JP2007260524A - Dehumidifier - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To perform efficient dehumidification by utilizing a heat pump even at the time of a low temperature by compounding the heat pump and a desiccant rotor by a small-sized simple constitution. <P>SOLUTION: The dehumidifier is equipped with the steam compression type heat pump 9 the desiccant rotor 18 for adsorbing humidity from supplied air in a moisture absorbing region 24 and heated by a heater 21 in a regeneration region 23 to discharge moisture, a first fan 11 for sucking air from a suction port 2 and supplying the sucked air to a radiator 7 to discharge the same from a blowoff port 3 and a second fan 12 for supplying the air sucked from the suction port 2 to the regeneration region 23 and further supplying the air supplied to the regeneration region 23 to a heat sink device 6 and further supplying the air to a hygroscopic region 24 to discharge the same from the blowoff port 3. The dehumidifier can be switched to either a single dehumidification operation 40 for operating the first and second fans 11 and 12 and a compressor 5 or a combined dehumidification operation 39 for operating the first and second fans 11 and 12, the compressor 5, a drive means 19 and the heater 21. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a dehumidifier that performs a combined dehumidifying operation using a vapor compression heat pump and a desiccant rotor.

As a dehumidifier that performs combined dehumidifying operation with a conventional heat pump and desiccant rotor, a regeneration passage of the heater and the desiccant rotor and one passage of the sensible heat exchanger are connected in an annular shape to form a circulation passage, and the desiccant rotor absorbs moisture. Water is released into the circulation passage by a heater, and the water is cooled by low-temperature air that has absorbed heat by a heat absorber of a heat pump flowing through the other passage of the sensible heat exchanger to recover the water (for example, Patent Document 1). reference).
JP 2004-28481 A

  Such a conventional dehumidifier does not have a means for increasing the relative humidity of the air absorbed by the desiccant rotor, and therefore cannot increase the moisture absorption efficiency in the desiccant rotor and cannot improve the dehumidification efficiency. There was a problem.

  In addition, since there is no means to increase the enthalpy of the air supplied to the heat absorber, the enthalpy difference between the heat absorber and the supply air is reduced at low temperatures such as in winter, and the dehumidification amount in the heat pump is greatly reduced. Since the dehumidifying operation is performed only with the desiccant rotor, there is a problem that energy efficiency is lowered.

  In addition, when the heat pump is operated at a low temperature such as in winter, a frost phenomenon may occur in the heat absorber, and it is necessary to provide a defrosting means such as a two-way valve in the heat pump in order to defrost the frost. There is a problem that the structure of the apparatus is complicated and the cost is increased.

  Moreover, since the air whose temperature rose compared with the original indoor air is supplied from a dehumidifier, there existed a subject that there was discomfort at high temperature, such as summer.

  In addition, a sensible heat exchanger for collecting the moisture absorbed by the desiccant rotor is required, and a circulation passage is formed in which the heater, the regeneration region of the desiccant rotor, and one passage of the sensible heat exchanger are connected in an annular shape. Since it is necessary, there is a problem that the apparatus configuration becomes complicated and the size is increased.

  The present invention solves the above-mentioned conventional problems, combines a heat pump and a desiccant rotor with a small and simple configuration, improves the dehumidification efficiency by increasing the relative humidity of the air absorbed by the desiccant rotor, Provides a dehumidifier that can efficiently dehumidify even when using a heat pump, can perform defrosting operation without providing a special member for defrosting, and can blow out low-temperature air to room air The purpose is to do.

  In order to achieve the above object, the first problem-solving means taken by the present invention is a compressor for compressing a refrigerant (8) in a main body (1) having an inlet (2) and an outlet (3). (5), a radiator (7) that radiates heat to the supply air by the refrigerant (8), a decompression mechanism (10) that expands and depressurizes the refrigerant (8), and an endotherm that the refrigerant (8) absorbs from the supply air. Rotated by a vapor compression heat pump (9) connected to the vessel (6) by piping and driving means (19), the moisture absorption region (24) absorbs moisture from the supply air and is heated in the regeneration region (23) to absorb moisture A desiccant rotor (18) that discharges air, a heater (21) that heats the regeneration region (23), and air is sucked from the suction port (2) and supplied to the radiator (7) to supply the air outlet The first air passage (13) discharged from (3) and the suction port Air is sucked from 2) and supplied to the regeneration region (23), and the air supplied to the regeneration region (23) is supplied to the heat absorber (6) and further supplied to the moisture absorption region (24). And a second air passage (14) that discharges from the air outlet (3).

  And the effect | action by the said 1st subject solution means does not provide the cyclic | annular circulation channel | path and the heat exchanger for a water | moisture content recovery in a main body (1), but the heat absorber (6) absorbs the moisture which the desiccant rotor (18) absorbed. In order to simplify and reduce the size of the apparatus by collecting it as condensed water, the air cooled by the heat absorber (6) and reduced in relative humidity is further supplied to the moisture absorption region (24). Thus, the relative humidity difference between the air passing through the moisture absorption region (24) and the regeneration region (23) of the desiccant rotor (18) can be increased, and the moisture absorption / release efficiency of the desiccant rotor (18) is increased. .

  Further, the second problem solving means is the first bypass for directly supplying the air sucked from the suction port (2) to a part of the air supplied to the heat absorber (6) in the second air passage (14). A path (42) is formed.

  The action of the second problem solving means is optimal for each of the regeneration region (23) and the heat absorber (6) by supplying the air sucked directly from the suction port (2) to the heat absorber (6). A high air flow rate can be secured, and the regeneration efficiency of the desiccant rotor (18) and the endothermic efficiency of the heat absorber (6) are enhanced.

  Further, the third problem-solving means is the second air passage (14), in which a part of the air sucked from the suction port (2) is removed from the regeneration region of the desiccant rotor (18) without passing through the heater (21). The first purge path (41) to be supplied to 23) is formed.

  The action of the third problem solving means is to supply air through the first purge path (41) to the regeneration region (23) located at the front stage and the rear stage of the heater (21) in the rotational direction of the desiccant rotor (18). The desiccant rotor (18) is cooled with air supplied to the rear stage of the heater (21) to accelerate moisture absorption in the moisture absorption region (24), and the desiccant rotor (18) is preheated with air supplied to the front stage of the heater (21). It is easy to release moisture.

  Further, the fourth problem solving means is a second method for supplying a part of the air sucked from the suction port (2) to the moisture absorption region (24) of the desiccant rotor (18) in the first air passage (13). A purge path (43) is formed.

  And the effect | action by the 4th problem-solving means can adsorb | suck a water | moisture content from the air by supplying the air attracted | sucked directly from the suction inlet (2) to the moisture absorption area | region (24), and desiccant rotor (18 ) To absorb and release moisture.

  Further, the fifth problem solving means is that at least a part of the air supplied to the radiator (7) of the first air passage (13) passes through the moisture absorption region (24) of the second air passage (14). It is set as the structure which supplies at least one part.

  The action of the fifth problem solving means is air that has been cooled by the heat absorber (6) and then has been given heat of adsorption by moisture absorption in the moisture absorption region (24), and has a lower temperature than room air. By supplying the air after passing through the moisture absorption region (24) of the second air passage (14) to the heat radiator (7) of the first air passage (13), the radiator is more directly supplied than the indoor air. The amount of heat released in (7) can be increased, and as a result, the amount of heat absorbed in the heat absorber (6) is increased, and condensation in the heat absorber (6) is promoted.

  The sixth problem solving means includes a first fan (11) for blowing air to the first air passage (13) and a second fan (12) for blowing air to the second air passage (14), and the first fan (11), a single dehumidifying operation (40) for operating the second fan (12) and the compressor (5), the first fan (11), the second fan (12), the compressor (5), The composite dehumidifying operation (39) for operating the driving means (19) and the heater (21) is configured to be switchable.

  Then, the action of the sixth problem solving means is that the combined dehumidification operation (39) is performed at low temperatures, and the high-humidity air containing the moisture released by the desiccant rotor (18) in the regeneration region (23) is absorbed. The dehumidifying efficiency is increased by operating the heat pump (9) by securing the difference in enthalpy from the refrigerant (8) by supplying to the vessel (6).

  The seventh problem solving means is configured to execute switching between the single dehumidifying operation (40) and the combined dehumidifying operation (39) based on the temperature of the air sucked from the suction port (2).

  The action of the seventh problem solving means is that the dehumidification amount is ensured by executing the combined dehumidification operation (39) when the air sucked from the suction port (2) is at a low temperature, otherwise only the heat pump (9). By performing the single dehumidifying operation (40) and suppressing power consumption, an efficient dehumidifying operation adapted to the environmental temperature is performed.

  The eighth problem solving means is configured to execute switching between the single dehumidifying operation (40) and the combined dehumidifying operation (39) based on the humidity of the air sucked from the suction port (2).

  The action of the eighth problem solving means is that the dehumidification amount is increased by executing the combined dehumidification operation (39) when the air sucked from the suction port (2) is highly humid, and the heat pump (9) otherwise. Only the single dehumidifying operation (40) is executed to suppress the power consumption, thereby performing an efficient dehumidifying operation adapted to the dehumidifying load.

  The ninth problem-solving means opens the exhaust port (4) on a surface different from the opening surface of the blower outlet (3) of the main body (1), and discharges the first fan (11) to the blower port (3). ) Or the exhaust port (4).

  The action of the ninth problem solving means is that the high-temperature air supplied to the radiator (7) by the first fan (11) and heated, and the moisture absorption region (24) and the heat absorber by the second fan (12). The exhaust form in which the low-humidity air supplied to (6) is dehumidified is separated into the blowout port (3) and the exhaust port (4) and discharged, and both high-temperature air and low-humidity air are discharged from the blowout port (3). The exhaust mode to be selected can be selected according to the purpose of use.

  The tenth problem solving means is configured to execute the single dehumidifying operation (40) when the discharge destination of the first fan (11) is set to the exhaust port (4).

  The action of the tenth problem solving means is that when the discharge destination of the first fan (11) is set to the exhaust port (4), the single dehumidifying operation (40) is executed, and the second fan (12). The temperature rise is suppressed by discharging the air blown from the air outlet (3) without giving the adsorption heat of the desiccant rotor (18) or the residual heat of the heater (21) to the air blown by the air.

  Further, the eleventh problem solving means is configured to execute a defrosting operation mode in which the heater (21) and the driving means (19) are operated when the temperature of the heat absorber (6) becomes less than a predetermined value. Is.

  The action of the eleventh problem solving means is that, when the heat absorber (6) is frosted and the temperature of the heat absorber (6) becomes less than a predetermined value, the defrosting operation mode is executed and the heat absorber (6 By removing the frost adhering without providing a special member for defrosting by supplying heat to the heater (21), the dehumidifier can be dehumidified again.

  The twelfth problem solving means is configured to stop the compressor (5) in the defrosting operation mode.

  The action of the twelfth problem solving means is to stop the endothermic action in the heat absorber (6) by stopping the compressor (5) in the defrosting operation mode, and to defrost the heat absorber (6). More effectively, the time for the defrosting operation mode is shortened.

  The thirteenth problem solving means is configured to adjust the air volume of the first fan (11) based on the temperature of the air sucked from the suction port (2).

  The action of the thirteenth problem solving means is to reduce the air volume of the first fan (11) when the temperature of the supply air is low, and conversely to reduce the air volume of the first fan (11) when the temperature of the supply air is high. By increasing, the amount of heat radiation in the radiator (7) is adjusted, and the operating pressure of the heat pump (9) is adjusted appropriately.

  In addition, the fourteenth problem solving means is configured to adjust the air volume of the first fan (11) based on the humidity of the air sucked from the suction port (2).

  The action of the fourteenth problem solving means reduces the air volume of the first fan (11) when the humidity of the supply air is low, and conversely reduces the air volume of the first fan (11) when the humidity of the supply air is high. By increasing, the operating pressure of the heat pump (9) is adjusted appropriately.

  The fifteenth problem solving means adjusts the air volume of the first fan (11) based on the temperature of the heat absorber (6).

  The action of the fifteenth problem solving means is to reduce the air volume of the first fan (11) when the temperature of the heat absorber (6) is low, and conversely when the temperature of the heat absorber (6) is high. The operating pressure of the heat pump (9) is appropriately adjusted by increasing the air volume of (11).

  In the dehumidifier according to claim 1 of the present invention, the moisture absorbed by the desiccant rotor (18) is provided in the heat absorber (6) without providing an annular circulation passage and a heat exchanger for collecting water in the main body (1). The desiccant rotor is constructed by simplifying and reducing the size of the apparatus by collecting it as condensed water, and further supplying the air that has been cooled by the heat absorber (6) and whose relative humidity has been lowered to the moisture absorption region (24). The relative humidity difference between the air passing through the moisture absorption region (24) and the regeneration region (23) of (18) can be increased, and the moisture absorption / release efficiency of the desiccant rotor (18) is increased, and the dehumidification efficiency is increased. Play.

  Moreover, the dehumidifier according to claim 2 of the present invention supplies each of the regeneration region (23) and the heat absorber (6) by supplying air sucked directly from the suction port (2) to the heat absorber (6). It is possible to secure an optimal air flow rate for the above, and it is possible to increase the regeneration efficiency of the desiccant rotor (18) and the heat absorption efficiency of the heat absorber (6), and to increase the dehumidification efficiency.

  In the dehumidifier according to claim 3 of the present invention, air is passed through the first purge path (41) to the regeneration region (23) located in the upstream and downstream of the heater (21) in the rotational direction of the desiccant rotor (18). The desiccant rotor (18) is cooled by the air supplied to the rear stage of the heater (21) to accelerate moisture absorption in the moisture absorption region (24) and the desiccant rotor (18) is supplied by the air supplied to the front stage of the heater (21). The effect of increasing the dehumidifying efficiency is achieved by preheating and releasing moisture easily.

  Moreover, the dehumidifier according to claim 4 of the present invention is capable of adsorbing moisture directly from the suction port (2) to the moisture absorption region (24), thereby allowing moisture to be absorbed from the air, and the desiccant rotor. The effect of increasing the moisture absorption amount and moisture release amount of (18) and improving the dehumidification efficiency is achieved.

  Further, the dehumidifier according to claim 5 of the present invention is air that has been cooled by the heat absorber (6) and then is given heat of adsorption by moisture absorption in the moisture absorption region (24), and has a lower temperature than indoor air. By supplying the air after passing through the moisture absorption region (24) of the second air passage (14) to the radiator (7) of the first air passage (13), thereby supplying indoor air directly. The heat radiation amount in the radiator (7) can be increased. As a result, the heat absorption amount in the heat absorber (6) is increased, the dew condensation in the heat absorber (6) is promoted, and the dehumidification efficiency is enhanced. .

  Further, the dehumidifier according to claim 6 of the present invention is a high-humidity air containing moisture released by the desiccant rotor (18) in the regeneration region (23) by executing the combined dehumidification operation (39) at low temperatures. Is supplied to the heat absorber (6), and the heat pump (9) is activated by securing the enthalpy difference from the refrigerant (8), thereby improving the dehumidifying efficiency.

  Further, in the dehumidifier according to claim 7 of the present invention, when the air sucked from the suction port (2) is at a low temperature, the dehumidifying amount is ensured by executing the combined dehumidifying operation (39), otherwise the heat pump (9 ) Only the dehumidifying operation (40) is performed, and the power consumption is reduced, thereby achieving an effect of performing an efficient dehumidifying operation adapted to the environmental temperature.

  The dehumidifier according to claim 8 of the present invention increases the dehumidification amount by executing the combined dehumidification operation (39) when the air sucked from the suction port (2) is highly humid, and otherwise the heat pump ( 9) Only the single dehumidifying operation (40) is executed to reduce the power consumption, thereby achieving an effect of performing an efficient dehumidifying operation adapted to the dehumidifying load.

  The dehumidifier according to claim 9 of the present invention includes high-temperature air supplied to the radiator (7) by the first fan (11) and heated, and a moisture absorption region (24) and a second fan (12). The exhaust form in which the low-humidity air supplied to the heat absorber (6) and dehumidified is separated into the outlet (3) and the outlet (4) and discharged, and the hot air and the low-humidity air are both blown out (3). There is an effect that the exhaust form to be discharged from can be selected according to the purpose of use.

  Further, in the dehumidifier according to claim 10 of the present invention, when the discharge destination of the first fan (11) is set to the exhaust port (4), the single dehumidifying operation (40) is executed and the second fan ( 12) The air blown by 12) is exhausted from the blowout port (3) without giving the heat of adsorption of the desiccant rotor (18) and the residual heat of the heater (21), and thus has an effect of suppressing room temperature rise.

  In the dehumidifier according to claim 11 of the present invention, when the heat absorber (6) is frosted and the temperature of the heat absorber (6) becomes lower than a predetermined value, the defroster operation mode is executed and the heat absorber. By removing the frost attached without providing a special member for defrosting by supplying the heat of the heater (21) to (6), the dehumidifying state can be achieved again, and the effect of dehumidifying efficiently Play.

  The dehumidifier according to claim 12 of the present invention stops the endothermic action in the heat absorber (6) by stopping the compressor (5) in the defrosting operation mode, thereby removing the heat absorber (6). The effect of performing frost more effectively and shortening the time of defrosting operation mode is produced.

  The dehumidifier according to claim 13 of the present invention reduces the air volume of the first fan (11) when the temperature of the supply air is low, and conversely when the temperature of the supply air is high, the dehumidifier of the first fan (11). By increasing the air volume, the heat radiation amount in the radiator (7) is adjusted, the operating pressure of the heat pump (9) is adjusted appropriately, and the reliability of the compressor (5) is ensured.

  The dehumidifier according to claim 14 of the present invention reduces the air volume of the first fan (11) when the supply air humidity is low, and conversely the first fan (11) when the supply air humidity is high. By increasing the air volume, there is an effect that the operating pressure of the heat pump (9) is appropriately adjusted.

  The dehumidifier according to claim 15 of the present invention reduces the air volume of the first fan (11) when the temperature of the heat absorber (6) is low, and conversely when the temperature of the heat absorber (6) is high. There is an effect that the operating pressure of the heat pump (9) is appropriately adjusted by increasing the air volume of one fan (11).

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(Embodiment)
Hereinafter, embodiments of the present invention will be described with reference to FIGS.

  FIG. 1 is a schematic cross-sectional view of a dehumidifier according to an embodiment of the present invention. As shown in the figure, a suction port 2 is formed on one side of a main body 1 formed in a substantially rectangular parallelepiped, and an outlet 3 is formed on an upper surface of the main body 1. The exhaust port 4 is opened on the side surface opposite to the suction port 2. Inside the main body 1, a compressor 5 is disposed at the bottom, a heat absorber 6 is disposed above it, and a heat radiator 7 is disposed above the compressor 5. As the refrigerant 8 which is a working fluid in this sealed circuit, for example, HCFC refrigerant (including chlorine, hydrogen, fluorine and carbon atoms in the molecule), HFC refrigerant (hydrogen, carbon and fluorine atoms in the molecule) Or the like, or a natural refrigerant such as hydrocarbon or carbon dioxide, or the like, to form the vapor compression heat pump 9. The heat absorber 6 and the heat radiator 7 are constituted by a fin tube type heat exchanger in which a plurality of fins are inserted into the hairpin tube so as to allow air circulation, and in the pipe connecting the heat absorber 6 and the heat radiator 7. For example, a capillary tube or an expansion valve is interposed as the decompression mechanism 10. Further, the first fan 11 is arranged at a position where the room air sucked from the suction port 2 can be blown to the radiator 7, and the second fan 12 is arranged at a position where the room air sucked from the suction port 2 can be blown to the heat absorber 6. The air passage is formed by the partition wall. In addition, the installation position of the 1st fan 11 and the 2nd fan 12 should just be a position which can ensure the said air path, and is not limited to the position of a present Example. As the first fan 11 and the second fan 12, a general blower composed of blades, a casing, a motor, and the like is used, and the amount of blown air can be changed by a plurality of output notches of the motor. The first fan 11 communicates with the suction port 2 on the suction side via the radiator 7, communicates with the blowout port 3 on the discharge side, forms the first air passage 13, and operates the first fan 11 from the suction port 2. An air blowing operation is performed in which the air is taken in, supplied to the radiator 7 and exhausted from the outlet 3. As for the 2nd fan 12, the suction side communicates with the blower outlet 3 through the heat sink 6 on the suction side and forms the second air passage 14, and when the second fan 12 is operated, the air is sucked from the suction port 2 and supplied to the heat sink 6. An air blowing operation for exhausting air from the air outlet 3 is performed. When the compressor 5 is operated here, the refrigerant 8 circulates in the sealed circuit in the order of the radiator 7, the decompression mechanism 10, and the heat absorber 6, and the high-temperature and high-pressure refrigerant 8 compressed by the compressor 5 is the first in the radiator 7. The low-temperature and low-pressure refrigerant 8 expanded by the decompression mechanism 10 absorbs heat from the air supplied by the second fan 12 while the heat pump 9 operates. . A damper 15 for switching the discharge destination of the first fan 11 to either the blowout port 3 or the exhaust port 4 is disposed on the discharge side of the first fan 11. The damper 15 includes a shielding plate for closing the air passage and a drive motor for moving the shielding plate. The drive motor is operated by an instruction from an operation unit (not shown) disposed on the upper surface of the main body 1. Thus, the shielding plate is configured to switch to one of a switching position 16 indicated by a solid line and a switching position 17 indicated by a broken line. When the damper 15 is set to a switching position 16 indicated by a solid line, the discharge side of the first fan 11 and the outlet 3 are in communication with each other, the passage to the exhaust port 4 is closed, and conversely, the switching position 17 indicated by a broken line is set. When set, the discharge side of the first fan 11 and the exhaust port 4 communicate with each other and the passage to the outlet 3 is closed. In this way, the damper 15 is configured to switch the discharge destination of the first fan 11 to either the blowout port 3 or the exhaust port 4. In addition, a disc-shaped desiccant rotor 18 is erected on the suction side of the second fan 12 so as to be rotatable, and driving means for rotating the desiccant rotor 18 at a speed of about 10 to 40 revolutions per hour in the circumferential direction. 19 is disposed on the outer peripheral side of the desiccant rotor 18. The drive means 19 includes a gear formed on the outer periphery of the desiccant rotor 18 and a drive motor that meshes with the gear, and applies a rotational force to the gear by the operation of the drive motor to rotate the desiccant rotor 18. It works like that. Further, the desiccant rotor 18 is divided into two regions with respect to the blowing direction of the second fan 12 by the partition plate 20, and a heater 21 is disposed on the windward side of the one partitioned region. An air passage is formed so that the heat absorber 6 is located on the leeward side. This desiccant rotor 18 has a honeycomb structure or corrugated cylindrical structure that can be ventilated in the axial direction, an inorganic adsorption type moisture absorbent such as silica gel or zeolite, or a moisture absorbent such as an organic polymer electrolyte (ion exchange resin), Or it is comprised by carrying one or more absorption type hygroscopic agents, such as lithium chloride, and has the characteristic that moisture absorption changes according to the surrounding environment. The heater 21 is disposed in the vicinity of the desiccant rotor 18, and the air supplied through the heater 21 to the desiccant rotor 18 and the desiccant rotor 18 itself are heated by the heat generated by the heater 21. . The heater 21 may be any one that can perform a heat generating operation. For example, a nichrome heater, a halogen heater, a carbon heater, a sheathed heater, a PTC heater, or the like can be used. It is preferable because the rotor 18 can be directly heated to a high temperature to efficiently release moisture. Further, on the opposite side of the heater 21 from the desiccant rotor 18, a reflecting plate 22 for reflecting the radiant heat dissipated by the heater 21 to the desiccant rotor 18 is disposed. The reflection plate 22 may be any shape as long as it can reflect the radiant heat dissipated by the heater 21, and can be formed by bending a glossy metal plate such as an aluminum plate or a stainless plate. Further, if the reflecting plate 22 is formed so as to also fix the heater 21, a fixing tool for the heater 21 is not required and the configuration can be simplified. Further, the reflection plate 22 can also act as a light shielding plate for blocking light emitted from the heat generation of the heater 21 from leaking from the suction port 2. And the desiccant rotor 18 is rotatably arranged on the suction side of the second fan 12, and is partitioned into two regions by the partition plate 20 in the blowing direction of the second fan 12, and the windward side of one of the partitioned regions And the second air passage 14 is formed so that the other area of the desiccant rotor 18 is located on the leeward side. Thus, when the second fan 12 is operated, the air sucked from the suction port 2 flows into one of the two regions partitioned by the partition plate 20 where the heater 21 is located, and the heater Due to the heat generated in 21, the temperature becomes high and is supplied to the desiccant rotor 18, then passes through the heat absorber 6, is cooled, and is supplied to the other region side of the desiccant rotor 18. The moisture absorbent carried on the desiccant rotor 18 absorbs moisture from air having relatively high humidity and low temperature, and has a characteristic of releasing moisture into air having relatively low humidity and high temperature. By contacting the high temperature air heated in one area where the heater 21 is disposed, moisture is released and regenerated, and in the other area, moisture is absorbed from the air cooled by the heat absorber 6. Therefore, one area where the heater 21 is disposed becomes a regeneration area 23 in which the desiccant rotor 18 releases moisture with respect to the supply air and regenerates, and the area where the air after passing through the other heat absorber 6 is supplied is the supply air. Therefore, the desiccant rotor 18 acts as a moisture absorption region 24 that absorbs moisture. Since the desiccant rotor 18 is rotated by the driving means 19, the moisture absorbent carried on the desiccant rotor 18 continuously moves in the moisture absorption region 24 and the regeneration region 23, and the moisture absorption operation and the regeneration region in the moisture absorption region 24 are performed. The moisture release operation at 23 is continuously performed. The air containing moisture released in the regeneration region 23 is in a high temperature and high humidity state and is supplied to the heat absorber 6 disposed on the leeward side. Since this high-temperature and high-humidity air also has an increased enthalpy, the enthalpy difference with the refrigerant 8 in the heat absorber 6 is expanded, a highly efficient heat absorption operation is performed, and the supplied air is cooled to a saturation temperature or lower. Moisture saturated during this cooling process drops downward as condensed water, is received by a drain pan (not shown), and then stored in a drain tank 25 disposed at the lower portion of the main body 1. On the other hand, the air that has been cooled to the saturation temperature or lower by the heat absorber 6 and has a high relative humidity (substantially saturated) is supplied to the moisture absorption region 24. As described above, the hygroscopic agent carried on the desiccant rotor 18 absorbs moisture from air having relatively high humidity and low temperature, and has a characteristic of releasing moisture to air having relatively low humidity and high temperature. Therefore, the relative humidity difference between the air passing through the regeneration region 23 and the air passing through the moisture absorption region 24 can be increased, and a highly efficient moisture absorption / release operation can be performed. Further, a reflecting plate 22 is disposed on the opposite side of the heater 21 to the desiccant rotor 18, and the radiant heat radiated from the heater 21 is reflected by the reflecting plate 22 toward the desiccant rotor 18 and reused for moisture release. The regeneration of the rotor 18 is further promoted. The reflecting plate 22 is preferably formed so as to cover the entire heater 21 when viewed from the opening of the suction port 2, and in this way, the radiant heat of the heater 21 can be reflected to the desiccant rotor 18 side without leakage, It is possible to shield the light emitted from the heater 21 from leaking from the suction port 2. In addition, a room temperature sensor 26 for detecting the temperature of air sucked from the suction port 2 and a humidity sensor 27 for detecting the humidity of the air are disposed at the opening of the suction port 2. The evaporative temperature sensor 28 and the condensation temperature sensor 29 are attached to the side piping 7. The detection values of the room temperature sensor 26, the humidity sensor 27, the evaporation temperature sensor 28, and the condensation temperature sensor 29 are output to a control means (not shown).

  FIG. 2 is a control block diagram of the dehumidifier. As shown in the figure, the control means 30 composed of a microcomputer inputs the detected values of the room temperature sensor 26, the humidity sensor 27, the evaporation temperature sensor 28, the condensation temperature sensor 29 and the operation instruction of the operation unit 31. The operation of the dehumidifier is controlled by outputting each operation instruction of the compressor 5, the first fan 11, the second fan 12, the driving means 19, the heater 21 and the damper 15.

  FIG. 3 is a diagram illustrating a schematic configuration of the operation unit 31. As shown in the figure, the operation unit 31 has a plurality of operation buttons and display lamps. The operation button 32 is an on / off switch for the main power supply of the dehumidifier, and the dehumidifier can be operated by setting the operation button 32 to “on”. The operation button 33 is an operation changeover switch, and by operating the operation button 33, three types of dehumidification modes of “dehumidification drying mode”, “automatic dehumidification mode”, and “cold air dehumidification mode” can be selected. The selection state of the dehumidifying mode can be confirmed by the lighting state of the display lamp at the upper part of the operation button 33. The operation button 34 is a switch for setting the timer operation of the dehumidifier. By operating the operation button 34, the operation of the dehumidifier can be stopped after 2, 4 and 8 hours. This off timer selection state can be confirmed by the lighting state of the display lamp at the top of the operation button 34. The operation button 35 is a selection switch for “internal drying mode” for drying water droplets condensed inside the main body 1, particularly the heat absorber 6. During the execution of the “internal drying mode”, the display lamp in the operation button 35 is lit to allow visual confirmation. The display unit 36 displays the humidity state of the space in which the main body 1 is installed. Based on the detection value of the humidity sensor 27, the display unit 36 displays three levels of high humidity, appropriate humidity, and low humidity. Is what you do. The indicator lamp 37 is for lighting and informing when the drain tank 25 is full or not installed, and the indicator lamp 38 blinks when an abnormality such as an abnormal temperature rise is detected. Information is provided.

  FIG. 4 is a table showing control operations in each dehumidifying mode. The control means 30 is programmed to execute the control operations shown in this list. As shown in the figure, when the “dehumidifying / drying mode” is selected by the operation button 33, the control unit 30 operates the compressor 5, the first fan 11, the second fan 12, the driving unit 19 and the heater 21. The damper 15 is set at the switching position 16. Then, the indoor air flows through the first air passage 13 by the operation of the first fan 11, and the air sucked into the main body 1 from the suction port 2 is supplied to the radiator 7 and heated by the heat radiation of the refrigerant 8, and the temperature rises. Since the damper 15 is set at the switching position 16 where the damper 15 communicates with the air outlet 3, the damper 15 is discharged from the air outlet 3 to the outside of the main body 1. Further, the room air flows through the second air passage 14 by the operation of the second fan 12, and the air sucked into the main body 1 flows into the regeneration area 23 of the desiccant rotor 18 divided by the partition plate 20. The air that has flowed into the regeneration region 23 is supplied to the desiccant rotor 18 as high-temperature air heated to more than two hundred degrees by the heater 21, and the desiccant rotor 18 promotes the release of moisture absorbed in the moisture absorption region 24, thereby increasing the desiccant rotor 18. Play. Highly humid air containing moisture released from the desiccant rotor 18 has its enthalpy raised and supplied to the heat absorber 6 downstream. In the heat absorber 6, the air in the high enthalpy state is cooled by the heat absorption of the refrigerant 8, and the water saturated in the cooling process is collected in the drain tank 25. Air cooled by the heat absorber 6 and having a high relative humidity at a low temperature is supplied to the moisture absorption region 24 of the desiccant rotor 18 to adsorb moisture. Then, the air is sucked into the second fan 12 and discharged from the blower outlet 3 to the outside of the main body 1 together with the air discharged from the first fan 11. In this way, in the “dehumidifying / drying mode”, a combined dehumidifying operation 39 combining the desiccant rotor 18 and the heat pump 9 is realized, and this combined dehumidifying operation 39 is performed by the operation of the driving means 19 and the heater 21. Moisture absorption / release operation is performed, moisture absorbed by the desiccant rotor 18 is released by the heat of the heater 21, and high enthalpy air containing the released moisture is cooled by the heat absorber 6 by the operation of the heat pump 9, and condensed water Since the dehumidifying capability is high and the exhaust temperature is high compared to the single dehumidifying operation 40 in which dehumidification is performed only by the heat pump 9 described later, the laundry and the like can be dried quickly.

  When the “automatic dehumidification mode” is selected by the operation button 33, the case is classified according to the detection value Tr of the room temperature sensor 26 and the detection value Hr of the humidity sensor 27. First, when the detection value Hr of the humidity sensor 27 is high humidity, for example, 40% or more, and the detection value Tr of the room temperature sensor 26 is low, for example, less than 15 ° C., the combined dehumidification operation 39 is the same as the “dehumidification drying mode” described above. Executed. When the ambient environmental humidity, that is, the detected value Hr of the humidity sensor 27 is high and the ambient environmental temperature, that is, the detected value Tr of the room temperature sensor 26 is low, the dehumidifying load is large and the heat absorber is used for dehumidifying only the heat pump 9. 6 is judged to be a situation where the enthalpy difference with the refrigerant 8 in 6 is small and it is difficult to secure the dehumidifying capacity, and the dehumidifying capacity 39 is executed by executing the combined dehumidifying operation 39 that combines the cooling dehumidification of the heat pump 9 and the moisture absorbing and releasing action of the desiccant rotor 18 And control to dehumidify quickly.

  Further, when the detection value Hr of the humidity sensor 27 is low humidity, for example, less than 40%, or even when the detection value Hr of the humidity sensor 27 is 40% or more, the detection value Tr of the room temperature sensor 26 is high, for example, 15 ° C. or more. In this case, the compressor 5, the first fan 11, and the second fan 12 are operated, and the single dehumidifying operation 40 for stopping the operation of the driving means 19 and the heater 21 is executed. As a result, the desiccant rotor 18 does not perform the moisture absorption regeneration operation, and the dehumidifying operation of only the heat pump 9 is performed. That is, the air sucked into the main body 1 from the suction port 2 by the operation of the first fan 11 is supplied to the radiator 7 and is heated by the heat radiation of the refrigerant 8 to rise in temperature, and the damper 15 communicates with the outlet 3. Since it is set at the switching position 16, it is discharged from the outlet 3 to the outside of the main body 1. Further, the air sucked into the main body 1 by the second fan 12 flows into the regeneration region 23 of the desiccant rotor 18 divided by the partition plate 20. At this time, since the desiccant rotor 18 is not driven, moisture is not released and the temperature does not change. Then, it is supplied to the heat absorber 6 downstream and cooled by the heat absorption of the refrigerant 8 to remove moisture, and then supplied to the moisture absorption region 24 of the desiccant rotor 18. At this time, since the desiccant rotor 18 is not driven, moisture is not adsorbed and the temperature does not change. After passing through the moisture absorption region 24, the air is sucked into the second fan 12 and discharged from the first fan 11 through the air outlet 3 to the outside of the main body 1. The dehumidifying capacity of the heat pump 9 greatly depends on the room temperature condition, and the dehumidifying capacity tends to increase as the temperature increases. Therefore, when the ambient humidity, that is, the detected value of the humidity sensor 27 is low, If the ambient humidity, that is, the detected value Tr of the humidity sensor 27 is high, but the ambient temperature, that is, the detected value Tr of the room temperature sensor 26 is high, the dehumidifying ability of the heat pump 9 even if the dehumidifying load is small or the dehumidifying load is large. Therefore, by performing the single dehumidifying operation 40 of only the heat pump 9, it is controlled to perform efficient dehumidification by reducing the energy input to the heater 21.

  When the “cold air dehumidifying mode” is selected by the operation button 33, the single dehumidifying operation 40 for operating the compressor 5, the first fan 11, and the second fan 12 is executed. The difference from the “automatic dehumidification mode” described above is that the damper 15 is set at the switching position 17. As a result, the air sucked into the main body 1 from the suction port 2 by the operation of the first fan 11 is supplied to the radiator 7 and is similarly heated by the heat radiation of the refrigerant 8 so that the temperature rises, and the damper 15 becomes the exhaust port 4. Therefore, the air is discharged from the exhaust port 4 opened on the opposite surface of the air outlet 3 to the outside of the main body 1. On the other hand, the air sucked into the main body 1 by the second fan 12 flows into the regeneration region 23 of the desiccant rotor 18 divided by the partition plate 20. At this time, since the desiccant rotor 18 is not driven, moisture is not released and the temperature does not change. Then, it is supplied to the heat absorber 6 downstream and cooled by the heat absorption of the refrigerant 8 to remove moisture, and then supplied to the moisture absorption region 24 of the desiccant rotor 18. At this time, since the desiccant rotor 18 is not driven, moisture is not adsorbed and the temperature does not change. After passing through the moisture absorption region 24, it is sucked into the second fan 12 and discharged from the blower outlet 3 to the outside of the main body 1. Accordingly, high-temperature air heated by the radiator 7 is exhausted from the exhaust port 4 that is the discharge destination of the first fan 11, and cooling and dehumidification is performed from the air outlet 3 that is the discharge destination of the second fan 12 by the heat absorber 6. The low temperature and low humidity air is discharged. When the user is located on the side of the air outlet 3 due to the low-temperature air, a feeling of cold air can be obtained. . Since the blower outlet 3 and the exhaust port 4 are opened on different surfaces of the main body 1, the low temperature air discharged from the blower outlet 3 and the high temperature air discharged from the exhaust port 4 are less likely to be mixed. In the “cold air dehumidification mode” in which only the low-temperature air is supplied, the user can obtain a cool air feeling.

  Further, depending on the use environment temperature, for example, when the environment temperature is low or low humidity, the enthalpy of air supplied to the heat absorber 6 is reduced, and a frosting phenomenon occurs in the heat absorber 6, so that the dehumidifying ability is increased. It will drop greatly. Therefore, the frost formation state is determined based on the detection value Te of the evaporation temperature sensor 28 provided in the side pipe of the heat absorber 6, and when the detection value Te is less than 0 ° C., the compressor 5 is stopped and driven. The defrosting operation is performed by operating the means 19 and the heater 21. In this defrosting operation, the heat absorbing operation in the heat absorber 6 is stopped by stopping the compressor 5 to increase the temperature of the heat absorber 6, and further, the heater 21 via the desiccant rotor 18 is operated by the operation of the driving means 19 and the heater 21. The frost adhering to the heat absorber 6 is quickly dissolved and removed by giving the heat to the air blown by the second fan 12 and supplying it to the heat absorber 6 at a high temperature. Here, if the rotation of the desiccant rotor 18 is stopped, the heat generated by the heater 21 is continuously supplied to a part of the desiccant rotor 18, so that the temperature of the desiccant rotor 18 rises too much and the hygroscopic agent deteriorates. The desiccant rotor 18 is rotated by the driving means 19 and the desiccant rotor 18 is cooled using the moisture absorption region 24. When the frost of the heat absorber 6 is completely removed and the detection value Te of the evaporation temperature sensor 28 is restored to a predetermined value, for example, 0 ° C. or more, the compressor 5 is operated again and the operation is resumed in the predetermined operation mode. I have to.

  When the “internal drying mode” is set by operating the operation button 35, the control unit 30 operates only the second fan 12, the driving unit 19, and the heater 21, and sets the damper 15 at the switching position 17. . The “internal drying mode” is for preventing the generation of mold and odor by drying water droplets attached to the heat absorber 6 when the dehumidifier is stored without being used for a long period of time. The air sucked into the main body 1 from the suction port 2 is supplied to the regeneration region 23 side of the desiccant rotor 18 by the operation of, and the heat of the heater 21 is supplied to the second through the desiccant rotor 18 by the operation of the driving means 19 and the heater 21. Water droplets attached to the heat absorber 6 are dried in a short time by giving the air blown by the fan 12 to a high temperature and supplying the air to the heat absorber 6. Here, the reason why the desiccant rotor 18 is rotated by the driving means 19 is to suppress an excessive temperature rise as described above. The air supplied to the heat absorber 6 passes through the moisture absorption region 24 of the desiccant rotor 18, is sucked into the second fan 12, and is discharged from the blowout port 3. This is to prevent the air blown out by the second fan 12 that sets the damper 15 at the switching position 17 from flowing back to the first fan 11 and the radiator 7.

  As described above, the control means 30 controls the compressor 5, the first fan 11, the second fan 12, the drive means 19, the heater 21, and the damper 15 according to each dehumidification mode, and performs the combined dehumidification operation 39 and the single dehumidification. By appropriately switching the operation 40, various operation modes corresponding to the use environment and the user's preference are realized.

  FIG. 5 is a graph showing the environmental temperature-dehumidifying capability characteristics in each dehumidifying mode. The graph in the figure shows the relationship between the environmental temperature and the dehumidifying capacity when the relative humidity of the environment where the dehumidifier is installed is set to 60%, and the dotted line data shows the dehumidifying capacity characteristics in the “dehumidifying cold air mode”, The broken line data indicates the dehumidifying ability characteristic in the “dry dehumidifying mode”, and the solid line data indicates the dehumidifying ability characteristic in the “automatic dehumidifying mode”. In the “dehumidifying cold air mode”, dehumidification is performed only by the endothermic action of the heat pump 9, so that the dehumidifying capacity is highly temperature-dependent, and the dehumidifying capacity is greatly reduced particularly under low temperature conditions. Further, in the “dehumidifying and drying mode”, in addition to the heat absorbing action of the heat pump 9, the moisture absorbing and releasing action of the desiccant rotor 18 by the operation of the driving means 19 and the heater 21 is added, and the dehumidifying ability is improved. In particular, under low temperature conditions, high enthalpy air heated and humidified in the heater 21 and the regeneration region 23 is supplied to the heat absorber 6, so that frost is prevented from adhering to the heat absorber 6, and the dehumidifying ability is greatly improved. In the “automatic dehumidification mode”, the drive means 19 and the heater 21 are operated when the detection value Tr of the room temperature sensor 26 is less than 15 ° C., and the drive means 19 and the heater 21 are stopped when the detection value Tr is 15 ° C. or more. . Therefore, when the environmental temperature is less than 15 ° C., the same dehumidifying ability as in the “dehumidifying and drying mode” is obtained, and when the environmental temperature is 15 ° C. or higher, the same dehumidifying ability as that in the “cold air dehumidifying mode” is obtained. As described above, by controlling based on the detection value Tr of the room temperature sensor 26, it is possible to perform an efficient and stable dehumidifying operation throughout the year regardless of temperature conditions.

  FIG. 6 is a graph showing the relationship between the set air volume of the first fan 11 and the temperatures of the heat absorber 6 and the radiator 7 at each environmental temperature. As shown in the figure, the air volume of the first fan 11 is controlled to be adjusted in three stages with respect to the environmental temperature indicated on the horizontal axis. In this control method, the ambient temperature, that is, the suction temperature into the main body 1 is detected by the room temperature sensor 26, and the control means 30 sets and switches the air volume notch of the first fan 11 based on the detected value Tr. It is realized by. The first fan 11 can switch the air volume in three stages of H notch, M notch and L notch. When the detected value Tr of the room temperature sensor 26 is 30 ° C. or higher, the H notch and detected value Tr is 10 ° C. or higher. When it is less than 30 ° C., it is set to M notch, and when it is less than 10 ° C., L notch is set. The heat pump 9 has a characteristic that the operating pressure changes in accordance with the environmental temperature. When the environmental temperature becomes high, the heat dissipating capacity in the radiator 7 decreases and the operating pressure rises. Conversely, the environmental temperature becomes low. As a result, the amount of heat absorbed by the heat absorber 6 decreases and the operating pressure decreases. An increase in operating pressure in a high temperature environment leads to an increase in the pressure of the compressor 5, and a decrease in operating pressure in a low temperature environment promotes frost formation on the heat absorber 6. Therefore, by adjusting the air volume of the first fan 11 according to the environmental temperature as described above, in a high temperature environment of 30 ° C. or higher, the amount of air supplied to the radiator 7 is increased to ensure the heat dissipation capability. The temperature of the air supplied by the second fan 12 by increasing the pressure of the radiator 7 by reducing the amount of air supplied to the radiator 7 in a low temperature environment of 10 ° C. or less while suppressing the increase in the high pressure of the compressor 5. The frost formation in the heat absorber 6 can be suppressed. The graph of FIG. 6 also shows the temperatures of the radiator 7 and the heat absorber 6 when the air volume of the first fan 11 is controlled. As shown in the figure, the temperature of the radiator 7 and the heat absorber 6 decreases stepwise as the air volume of the first fan 11 is increased, and heat is dissipated by adjusting the air volume of the first fan 11 according to the environmental temperature. It can be seen that it is possible to operate the heat pump 9 in an appropriate use range by controlling the temperatures of the heat sink 7 and the heat absorber 6 within a desired range.

  Moreover, although not shown in figure, it is good also as a structure which adjusts the setting air volume of the 1st fan 11 with the relative humidity of each environment. In this control method, the environmental relative humidity, that is, the suction relative humidity into the main body 1 is detected by the humidity sensor 27, and the control means 30 sets and switches the air volume notch of the first fan 11 based on the detected value Hr. It is realized by doing. When the detection value Hr of the humidity sensor 27 is equal to or greater than an arbitrary set value (for example, 60%), the H notch is detected. When the detected value Hr is in an arbitrary set value state (for example, 40% to less than 60%), When Hr is less than an arbitrary set value (for example, less than 40%), it is set to L notch. The heat pump 9 has a characteristic that the operating pressure of the refrigerant changes according to the environmental relative humidity, and the environmental relative humidity affects the moisture absorption / release of the desiccant rotor 18. When the environmental relative humidity becomes high, the heat dissipating capacity in the radiator 7 decreases and the operating pressure rises. Conversely, when the environmental relative humidity becomes low, the heat absorption amount in the heat absorber 6 decreases and the operating pressure decreases. . In addition, when the environmental relative humidity becomes high, the moisture release from the desiccant rotor 18 increases. Conversely, when the environmental relative humidity becomes low, the moisture release decreases. The moisture release amount of the desiccant rotor 18 greatly affects the state of the air flowing into the heat absorber 6 and makes the refrigerant operating pressure of the heat pump 9 increase and decrease significantly. An increase in operating pressure in a high humidity environment leads to an increase in the pressure of the compressor 5, and a decrease in operating pressure in a low humidity environment promotes frost formation on the heat absorber 6. Therefore, by adjusting the air volume of the first fan 11 according to the environmental relative humidity as described above, in a high-humidity environment, the amount of air supplied to the radiator 7 is increased to ensure the heat dissipation capability and the compressor. 5 is suppressed, and in a low humidity environment, the amount of air supplied to the radiator 7 is reduced to increase the pressure of the radiator 7 to increase the temperature of the air supplied by the second fan 12 in the heat absorber 6. Frosting can be suppressed. In this way, by adjusting the air volume of the first fan 11 according to the environmental relative humidity, the temperature of the radiator 7 and the heat absorber 6 can be controlled within a desired range, and the heat pump 9 can be operated in an appropriate usage range. Is possible.

  Further, although not shown, a configuration in which the set air volume of the first fan 11 is adjusted by the refrigerant evaporation temperature of the heat absorber 6 may be adopted. In this control method, the refrigerant evaporation temperature of the heat absorber 6 is detected by the evaporation temperature sensor 28 installed in the heat absorber 6, and the control means 30 sets the air volume notch of the first fan 11 based on the detected value Te. This is realized by switching. When the detection value Te of the evaporation temperature sensor 28 is not less than an arbitrary set value (for example, 5 ° C.), it is H notch. When the value Te is less than an arbitrary set value (for example, less than 0 ° C.), the fan is set to stop operating. An increase in the operating pressure of the refrigerant leads to an increase in the high pressure of the compressor 5, and a decrease in the operating pressure of the refrigerant promotes frost formation on the heat absorber 6. Therefore, by adjusting the air volume of the first fan 11 according to the refrigerant evaporation temperature of the heat absorber as described above, the heat dissipation capability can be increased by increasing the amount of air supplied to the radiator 7 in a situation where the refrigerant evaporation temperature is high. To suppress the increase in the high pressure of the compressor 5, and in a situation where the refrigerant evaporation temperature is low, the pressure of the radiator 7 is increased by reducing the amount of air supplied to the radiator 7, and the second fan 12 is supplied. The temperature of the air to perform can be raised and frost formation in the heat absorber 6 can be suppressed. Thus, by adjusting the air volume of the first fan 11 according to the refrigerant evaporation temperature, the temperatures of the radiator 7 and the heat absorber 6 can be controlled within a desired range, and the heat pump 9 can be operated in an appropriate usage range. Is possible.

  FIG. 7 is a diagram showing a configuration in which various bypass paths and purge paths are arranged in order to improve the dehumidifying efficiency of the dehumidifier. A description of the same parts as those described above will not be repeated. A first purge path 41 that supplies a part of the air sucked from the suction port 2 to the regeneration region 23 of the desiccant rotor 18 without passing through the heater 21 is formed in the second air path 14 that is blown by the second fan 12. Has been. The air flowing through the first purge path 41 is supplied to the front stage and the rear stage of the heater 21 in the rotational direction of the desiccant rotor 18. The air supplied to the subsequent stage of the heater 21 removes the residual heat of the heater 21 stored in the desiccant rotor 18 to cool the desiccant rotor 18 and accelerates moisture absorption in the moisture absorption region 24 located in the subsequent stage in the rotation direction. Do. On the other hand, the air supplied to the front stage of the heater 21 is supplied to the desiccant rotor 18 with the temperature raised by the radiant heat dissipated by the heater 21. When this high-temperature air preheats the desiccant rotor 18, the amount of direct heat of the heater 21 used for increasing the sensible heat of the desiccant rotor 18 is reduced, and the direct heat of the heater 21 is more effectively used for moisture release. . By supplying air to the desiccant rotor 18 through the first purge path 41 in this way, the moisture absorption efficiency and the regeneration efficiency are increased, and a highly efficient dehumidifying operation is possible. Further, the second air passage 14 blown by the second fan 12 is supplied with a part of the air sucked from the suction port 2 to the heat absorber 6 without passing through the heater 21 and the regeneration region 23 of the desiccant rotor 18. One bypass path 42 is formed. By allowing air to flow through the first bypass path 42, the imbalance between the air volume suitable for regeneration of the desiccant rotor 18 and the air volume suitable for cooling and dehumidification in the heat absorber 6 is eliminated, and the dehumidification efficiency is increased. . The air volume ratio between the air directly supplied to the heat absorber 6 through the first bypass path 42 and the air supplied to the heat absorber 6 through the regeneration region 23 of the desiccant rotor 18 can be appropriately designed. In order to effectively perform the heat absorption of 9 and the regeneration of the desiccant rotor 18, it is preferable to supply 10% to 70% of the entire air supplied to the heat absorber 6 to the regeneration region 23. As described above, the condensed water generated by the cooling and dehumidification in the heat absorber 6 includes moisture absorbed by the desiccant rotor 18 in the moisture absorption region 24 and moisture removed by cooling the air directly supplied from the suction port 2 to the heat absorber 6. Both are included, and the improvement of the condensation efficiency in the heat absorber 6 is promoted. Further, the first air passage 13 blown by the first fan 11 passes the air sucked from the suction port 2 through a part of the moisture absorption region 24 of the desiccant rotor 18 and supplies the second purge passage 43 to the radiator 7. Is formed. The air flowing through the second purge path 43 is supplied to the front and rear stages of the regeneration region in the rotational direction of the desiccant rotor 18. The air supplied to the rear stage of the regeneration region 23 removes the residual heat stored in the desiccant rotor 18 by being input in the regeneration region 23 to cool the desiccant rotor 18, and absorbs moisture in the moisture absorption region 24 located downstream of the rotation direction. It works to speed up. Depending on the environmental temperature and humidity, moisture is absorbed into the desiccant rotor 18 also in the second purge air passage 43. On the other hand, the air supplied to the front stage of the regeneration region 23 has a function of preheating the desiccant rotor 18 cooled by the air cooled by the heat absorber 6. That is, the desiccant rotor 18 is preheated with room air, the amount of direct heat of the heater 21 used for increasing the sensible heat of the desiccant rotor 18 is reduced, and the direct heat of the heater 21 is more effectively used for moisture release. Become. By supplying air to the desiccant rotor 18 through the second purge path 43 in this manner, the moisture absorption efficiency and the regeneration efficiency are increased, and a highly efficient dehumidifying operation is possible. In addition, the first air passage 13 blown by the first fan 11 has a second bypass route for supplying a part of the air after passing through the moisture absorption region 24 of the desiccant rotor 18 in the second air passage 14 to the radiator 7. 44 is formed. The air flowing through the second bypass path 44 is air that has passed through the regeneration region 23 of the desiccant rotor 18, the heat absorber 6, and the moisture absorption region 24 of the desiccant rotor 18 by the second fan 12, and has a lower temperature than the room air. It is air. By introducing air having a temperature lower than the room air into the radiator 7, the radiator 7 can be cooled more efficiently than cooling with the room air. In this way, by supplying a part of the air in the second air passage 14 to the radiator 7 by the second bypass passage 44, the heat pump 9 can be operated efficiently, and the dehumidifying operation is performed efficiently. .

  As described above, with the configuration and operation described above, the dehumidifier of the present embodiment has the following effects.

  While the main body 1 is not provided with an annular circulation passage and a heat exchanger for water recovery, the moisture absorbed by the desiccant rotor 18 is recovered as condensed water by the heat absorber 6 to simplify and reduce the size of the apparatus. Further, by supplying the air that has been cooled by the heat absorber 6 and whose relative humidity has been lowered to the moisture absorption region 24, the relative humidity difference between the air passing through the moisture absorption region 24 and the regeneration region 23 of the desiccant rotor 18 can be increased. In addition, the moisture absorption / release efficiency of the desiccant rotor 18 can be increased, and the dehumidification efficiency can be increased.

  In addition, by supplying the air sucked directly from the suction port 2 to the heat absorber 6 from the first bypass path 42, it is possible to secure an optimum air flow rate in each of the regeneration region 23 and the heat absorber 6, and the desiccant rotor. Thus, the regeneration efficiency of 18 and the heat absorption efficiency of the heat absorber 6 can be increased, and the dehumidification efficiency can be increased.

  Further, air is supplied through the first purge path 41 to the regeneration region 23 located in the upstream and downstream of the heater 21 in the rotational direction of the desiccant rotor 18, and the desiccant rotor 18 is cooled by the air supplied to the downstream of the heater 21 to absorb moisture. The dehumidifying efficiency can be increased by speeding up moisture absorption at 24 and preheating the desiccant rotor 18 with air supplied to the front stage of the heater 21 to facilitate release of moisture.

  Further, by supplying the air sucked directly from the suction port 2 to the moisture absorption region 24, moisture can be adsorbed from the air, the moisture absorption amount and the moisture release amount of the desiccant rotor 18 are increased, and the dehumidification efficiency is improved. be able to.

  In addition, after being cooled by the heat absorber 6, after passing through the moisture absorption region 24 of the second air passage 14, the temperature of which is lower than the room air by the air that has been given adsorption heat by moisture absorption in the moisture absorption region 24. Is supplied to the radiator 7 of the first air passage 13 so that the amount of heat released in the radiator 7 can be increased as compared with the case where the indoor air is directly supplied. As a result, the amount of heat absorbed in the heat absorber 6 is increased. The condensation in the heat absorber 6 can be promoted, and the dehumidification efficiency can be increased.

  In addition, when the temperature is low, the combined dehumidifying operation 39 is executed to supply the humidified air containing the moisture released by the desiccant rotor 18 in the regeneration region 23 to the heat absorber 6 to ensure the enthalpy difference with the refrigerant 8. Thus, the heat pump 9 can be operated to increase the dehumidification efficiency.

  Further, when the air sucked from the suction port 2 is at a low temperature, the dehumidifying amount is secured by executing the combined dehumidifying operation 39, and otherwise, the environment is controlled by reducing the power consumption by executing the single dehumidifying operation 40 of only the heat pump 9. Efficient dehumidifying operation adapted to the temperature can be performed.

  Further, when the air sucked from the suction port 2 is highly humid, the dehumidifying amount is increased by executing the combined dehumidifying operation 39, and otherwise, the single dehumidifying operation 40 of only the heat pump 9 is executed to suppress the power consumption. An efficient dehumidifying operation adapted to the dehumidifying load can be performed.

  Further, the high-temperature air supplied and heated by the radiator 7 by the first fan 11 and the low-humidity air supplied by the second fan 12 to the moisture absorption region 24 and the heat absorber 6 are dehumidified. According to the purpose of use, an exhaust form that is separated into four and discharged and an exhaust form that discharges both high-temperature air and low-humidity air from the outlet 3 can be selected.

  Further, when the discharge destination of the first fan 11 is set to the exhaust port 4, the single dehumidifying operation 40 is executed, and the adsorption heat of the desiccant rotor 18 and the residual heat of the heater 21 are added to the air blown by the second fan 12. By discharging from the air outlet 3 without giving it, an increase in the room temperature can be suppressed.

  Further, when the heat absorber 6 is frosted and the temperature of the heat absorber 6 becomes lower than a predetermined value, the defrosting operation mode is executed to supply the heat of the heater 21 to the heat absorber 6 for defrosting. By removing the attached frost without providing a special member, it is possible to dehumidify again and efficiently dehumidify.

  Further, in the defrosting operation mode, by stopping the compressor 5, the endothermic action in the heat absorber 6 is stopped, the defrosting of the heat absorber 6 is performed more effectively, and the time of the defrosting operation mode is shortened. Can do.

  Further, when the temperature of the supply air is low, the air volume of the first fan 11 is decreased, and conversely, when the temperature of the supply air is high, the air volume of the first fan 11 is increased to adjust the heat dissipation amount in the radiator 7, and the heat pump 9 can be adjusted appropriately, and the reliability of the compressor 5 can be ensured.

  In addition, when the supply air humidity is low, the air flow of the first fan 11 is reduced. Conversely, when the supply air humidity is high, the air flow of the first fan 11 is increased to appropriately adjust the operating pressure of the heat pump 9. Can do.

  In addition, when the temperature of the heat absorber 6 is low, the air volume of the first fan 11 is reduced. Conversely, when the temperature of the heat absorber 6 is high, the air volume of the first fan 11 is increased to appropriately adjust the operating pressure of the heat pump 9. can do.

  The contents described above are only described for one mode for carrying out the invention, and the present invention is not limited to the above embodiment.

  For example, in the above embodiment, the suction port 2 is opened on one side surface of the main body 1, the outlet port 3 is opened on the upper surface of the main body 1, and the exhaust port 4 is opened on the side surface opposite to the suction port 2. The position may be provided at the position, and is not limited to the above position.

  In the above-described embodiment, the damper 15 is switched in two stages: a switching position 16 where the discharge destination of the first fan 11 is set on the outlet 3 side and a switching position 17 which is set on the exhaust port 4 side. However, the switching pattern of the damper 15 is not limited to the above two stages. For example, it may be configured to be set at an intermediate position between the switching position 16 and the switching position 17, and the discharge destination of the first fan 11 may be set to both the outlet 3 and the outlet 4. The switching pattern of the damper 15 can be applied to various patterns such as two stages of the switching position 16 and the intermediate position, two stages of the intermediate position and the switching position 17, and three stages of the switching position 16 and the intermediate position and the switching position 17. it can.

  In the above embodiment, air is supplied from the suction port 2 to both the front and rear stages of the heater 21 in the rotational direction of the desiccant rotor 18 by the first purge path 41. The first purge path 41 may be configured to supply air to only one of them.

  In the above embodiment, air is supplied from the suction port 2 to both the front and rear stages of the regeneration region 23 in the rotational direction of the desiccant rotor 18 by the second purge path 43. The second purge path 43 may be configured to supply air to only one of the subsequent stages.

  Further, in the above embodiment, in the “automatic dehumidification mode”, the combined dehumidification operation in which the detection value Tr of the room temperature sensor 26 is less than 15 ° C. and the heater 21 and the drive means 19 are operated to combine the moisture absorption / desorption action of the desiccant rotor 18. 39, the heater 21 and the drive means 19 are stopped when the detected value Tr is 15 ° C. or higher, and the single dehumidifying operation 40 is performed in which the dehumidification is performed only by the heat pump 9, but for example, the output of the heater 21 is large, It is configured to be switchable to two small steps, and the combined dehumidification operation 39 is executed by setting the output of the heater 21 to a large value when the detection value Tr is less than 10 ° C. The multi-dehumidification operation 39 is executed by setting the output of 21 small, and the heater 21 is stopped when the detection value Tr is 20 ° C. or higher and the single dehumidification operation 40 is executed. It may be in operation form.

  Moreover, in the said embodiment, although it controlled so that the heater 21 was stopped when "dehumidification cold wind mode" was selected by the operation part 31, it comprised so that the output of the heater 21 could be adjusted and "dehumidification cold wind mode" The heater 21 may be controlled to operate at a low output. In that case, the desiccant rotor 18 may perform the moisture absorption / release action while operating the driving means 19 to supply cold air.

  In addition, a filter is detachably disposed on the opening surface of the suction port 2 to suppress the inflow of foreign matter into the main body 1 or a louver mechanism is provided at the exhaust port 4 or the air outlet 3 to change the exhaust air exhaust direction. You may design suitably, such as comprising.

  Further, an exhaust duct may be provided in the exhaust port 4 so as to be detachable, and the high-temperature air discharged from the exhaust port 4 may be discharged away from the air outlet 3. In this case, when the exhaust from the exhaust duct is discharged to a space different from the space where the main body 1 is disposed, only low-temperature air from the outlet 3 is supplied to the space where the main body 1 is placed. Can also improve comfort.

  In addition, the damper 15 is switched by moving the shielding plate by the drive motor. However, the operation unit 31 on the upper surface of the main body 1 is provided with a lever connected to the shielding plate so as to be switched manually. Also good. In that case, it is desirable that a magnet is provided on the shielding plate and a position detector such as a Hall element is provided at any position, for example, the switching position 16 side, so that the set position of the damper 15 can be detected.

  As described above, the dehumidifier according to the present invention combines a heat pump and a desiccant rotor in a small and simple configuration, and can efficiently dehumidify using a heat pump even at low temperatures. A dehumidifier, a dryer, and a clothes dryer It is suitable for applications where a highly efficient dehumidifying function is desired, such as a machine, a washing dryer, a bathroom ventilation dryer, a solvent recovery device or an air conditioner.

Schematic sectional view of a dehumidifier according to Embodiment 1 of the present invention Control block diagram of the dehumidifier Schematic configuration diagram of the operation unit of the dehumidifier The figure which shows the control operation list according to operation mode of the same dehumidifier Dehumidifying capacity characteristics graph for each operating mode of the dehumidifier A graph showing the relationship between the set air volume of the first fan and the temperature of the heat absorber and radiator at each environmental temperature of the dehumidifier Schematic sectional view of other dehumidifiers

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Main body 2 Suction port 3 Outlet 4 Exhaust port 5 Compressor 6 Heat absorber 7 Radiator 8 Refrigerant 9 Heat pump 10 Depressurization mechanism 11 First fan 12 Second fan 13 First air path 14 Second air path 18 Desiccant rotor 19 Drive Means 21 Heater 23 Regeneration area 24 Moisture absorption area 39 Combined dehumidification operation 40 Single dehumidification operation

Claims (15)

A compressor (5) for compressing the refrigerant (8) and a radiator (7) for radiating heat to the supply air in the main body (1) having the inlet (2) and the outlet (3) opened. A vapor compression heat pump (9) connected by piping to a decompression mechanism (10) that expands and decompresses the refrigerant (8) and a heat absorber (6) that absorbs heat from supply air by the refrigerant (8); A desiccant rotor (18) that rotates by means (19) and absorbs moisture from the supply air in the moisture absorption region (24) and is heated in the regeneration region (23) to release moisture, and a heater for heating the regeneration region (23) (21), a first air passage (13) that sucks air from the suction port (2), supplies the air to the radiator (7), and discharges it from the outlet (3); and the suction port (2) ) Is sucked in and supplied to the regeneration area (23), A second air passage (14) for supplying air supplied to the region (23) to the heat absorber (6), and further supplying the air to the moisture absorption region (24) and discharging it from the outlet (3). Dehumidifier equipped. The first bypass path (42) for directly supplying the air sucked from the suction port (2) to a part of the air supplied to the heat absorber (6) in the second air path (14). The dehumidifier according to 1. In the second air passage (14), a first purge route (a part of the air sucked from the suction port (2) is supplied to the regeneration region (23) of the desiccant rotor (18) without passing through the heater (21). The dehumidifier according to claim 1 or 2, wherein 41) is formed. In the first air passage (13), a second purge path (43) is formed for supplying a part of the air sucked from the suction port (2) to the moisture absorption region (24) of the desiccant rotor (18). Item 4. The dehumidifier according to any one of Items 1 to 3. At least a part of the air that has passed through the moisture absorption region (24) of the second air passage (14) is supplied to at least a part of the air supplied to the radiator (7) of the first air passage (13). The dehumidifier according to any one of claims 1 to 4. A first fan (11) for blowing air to the first air path (13) and a second fan (12) for blowing air to the second air path (14) are provided, and the first fan (11) and the second fan (12 And a single dehumidifying operation (40) for operating the compressor (5), the first fan (11), the second fan (12), the compressor (5), the drive means (19) and the heater (21). The dehumidifier according to any one of claims 1 to 5, wherein the combined dehumidifying operation (39) for operating the switch is configured to be switchable. The dehumidifier according to claim 6, wherein the switching between the single dehumidifying operation (40) and the combined dehumidifying operation (39) is performed based on the temperature of the air sucked from the suction port (2). The dehumidifier according to claim 6 or 7, wherein the switching between the single dehumidifying operation (40) and the combined dehumidifying operation (39) is performed based on the humidity of the air sucked from the suction port (2). The exhaust port (4) is opened on a surface different from the opening surface of the air outlet (3) of the main body (1), and the discharge destination of the first fan (11) is either the air outlet (3) or the air outlet (4). The dehumidifier according to any one of claims 6 to 8, wherein the dehumidifier is configured to be switchable. The dehumidifier according to claim 9, wherein the single dehumidifying operation (40) is performed when the discharge destination of the first fan (11) is set to the exhaust port (4). 11. The defrosting operation mode in which the heater (21) and the drive means (19) are operated when the temperature of the heat absorber (6) is lower than a predetermined value. Dehumidifier as described. The dehumidifier according to claim 11, wherein the compressor (5) is stopped in the defrosting operation mode. The dehumidifier according to any one of claims 6 to 12, wherein the air volume of the first fan (11) is adjusted based on the temperature of air sucked from the suction port (2). The dehumidifier according to any one of claims 6 to 13, wherein the air volume of the first fan (11) is adjusted based on the humidity of air sucked from the suction port (2). The dehumidifier according to any one of claims 6 to 14, wherein the air volume of the first fan (11) is adjusted based on the temperature of the heat absorber (6).

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