JP2006341217A - Dehumidifier - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a dehumidifier capable of preventing the loss of sensible heat caused by heat transmission from a regeneration zone of a dehumidifying rotor to its dehumidifying zone and preventing the decrease of dehumidifying capability of the dehumidifying zone caused by moisture absorption that occurs in its purge zone. <P>SOLUTION: The dehumidifier is composed of a rotating dehumidifying rotor (1), an air supply device (2) that is constituted so as to feed air to be dehumidified to the dehumidifying zone (11) and the purge zone (12) of the dehumidifying rotor (1), an air supply line (L0) that supplies the regeneration zone (13) of the dehumidifying rotor (1) with the air fed from the air supply device (2) to the purge zone (12) of the dehumidifying rotor (1), and a heating device (4, 62) disposed in communication with the air supply line (L0). <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a dehumidifier that removes moisture in indoor air, and more particularly to a dry dehumidifier (desiccant dehumidifier) that uses a solid hygroscopic material such as silica gel or zeolite as the hygroscopic material.

  There are two types of indoor dehumidification means: compression-type supercooling dehumidification and desiccant-type moisture adsorption dehumidification.

  The supercooling dehumidification by the compression method has low power consumption and excellent energy saving, and the gradual mass increases as the temperature becomes high, and exhibits excellent dehumidifying performance especially for hot and humid air in summer.

  On the other hand, the moisture adsorption dehumidification by the desiccant method requires less compressors than the compression method, so that the operation sound is low, the device can be made small and light, and the dehumidifying ability for low temperature and high humidity air is particularly excellent. Based on the high efficiency in a low-temperature and high-humidity environment, for example, as a dehumidification technique suitable for applications such as anti-condensation measures in winter in the Sea of Japan, it has rapidly spread in recent years.

The general disadvantage of these dehumidifiers is that, firstly, the enthalpy of air exhausted from dehumidification is always higher than the air sucked into the dehumidifier, which increases the burden on the air conditioner in the room in summer. There is a point.
And as a 2nd fault, there exists a point which requires the space for installation large apparatus.

In the desiccant type dehumidifier, several techniques have been proposed in order to improve these disadvantages.
As one of them, a purge zone is provided in the dehumidification rotor in addition to the dehumidification zone and regeneration zone, and a part of the dehumidified air is bypassed and supplied to the purge zone, so that excess sensible heat in the regeneration zone is dehumidified. A technique for preventing inflow into the zone has been proposed (see, for example, Patent Document 1).
According to this technology, it is possible to suppress an increase in the burden on the air conditioner in the room.

  In addition, a technique has been proposed in which the air path in the desiccant air conditioner is devised so that air is sent to two air paths with one fan, the equipment configuration is simplified, and the equipment size is reduced ( For example, see Patent Technology 2).

However, in the technique of Patent Document 1, the sensible heat loss to the dehumidification zone can be reduced, but the air that has passed through the purge zone is trapped (purged) and dehumidified at the same time. There is a concern of causing a decline in
Here, in general, the regeneration air having lower humidity improves the regeneration capacity in the regeneration zone, and accordingly, the dehumidification capacity also improves. However, in the technique of Patent Document 1, exhaust gas of a micro gas turbine is used as the regeneration air. In comparison with the air flow rate passing through the purge zone, an overwhelming amount of micro gas turbine exhaust gas is supplied. Therefore, the effect of reducing the humidity of the regeneration air in the purge zone becomes extremely small, and the adverse effect of the reduction in the dehumidifying capacity in the dehumidifying zone becomes greater.
In addition, since two fans are used, an increase in the size of the apparatus is inevitable.

In Patent Document 2, since a large amount of sensible heat accumulated in the regeneration zone in the desiccant rotor flows into the dehumidification zone, the enthalpy of the air supplied to the room rises during the dehumidification process, and the air conditioner load in the room It becomes a factor to increase. Therefore, the energy-saving property of indoor air-conditioning equipment (compression air conditioner, radiation cooling system, etc.) is impaired.
In particular, in a type of cooling system that radiates cold (so-called “radiant cooling system”), there is a possibility of causing a situation in which the air conditioning load becomes larger than the cooling capacity.
JP-A-2005-55049 JP 2002-102641 A

  The present invention has been proposed in view of the above-described problems of the prior art, and prevents sensible heat loss caused by the heat quantity in the regeneration area of the dehumidification rotor being transferred to the dehumidification area, and absorbs moisture in the purge area. An object of the present invention is to provide a dehumidifier capable of preventing a decrease in dehumidifying capacity of a dehumidifying area due to the occurrence of the dehumidification.

  The dehumidifier of the present invention includes a rotating dehumidification rotor (1) and an air supply device (for example, a blower 2) that supplies air to be dehumidified to the dehumidification rotor (1). 2) sucks and pressurizes air to be dehumidified, and pressurizes the pressurized air into a region corresponding to the dehumidifying region (or processing region 11) of the dehumidifying rotor (1) and a region corresponding to the purge region (12). The air supplied from the air supply device (for example, blower 2) to the purge area (12) of the dehumidification rotor (1) is supplied to the regeneration area (13) of the dehumidification rotor (1). It has a line (L0) and a heating device (heat source 4, heat dissipation surface 62 of thermoelectric element) interposed in the line (L0) (FIG. 1: claim 1).

  The dehumidifier of the present invention includes a rotating dehumidification rotor (1) and an air supply device (for example, a blower 2) that supplies air to be dehumidified to the dehumidification rotor (1). The blower 2) sucks air that has passed through the dehumidifying area (11) of the dehumidifying rotor (1) and pressurizes the sucked air to correspond to the dehumidifying area (or processing area 11) of the dehumidifying rotor (1). And an area corresponding to the purge area (12). The air supplied from the air supply device (for example, the blower 2) to the purge area (12) of the dehumidification rotor (1) is supplied to the dehumidification rotor ( 1) The line (L0) supplied to the regeneration zone (13) and the heating device (the heat source 4, the heat radiation surface 62 of the thermoelectric element) interposed in the line (L0) (FIG. 3: Claim 2).

  In the present invention, it is preferable to install a heat exchanger (5) in a line (L3) for supplying air that passes through the dehumidification zone (11) of the dehumidification rotor (1) to the room (E) (FIG. 4: claim). Item 3).

  Moreover, you may interpose a heat exchanger (51) in the line (L2) which connects an air supply apparatus (2) and a dehumidification rotor (1) (FIG. 5: Claim 4).

  Alternatively, a heat exchanger (51) may be interposed on the upstream side of the air supply device (2) (FIG. 6: claim 5).

  A heat exchanger (51) is interposed in a line (L50) through which air passes through the purge zone (12) and the regeneration zone (13) of the dehumidification rotor (1), and the line (L50) is placed in the room (E ) Side is preferable (FIG. 7: Claim 6).

  In the present invention, a thermoelectric element (6) is provided, and the heat dissipation surface (62) of the thermoelectric element (6) is heated from the purge area (12) to heat the air flowing toward the regeneration area (13) of the dehumidification rotor (1). The cooling surface (61) of the thermoelectric element (6) is directed to the room (E) (via the dehumidification area 11 of the dehumidification rotor 1). The line (L0) communicates with the regeneration area (13). In order to cool the air, it is preferably interposed in a line (L3) from the dehumidification zone (11) to the room (E) (FIG. 11: claim 7).

According to the present invention having the above-described configuration, the latent heat flowing from the regeneration zone (13) to the dehumidification zone (11) is removed by the air passing through the purge zone (12). Therefore, the dehumidification zone (11) is prevented from being heated by the amount of heat in the regeneration zone (13) (heat held by the regenerated desiccant in the dehumidification rotor 1). As a result, loss due to the temperature rise of the dehumidified air (so-called “sensible heat loss”) can be prevented.
Also, only the air dehumidified with the desiccant (existing in the purge area 12) is used for regeneration via the purge area (12). That is, the regeneration process can be performed only with the air dehumidified in the purge zone (12), so that the regeneration efficiency is improved. This more than compensates for the disadvantage of dehumidification in the purge zone (12).

  Moreover, according to this invention, the water | moisture content exceeding a dew point can be removed by temperature-falling the air which does not go through the dehumidification area | region (11) of a dehumidification rotor (1) with a heat exchanger (51). If comprised in that way, the fall of the dehumidification performance by dehumidifying in a purge area | region (12) can be compensated.

  Alternatively, it is possible to reduce the cooling load by lowering the temperature of the air that does not pass through the dehumidification zone (11) of the dehumidification rotor (1) with the heat exchanger (51) (temperature increase during heating).

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

First, a first embodiment will be described with reference to FIG.
A dehumidifier 101 according to the first embodiment of FIG. 1 includes a dehumidification rotor 1, a blower 2, and a casing 3, and the casing 3 is attached to a wall W in the room E.

  As shown in FIG. 2, the dehumidifying rotor 1 is divided into a dehumidifying area 11, a purge area 12, and a regeneration area 13 that are processing areas.

  The dehumidifying rotor 1 is disposed in the casing 3, and the blower 2 is disposed on the air inlet 31 side formed in the casing 3 with respect to the rotor 1.

A dry air return port 32 for returning the dehumidified air to the room E is formed above the dehumidifying rotor 1 of the casing 3 in FIG. 1 on the opposite side (right side in the drawing) to the blower 2.
Further, the casing 3 is formed with an exhaust port 33 for exhausting the air that has passed through the regeneration zone 13 of the dehumidifying rotor 1, that is, exhaust containing moisture, from the dehumidifier 101 to the outdoor F.

  The purge area 12 and the regeneration area 13 of the dehumidifying rotor 1 communicate with each other through a line L0, and the line L0 is provided with a heater 4 as a heat source.

Part of the air to be dehumidified (the air flowing through the line L1) sucked into the blower 2 from the room E passes through the dehumidifying area 11 of the dehumidifying rotor 1 at that time. Water (containing the air flowing through L2) is removed.
The air from which moisture has been removed is returned to the room E again via the line L3 and the dry air return port 32.

  The remainder of the air sucked into the blower 2 (air flowing through the line L4) is heated when it passes through the purge region 12 of the dehumidifying rotor 1, and is heated by the heater 4 in the line L0. Then, the moisture contained in the desiccant in the regeneration zone 13 is removed (from the desiccant in the regeneration zone 13) by the heated air. Air (exhaust gas) containing moisture removed from the desiccant in the regeneration zone 13 is exhausted to the outdoor F through the exhaust port 33 from the line L5.

  In the first embodiment shown in FIGS. 1 and 2, the sensible heat flowing from the regeneration zone 13 to the dehumidifying zone 11 is removed by the air passing through the purge zone 12. Therefore, the dehumidification zone 11 is prevented from being heated by the heat amount of the regeneration zone 13 (heat held by the regenerated desiccant in the dehumidification rotor 1).

  The air heated after passing through the purge zone 12 is further heated by the heater 4, and then its entire flow rate is sent to the regeneration zone 13 of the dehumidifying rotor 1, and the dehumidifying rotor 1 is heated by the amount of heat held by the heated air. The desiccant in the reproduction area 13 is reproduced.

  If the configuration is as shown in FIG. 1, the configuration is simple, and the pressure loss is reduced by the simplification of the structure.

With such a configuration, when high-humidity air (air to be dehumidified) passes through the purge region 12, the high-humidity air that passes through the purge region 12 by the desiccant (regenerated desiccant) in the purge region 12 Is dehumidified.
Here, it is preferable that the air used for regeneration does not contain moisture. In that sense, it is advantageous that the air sent to the regeneration zone 13 passes through the purge zone 12 before that.

  Furthermore, in the first embodiment shown in FIGS. 1 and 2, unlike the technique of Patent Document 1, a large amount of air (exhaust gas from the micro gas turbine) that has passed through the purge zone is sent to the regeneration zone. It is not necessarily done. Therefore, the effect of dehumidifying the air in the purge area is clearly exhibited.

In the blower 2 as an air supply device, the ratio of the flow rate toward the dehumidification zone 11 and the flow rate toward the purge zone 12 of the dehumidification rotor 1 becomes a predetermined ratio, and the pressure loss in the purge zone 12 and the pressure loss in the regeneration zone 13 and the pipe The exhaust amount after passing through the road resistance is configured to be a predetermined amount.
A certain amount of exhaust is required for indoor air exchange (ventilation). Here, regarding the exhaust amount, it is necessary to consider the pressure loss in both the purge region 12 and the regeneration region 13, and the “pressure loss” relates to the area ratio, the flow rate ratio, the pipe resistance, and the like of the dehumidifying rotary 1.

Next, the dehumidifier 102 of 2nd Embodiment is demonstrated with reference to FIG.
In the first embodiment of FIG. 1, high-humidity air is blown by the blower 2 to the dehumidifying area (processing area) 11 side and the purge area 12.
In contrast, in the second embodiment of FIG. 3, high-humidity air (L 11) is sucked (L 12) into the blower 2 via the dehumidifying area 11 of the dehumidifying rotor 1.
The dehumidified air sucked into the blower 2 (L12) is sent to the indoor E side (L13) and the purge area 12 (L14) of the dehumidifying rotor 1, respectively.

  Regarding other configurations and operational effects, the second embodiment of FIG. 3 is the same as the first embodiment of FIG.

 Next, the dehumidifier 103 of 3rd Embodiment is demonstrated with reference to FIG.

In the third embodiment of FIG. 4, heat exchange is performed in a line L <b> 3 that guides the air dehumidified via the dehumidification area (treatment area) 11 of the dehumidification rotor 1 to the room E, as compared with the embodiment of FIG. 1. In this embodiment, the air dehumidified by the heat exchanger 5 is cooled (heated if heating).
If the dehumidified air is cooled (or heated) and supplied to the room E by the heat exchanger 5, the load (cooling load or heating load) of the air conditioning equipment (not shown) in the room E (not shown) is reduced.

  Other configurations and effects in the third embodiment of FIG. 4 are the same as those of the first embodiment of FIG.

  Next, the dehumidifier 104 of 4th Embodiment is demonstrated with reference to FIG.

In 3rd Embodiment of FIG. 4, the heat exchanger 5 was interposed in the line L3 through which the air dehumidified via the dehumidification area (processing area) 11 flows. On the other hand, 4th Embodiment of FIG. 5 is Embodiment which interposed the heat exchanger 51 in the line L2 which connects the blower 2 and the process area 11 of the dehumidification rotor 1.
In FIG. 5, the air blown out from the blower 2 (air to be dehumidified) is cooled or cooled by the heat exchanger 51. As a result of the cooling, the air to be dehumidified is turned on, so that the moisture w (depicted as a drain in FIG. 5) beyond the dew point is removed.
Here, in the heat exchanger 51, for example, a refrigerant pipe and a cold water pipe (not shown) communicate with each other.

In the desiccant method, the higher the relative humidity of the air to be dehumidified, the higher the efficiency.
In FIG. 5, since the water w below the dew point is removed by the heat exchanger 51, the relative humidity of the air to be dehumidified sent to the dehumidification rotor 1 is approximately 100%. As a result, the dehumidification efficiency is improved.

  Other configurations and effects in the fourth embodiment shown in FIG. 5 are the same as those in the embodiment shown in FIGS.

 Next, the dehumidifier 105 of 5th Embodiment is demonstrated with reference to FIG.

In 4th Embodiment of FIG. 5, the heat exchanger 51 was interposed in the line 12 which connects the blower 2 and the process area 11 of the dehumidification rotor 1. On the other hand, in the fifth embodiment of FIG. 6, a heat exchanger 51 is interposed in a line L1 (upstream position where the fan sucks the air to be dehumidified) that supplies the air to be dehumidified to the blower 2. Yes.
By configuring in this way, the air sucked into the blower 2 (air to be dehumidified) is cooled by the heat exchanger 51 and the temperature is lowered, and the water w exceeding the dew point is removed.

  Other configurations and effects in the fifth embodiment of FIG. 6 are the same as those of the fourth embodiment of FIG.

 Next, the dehumidifier 106 of 6th Embodiment is demonstrated with reference to FIG.

 The sixth embodiment of FIG. 7 is an example in which a heat exchanger 51 is interposed in a line L50 through which air after regeneration of the desiccant in the regeneration region 13 of the dehumidifying rotor 1 flows.

By lowering the temperature of the air after regeneration of the desiccant with the heat exchanger 51, the water w in excess of the dew point in the air can be removed.
The air from which moisture has been removed by the heat exchanger 51 is low-humidity air, so that it is not exhausted outside the system, for example, outdoors (or outdoors), and into the room E, similarly to the air passing through the treatment area 11. Supplied.

  The other configurations and effects in the sixth embodiment in FIG. 7 are the same as those in the embodiment in FIGS.

 Next, the dehumidifier 107 of 7th Embodiment is demonstrated with reference to FIG.

The seventh embodiment of FIG. 8 is an embodiment in which the third embodiment of FIG. 4 and the sixth embodiment of FIG. 7 are combined.
In the embodiment of FIG. 8, the heat exchanger 5 is interposed in a line L <b> 3 that guides the dehumidified air to the room E via the treatment area (dehumidification area) 11 of the dehumidification rotor 1. At the same time, a heat exchanger 51 is interposed in a line L50 through which air after regenerating the regeneration region 13 of the dehumidifying rotor 1 flows.

With such a configuration, the air dehumidified by the dehumidifying rotor 1 is cooled (or heated) by the heat exchanger 5 and supplied to the room E, thereby reducing the load on the air conditioning equipment (cooling load or heating load). I can do it.
Further, since the air after regeneration of the desiccant is cooled by the heat exchanger 51 and the moisture w exceeding the dew point is removed, a certain amount of moisture is removed from the air passing through the heat exchanger 51. The humidity is low. Then, such low-humidity air is supplied to the room E (not shown) in the same manner as the air that has passed through the treatment area 11 without being exhausted to the outside (outdoor) F.

  Other configurations and operational effects are also the same as those of the embodiment of FIGS.

 Next, the dehumidifier 108 of 8th Embodiment is demonstrated with reference to FIG.

The eighth embodiment of FIG. 9 is an embodiment according to a combination of the embodiment of FIG. 4 and the embodiment of FIG.
That is, in the eighth embodiment of FIG. 9, the heat exchanger 5 is interposed in the line L3 that guides the air dehumidified through the treatment area 11 of the dehumidification rotor 1 to the room E, and the blower 2 and A heat exchanger 51 is interposed in a line L2 that communicates with the treatment area 11 of the dehumidifying rotor 1.

After the temperature of air blown from the blower 2 (air to be dehumidified) is lowered by the heat exchanger 51 to remove the moisture w exceeding the dew point, the air from which the moisture exceeding the dew point has been removed is removed by the dehumidifying rotor 1. Further dehumidification. Thereby, the further improvement of a dehumidification capability is anticipated.
And since the temperature is lowered (or raised) by the heat exchanger 5 in the line L3 and supplied to the room E, the load (cooling load or heating load) of the air conditioning equipment is reduced.

 About another structure and effect, it is the same as that of embodiment of FIG. 4 and embodiment of FIG.

Next, the dehumidifier 109 of 9th Embodiment is demonstrated with reference to FIG.
The ninth embodiment of FIG. 10 is an embodiment according to the combination of the embodiment of FIG. 4, the embodiment of FIG. 5, and the embodiment of FIG.

 That is, in the ninth embodiment of FIG. 10, the heat exchanger 5 is interposed in the line L3 that guides the air dehumidified through the treatment area 11 of the dehumidification rotor 1 to the room E, and the blower 2 and the dehumidification are installed. A heat exchanger 51 is interposed in a line L2 that communicates with the treatment area 11 of the rotor 1, and a heat exchanger 51 is interposed in a line L50 through which air after regenerating the regeneration area 13 of the dehumidifying rotor 1 flows. ing.

The temperature of air blown out from the blower 2 (air to be dehumidified) is lowered by the heat exchanger 51, and the water w exceeding the dew point is removed. And since the air from which the water | moisture-content w exceeding the dew point was removed is further dehumidified by the dehumidification rotor 1, a dehumidification capability improves.
And since the temperature is lowered (or raised) by the heat exchanger 5 in the line L3 and supplied to the room E, the load (cooling load or heating load) of the air conditioning equipment is reduced.
Further, the air after regeneration of the desiccant is cooled by the heat exchanger 51 to remove the water w exceeding the dew point. In other words, since the moisture is removed by the heat exchanger 51, the humidity of the air flowing through the line L50 decreases. As a result, the air whose humidity has decreased can be supplied to the room E in the same manner as the air passing through the treatment area 11 without being exhausted outside the system (outdoor or outdoor).

 About another structure and effect, it is the same as that of 3rd Embodiment of FIG. 4, 4th Embodiment of FIG. 5, and 6th Embodiment of FIG.

Next, the dehumidifier 110 of 10th Embodiment is demonstrated with reference to FIG.
In the tenth embodiment of FIG. 11, the heat radiation surface 62 of the thermoelectric element 6 is connected to the line L0 extending from the purge area 12 to the regeneration area 13 as a heat source for heating the air supplied to the regeneration area 13 via the purge area 12. The cooling surface 61 of the thermoelectric element 6 is replaced with a line L3 in place of the heat exchanger (for example, reference numeral 5 in FIG. 4) that is interposed and is cooled before the dehumidified air is supplied to the room E. It is arranged.

 According to the embodiment of FIG. 11, compared to the third embodiment of FIG. 4, there is no need to lay out a pipe through which a low-temperature fluid (high-temperature fluid during cooling: high-temperature fluid during heating) flows in the heat exchanger. Can be simplified.

 About another structure and an effect, it is the same as that of 3rd Embodiment of FIG.

Next, the dehumidifier 111 of 11th Embodiment is demonstrated with reference to FIG.
The eleventh embodiment of FIG. 12 is an embodiment in which the third embodiment of FIG. 4 is combined with an air conditioning unit using a radiation panel.

 In 11th Embodiment of FIG. 12, the cooling unit 7, the heat exchanger 8 for an air conditioning, and the radiation panel 9 for air conditioning are combined with the dehumidifier 111 substantially the same as 3rd Embodiment of FIG.

 Here, the radiant panel (for example, ceiling panel) 9 is a panel that receives cold heat (hot water) from cold water (hot water) supplied from the air conditioning heat exchanger 8 through the air conditioning line (cold water line) Lc into the panel 9. 9 is configured to radiate to the room E to be air-conditioned.

 In the case of cooling using the radiant panel 9 (radiant cooling), the temperature of the cold water sent to the radiant panel 9 is 12 to 13 ° C. And the cold water temperature sent to the radiation panel 9 from the heat exchanger 8 for an air conditioning is 9 degreeC, for example. Therefore, for example, if the temperature of 9 ° C. cold water is raised to 12 to 13 ° C. by the heat exchanger 5 of the dehumidifier 111 and then sent to the radiation panel 9, the temperature of the cold water reaching the radiation panel is just improved. Therefore, when the chilled water line Lc is communicated with the heat exchanger 5, the “bound” chilled water line Lc is communicated to the heat exchanger 5 in series with the radiation panel 9 instead of the “return” chilled water line. ing.

Next, a twelfth embodiment will be described with reference to FIG.
The twelfth embodiment in FIG. 13 differs from the eleventh embodiment in FIG. 12 in the connection method of the fluid lines from the air conditioning system to the heat exchanger 5 interposed in the line L3 of the dehumidifier 112.

That is, in the eleventh embodiment in FIG. 12, the cold water line Lc toward the radiation line is communicated with the heat exchanger 5 of the dehumidifier 111. On the other hand, in the twelfth embodiment of FIG. 13, the refrigerant line La through which the refrigerant circulating in the cooling unit 7 flows is branched, and the branch line Lc2 communicates with the heat exchanger 5.
Delivery of cold water to the radiation panel 9 is performed by a cold water line Lc1 provided separately from the branch line Lc2.

 About another structure and an effect, it is the same as that of 11th Embodiment of FIG.

 In 11th Embodiment of FIG. 12 and 12th Embodiment of FIG. 13, the dehumidifier 112 similar to the dehumidifier 103 of FIG. 4 is shown, but it replaces with the dehumidifier 103 of FIG. A dehumidifier similar to that shown in FIG. 10 can be used.

  It should be noted that the illustrated embodiment is merely an example, and is not a description to limit the technical scope of the present invention.

The schematic diagram explaining the structure of 1st Embodiment of this invention. Explanatory drawing of the dehumidification rotor concerning embodiment of this invention. The schematic diagram explaining the structure of 2nd Embodiment of this invention. The schematic diagram explaining the structure of 3rd Embodiment of this invention. The schematic diagram explaining the structure of 4th Embodiment of this invention. The schematic diagram explaining the structure of 5th Embodiment of this invention. The schematic diagram explaining the structure of 6th Embodiment of this invention. The schematic diagram explaining the structure of 7th Embodiment of this invention. The schematic diagram explaining the structure of 8th Embodiment of this invention. The schematic diagram explaining the structure of 9th Embodiment of this invention. The schematic diagram explaining the structure of 10th Embodiment of this invention. The schematic diagram explaining the structure of 11th Embodiment of this invention. The schematic diagram explaining the structure of 12th Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Dehumidification rotor 2 ... Air supply apparatus / blower 3 ... Casing 4 ... Heat source / heater 5 ... Heat exchanger 6 ... Thermoelectric element 7 ... Refrigeration unit 8 ... Heat exchanger 9 for air conditioning ... Radiation panel 11 ... Treatment area / dehumidification area 12 ... Purge area 13 ... Regeneration area 31 ... Air inlet 32 ... Dry air return port 33 ... -Exhaust port 51 ... Heat exchanger 61 ... Cooling surface 62 ... Heat dissipation surface

Claims (7)

  A dehumidification rotor that rotates, and an air supply device that supplies air to be dehumidified to the dehumidification rotor, the air supply device sucks and pressurizes the air to be dehumidified, and depressurizes the pressurized air And a line for supplying air supplied from the air supply device to the purge area of the dehumidification rotor to the regeneration area of the dehumidification rotor. A dehumidifier comprising a heating device interposed in the line.   A dehumidification rotor that rotates, and an air supply device that supplies air to be dehumidified to the dehumidification rotor. The air supply device sucks air that has passed through the dehumidification area of the dehumidification rotor and applies the sucked air. The air is supplied to the area corresponding to the dehumidification area of the dehumidification rotor and the area corresponding to the purge area, and the air supplied from the air supply device to the purge area of the dehumidification rotor is used as the regeneration area of the dehumidification rotor. A dehumidifier having a supply line and a heating device interposed in the line.   The dehumidifier according to any one of claims 1 and 2, wherein a heat exchanger is interposed in a line for supplying air that has passed through the dehumidifying area of the dehumidifying rotor to the room.   The dehumidifier according to claim 1, wherein a heat exchanger is provided in a line communicating the air supply device and the dehumidification rotor.   The dehumidifier according to claim 1, wherein a heat exchanger is interposed on the upstream side of the air supply device.   The dehumidifier according to any one of claims 1 and 2, wherein a heat exchanger is interposed in a line through which air passes through the purge area and the regeneration area of the dehumidification rotor, and the line communicates with the indoor side.   A thermoelectric element is provided, and the heat dissipation surface of the thermoelectric element is interposed in a line communicating from the purge area to the regeneration area in order to heat the air flowing toward the regeneration area of the dehumidification rotor, and the cooling surface of the thermoelectric element faces the room The dehumidifier according to any one of claims 1 and 2, wherein the dehumidifier is interposed in a line from the dehumidification zone to the room to cool the air.

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