JP6442150B2 - Dry type dehumidifier and its operating method - Google Patents

Description

The present invention relates to a dry dehumidifier having an adsorption rotor and an operation method thereof .

  In recent years, lithium batteries for use in hybrid vehicles and electric vehicles have been developed, and the scale of mass production has been expanded in the lithium battery production factories, and large-scale factories are being constructed. However, a dry room used for producing a lithium battery consumes a lot of energy, and in particular, a dehumidifying device consumes a lot of energy.

  Thus, several dry energy-saving methods using a suction rotor to reduce the amount of heat for regeneration and improve the operation efficiency have been proposed. For example, Patent Document 1 discloses a dew point at the treatment outlet of a dehumidification rotor. A dry dehumidifier that controls the capacity of a regenerative heater according to temperature is disclosed. Further, as shown in Patent Documents 2 and 3, there is also disclosed a dry type dehumidifying device that improves the operation efficiency by controlling the regenerative air volume. Further, as shown in Patent Documents 4 and 5, there is also disclosed a dry type dehumidifying device that improves the operation efficiency by controlling the rotation speed of the adsorption rotor. Further, as shown in Patent Document 6, the dry type of measuring the temperature and humidity of the outside air as the processing air and controlling the refrigerant temperature of the cooling means for cooling the outside air based on the temperature and humidity to reduce the energy consumption. A dehumidifying device is also disclosed.

Japanese Patent No. 3266326 JP 2010-99652 A JP 2010-110636 A JP 2010-247040 A JP 2010-27041 A JP 2009-208001 A

  As shown in Patent Documents 1 to 6, conventionally, methods for improving the operation efficiency have been proposed. However, depending on the method of using the dry dehumidifier, a large amount of energy is used to adjust the temperature of the supply air. There was a case. For this reason, further improvement in operating efficiency has been desired for a dry dehumidifier using an adsorption rotor.

  In particular, the dehumidifying device of Patent Document 6 includes only a cooling coil. When the humidity of the outside air is low, such as in winter, the supply air cannot be reheated and supplied. That is, when the dew point temperature of the outside air is high, the amount of increase in temperature at the time of dehumidification increases, so it can be dealt with only by cooling. However, when the dew point temperature of the outside air is low, such as in winter, the temperature rise amount at the adsorption rotor is small (about 1 to 4 °), and it is necessary to reheat and supply the supply air. The dehumidifier of Document 6 could not reheat the supply air.

  The present invention has been made in view of such a point, and in a dry dehumidifier having both a cooling coil for cooling the processing air and a heater for heating the processing air, the operation efficiency is further improved than before. The purpose is to save energy.

  The adsorption rotor of the dry-type dehumidifying device has a higher dehumidifying capacity at a lower temperature. For this reason, outside air (process air) is cooled by a cooling coil (precooler) and supplied to the adsorption rotor at the dehumidifying inlet of the adsorption rotor. When the load of dehumidification is small, the air is supplied without being heated by the adsorption rotor so much, and then it is necessary to raise the temperature with a heater and supply the air. Especially in winter, this tendency appears strongly because the humidity of outside air is low.

  Therefore, in the present invention, when the load of dehumidification is small, the temperature of the outside air (process air) at the dehumidification inlet is raised to reduce the amount of heat of reheating in the heater. Specifically, the dew point temperature of the outside air (process air) at the dehumidification inlet is measured (or estimated), and the cooling capacity of the outside air (process air) at the dehumidification inlet is changed accordingly. Thereby, both the cooling energy in the cooling coil and the heating energy in the heater are reduced, and a large energy saving effect can be obtained. Further, the present invention does not require an increase in special equipment or the like, and energy saving can be achieved at low cost simply by adding a control function. The present invention has been made by such inventors' research.

According to the present invention, an apparatus for dehumidifying a processing air by passing the processing air through a rotatable adsorption rotor, wherein the air passing area located on the end face side of the adsorption rotor has a dehumidification area. These areas are arranged so that the purge area is located before moving from the regeneration area to the dehumidification area by the rotation of the adsorption rotor. In a dry dehumidifier equipped with a cooling coil for cooling the processing air and a heater for heating the processing air on the outlet side of the dehumidifying area,
Measure or estimate the dehumidifying inlet dew point temperature, which is the dew point temperature of the processing air entering the dehumidifying zone, and cool the processing air with the cooling coil and process with the heater based on the measured or estimated dehumidifying inlet dew point temperature. A control device capable of executing control for heating the air and rotor rotation speed control for controlling the rotation speed of the adsorption rotor. The control device is a low dew point air that is dehumidified and supplied to the low dew point space. When the temperature is equal to or higher than a predetermined temperature, control of cooling the processing air by the cooling coil and heating of the processing air by the heater is executed. When the temperature is lower than the predetermined temperature, the rotor rotation speed control is executed. A dry-type dehumidifying device is provided.
According to the present invention, there is provided a device for dehumidifying the processing air by passing the processing air through a rotatable adsorption rotor, wherein the air passage area located on the end face side of the adsorption rotor has a dehumidification treatment. 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 adsorption rotor. Is a dehumidifying inlet which is a dew point temperature of the processing air entering the dehumidifying area in a dry dehumidifying apparatus having a cooling coil for cooling the processing air and a heater for heating the processing air on the outlet side of the dehumidifying area Measures or estimates the dew point temperature, controls the cooling of the processing air by the cooling coil and the heating of the processing air by the heater, and controls the rotation speed of the adsorption rotor based on the measured or estimated dehumidification inlet dew point temperature You And a control device capable of performing rotor speed control, and the control device performs processing by the cooling coil when the temperature of the low dew point air supplied to the low dew point space after being dehumidified is equal to or higher than a predetermined temperature. Provided is a method for operating a dry dehumidifier, wherein control is performed to cool air and heat processing air by the heater, and if the temperature is lower than a predetermined temperature, the rotor rotational speed control is executed. Is done.

  In the present invention, the dehumidification inlet dew point temperature is first measured or estimated, and based on the measured or estimated dehumidification inlet dew point temperature, the dehumidification outlet dew point temperature that is the dew point temperature of the supply air from the dehumidification zone is obtained. . Then, it is determined whether or not the set value of the dehumidifying inlet temperature can be increased or increased from the dehumidified outlet dew point temperature, and when it is determined that the set value can be increased, the set value is increased, When the cooling energy of the heater is controlled to reduce the cooling energy of the heater and to reduce the heating energy of the heater, if the dehumidifying capacity of the adsorption rotor is sufficient, the cooling capacity of the processing air by the cooler is reduced and reduced accordingly. Increase the dehumidifying inlet temperature, which is the temperature of the process air entering the wet area. That is, for example, the dehumidifying inlet temperature is set to 12 ° C. in the summer, and the dehumidifying inlet temperature is set to 16 ° C. in the winter. Thereby, in winter when the humidity of the outside air is low, the cooling energy in the cooling coil can be reduced while maintaining a predetermined dehumidifying effect. Along with this, the heating energy in the heater can also be reduced. As described above, according to the present invention, the energy that has been wasted by cooling and reheating so far can be reduced, and energy saving can be achieved.

  When the temperature of the low dew point air that is dehumidified and supplied to the low dew point space is lower than a predetermined temperature, control related to both the cooling of the processing air by the cooling coil and the heating of the processing air by the heater is performed. You may make it stop and switch to the state which controls the rotation speed of an adsorption | suction rotor. In addition, when the temperature of the low dew point air exceeds a predetermined temperature, in addition to controlling the cooling of the processing air by the cooling coil and the heating of the processing air by the heater, the regeneration of the adsorption rotor is completed in the purge area. In this way, the regeneration air volume may be controlled.

According to the present invention, a large energy saving effect can be obtained by reducing energy that has been wasted by cooling and reheating so far. In the present invention, it is not necessary to increase the number of special devices and the like, and by adding a control function, the operation efficiency of the dry dehumidifier can be improved and energy can be saved at low cost. In addition, consumption of steam and the like used in the heating coil is reduced, and CO ₂ is reduced.

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 relationship between the dehumidification inlet temperature (degreeC) and the dehumidification inlet dew point temperature (degreeC DP) in case dehumidification exit dewpoint temperature is -55 degreeCDP. It is a graph which shows the exit temperature in each position angle of a regeneration zone and a purge zone when the operation method by regeneration air volume control is carried out. It is explanatory drawing which showed typically the outline of the system | strain of the dry-type dehumidification apparatus for implementing the driving | running method concerning embodiment which enabled switching of rotor rotation speed control. It is a graph which shows the relationship between suitable rotation speed and dehumidification zone entrance absolute humidity for every rotor rotation speed. It is a graph which shows the relationship between suitable regeneration temperature and dehumidification zone entrance absolute humidity for every regeneration temperature. It is explanatory drawing in the case of controlling the heating capability of a heating coil based on supply air temperature. It is explanatory drawing in the case of controlling the heating capability of a heating coil based on the room temperature of low dew point space. It is explanatory drawing in the case of switching the cooling capacity of a cooling coil with a cooling tower and a heat exchanger.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows an outline of a system of a dehumidifying system using a dry dehumidifying device 1 for carrying out the operating method according to the present embodiment, and this system is installed in a low dew point space (not shown). The system is configured to supply low dew point air SA.

  As shown in FIGS. 2 and 3, the dry dehumidifying device 1 that forms the core of the system has a configuration in which area dividing cassettes 12 and 13 are arranged on both end faces of a rotor 11 that rotates by driving of a motor 10. ing. The end surface of the rotor 11 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). A moisture absorbing material such as lithium chloride, silica gel, or zeolite is attached to the rotor 11 of the dry dehumidifier 1.

  Each of the three passage areas, the dehumidifying area 11a, the regeneration area 11b, and the purge area 11c, has one of the radially formed sections, that is, substantially fan-shaped. In this embodiment, the central angle θ of each passing zone is 270 ° for the dehumidifying zone 11a, 60 ° for the regeneration zone 11b, and 30 ° for the purge zone 11c. Is set.

  The outside air (process air) OA to be dehumidified is taken in through the process duct 22 by the process fan 21, cooled by the two cooling coils 23 and 24 (precooler), and then introduced into the dehumidified area 11a of the rotor 11. The Of these two cooling coils 23, 24, the upstream cooling coil 23 is an auxiliary cooling means. For example, when the outside air temperature is high, such as in summer, water is passed through the cooling coil 23. When the outside air temperature is low, such as in winter, on / off control is performed such that water flow to the cooling coil 23 is stopped. On the other hand, a flow rate control valve 26 is provided in the chilled water pipe 25 for passing cooling water through the cooling coil 24 on the downstream side, and the set value of cooling by the cooling coil 24 can be changed by controlling the amount of water flow. It is like that.

  In the processing duct 22, a return air duct 27 is connected between the two cooling coils 23 and 24 to join the air returned from the low dew point space (not shown). Part of the air discharged from the low dew point space (not shown) is mixed with the outside air (process air) OA through the return air duct 27.

And after the outside air OA is cooled by these cooling coils 23 and 24, the dehumidification treatment is performed in the dehumidifying zone 11a and the air having a low dew point, for example, an absolute humidity of 6.7 × 10 ⁻³ g / kg, It is led out from the rotor 11 as supply air through the supply duct 30. The supply duct 30 is provided with a heating coil 31 as a heater. The dehumidified air is then reheated by the heating coil 31 and the temperature is adjusted, and then the low dew point space SA (see FIG. Not shown).

  The heat source water pipe 32 for passing the heat source water through the heating coil 31 is provided with a flow rate control valve 33, and the heating capacity (reheat capacity) by the heating coil 31 can be changed by controlling the amount of water flow. It is like that.

  A portion of the air that has been dehumidified in the dehumidifying zone 11a and has a low dew point is introduced into the purge zone 11c through the purge introduction duct 35 branched from the supply duct 30, and the air that has left the purge zone 11c is purged. It is sent to the lead-out duct 36. The purge outlet duct 36 is connected to a regeneration exhaust duct 37 through which air after leaving the regeneration zone 11b flows, and the air leaving the purge zone 11c is mixed with the air after leaving the regeneration zone 11b.

  The air in the regeneration exhaust duct 37 is exhausted EA to the outside by the regeneration fan 40, but the regeneration introduction duct 41 is provided between the purge outlet duct 36 and the exhaust outlet in the regeneration exhaust duct 37. It is connected. The regeneration introduction duct 41 is provided with a regeneration heater 42. The air in the regeneration introduction duct 41 heated to, for example, 140 ° C. by the regeneration heater 42 is regenerated air to the regeneration zone 11 b of the rotor 11. Supplied with.

  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 35 in the supply duct 30, and an introduction damper D2 is provided in the purge introduction duct 35. It has been. An exhaust damper D3 is provided downstream of the connection point of the regeneration exhaust duct 37 with the regeneration introduction duct 41. The regeneration introduction duct 41 is provided with a regeneration circulation damper D4. Further, the processing duct 22 is provided with an outside air introduction damper D5.

  Next, the control system will be described. As shown in FIG. 1, on the inlet side of the dehumidifying zone 11a in the processing duct 22, the dehumidifying inlet temperature which is the temperature of the outside air OA just before being introduced into the dehumidifying zone 11a. A dehumidifying inlet dew point temperature sensor 45 for measuring the dehumidifying inlet dew point temperature sensor 45 for measuring the dehumidifying inlet dew point temperature which is the dew point temperature of the immediately preceding outside air OA is installed. A supply air temperature sensor 47 that measures the supply air temperature, which is the temperature of the low dew point air SA supplied to the low dew point space (not shown), is installed on the outlet side of the supply duct 30.

  As shown in FIGS. 1 to 3, a purge outlet temperature sensor 48 for detecting the outlet temperature of the purge air is installed at a location near the regeneration zone 11b in the purge zone 11c. As shown in FIG. 3, the purge outlet temperature sensor 48 is located at a point near the regeneration zone 11b in the purge zone 11c, more specifically, at the boundary between the dehumidification zone 11a and the regeneration zone 11b. When the angle θ = 0 ° and the position angle θ of the boundary between the purge area 11c and the dehumidifying area 11a = 90 °, the angle θ is set at about 65 °.

  The dehumidifying inlet temperature, the dehumidifying inlet dew point temperature, the supply air temperature, and the purge air outlet temperature detected by each of these temperature sensors 45 to 48 are input to the control unit CU. As shown in FIG. 1, the control unit CU opens and closes the flow control valve 26 provided in the chilled water pipe 25 based on the dehumidifying inlet temperature, the dehumidifying inlet dew point temperature, and the supply air temperature. While controlling cooling capacity, the flow control valve 33 provided in the heat-source water piping 32 is opened and closed, and the heating capability by the heating coil 31 is controlled. Further, as shown in FIG. 1, the control unit CU controls the regeneration air volume by controlling the regeneration fan 40 or the regeneration circulation damper D4 based on the purge air outlet temperature detected by the purge outlet temperature temperature sensor 48. To do. The control of the regeneration fan 40 is inverter control.

  Further, as shown in FIG. 1, the control unit CU controls both the regeneration fan 40 and the regeneration circulation damper D4 on the basis of the purge air outlet temperature detected by the purge outlet temperature temperature sensor 48, and the purge air volume. It is also possible to perform control to keep the value at a predetermined value.

  The dehumidifying system having the dry dehumidifying apparatus 1 according to the embodiment of the present invention has the above-described configuration, and an operation example thereof will now be described. FIG. 4 shows a dehumidification inlet temperature (° C.) and a dehumidification inlet dew point temperature (° C. DP) when the dew point temperature (dehumidification outlet dew point temperature) of air dehumidified in the dehumidification zone 11a is −55 ° C. DP. ). This relationship varies depending on the dehumidification outlet dew point temperature. The control unit CU stores in advance the relationship between the dehumidifying inlet dew point temperature (° C.) and the dehumidifying inlet dew point temperature (° C. DP) with respect to the dehumidifying outlet dew point temperature.

  For example, when the dehumidification outlet dew point temperature is −55 ° C. DP, in order to supply low dew point air SA reheated by the heating coil 31 and adjusted to 18 ° C. to a low dew point space (not shown), It is necessary to set the temperature of the air dehumidified in the wet area 11a (dehumidification outlet temperature) to 18 ° C. or lower. At that time, assuming that the dehumidifying inlet dew point temperature is -13.5 ° C. DP, the dehumidifying inlet temperature obtained from the relationship shown in FIG. 4 is 15.5 ° C. Therefore, in this example, the setting of the dehumidifying inlet temperature can be increased to a maximum of 15.5 ° C. That is, for example, in the case of this example, the dehumidifying inlet temperature is set to 12 ° C. in the summer, but in this case, the dehumidifying inlet temperature can be increased to a temperature higher than 12 ° C. (maximum 15.5 ° C.). it can.

  The control unit CU determines from the dehumidification inlet dew point temperature measured by the dehumidification inlet dew point temperature sensor 46 whether the set value of the dehumidification inlet temperature can be increased (whether it can be increased) or to what extent it can be increased. Find out how far you can go (up to 15.5 ° C). If it is determined that the set value can be increased, the set value of the dehumidifying inlet temperature is raised to a higher temperature within a range of 15.5 ° C. at the maximum. When the setting of the dehumidifying inlet temperature is changed to a higher temperature in this way, the control unit CU controls the flow rate control valve 26 provided in the chilled water pipe 25 so as to lower the cooling capacity by the cooling coil 24. (Cascade control). Thus, when the dehumidifying capacity of the adsorption rotor is sufficient, by reducing the cooling capacity of the processing air by the cooling coil 24 and increasing the dehumidifying inlet temperature, the predetermined dehumidifying is performed when the outside air humidity is low, such as in winter. The cooling energy in the cooling coil 24 can be reduced while maintaining the effect.

  Further, the heating energy in the heating coil 31 can be reduced as the cooling capacity of the processing air by the cooling coil 24 is lowered. That is, when the cooling capacity of the processing air by the cooling coil 24 is lowered, the dehumidification outlet temperature also rises. In such a case, the control unit CU controls the flow rate control valve 33 provided in the heat source water pipe 32 to adjust the heating capacity of the heating coil 31 to be lowered. Thus, when the cooling capacity of the cooling coil 24 is lowered, the heating energy in the heating coil 31 can also be reduced.

In this way, energy that has been wasted in the past by cooling and reheating can be reduced, and energy saving is achieved. In addition, since the consumption of steam and the like used in the heating coil 31 is reduced, CO ₂ is also reduced. Regardless of the set value of the dehumidifying inlet temperature, the correlation between the opening of the flow control valves 26 and 33 and the output of the electric heater or the like (heater) is obtained in advance from FIG. The cooling energy and the heating energy can be reduced by performing the lowering control.

  In the above description, the case where the dehumidifying inlet dew point temperature is −13.5 ° C. DP and the dehumidifying inlet temperature is 15.5 ° C. has been described as an example. Similarly, from the relationship shown in FIG. Is -10 ° C DP, the dehumidifying inlet temperature is 12 ° C, and dehumidifying inlet dew point is -18 ° C DP, the dehumidifying inlet temperature is 13.5 ° C.

  In addition, this dehumidification system can also implement so-called regeneration air volume control described below. FIG. 5 shows the position angle θ (coordinates) in the rotational direction of the rotor 11 of the dry dehumidifier 1 and the outlet temperatures in the regeneration zone 11b and the purge zone 11c.

  In this operation example, the rotor 11 immediately after moving to the regeneration zone 11b through the dehumidification zone 11a first adsorbs more moisture on the exit side of the regeneration zone 11b (= inlet side of the dehumidification zone 11a). In addition, the inlet side of the regeneration zone 11b (the outlet side of the dehumidifying zone 11a) is in a desorbed and dry state.

  In the initial stage (A to B) of regeneration, first, the temperature of the rotor 11 in the dry region where moisture on the inlet side is not adsorbed is increased by high-temperature / low-humidity regeneration air. At this stage, the outlet air temperature remains at about 12 ° C. and hardly changes.

  In the next stage C to D, the high-temperature / low-humidity regeneration air that has flowed into the area where moisture is adsorbed flows through the rotor 11 to the outlet side while the rotor 11 is heated and desorbed. However, at that time, the temperature of the regeneration 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 (regeneration air and rotor that cannot contribute to desorption). 11 is an adsorption / desorption equilibrium / thermal equilibrium state). This equilibrium air temperature is about 60 ° C. in this example. Since the equilibrium state is maintained in the vicinity of the outlet of the regeneration zone 11b until the stage E nearing completion of desorption of the entire area of the rotor 11, a state where the outlet temperature is constant continues for a while.

  In this operation example, based on the outlet temperature of the purge zone 11c detected by the purge outlet temperature sensor 48 installed at the position angle θ = 65 ° close to the regeneration zone 11b in the purge zone 11c, the regeneration fan 40 or Since the regeneration circulation damper D4 is controlled to control the regeneration air volume, for example, when the predetermined temperature that is the target of the control is 100 ° C., the outlet temperature at that point in the purge zone 11c is 100 ° C. Then, the control for reducing the reproduction air volume is performed.

  As a result, the rotor 11 moves to the purge section 11c in the state of E to F immediately before the completion of desorption. Here, in the rotor 11 in the state E, most of the region except for the vicinity of the outlet reaches about 140 ° C. Further, since the heat capacity per volume of the rotor 11 is much larger than the heat capacity of air, the rotor 11 in the state E is in a high temperature heat storage state. When low temperature purge air is passed through the rotor 11, the purge air is quickly heated to 140 ° C., and the heat storage effect of the rotor 11 causes the high temperature / low humidity purge air to adsorb moisture for a while. The temperature is continuously increased and desorbed (F to G). As a result, for example, at the stage immediately before the position angle θ = 70 °, the outlet temperature reaches a peak of about 120 ° C. that can be regarded as the regeneration completion temperature. After that, the outlet temperature in the region (H) near the dehumidifying zone 11a in the purge zone 11c becomes 20 ° C. or lower due to the temperature drop by the low temperature and low humidity purge air.

  As described above, in the present operation example, the regeneration fan 40 or the regeneration circulation damper D4 is based on the outlet temperature of the purge section 11c detected by the purge outlet temperature sensor 48 installed near the regeneration section 11b in the purge section 11c. Is controlled so that the outlet air temperature immediately before the position angle θ = 70 ° is higher than the temperature at the point closest to the regeneration zone and equal to or higher than the regeneration completion temperature. Therefore, it is possible to save energy required for regeneration as compared with the conventional case. More specifically, in comparison with the case where the regeneration air volume control is not performed, the amount of heat (heat amount) which is 140 ° C. at the position angle θ = 40-60 ° when the regeneration air volume control is not performed is 60 ° C. It is only necessary to maintain the amount of energy, and energy can be saved accordingly.

  In this operation example, the installation position of the purge outlet temperature sensor 48 is set to a position of the position angle θ = 65 °, and a predetermined temperature, which is a control target temperature, is set to 100 ° C. to control the regeneration air volume. However, this was set by investigating that if the temperature reached 100 ° C. at the position angle θ = 65 ° in advance by a prior operation or the like, it reached 120 ° C., which was the regeneration completion temperature, after that. Therefore, the setting of the control point and the predetermined temperature is not limited to this example.

  Next, as described above, controlling the cooling capacity of the cooling coil 24 and the heating capacity of the heating coil 31 based on the dehumidifying inlet dew point temperature is a low dew point supplied to a low dew point space (not shown). This is effective when the temperature of the air SA is relatively high, but when the temperature of the low dew point air SA supplied to the low dew point space (not shown) is relatively low, the rotor speed control described below is effective. is there. In the rotor rotation speed control, the dehumidifying capacity is limited to the last minute in the winter, and therefore cannot be performed simultaneously with the operation method according to the present invention. Therefore, next, the dry reduction shown in FIG. 6 can be implemented, in which the cooling method of the cooling coil 24 and the heating capability of the heating coil 31 are controlled and the operation method can be switched between the case of controlling the rotor speed. The wet device 2 will be described.

  The dry dehumidifying device 2 shown in FIG. 6 basically has the same configuration as the dry dehumidifying device 1 described above with reference to FIGS. 1 to 3, and common constituent elements are denoted by the same reference numerals. Therefore, the overlapping description is omitted. In the dry dehumidifying device 2 shown in FIG. 6, in addition to the dry dehumidifying device 1 described in FIGS. 1 to 3, a dehumidifying zone inlet temperature sensor 50 that detects the inlet temperature of the dehumidifying zone 11a, and the dehumidifying zone 11a. Is provided with a dehumidifying zone outlet temperature sensor 51 for detecting the outlet temperature of the dehumidifying zone, and the inlet temperature detected by the dehumidifying zone inlet temperature sensor 50 and the outlet temperature detected by the dehumidifying zone outlet temperature sensor 51 are controlled by the control device. Input to CU. Furthermore, in this dry type dehumidifier 2, the control unit CU can change the number of rotations of the rotor 11 by inverter control of the drive of the motor 10. The control unit CU also has a function of controlling the exhaust damper D3.

  Next, an operation example of a dehumidification system having this dry dehumidifier 2 will be described. As an example, when the temperature of the low dew point air SA supplied to the low dew point space (not shown) is 16 ° C. or higher, an operation for controlling the cooling capacity of the cooling coil 24 and the heating capacity of the heating coil 31 is performed. A case where the operation is switched to the operation by the rotor rotation speed control when the temperature of the dew point air SA is less than 16 ° C. will be described.

For example, when the dehumidification outlet dew point temperature is −55 ° C. DP and the temperature of the low dew point air SA supplied to the low dew point space (not shown) is 16 ° C. or higher, the control unit CU is similar to the above. From the relationship shown in FIG. 4, it is determined how far the setting of the dehumidifying inlet temperature can be raised, and if it is determined that the set value can be raised, the setting of the dehumidifying inlet temperature is changed to a higher temperature. Then, the control unit CU controls the flow rate control valve 26 provided in the chilled water pipe 25 to adjust so as to reduce the cooling capacity by the cooling coil 24 (cascade control). Thus, the cooling energy in the cooling coil 24 can be reduced. Further, as the cooling capacity of the processing air by the cooling coil 24 is lowered, the heating energy in the heating coil can also be reduced. As a result, energy saving is achieved and CO _{2 is} reduced.

  Similarly, when the temperature of the low dew point air SA is 16 ° C. or higher, so-called regeneration air volume control can be performed together. By implementing the regeneration air volume control together, it is possible to further save energy.

  On the other hand, when the temperature of the low dew point air SA supplied to the low dew point space (not shown) is less than 16 ° C., the rotor speed control described below is effective. For example, when the dehumidification outlet dew point temperature is −55 ° C. DP, in order to supply low dew point air SA reheated by the heating coil 31 to 16 ° C. and supplied to the low dew point space (not shown), It is necessary to set the temperature of the air dehumidified in the wet area 11a (dehumidification outlet temperature) to 16 ° C. or lower. At that time, assuming that the dehumidifying inlet dew point temperature is −11.5 ° C. DP, the dehumidifying inlet temperature obtained from the relationship shown in FIG. 4 is 13.5 ° C. Therefore, in this example, the setting of the dehumidifying inlet temperature can only be increased up to 13.5 ° C. Further, when the dehumidifying inlet dew point is −10 ° C. DP, the dehumidifying inlet temperature is 12 ° C. In this case, for example, if the dehumidifying inlet temperature is set to 12 ° C. in summer, the dehumidifying inlet temperature is 12 ° C. The inlet temperature setting cannot be increased. In such a case, it is effective to switch to the operation by the rotor rotation speed control.

7, in a dry down humidity device 2 shown in FIG. 6 illustrates every rotor rotational speed relationship between the absolute humidity x _A preferred regeneration air volume dehumidification zone inlet air. Further, FIG. 8, in a dry down humidity device 2 shown in FIG. 6 illustrates every regeneration temperature the relationship between the absolute humidity x _A preferred regeneration air volume dehumidification zone inlet air. 7 and 8 show cases where the wind speed of the dehumidification zone surface is 2.0 meters / second.

Play air volume, the rotor rotational speed omega, the regeneration temperature T _reg, dividing Shimekazeryou F _pro, is controlled to be suitable regeneration air volume with respect to the dehumidification zone inlet temperature T _A and dehumidification zone inlet absolute humidity x _A. That is, the dehumidification zone inlet absolute humidity x _A, preferred regeneration airflow F _{reg, opt,} the rotor rotational speed omega, the regeneration temperature T _reg, dividing Shimekazeryou F _pro and dehumidification zone inlet temperature T _A is have a certain relevance You can see that Therefore, conversely, the absolute humidity x _A of the dehumidification zone inlet air can be estimated from the preferred regeneration air volume F _{reg, opt} , the rotor speed ω, the regeneration temperature T _reg , the dehumidification air volume F _pro and the dehumidification zone inlet temperature T _A. it can. For this reason, experiments and simulations have been made in advance on the relationship between the preferred regeneration air volume F _{reg, opt} , rotor speed ω, regeneration temperature T _reg , dehumidification air volume F _pro and dehumidification zone inlet temperature T _A, and dehumidification zone inlet absolute humidity x _A Are stored in the storage device of the control arithmetic unit CU as estimated humidity information in the form of a relational expression (for example, the following expression (1)) or a humidity estimation processing map. The control arithmetic unit CU then selects the suitable regeneration air volume F _{reg, opt} determined by the control of the regeneration air volume, the currently set rotor rotational speed ω and the regeneration temperature T _reg , and the dehumidification air volume F _pro measured by the air flow meter 23. When the dehumidifying zone inlet temperature T _A measured by the temperature sensor 42 is received, the absolute humidity x _A of the dehumidifying zone inlet air is estimated by performing calculation using this relational expression or referring to the humidity estimation processing map. . Control calculation unit CU, preferably reproduction airflow F _{reg, opt,} the rotor rotational speed omega, the regeneration temperature T _reg, removal Shimekazeryou F _pro and dehumidification zone inlet temperature T _A by calculating by substituting the equation (1), preferably It can be estimated absolute humidity x _a dehumidification zone inlet air according to the regeneration air volume.

x _A
= f (F _{reg, opt} , ω, T _reg ,
F _pro , T _A ) (1)

When the setting of the dehumidifying inlet temperature cannot be increased, the control arithmetic unit CU uses the absolute humidity x _A of the dehumidifying zone inlet air to lower the rotor rotational speed (or lower the regeneration temperature) when the humidity is low, When the humidity is high, variable control is performed so as to increase the rotational speed of the rotor (or increase the regeneration temperature).

  As mentioned above, although embodiment of this invention was illustrated and demonstrated, this invention is not limited to this form. For example, as shown in FIG. 9, the heating capacity of the heating coil 31 can be controlled based on the supply air temperature detected by the supply air temperature sensor 47. In this case, in order to perform room temperature control of the low dew point space 55, an air conditioner (AHU) 56 may be separately installed. The configuration shown in FIG. 9 is effective, for example, when there is a production device 57 that requires temperature management inside the low dew point space 55.

  For example, as shown in FIG. 10, the heating capability of the heating coil 31 can be controlled based on the room temperature detected by the temperature sensor 58 installed in the low dew point space 55. The configuration shown in FIG. 10 is effective when, for example, the air volumes of the dry dehumidifiers 1 and 2 are sufficiently large.

  In order to switch the cooling capacity in the cooling coil 24, as shown in FIG. 11, the chilled water pipe 25 is formed into an annular circulation path through which the cooling water circulates by the operation of the pump 60. There may be provided a cooling tower 61 for direct contact with the cooling tower and a heat exchanger 62 for cooling the cooling water with a refrigerant. Then, by providing a bypass passage 65 that bypasses the cooling tower 61 and a bypass passage 66 that bypasses the heat exchanger 62, the cooling water passing through the cooling coil 24 is cooled by the cooling tower 61, and the cooling water is By switching to the state of cooling with the refrigerant in the heat exchanger 62, the cooling capacity of the cooling coil 24 can be easily switched.

  In addition to detecting the dehumidifying inlet dew point temperature by the dehumidifying inlet dew point temperature sensor 46, the dehumidifying inlet dew point temperature can also be estimated based on other information. For example, the dehumidifying inlet dew point temperature may be estimated from the dew point temperature of the outside air (process air) OA introduced through the process duct 22. Further, it is reduced from the difference between the inlet temperature of the dehumidifying zone 11 a detected by the dehumidifying zone inlet temperature sensor 50 shown in FIG. 6 and the outlet temperature of the dehumidifying zone 11 a detected by the dehumidifying zone outlet temperature sensor 51. The wet inlet dew point temperature may be estimated.

  Moreover, in this invention, as shown to Unexamined-Japanese-Patent No. 2011-230098 which concerns on the same applicant, after dehumidifying area 11a is divided into 2 and the air which went out of the purge area 11c is heated, one dehumidifying area It is also possible to apply a configuration in which the air discharged therefrom is further heated to be guided to the other dehumidifying area and exhausted and recirculated as described above. In order to reduce the cooling amount and heating amount when the cooling load is low, not only the flow rate control but also the cooling load of the heat medium temperature may be reduced by operating a heat source device such as a compressor or a refrigerator.

  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.

DESCRIPTION OF SYMBOLS 1, 2 Drying dehumidifier 10 Motor 11 Rotor 12, 13 Area division | segmentation cassette 11a Humidification area 11b Regeneration area 11c Purge area 12a Humidification inlet 12b Regeneration outlet 12c Purge outlet 21 Processing fan 22 Processing duct 22, 24 Cooling coil 25 Cooling water Pipe 30 Supply duct 31 Heating coil 32 Heat source water pipe 35 Purge introduction duct 37 Regeneration exhaust duct 40 Regeneration fan 41 Regeneration introduction duct 42 Regeneration heater 45 Dehumidification inlet temperature sensor 46 Dehumidification inlet dew point temperature sensor 47 Supply temperature sensor 48 Purge Outlet temperature sensor 50 Dehumidification zone inlet temperature sensor 51 Dehumidification zone outlet temperature sensor 55 Low dew point space 56 Air conditioner (AHU)
57 Production equipment 58 Temperature sensor 60 Pump 61 Cooling tower 62 Heat exchanger 65, 66 Bypass CU Control device D1 Supply damper D2 Introduction damper D3 Exhaust damper D4 Regenerative circulation damper D5 Outside air introduction damper

Claims (2)

An apparatus for dehumidifying the processing air by passing the processing air through a rotatable adsorption rotor, wherein the air passing area located on the end face side of the adsorption rotor includes a dehumidification area, a regeneration area, and a purge area. These areas are arranged so that the purge area is located before the transition from the regeneration area to the dehumidifying area by the rotation of the adsorption rotor, and cooling is performed to cool the processing air at the entrance side of the dehumidifying area. In a dry dehumidifier equipped with a coil and equipped with a heater for heating the processing air on the outlet side of the dehumidifying area,
Measure or estimate the dehumidifying inlet dew point temperature, which is the dew point temperature of the processing air entering the dehumidifying zone, and cool the processing air with the cooling coil and process with the heater based on the measured or estimated dehumidifying inlet dew point temperature. A control device capable of executing control for heating air and rotor rotation speed control for controlling the rotation speed of the adsorption rotor;
When the temperature of the low dew point air that is dehumidified and supplied to the low dew point space is equal to or higher than a predetermined temperature, the control device controls the cooling of the processing air by the cooling coil and the heating of the processing air by the heater. When the temperature is lower than a predetermined temperature, the rotor rotational speed control is executed. An apparatus for dehumidifying the processing air by passing the processing air through a rotatable adsorption rotor, wherein the air passing area located on the end face side of the adsorption rotor includes a dehumidification area, a regeneration area, and a purge area. These areas are arranged so that the purge area is located before the transition from the regeneration area to the dehumidifying area by the rotation of the adsorption rotor, and cooling is performed to cool the processing air at the entrance side of the dehumidifying area. In a dry dehumidifier equipped with a coil and equipped with a heater for heating the processing air on the outlet side of the dehumidifying zone, the dehumidifying inlet dew point temperature, which is the dew point temperature of the processing air entering the dehumidifying zone, is measured or estimated. A control for cooling the processing air by the cooling coil and heating the processing air by the heater based on the measured or estimated dehumidification inlet dew point temperature, and a rotor speed control for controlling the rotation speed of the adsorption rotor; Have executable control device,
When the temperature of the low dew point air that is dehumidified and supplied to the low dew point space is equal to or higher than a predetermined temperature, the control device controls the cooling of the processing air by the cooling coil and the heating of the processing air by the heater. And when the temperature is lower than a predetermined temperature, the rotor rotational speed control is executed.

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