JP5570717B2 - Operation method of dry dehumidifier - Google Patents

Description

  The present invention relates to a method for operating a dry dehumidifier having an adsorption rotor.

  Several proposals have been made to improve the operating efficiency of a dry dehumidifier using an adsorption rotor. An energy-saving method that focuses on changes in the regeneration air volume, regeneration temperature, purge air volume, and rotor speed. As for, the following may be mentioned.

  First, there is an apparatus that measures the regeneration outlet temperature, controls the regeneration air volume so that the regeneration outlet temperature is constant, and controls the purge air volume so that the purge outlet temperature is constant (Patent Document 1). In this method, when the regeneration outlet temperature reaches a certain value, it is determined that regeneration is completed, and the regeneration air volume is controlled so that the regeneration completion state is always maintained.

  This will be described in more detail. FIG. 8 shows that the air passing area located on the end surface side along the rotation direction of the rotor 101 shown in FIG. 9 is divided into a dehumidifying area 101a, a regeneration area 101b, and a purge area 101c. The distribution of the outlet air temperature in the regeneration zone 101b and purge zone 101c of the rotor 101 is shown. The heat of the regeneration air is initially used to increase the temperature of the rotor (a to d in the figure), and then Used as heat of desorption of adsorbed moisture (de in the figure). And the characteristic that temperature rises further with completion | finish of a water | moisture-content desorption (ef in a figure) is shown. In view of such characteristics, when controlling the regeneration air volume based on the regeneration temperature, conventionally, as shown in FIG. 9, for example, the coordinate θ (= position angle θ) in the rotation direction of the rotor 101 in the regeneration zone 101b is 50 °. A temperature sensor 102 is installed around the position, and the regeneration air volume is controlled so that the temperature at this position is constant.

  In addition, there has also been proposed one that detects the regeneration outlet air temperature and controls the capacity of a heater that heats the regeneration air so that the regeneration outlet air temperature becomes constant (Patent Document 2). This is intended to achieve an energy saving effect by lowering the regeneration air temperature.

JP-A-11-523 JP 2003-24737 A

  The prior art described in Patent Document 1 has been made on the basis of the knowledge that the dehumidifying ability does not change even if the air volume in the regeneration area with respect to the dehumidifying area is set to 0.2 times to less than 0.4 times. Based on this, it is possible to operate by setting the air volume in the regeneration zone to be 0.2 to less than 0.4 times. As a result, a more compact system is sufficient, and the energy, fan, and multistage required for regeneration and purge are sufficient. By reducing the energy required for processing in the first-stage dehumidifier when connected to, a large energy saving effect as a whole can be obtained. However, due to the nature of the invention, it could not be used in a region where the ratio of the regenerated air volume to the treated air volume is less than 0.2 times.

  On the other hand, in the prior art described in Patent Document 2, since the dehumidification outlet air dew point is affected by the temperature and relative humidity of the regeneration air, the regeneration air temperature cannot be lowered in order to maintain the treatment outlet air dew point. There is. In particular, when the treatment outlet air dew point is a low dew point, there is a problem that it is difficult to lower the regeneration temperature and the energy saving effect is lowered.

  The present invention has been made in view of the above points, and is independent of the ratio of the regeneration air volume to the treatment air volume, and moreover, is less affected by the dew point at the dehumidification treatment outlet than in the prior art to control the regeneration air volume to dry and dry. The object is to improve the operating efficiency of the dehumidifier.

  According to the inventors' knowledge, it has been found that the regeneration efficiency of the rotor is poor in the winter when the humidity is lower than in the summer, and so far the aim is to improve the regeneration efficiency by changing the amount of regeneration air according to the load. Have been conducting experiments. As a result of such an experiment, it was found that when the regeneration air volume is lowered, the purge air is heated by the heat accumulation of the rotor in the purge area and the rotor is regenerated even if the regeneration is not completely completed in the regeneration area. . That is, it has been found that regeneration is possible while cooling the rotor even in the purge zone.

The present invention has been made by such inventors' research, and is a device for dehumidifying the processing air by passing the processing air through a rotatable rotor, and is located on the end face side of the rotor. The air passing area is divided into a dehumidifying area, a regeneration area, and a purge area, and each of these areas is arranged so that the purge area is located before the transition from the regeneration area to the dehumidifying area by the rotation of the rotor. In the dry dehumidifier , the outlet temperature is the highest among the points located on the regeneration zone side by dividing the purge zone in the middle in the circumferential direction with the purge air volume introduced into the purge zone constant. The purged air having no temperature distribution after passing through the purge zone so that the temperature of the exhaust gas is higher than the outlet temperature of the regeneration zone during the transition from the regeneration zone to the purge zone and equal to or higher than the regeneration completion temperature. of Based on the time, and controls the reproduction air volume to be introduced into the regeneration sector, it is to operate the dry down dehumidifier.

  In this type of dry dehumidifier equipped with a rotor having a dehumidifying zone, a regeneration zone and a purge zone, the outlet temperature of the regeneration zone and the purge zone during the regeneration of the rotor is the temperature as shown in FIG. The rotor that has changed and has just moved to the regeneration zone through the dehumidification zone is adsorbing more moisture on the exit side of the regeneration zone (= the entrance side of the dehumidification zone) The inlet side (= the outlet side of the dehumidifying zone) is in an unadsorbed dry state. In the first stage of regeneration, first, the temperature of the rotor in the dry region where moisture is not adsorbed on the inlet side is increased by the high-temperature, low-humidity regeneration air. At this stage, the air temperature at the outlet remains almost 12 ° C. (ab in the figure).

  Then, at a stage where the regeneration zone has moved slightly to the purge zone side, the high-temperature / low-humidity regeneration air that has flowed into the area where moisture is adsorbed moves through the rotor on the outlet side while heating the rotor and desorbing moisture. At this time, the temperature of the regenerated air decreases due to desorption heat (heat absorption when moisture is desorbed), and the relative humidity increases, resulting in a low-temperature, high-humidity air condition that cannot contribute to desorption (regeneration). Air and rotor are in an adsorption / desorption equilibrium / thermal equilibrium state). The air temperature in this equilibrium state is about 60 ° C. in the example of FIG. Until the desorption of the entire rotor area is nearing completion, the equilibrium state is maintained near the outlet of the regeneration zone, and the outlet temperature remains constant for a while. When the desorption is completed, the temperature of the outlet air rises from 60 ° C. to 140 ° C. (f in FIG. 8).

  In the present invention, the steps from a to e are the same as in the conventional operation. However, according to the present invention, the rotor is moved to the purge zone in the state of e to f immediately before the completion of desorption by controlling and restricting the regeneration air volume. The purpose is to control the transition. By controlling in this way, as described above, even if regeneration is not completely completed in the regeneration zone, the purge air is heated by the accumulated heat of the rotor in the purge zone to regenerate the rotor, and the rotor is also cooled in the purge zone. However, since it has been found that regeneration is possible, regeneration of the rotor is possible even when the point where the temperature of the outlet air rises from 60 ° C. to 140 ° C., for example, is in the purge zone.

  More specifically, in the rotor in the state e in FIG. 8, most of the region except for the vicinity of the outlet reaches, for example, 140 ° C. at which the regeneration completion temperature can be determined. Further, since the heat capacity per volume of the rotor is much larger than the heat capacity of air, the rotor in the state e is in a high temperature heat storage state. When low-temperature purge air is allowed to flow through this rotor, the purge air quickly rises to 140 ° C, and moisture is adsorbed by the high-temperature, low-humidity purge air for a while due to the heat storage effect of the rotor. The temperature is raised and desorbed as it continues to be fed into the area. The present invention utilizes such a phenomenon, and completes the temperature rise and desorption in the purge zone by utilizing the amount of heat stored in the rotor exiting the regeneration zone.

Therefore, the temperature at the point where the outlet temperature is the highest among the points located on the regeneration zone side by dividing the purge zone in the center in the center is the outlet of the regeneration zone at the time of transition from the regeneration zone to the purge zone. The dew point temperature of the air required for proper regeneration and dehumidification processing even if the regeneration air volume is reduced by controlling the regeneration air volume to be introduced into the regeneration zone so that it is higher than the temperature and equal to or higher than the regeneration completion temperature. It becomes possible.

In such a case, it is only necessary to control the regeneration air volume by detecting the outlet temperature in the purge area to directly detect the completion of regeneration. For example, a temperature sensor is installed at each predetermined position angle at the outlet of the purge area. Therefore, the temperature at the point where the outlet temperature is the highest among the points located on the regeneration zone side by dividing the purge zone into two in the circumferential direction is the outlet of the regeneration zone at the time of transition from the regeneration zone to the purge zone. The regeneration air volume may be controlled while looking at the measurement results of each temperature sensor so that the temperature is higher than the temperature and equal to or higher than the regeneration completion temperature. Depending on the rotor structure, the sensor for detecting the outlet temperature in the purge zone may be used. There may be restrictions on the installation.

  Therefore, as a result of intensive studies by the inventors, the temperature of the purged air (that is, the average temperature of the purge outlet air) with no temperature distribution after passing through the purge zone is regenerated when the purge air volume is constant. It was found that there is a correlation between the distribution of outlet temperatures in the regeneration zone and the purge zone as the air flow ratio changes.

  This will be described with reference to the drawing. In FIG. 1, the outlet air temperature at the rotation direction coordinate (position angle) for each regeneration air volume ratio in the regeneration zone and the purge zone is shown. When the regeneration air volume ratio α is reduced), the distribution curve of the outlet air temperature shifts to the right in the figure, and the outlet temperature at any point near the regeneration area in the purge area is the most purged in the regeneration area. It can be confirmed that there is a regeneration air volume ratio α that is higher than the exit temperature at the point closer to the area and at or above the regeneration completion temperature (for example, 130 ° C.). In the example of FIG. 1, α = 0.060.

When the relationship between the change in the regeneration air flow rate ratio shown in FIG. 1 and the temperature of the purged air in the state in which the temperature distribution disappears after passing through the purge zone is examined, as shown in FIG. It was confirmed that there is. Therefore, for example, a temperature sensor is installed at every predetermined position angle at the outlet of the purge area , so that the outlet temperature is the highest among the points located on the regeneration area side by dividing the purge area in the circumferential direction in two at the center. Control the regenerative air volume while observing the measurement results from each temperature sensor so that the temperature at the point is higher than the outlet temperature of the regeneration zone at the time of transition from the regeneration zone to the purge zone and above the completion temperature of the regeneration Even if not, the purge air volume is controlled based on the temperature of the purged air after passing through the purge zone and the temperature distribution disappears, so that the purge zone is divided into two at the center and positioned on the regeneration zone side. Of the points, the temperature of the point having the highest outlet temperature can be higher than the outlet temperature of the regeneration zone at the time of transition from the regeneration zone to the purge zone , and can be equal to or higher than the regeneration completion temperature.

  According to the present invention, the regeneration air volume is controlled based on the temperature of the purged air in the state in which the temperature distribution has disappeared after passing through the purge zone, so that the regeneration is completed. The ratio with respect to the air volume does not need to be particularly limited. Therefore, the present invention can be implemented even in a region where the ratio of the regenerated air volume to the processed air volume is less than 0.2 times. In addition, since the regenerative air volume is the target of control rather than the regenerative heater, the controllable range is wider than the conventional technology that controls the regenerative heater (that is, it is possible to cope with a lower dew point), and the operation is more efficient than conventional Can maintain energy saving effect. Moreover, since the saturated vapor pressure of the regenerative air is higher when the regeneration air volume is reduced and the regeneration temperature is kept higher than when the regeneration air volume is kept constant and the regeneration temperature is lowered, the regeneration vapor is higher in saturation air pressure. As described above, the present invention is more efficient in regeneration than the method of controlling the capacity of the heater for heating the regeneration air. Further, the energy consumed by the regeneration fan that supplies the regeneration air can also be saved as compared with the technique described in Patent Document 2.

  The regeneration completion temperature referred to in the present invention refers to a temperature at which regeneration can be determined to be completed, and differs depending on the moisture absorbent material accommodated in the rotor. In the case of a hygroscopic material used and its configuration, for example, 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, the temperature is 60 ° C. to 160 ° C. Yes (in the case of a so-called low temperature regeneration type zeolite rotor that has been recently marketed, it can be judged that regeneration is completed at about 60 ° C.)

When carrying out the present invention, for example, in a state where the purge air volume is constant, the temperature at the point where the outlet temperature is the highest among the points located on the regeneration zone side by dividing the purge zone in the center in the circumferential direction, A predetermined temperature of the purged air that is higher than the regeneration zone outlet temperature at the time of transition from the regeneration zone to the purge zone and that is equal to or higher than the regeneration completion temperature is obtained in advance, and the purged air is at the predetermined temperature. The regenerating air volume introduced into the regeneration area may be controlled so that

Speaking of the example of FIG. 1 above, when the regeneration air flow ratio α = 0.060 , the outlet temperature of the points located on the regeneration zone side by dividing the purge zone into two in the circumferential direction at the center. The temperature at the highest point is higher than the outlet temperature of the regeneration zone during the transition from the regeneration zone to the purge zone and higher than the regeneration completion temperature (for example, 130 ° C.). As shown in FIG. Since the temperature of the purged air when the air flow ratio α = 0.060 is about 58 ° C., a temperature sensor is installed in the flow path through which the purged air flows, and regeneration is performed so that the temperature sensor becomes 58 ° C. The air volume may be controlled.

  In the present invention, the post-purge air is air having no temperature distribution after passing through the purge zone. Such air is, for example, natural in the flow path after leaving the purge zone, for example, downstream of the duct. However, if the duct flow path to the downstream side becomes long, there may be a case where the average temperature of the air after passing through the purge zone to be measured due to heat loss from the duct cannot be measured accurately. Therefore, for example, the air after passing through the purge zone may be agitated, and the temperature after the agitation may be measured using the air after the agitation as the purged air.

  Such agitation may be performed by, for example, a damper, a propeller, a current plate, or an elbow provided in a duct through which air flows after passing through the purge zone.

  When the processing air volume to be dehumidified is changed, it is preferable to change the rotor rotation speed and the constant value of the purge air volume in proportion to the change. That is, when the rotor speed is reduced to, for example, half of the rating with the change in the processing air volume, the constant value of the purge air volume is also set to half. In the present invention, since the regeneration air volume is controlled by the temperature of the purged air, as a premise, the temperature distribution at the purge zone outlet needs to be constant even when the rotational speed of the rotor is changed. For this purpose, the total purge air volume (purge time × purge air volume) needs to be constant, and it is preferable to make the rotor rotational speed and the purge air volume proportional. By changing in proportion to this, the temperature distribution in the purge zone does not change. Therefore, even if the rotation speed and the purge air volume are changed, the regeneration air volume control assuming the distribution of the outlet temperature in the purge area is also affected. There is no.

  Such a method is effective for reducing the supply air volume when the human body load is low at night or on holidays, for example, in a system that supplies air after dehumidification treatment to a dry room that operates for 24 hours. Driving is possible. According to the inventors, for example, when the dehumidification treatment air volume is reduced to half of the rated value, when only the regeneration air volume is changed and when the regeneration air volume, the rotation speed, and the purge air volume are changed, It is estimated that the amount of heat can be reduced by 25%.

Furthermore, in the configuration in which a part of the processing air volume is used as the purge air volume, the purge air volume can be reduced, and therefore the ratio of the supply air volume per processing air volume can be increased. More specifically, according to the inventors' calculations,
(1) When the supply air volume is half of the rating (2) Compared with the case where the supply air volume is half the rating and the rotation speed and purge air volume are also half the rating, the supply air volume is halved and the purge air volume is changed. In the case of not (1), the ratio of (supply air volume / process air volume) is 0.82. On the other hand, in the case of (2) in which not only the supply air volume but also the rotation speed and purge air volume are halved, the ratio of (supply air volume / process air volume) is 0.9 as in the rated operation.

  Thus, in order to supply the same air volume to the target object, the process air volume is smaller when the rotational speed and the purge air volume are reduced. It is clear that when the same air volume is supplied, the smaller the processing air volume, the more energy is saved (reduction in conveyance power and reduction in the amount of regenerated heat).

  In controlling the amount of purge air passing through the purge zone to be a predetermined value, the dry dehumidifier is configured so that a part of the air after the dehumidification treatment that has passed through the dehumidification zone is introduced into the purge zone. When the air that has passed through the regeneration zone is mixed with the air that has passed through the regeneration zone, and a part of it is heated by a heater and introduced into the regeneration zone, control is performed so that the differential pressure at the inlet and outlet of the purge zone is constant. That's fine.

  The outlet dew point temperature of the dehumidified air is related to the relative humidity of the regeneration air, and when it is regenerated with air having a low relative humidity, air with a lower dew point can be obtained. Therefore, if the regeneration temperature is the same, the relative humidity of the regeneration air is low in winter or the like when the load is very low, and the air may have a dew point lower than the design standard. Even in the present invention, even when the regeneration air volume is reduced, it is conceivable that the treatment outlet air has a dew point lower than the design value because the relative humidity of the regeneration air is low when the load is extremely low. Therefore, it is possible to raise the dew point temperature at the dehumidification processing outlet by controlling the regeneration heater to lower the regeneration temperature itself and increasing the relative humidity of the regeneration air, as well as controlling the regeneration air volume.

  From this point of view, regeneration to be introduced into the regeneration area based on the dew point temperature on the outlet side of the dehumidification area, the dew point temperature of the target room to which the dehumidified air is supplied, or the dew point temperature of the return air returned from the target room to the dehumidification area It can be proposed to further control the heater that heats the air.

  By reducing both the regenerative air volume and the regenerative heater capacity at the time of low load, regeneration is performed in order to secure the dew point temperature of the supply air, which is seen in the capacity control of the regenerative heater according to the conventional processing load. It is possible to solve the problem that the output of the heater cannot be sufficiently reduced and the energy saving effect is low.

  According to the present invention, it is possible to improve the operation efficiency of the dry dehumidifier regardless of the ratio of the regeneration air volume to the processing air volume and without being affected by the dew point of the dehumidifying air outlet.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 3 shows an outline of a system of a dehumidification system using the dry dehumidifier 1 for carrying out the operation method according to the present embodiment, and this system is installed in a low dew point space (not shown). It is configured as a system that supplies low dew point air.

  As shown in FIGS. 4 and 5, the dry-type dehumidifying apparatus 1 that forms the core of the system has a configuration in which segmented cassettes 12 and 13 are disposed on both end faces of a rotating rotor 11. On the end surface of the rotor 11, the air is divided into three air passage areas, a dehumidification area 11a, a regeneration area 11b, and a purge area 11c, in the order of the rotation direction of the rotor 11 indicated by the arrows in FIGS. A dehumidifying 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 face of the section dividing cassette 12 corresponding to each section. A dehumidification outlet, a regeneration inlet, and a purge inlet are also formed on the outer end face of the zone division cassette 13 corresponding to the three zones (all not shown). In the rotor 11 of the dry dehumidifier 10, a hygroscopic material such as lithium chloride, silica gel, or zeolite is accommodated.

  The three passing areas, the dehumidifying area 11a, the regeneration area 11b, and the purge area 11c, are each in the form of one of the radially formed sections, that is, substantially fan-shaped, and the central angle θ of each passing area is In this embodiment, the central angle θ1 of the dehumidifying zone 11a is set to 270 °, the central angle θ2 of the regeneration zone 11b is set to 60 °, and the central angle θ3 of the purge zone 11c is set to 30 °.

The processing air to be dehumidified is introduced through the processing duct 22 by the processing fan 21, cooled by, for example, the precooler 23, and then introduced into the dehumidifying area 11 a of the rotor 11. Then, the air that has been dehumidified in the dehumidification zone 11 a and has a low dew point, for example, an absolute humidity of 6.7 × 10 ⁻³ g / kg, is led out from the rotor 11 as supply air through the supply duct 24. Thereafter, for example, after necessary temperature adjustment, the air is supplied to the low dew point space as supply air.

  A portion of the air that has been dehumidified in the dehumidification zone 11a and has a low dew point is introduced into the purge zone 11c through the purge introduction duct 25 branched from the supply duct 24, and the air that has left the purge zone 11c is purged. It is sent to the outlet duct 26. The purge outlet duct 26 is connected to a regeneration exhaust duct 27 through which air after exiting the regeneration zone 11b flows, and the air exiting the purge zone 11c is mixed with the air exiting the regeneration zone 11b.

  The air in the regeneration exhaust duct 27 is exhausted to the outside by the regeneration fan 31. A regeneration introduction duct 32 is connected between the purge outlet duct 26 in the regeneration exhaust duct 27 and the exhaust outlet. Has been. A regeneration heater 33 is provided in the regeneration introduction duct 32, and the air in the regeneration introduction duct 32 heated to, for example, 140 ° C. by the regeneration heater 33 is regenerated air as the regeneration zone 11b of the rotor 11. Supplied to.

  Next, the main damper of this system will be described. First, a supply damper D1 is provided downstream of the branch point of the purge introduction duct 25 in the supply duct 24, and an introduction damper D2 is provided in the purge introduction duct 25. It has been. An exhaust damper D3 is provided on the downstream side of the regeneration fan 31 downstream of the connection point of the regeneration exhaust duct 27 with the regeneration introduction duct 32. The regeneration introduction duct 32 is provided with a regeneration circulation damper D4.

  Next, the control system will be described. As shown in FIGS. 3 and 4, a temperature sensor 41 for detecting the temperature of the purged air flowing in the purge outlet duct 26 is installed on the downstream side of the purge outlet duct 26. ing. A signal of the purged air temperature detected by the temperature sensor 41 is input to the control unit CU. As shown in FIG. 3, the control unit CU controls the regeneration air volume by controlling the regeneration fan 31 or the regeneration circulation damper D4 based on the temperature of the purged air detected by the temperature sensor 41. The control of the regeneration fan 31 is inverter control.

  In the present embodiment, the temperature sensor 41 is installed on the downstream side of the purge outlet duct 26. On the upstream side of the purge outlet duct 26, for example, a stirring function such as a damper, a propeller, a current plate, and an elbow is provided. Members may be provided, and the temperature sensor 41 may be installed so as to detect the air flowing through the purge outlet duct 26 on the downstream side of these members. In such a case, even if the temperature sensor 41 is installed on the upstream side of the purge outlet duct 26, the temperature of the purged air can be accurately detected.

  Further, as shown in FIG. 3, the control unit CU controls both the regeneration fan 31 and the regeneration circulation damper D4 based on the temperature of the purged air detected by the temperature sensor 41 to set the purge air amount to a predetermined value. Control to keep at.

  The differential pressure signal at the inlet / outlet of the purge zone 11c detected by the differential pressure gauge 51 that detects the differential pressure at the inlet / outlet of the purge zone 11c of the rotor 11 is input to the control unit CU as shown in FIG. The control unit CU can control the exhaust damper D3 based on the differential pressure at the inlet / outlet of the purge section 11c.

  As shown in FIG. 3, the air after the dehumidification process upstream of the branch point of the supply duct 24 with the purge introduction duct 25 is detected by the dew point sensor 61, and after the dehumidification process detected by the dew point sensor 61. The dew point temperature of the air is input to the control unit CU. The control unit CU can control the capacity of the regenerative heater 33 based on the dew point temperature of the air after the dehumidification process.

  As shown in FIG. 3, the differential pressure signal at the entrance / exit of the dehumidifying zone 11a detected by the differential pressure gauge 71 that detects the differential pressure at the entrance / exit of the dehumidifying zone 11a is, as shown in FIG. Is input. The control unit CU can control the drive unit 72 that rotates the rotor 11 and the purge air volume based on the differential pressure at the inlet / outlet of the dehumidifying zone 11a. For example, when the signal of the differential pressure gauge 71 provided for detecting the processing air volume is halved from 300 Pa to 150 Pa, the rotation speed is reduced by halving the output of the inverter of the drive device 72 that controls the rotation speed of the rotor 11. Lower. At the same time, the setting value of the differential pressure gauge 51 for detecting the purge air amount is changed from 300 Pa to 150 Pa, for example, so that the purge air amount is halved. In order to change the purge air volume at this time, the purge differential pressure is controlled to be constant by the inverter of the regeneration fan 31 and / or the exhaust damper D3.

The dehumidification system having the dry dehumidifier 1 has the above-described configuration, and an operation example thereof will be described next. As described with reference to FIGS. 1 and 2, for example, when the regeneration air flow ratio α = 0.060, the outlet temperature at the point near the regeneration zone in the purge zone is the outlet at the point closest to the purge zone in the regeneration zone. The temperature sensor 41 is obtained in advance that the temperature of the purged air is about 60 ° C. when the temperature is higher than the temperature and is equal to or higher than the regeneration completion temperature (for example, 130 ° C.) and the regeneration air volume ratio α = 0.060. The control unit CU controls the regeneration fan 31 or the regeneration circulation damper D4 to control the regeneration air volume so that the temperature detected by the above is 60 ° C. The regeneration air volume ratio α is represented by the regeneration area passing air volume (m ³ (N) min) / dehumidification area passing air volume (m ³ (N) min).

  As a result, the temperature distribution of the rotation direction coordinate θ of each outlet temperature of the regeneration zone 11b and the purge zone 11c of the rotor 11 is, for example, immediately before the position angle θ = 70 °, the outlet temperature reaches a peak and the regeneration completion temperature. It can be regarded as about 120 ° C., and the temperature of the outlet in the region (H) near the dehumidification zone 11a in the purge zone 11c becomes 20 ° C. or less due to the temperature drop by the low temperature / low humidity purge air.

Therefore, it is possible to save energy required for regeneration as compared with the conventional case. More specifically, in comparison with the conventional technique shown in FIG. 9 , the amount (heat amount) of 140 ° C. at the position angle θ = 40-60 ° in the conventional technique is maintained at 60 ° C. It becomes possible to save energy by that much.

  When the processing air volume itself of the dehumidifying process is changed, it is preferable to change the predetermined number of rotations of the rotor 11 and the purge air volume in proportion to the change. This is because the present invention controls the regeneration air volume based on the outlet temperature of the purge zone 11c, so that the temperature distribution on the outlet side of the purge zone 11c must be kept constant even when the rotational speed of the rotor 11 changes. Because there is. Therefore, for example, when the processing air volume is changed from 10 CMM to 5 CMM, the rotational speed of the rotor 11 is halved from 4 RPH, for example, to 2 RPH, and at the same time, the predetermined value of the purge air volume is set to half (for example, 1 CMM → 0.5 CMM). ). According to the inventors' estimation, when the processing air volume is reduced to half of the rating, only the regeneration air volume is changed, and when the regeneration air volume, the rotation speed, and the purge air volume are simultaneously changed as in the present invention. It is considered that the amount of heat for regeneration can be reduced by 25%. Furthermore, since the purge air volume using a part of the processing air volume can be reduced, the ratio of the supply air volume per processing air volume can be increased. Actually, if the processing air volume changes, the absolute humidity of the processing air may change.Therefore, this is not exactly proportional, but the processing air volume is limited only if the absolute humidity of the processing air is the same. Proportional.

  In the present invention, the amount of regenerated air can be significantly reduced by controlling the amount of regenerated air based on the temperature of the air after purging. However, as described above, the relative humidity of the regenerated air is considerable in low load winter seasons and the like. In some cases, the air may have a dew point lower than the design standard. FIG. 6 shows such a phenomenon. For example, when the load is low, the humidity may be reduced by 10 ° C. lower than the design specification of −60 ° C. compared to the case of high load. In that case, the control unit CU controls the regeneration heater 33 based on the dew point temperature detected by the dew point sensor 61, and lowers the regeneration temperature (for example, as shown in FIG. By reducing the temperature to 120 ° C., it is possible to control the dew point temperature of the air after being dehumidified in the dehumidifying zone 11a, and to realize a dew point temperature of −60 ° C. of the design specification.

As a result of experiments conducted by the inventors, the fan, damper, and rotor speed were not controlled, but all were operated at a fixed rated value, and the regeneration air volume control and the control to make the purge air volume constant were performed. As a result of comparison with the embodiment of the present invention, it can be seen that according to the embodiment of the present invention, about half the regeneration air volume is sufficient in the summer, and about one third of the regeneration air volume is necessary in the winter, It was confirmed that the energy saving effect of the present invention was high.

  The present invention is useful for a dry dehumidifier having a so-called rotor, and can also be applied to a dry dehumidifier having a multistage connection of rotors.

It is a graph which shows the exit temperature in each position angle of a regeneration zone and a purge zone when changing the regeneration air volume ratio explaining the principle of the present invention. It is a graph which shows the relationship between the regeneration air volume ratio and the temperature of the air after purge. It is explanatory drawing which showed typically the outline of the system | strain of the dry-type dehumidification apparatus for enforcing the operating method concerning embodiment. It is a perspective view of the rotor used for the dry-type dehumidifier of FIG. It is an end view of the axial direction of the rotor used for the dry-type dehumidifier of FIG. It is a graph which shows the heat processing heat quantity of the prior art with respect to the process inlet absolute humidity of the winter season with respect to the summer, and this invention. It is a graph of the calculation result and experiment result which show the supply dew point temperature with respect to the reproduction | regeneration air volume ratio at the time of low load and high load. It is a graph which shows the exit temperature in each position angle of a regeneration zone and a purge zone when the driving | operation method concerning a prior art is implemented. It is an end view of the axial direction of the rotor concerning a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Dry type dehumidifier 11 Rotor 11a Humidification area 11b Regeneration area 11c Purge area 12, 13 Area division cassette 21 Processing fan 22 Processing duct 23 Precooler 24 Supply duct 25 Purge introduction duct 26 Purge derivation duct 27 Regenerative exhaust duct 27
31 regeneration fan 32 regeneration introduction duct 33 regeneration heater 41, 81 temperature sensor 51, 71 differential pressure gauge 61 dew point sensor 72 drive unit CU control unit D1 supply damper D2 introduction damper D3 exhaust damper D4 regeneration circulation damper

Claims (6)

An apparatus for dehumidifying the processing air by passing the processing air through a rotatable rotor, wherein the air passing area located on the end face side of the rotor is divided into a dehumidifying area, a regeneration area, and a purge area. In a dry dehumidifying device that is partitioned and arranged so that the purge zone is located before moving from the regeneration zone to the dehumidifying zone by rotation of the rotor,
The temperature at the point where the outlet temperature is the highest among the points located on the regeneration zone side by dividing the purge zone into two in the center in the circumferential direction with the purge air volume introduced into the purge zone constant .
Higher than the outlet temperature of the regeneration zone during the transition from the regeneration zone to the purge zone ,
And so that it is above the regeneration completion temperature,
A method of operating a dry dehumidifier characterized by controlling the amount of regeneration air to be introduced into the regeneration zone based on the temperature of the purged air having no temperature distribution after passing through the purge zone. With the purge air flow constant, the purge zone is divided into two at the center in the circumferential direction, and the temperature at the highest outlet temperature of the points located on the regeneration zone side is transferred from the regeneration zone to the purge zone. A predetermined temperature of the purged air that is higher than the outlet temperature of the regeneration zone and at or above the regeneration completion temperature is determined in advance, and is introduced into the regeneration zone so that the purged air reaches the predetermined temperature. The method of operating a dry dehumidifier according to claim 1, wherein the amount of regenerated air to be controlled is controlled. The method of operating a dry dehumidifier according to claim 1 or 2, wherein the air after passing through the purge zone is stirred, and the temperature of the air after stirring is set as the temperature of the air after purge. The dry dehumidification according to any one of claims 1 to 3, wherein the agitation is performed by a damper, a propeller, a baffle plate or an elbow provided in a duct through which air flows after passing through a purge section. How to operate the device. 5. When the dehumidification treatment air volume is changed, the value of the rotor rotation speed and the constant purge air volume are changed in proportion to the change. Operation method of dry dehumidifier. Heating the regeneration air to be introduced into the regeneration zone based on the dew point temperature on the outlet side of the dehumidification zone, the dew point temperature of the target room to which the dehumidified air is supplied, or the dew point temperature of the return air returned from the target room to the dehumidification zone The operation method of the dry dehumidifier according to any one of claims 1 to 5, wherein the heater is controlled.

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