The end face 1 is divided into three air passage areas of a dehumidification area 11a, a regeneration area 11b, and a purge area 11c in the order of the rotation of the rotor 11 indicated by the arrow in FIG. A dehumidification inlet 12a, a regeneration outlet 12b, and a purge outlet 12c for connecting to a duct or the like are formed on the outer end surface of the chamber 12 corresponding to each of these sections. A dehumidification outlet, a regeneration inlet, and a purge inlet are also formed on the outer end surface of the chamber 13 corresponding to the three sections (all are not shown). The rotor 11 of the dry dehumidifier 10 contains a hygroscopic material such as lithium chloride, silica gel, and zeolite.

A dehumidification area 11 which is the three passage areas.
a, the regeneration zone 11b, and the purge zone 11c are each one of radially sectioned shapes, that is, substantially fan-shaped, and the central angle θ of each passage zone is the dehumidification zone 11a
Are set at 270 °, the center angle θ2 of the regeneration section 11b is set at 60 °, and the center angle θ3 of the purge section 11c is set at 30 °. Therefore, the area ratio of each passage area is
9: 2: 1, and the area ratio between the dehumidification area 11a and the other areas (regeneration area 11b + purge area 11c) is 3: 3.
It is 1. The thickness of the rotor 11 is 400 mm. The rotation speed of the rotor 11 is 6 rotations / hour.

The air which has been dehumidified and has a low dew point in the dehumidifying section 11a of the rotor 11 of the dry dehumidifying apparatus 10 having the above-mentioned structure is adjusted to a predetermined temperature by the heater 21 and the aftercooler 22, and then supplied. The air SA is supplied to the low dew point space R.

Another part of the return air RA2 from the low dew point space R
Is purged through a purge system return air duct 23 and is supplied as purge air to the purge section 11c of the rotor 11 of the dry dehumidifier 10.
To cool the rotor 11.

The purge air that has passed through the purge section 11c of the rotor 11 is led to the regeneration system Z, where it is combined with the air in the regeneration circulation system P by the second stage regeneration fan 26 and mixed therewith. The air mixed in this way is
Most of this is sent to the second stage regeneration heater 28 through the regeneration system duct 27, and after being heated to, for example, 120 ° C. by the regeneration heater 28, is introduced into the regeneration section 11b of the rotor 11 of the dry dehumidifier 10. Because

A part of the air from the regeneration system Z passes through the first-stage regeneration heater 30 by the operation of the first-stage regeneration fan 29, and is heated to the regeneration zone 5b of the first-stage dry dehumidifier 5. It is introduced and used for regeneration of the rotor of the first-stage dry dehumidifier 5. Thereafter, the exhaust gas is exhausted out of the system as exhaust EA. On the other hand, the air of the remaining regeneration system Z that does not pass through the first stage regeneration heater 30 is passed through the regeneration excess air circulation duct 31 to the above-mentioned regeneration excess air cooling cooler 3.
After being cooled there, it is mixed with the introduced outside air OA and introduced into the dehumidifying section 5a of the first-stage dry dehumidifying device 5 to be dehumidified. That is, it is reused as a part of the processing air. D1 to D8 in FIG. 1 are dampers interposed in a duct for adjusting the air volume.

The two-stage dry dehumidification system using the dry dehumidifier 10 according to the present embodiment is configured as described above, and as described above, the dehydration of the first stage dry dehumidifier 5 is reduced. The air dehumidified in the wet area 5a is further cooled and dehumidified by the precooler 8, and then further dehumidified by the dehumidification area 11a of the second-stage dry dehumidifier 10, and then the heater 2
1. The temperature is adjusted by the aftercooler 22 and supplied to the low dew point space R. Return air RA from low dew point space R
2 is a purge area 11 of the rotor 11 of the dry dehumidifier 10.
c, while the air heated by the regeneration heater 28 is introduced into the regeneration section 11 b of the rotor 11.

In this case, the ratio of the dehumidifying zone 11a and the regeneration zone 11b located at the end face of the rotor 11 is 9: 2,
Therefore, the flow rate of the regeneration air passing through the regeneration section 11b is 9/2 of the air to be dehumidified, that is, 0.22.
According to an examination by the inventor, even if the passing air volume of the regeneration air is 0.22 times that of the air subjected to the dehumidification process, as shown in the graph of FIG. The required dew point temperature (−50 ° C.) can be supplied to the space R. Further, according to the graph, it can be confirmed that substantially the same dehumidifying ability is obtained even when the flow rate of the regeneration air is 0.25 times the air to be dehumidified. However, if it is about 0.15 times, the dew point temperature rises to about -47 ° C, which is not preferable. Therefore, as described in the present invention, if the air volume ratio is set to be more than 0.2 times, the required dew point temperature can be supplied to the low dew point space R. In the graph, the absolute humidity at the inlet of the processing air introduced into the dehumidification area is 1 g / kg '(dew point temperature-
20 ° C).

Although the dehumidifying capacity is equivalent to that of the conventional dry dehumidifier of this type, the end face of the rotor 11 of the dry dehumidifier 10 used in the present embodiment (FIG. 3) is different from that of the conventional dry dehumidifier. As is clear from comparison of the end face of the rotor 101 (FIG. 7) of the dry dehumidifier 100, the area of the dehumidifying section 11a of the dry dehumidifier 10 used in the present embodiment is 1.2 times as large as the conventional one. Area. In other words,
In the case where the rotors having the same diameter are used, this embodiment has the following advantages.
As a result, twice the amount of dehumidified air can be obtained. Reproduction area 1
The area of 1b is smaller than before, and the amount of regenerated air is smaller than before. Therefore, when the dehumidification process is performed with a predetermined air volume, the diameter of the rotor can be reduced in the present embodiment, and accordingly, the air volume of the regeneration air can be reduced as compared with the related art. Therefore, the energy required for the regeneration heater 28 can be saved. At the same time, since the amount of purge air can be reduced, the amount of introduced outside air OA can be reduced, and as a result, the size of the first-stage dry dehumidifier 5 can be reduced.
In addition, the rating of the fan used in the system need only be smaller than before. Therefore, it is possible to significantly save energy as a whole system as compared with the related art, and it is possible to reduce the size of equipment.

According to the two-stage dry dehumidification system using the dry dehumidification device 10 according to the present embodiment, a conventional two-stage dry dehumidification system of this kind, that is, a second-stage dry dehumidification device 10 is used. As compared with the system using the dry dehumidifier 100 shown in FIGS.
It was confirmed that the energy consumption could be reduced by about 30% in total.

The rotor 1 of the second-stage dry dehumidifier 10
The size of 1 is sufficient at 83% of that of the conventional type, and the same level of dehumidification processing is possible for the rotor of the first-stage dry dehumidifier 5 with the size of 2/3 of the conventional first-stage rotor. As described above, since equipment such as various heaters, coolers, and fans can be downsized, the cost of equipment can be significantly reduced. Therefore, both the initial cost and the running cost can be reduced.

Incidentally, the performance of this type of dry dehumidifier is also related to the rotation speed of the rotor. In other words, the higher the number of revolutions, the higher the dehumidifying ability increases, but if the number of revolutions is too high, the regenerative ability becomes insufficient, and the dehumidifying ability decreases. In particular, in the dry dehumidifier for low dew point installed in the second stage, if the rotation speed is increased, the cooling in the purge becomes insufficient, and the capacity decreases at a lower rotation speed compared to the normal dehumidification device. Tend to. In terms of calorific value, the higher the number of revolutions, the greater the amount of heat for heating the rotor itself (regeneration zone) and the amount of heat for cooling (purge zone and dehumidification zone), so that the heat quantity per dehumidification amount increases. Therefore, it is preferable that this type of dry dehumidifier for low dew point operates at a low rotation speed.

The dry dehumidifier 50 shown in FIG. 5 shows an example suitable for such a low rotation, for example, 4 revolutions / hour. The air of the dry dehumidifier 50 located on the end face of the rotor 51 of the dehumidifier 50 is shown. As in the case of the above-mentioned dry dehumidifier 10, the passage area is divided into three sections: a dehumidification section 51a, a regeneration section 51b, and a purge section 51c.
The central angle θ of each passing area is
The central angle θ1 of the dehumidification area 51a is 270 °, and the regeneration area 51
b is 45 °, and the central angle θ3 of the purge section 51c is 45 °.
Is set to 45 °. Therefore, the area ratio of each passage area is 6: 1: 1.

When the dry dehumidifier 50 is used in place of the dry dehumidifier 10, the capacity is slightly lower than that of the above embodiment, but the area of the regeneration section 51b is smaller than that of the dry dehumidifier 10. Is further reduced, the air volume and energy required for regeneration can be further reduced, and the overall energy consumption can be smaller than that of the system of the above embodiment.

By the way, the heat of the regeneration air passing through the high-temperature regeneration section is influenced by the heating of the rotor in the area near the dehumidification section, and the moisture in the middle of the area (closer to the purge section). Used for evaporation. Therefore, the outlet temperature distribution of the regeneration air has a low temperature on the dehumidification area side,
The temperature increases near the purge area. Such a temperature distribution has a small change on the dehumidification area side as the dehumidification load increases, but appears as a temperature decrease on the purge area side.

Therefore, the inventor pays attention to such distribution characteristics, and controls the amount of regeneration air or the amount of purge air using the outlet temperature of the regeneration zone near the purge zone or the exit temperature of the purge zone near the dehumidification zone. Thus, when the dehumidification load is small, it is possible to propose an invention aimed at reducing energy consumption of regeneration, which was conventionally input more than necessary, to save energy.

The conventional dry dehumidifier 10 shown in FIG.
According to the rotor 101 of FIG.
When viewed from the axial direction of the rotor 101, the lines a, b, which divide the reproduction area 101b located at the end face of the rotor 101 into five equal parts.
A temperature sensor (not shown) is located on the lines e and f that divide the purge area 101c into three equal parts on the lines c and d and near the end face of the rotor 101 (about 50 mm away from the end face of the rotor 101). ) And circles on each of the lines in FIG.
At the points indicated by the marks, when the air volume passing through the regeneration zone 101b is changed with respect to the air volume passing through the dehumidification zone 101a, each line a, b,
The temperature distribution at the measurement points on c, d, e, and f was examined.

As a result, characteristics as shown in the graph of FIG. 7 were obtained. In this graph, the term “optimal air volume” means that the air volume passing through the regeneration zone 101b with respect to the air volume passing through the dehumidifying zone 101a, ie, the air volume passing through the regeneration zone 101b, ie, the ratio of the regeneration air volume is 0.2. Means that the ratio is 0.4, and that the air volume is too small means that the ratio is 0.15.

According to this, in the reproduction section 101b, at the measurement point on the line d, the temperature is high when the dehumidification load is small, and the temperature is low when the dehumidification load is large. Therefore, the temperature (target temperature) at the time of the optimal air volume in d is obtained in advance, and the optimal air volume can be obtained by controlling the air volume to approach the target temperature.

Similarly, in the purge section 101c,
The temperature characteristics at the measurement point of the line f are lower in the order of the underflow, the optimal flow, and the overflow. Therefore, the temperature (target temperature) at the time of the optimal air flow at f is obtained in advance and the purge air flow is controlled so as to approach the target temperature, whereby the optimal purge air flow can be obtained.

As described above, if the regeneration outlet temperature and the purge outlet temperature measured by the temperature sensor installed at a predetermined location are controlled so as to approach the target temperature, the required operation can be performed without requiring an excessive air volume. Can be implemented.

The dry dehumidifier 60 shown in FIG. 8 is designed to save energy by controlling the outlet temperature to approach the target temperature. That is, similarly to the above-mentioned dry dehumidifier 10, the passage of air in the chamber 62 located on the end face side of the rotor 61 in the dry dehumidifier 60 is changed to the rotor 6.
In the order of one rotation, it is divided into three sections of a dehumidification section 61a, a regeneration section 61b, and a purge section 61c. However, the area ratio of each area is set to be the same as the area ratio in the conventional dry dehumidifier 100 shown in FIGS.

A temperature sensor 63 for detecting an outlet temperature of the regeneration air is provided at a position, for example, about 50 mm in the axial direction from the end face of the rotor 61 in the regeneration section 61b in the chamber 62 and near the purge section 61c. ing.

The dry dehumidifier 60 having such a configuration can be used in the two-stage dry dehumidifier system shown in FIG. 1 instead of the dry dehumidifier 10 according to the above embodiment. In such a case, the regeneration fan 26 is controlled by an inverter (for example, the regeneration fan 26 is controlled so that the temperature detected by the temperature sensor 63 approaches the previously determined target temperature (the temperature of the optimal air volume indicated by the line d in FIG. 7). Motor inverter control)
If the reproducing air volume is adjusted by controlling the opening degree of the damper D5 to adjust the reproducing air volume, an optimum reproducing air volume can be obtained. Therefore, it is possible to save heat energy and the like required for regeneration, and accordingly, the exhaust air volume,
Energy saving based on a reduction in the amount of outside air introduced can be achieved.
In addition, since such control is performed based on the temperature from the temperature sensor 63, the control is easy and the responsiveness is good. Since the creation of an excessive air volume is prevented, the energy saving effect is higher than before.

The dry dehumidifier 60 performs such control based on the outlet temperature of the regeneration air detected by the temperature sensor 63 provided in the regeneration section. As shown in FIG.
1c, a temperature sensor 64 for detecting an outlet temperature of the purge air is installed at a position near the dehumidification area 61a, and the outlet temperature of the purge air detected by the temperature sensor 64 is set to a value before the outlet temperature of the purge air obtained in advance. The purge air volume may be controlled so as to approach the delivery target temperature (the temperature of the optimal air volume on line f in FIG. 7). By doing so, the amount of purge air can be reduced as compared with the conventional case, and accordingly, the amount of exhaust air and the amount of outside air taken in can also be reduced.

In order to control the amount of purge air based on the temperature of the outlet of the purge air detected by the temperature sensor 64, the opening degree of the damper D4 is controlled by using the two-stage dry dehumidification system shown in FIG. Adjusting or inverter-controlling the purge fan 65 provided in the purge system (for example, inverter-controlling the motor of the purge fan 65)
It can be done by doing.

[0049]

According to the present invention, it is possible to reduce the energy required for operation as compared with conventional dry dehumidifiers of the same kind, and to make various equipment such as a blower compact. It is possible.

[Brief description of the drawings]

FIG. 1 is an explanatory view schematically showing a configuration of a two-stage dry dehumidification system according to an embodiment of the present invention.

FIG. 2 is a perspective view of a rotor portion of a second-stage dry dehumidifier used in the two-stage dry dehumidification system of FIG. 1;

FIG. 3 is a front view of the dry dehumidifier of FIG. 2 as viewed from an axial direction.

FIG. 4 is a graph showing a relationship between a ratio of a regeneration air volume to a dehumidification air volume of a dry dehumidification device and a dew point temperature of dehumidification area outlet air.

FIG. 5 is a front view of the rotor of another dry dehumidifier that can be used in the two-stage dry dehumidifier system of FIG. 1 as viewed from the axial direction of a rotor.

FIG. 6 is an explanatory diagram showing measurement points when measuring outlet temperatures in a regeneration zone and a purge zone in a dry dehumidifier.

FIG. 7 is a graph showing a relationship between outlet temperature and air flow in a regeneration zone and a purge zone in a dry dehumidifier.

FIG. 8 is an explanatory diagram showing a mounting position of a temperature sensor in a dry dehumidifier according to another embodiment.

FIG. 9 is a perspective view of a rotor portion of a second-stage dry dehumidifier used in a conventional two-stage dry dehumidification system.

10 is a front view of the dry dehumidifier of FIG. 9 as viewed from the axial direction.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Dry dehumidifier (1st stage) 10 Dry dehumidifier (2nd stage) 11 Rotor 11a Dehumidification area 11b Regeneration area 11c Purge area 12, 13 Chambers 14, 15 Temperature sensor D1-D8 Damper R Low dew point space

Claims (11)

[Claims] 1. An apparatus for passing process air through a rotatable rotor to dehumidify the process air, wherein an air passage area located on an end face side of the rotor has a dehumidification area, a regeneration area, A dry dehumidifier which is divided into a purge zone and each of these zones is arranged so that the purge zone is located before the transition from the regeneration zone to the dehumidification zone by rotation of the rotor; A dry air dehumidifying device, wherein the ratio Z of the passing air volume is set to 0.2 ≦ Z <0.4 when the dehumidification area is set to 1. 2. An apparatus for passing process air through a rotatable rotor to dehumidify the process air, wherein an air passage area located on an end face side of the rotor has a dehumidification area, a regeneration area, A dry dehumidifying device which is partitioned into a purge section and which is arranged such that the purge section is located before the transition from the regeneration section to the dehumidification section by rotation of the rotor; A method of operating a dry dehumidifier, characterized in that the flow rate of the regenerated air is controlled so that the outlet temperature of the dry dehumidifier approaches a predetermined value. 3. The method for operating a dry dehumidifier according to claim 2, wherein the amount of the regenerated air is controlled by inverter-controlling a blower for blowing air to the regenerating area. 4. The dry dehumidifier according to claim 2, wherein the flow rate of the regeneration air is controlled by adjusting the opening of a damper interposed in a regeneration system connected to the regeneration zone. how to drive. 5. An apparatus for passing process air through a rotatable rotor to dehumidify the process air, wherein an air passage area located on an end face side of the rotor has a dehumidification area, a regeneration area, A dry dehumidifier which is divided into a purge section and each of these sections is arranged such that the purge section is positioned before the transition from the regeneration section to the dehumidification section by rotation of the rotor; The ratio Z of the passing air volume of
A method for operating a dry-type dehumidifier, characterized in that when the dehumidification area is 1, the operation is performed while setting 0.1 ≦ Z <0.2. 6. An apparatus for passing process air through a rotatable rotor to dehumidify the process air, wherein an air passage area located on an end face side of the rotor has a dehumidification area, a regeneration area, A dry dehumidifier which is divided into a purge section and each of these sections is arranged such that the purge section is positioned before the transition from the regeneration section to the dehumidification section by rotation of the rotor; A method for operating a dry-type dehumidifier, characterized in that a flow rate of a purge air is controlled so that a temperature of an approaching outlet approaches a predetermined value. 7. The method for operating a dry dehumidifier according to claim 6, wherein the amount of purge air is controlled by inverter-controlling a blower for blowing air to the purge area. 8. The dry dehumidifier according to claim 6, wherein the amount of purge air is controlled by adjusting an opening of a damper interposed in a purge system connected to the purge section. how to drive. 9. An apparatus for passing process air through a rotatable rotor to dehumidify the process air, wherein an air passage area located at an end face of the rotor includes a dehumidifying area, a regeneration area, and a purging area. In a dry dehumidifier in which these sections are arranged so that the purge sections are located before the transition from the regeneration section to the dehumidification section by rotation of the rotor, the sections are located on the end face side of the rotor. A dry dehumidifier, wherein the ratio of the area of the dehumidified area to the area of the other area is 3: 1. 10. The dry dehumidifier according to claim 9, wherein the ratio of the area of the regeneration zone to the area of the purge zone is 2: 1. 11. The dry dehumidifier according to claim 9, wherein the ratio of the area of the regeneration zone to the area of the purge zone is 1: 1.