CN101184547B - Dehumidifier - Google Patents

Abstract

A dehumidifier comprising a moisture absorbing route (6) for feeding air to a dehumidifying rotor (2) to absorb its moisture to the dehumidifying rotor, a circulation route (8) for circulating regenerated air to the dehumidifying rotor (2) to release the moisture therefrom, a heater (9) heating the regenerated air fed to the dehumidifying rotor (2), and a heat exchanger (10) having a regenerated air passage (11) forming one section of the circulation route (8) and a cooling air passage (12) for flowing cooling air therein. The heat exchanger (10) is formed by stacking a plurality of heat transfer plates through predetermined spaces. The regenerated air and the cooling air alternately flow through the spaces between the heat transfer plates to form the regenerated air passage (11) and the cooling air passage (12), the spaces between the heat transfer plates are kept by space ribs formed integrally with the heat transfer plates, and the regenerated air and the cooling air are heat-exchanged through the heat transfer plates to condense the moisture in the regenerated air.

Description

Dehumidification device

technical field

The present invention relates to a dehumidification device that performs dehumidification by condensing and recovering moisture absorbed by a dehumidification rotor through a heat exchanger. the

Background technique

As a conventional dehumidifier that performs dehumidification by condensing and recovering the moisture absorbed by the dehumidification rotor with a heat exchanger, there is a device having a structure that supplies and releases the moisture absorbed by the dehumidification rotor to regeneration air heated to a high temperature by a heater, and The high-humidity regeneration air containing the released moisture is cooled by the cooling air in the heat exchanger to recover the moisture as condensed water, and the moisture-removed regeneration air is returned to the heater for circulation. In the structure of this regeneration air circulation type, there is such an advantage that high-humidity regeneration air is not exhausted to the outside of the device, so the regeneration air becomes a high-humidity state, and the enthalpy difference with the cooling air increases, and moisture can be efficiently recovered by the heat exchanger. . Conversely, if the reconditioning air and cooling air leak more, the amount of condensed water recovered will decrease. Therefore, the heat exchanger requires airtightness between the reconditioning air passage and the cooling air passage. In addition, cooling the regeneration air to the lowest possible temperature and reducing the amount of saturated water vapor can condense more moisture, so it is also necessary to improve the heat exchange efficiency of the heat exchanger. the

As a heat exchanger used in such a dehumidifier, there is a heat exchanger having a structure in which a corrugated spacer plate is inserted between a plurality of flat plate-shaped heat transfer plates, and the wave formation direction of the corrugated spacer plate is Alternately staggered by 90°, the top edge of the heat conduction plate and the spacer plate are fixed with adhesive, etc., and the regeneration air passage through which the regeneration air flows and the cooling air passage through which the cooling air flows are formed every other layer in a direction perpendicular to each other to conduct heat. exchange. This technical content is disclosed in JP-A-10-323 (page 3, FIG. 2 ). the

In addition, there is also a structure in which the passage group forming body divided into a plurality of passages is laminated in multiple layers, and the direction of the passage is alternately changed by 90° in each layer, and the regeneration air is supplied to every other layer of the stacked passage group forming body. Alternate vertical flow with cooling air for heat exchange. In this structure, the passage group forming body can make its own wall thickness as thin as possible, and in addition, it can make the adjacent surfaces closely contact, thereby increasing the contact area and improving the heat exchange rate. This technical content is disclosed in JP-A-11-128654 (page 3, FIG. 3 ). the

In addition, there is also a structure that uses a hollow resin molded member that forms a plurality of tubular heat transfer pipes by blow molding or the like, flows regenerating air into the plurality of heat transfer pipes, and flows cooling air into the plurality of heat transfer pipes. The external gap of each heat pipe is used for heat exchange (for example, Patent Document 3). The technical contents are disclosed in JP-A-2003-269746. the

As mentioned above, various forms of heat exchangers used in dehumidifiers have been proposed. In the heat exchanger disclosed in JP-A-10-323, a plurality of heat transfer plates are stacked with spacer plates interposed therebetween, and the heat transfer surfaces are densely formed to achieve miniaturization. the

However, in this heat exchanger, since the dimensional accuracy of the waveform of the partition plate is directly related to the dimensional error of the passage interval, it is difficult to ensure a good passage interval, the ventilation resistance becomes high, and the weight of the increased number of partition plates becomes heavy. the

In addition, in order to ensure the airtightness of the regeneration air passage and the cooling air passage, it is necessary to fix the top edge of the spacer plate to the heat transfer plate with an adhesive, etc., due to deviations in the application of the adhesive and adhesion caused by condensed water The strength is lowered, it is difficult to maintain and ensure airtightness, and the weight of the adhesive agent to be applied and the number of spacer sheets are increased to increase the weight. the

In addition, since the passage interval is defined by the wave height of the partition plate, there is a limit to the wave height ensuring strength, and it is difficult to appropriately adjust the passage interval according to the air conditions of the regeneration air and cooling air, such as the state of water drop generation or the state of impurity content. the

In addition, the water droplets condensed at the corrugated corners of the partition plate in the reconditioning air passage are not easy to drop and stay in the passage due to surface tension, which increases the passage resistance. the

In addition, when impurities are mixed into the reconditioning air passage, they accumulate in the passage, lowering the ventilation resistance and sometimes causing no ventilation. the

In the heat exchanger disclosed in Japanese Unexamined Patent Publication No. 11-128643, there are two outer wall surfaces of each passage group forming body and bonding surfaces between the outer surfaces between the regenerating air and the cooling air, so the thermal resistance becomes high and the heat exchange rate is high. Efficiency is reduced. In addition, variation in adhesive coating on the bonding surface makes it difficult to maintain heat exchange efficiency. the

In addition, water droplets condensed on the corners of the plurality of internal passages provided on the passage group forming body on the reconditioning air passage side are not easily dripped due to surface tension and remain in the internal passages, increasing the ventilation resistance. the

In addition, when the reconditioning air circulation path is incorporated into the junction of the reconditioning air path of the heat exchanger, it is difficult to ensure airtightness with respect to the cooling ventilation path, and the reconditioning air may leak. the

In addition, when impurities are mixed into the reconditioning air passage, they accumulate in the passage, lowering the ventilation resistance and sometimes causing no ventilation. the

The heat exchanger disclosed in Japanese Unexamined Patent Application Publication No. 2003-269746 is composed of a hollow resin molded part, and ensures airtightness and simplifies the structure. the

However, since the hollow heat exchanger makes the large heat pipe into a tube shape, the heat transfer area that can be formed in the same volume is only about 1/5 of that of the laminated heat exchanger exemplified in the above-mentioned Patent Document 1, and the heat exchange efficiency is not good. the

In addition, due to the low heat exchange efficiency, a high-humidity state with a dew point temperature of around 40°C is formed in the regeneration air passage, so the amount of water discharged to the outside of the device due to the leakage of the regeneration air increases, and the dehumidification performance decreases, and the dehumidification rotor needs to be regenerated. The air in the air is also heated to a high temperature to increase the dryness, so the energy increases, and the dehumidification efficiency (condensation latent heat of dehumidified moisture/energy required for dehumidification) deteriorates. the

In addition, forming the heat transfer surface into a tubular shape requires a predetermined wall thickness, specifically, an average wall thickness of about 0.5 to 1.0 mm, which increases the thermal resistance and reduces the heat exchanger. get heavier. the

In addition, as the above-mentioned heat exchanger, resin molded parts are generally used, but when the dehumidification rotor stops or the cooling air volume decreases in abnormal conditions, the regeneration air flowing into the heat exchanger becomes abnormally high temperature exceeding the heat-resistant temperature of the resin, which may cause heat exchange. device deterioration. the

Contents of the invention

The present invention provides a heat exchanger capable of suppressing ventilation resistance by properly maintaining passage intervals, realizing improvement in heat exchange efficiency, size reduction, and less water drop retention in regeneration air passages, thereby improving dehumidification efficiency (condensation potential of dehumidified moisture) heat/energy required for dehumidification) of the dehumidifier. the

In addition, the present invention provides a heat exchange device capable of improving the heat exchange efficiency by mounting it, reducing the size and weight, reducing the retention of water droplets in the reconditioning air passage, and improving the airtightness of the reconditioning air passage and the cooling air passage without using an adhesive. It is a dehumidification device that improves the dehumidification efficiency (the latent heat of condensation of the dehumidified water/the energy required for dehumidification). the

In addition, the present invention provides a heat exchanger capable of improving heat exchange efficiency, reducing size and weight, and having less water droplet stagnation in the reconditioning air passage, and enabling adjustment of passage intervals suitable for reconditioning air and cooling air to improve dehumidification efficiency. (Latent heat of condensation of dehumidified moisture/energy required for dehumidification) dehumidification device. the

In addition, the present invention provides a heat exchanger capable of improving heat exchange efficiency by mounting it, achieving reduction in size and weight, less water droplet stagnation in the reconditioning air passage, high reliability when the temperature of the reconditioning air becomes high, and capable of suppressing the incorporation of impurities. , to improve the dehumidification efficiency (the latent heat of condensation of the dehumidified water/the energy required for dehumidification) of the dehumidification device. the

A dehumidifier according to the present invention includes: a dehumidification rotor that absorbs moisture from supply air and regenerates it by releasing moisture to heated air; a moisture absorption path that supplies air to the dehumidification rotor to absorb moisture; and circulates regenerated air to the dehumidification rotor. and a circulation path for releasing moisture; a heater for heating regeneration air supplied to the dehumidification rotor; and a heat exchanger having a regeneration air path forming a part of the circulation path and a cooling air path through which cooling air flows, wherein the The heat exchanger has a structure in which a plurality of thin plate-shaped heat transfer plates are stacked at predetermined intervals, and reconditioning air and cooling air are alternately flowed into the lamination gaps of the heat transfer plates to form the reconditioning air passage and the cooling air. The channel maintains the stacking interval of the heat conduction plates through the spacer ribs formed integrally with the heat conduction plates, enables the reconditioning air and the cooling air to exchange heat through each of the heat conduction plates, and condenses moisture in the reconditioning air. the

According to such a configuration, the following effects are obtained. That is, the passage interval between the reconditioning air passage and the cooling air passage can be appropriately ensured by the partition rib formed integrally with the plurality of heat transfer plates, and an increase in ventilation resistance can be suppressed. In addition, heat exchange between the reconditioning air and the cooling air can be performed through only one of the heat transfer plates, thereby improving heat exchange efficiency. In addition, the heat transfer surface is compactly formed without providing other parts such as a partition plate, and the size and weight of the heat exchanger can be reduced. In addition, it is possible to suppress the stagnation of water droplets due to surface tension without providing a corner portion such as a partition plate or a passage dividing plate, and allow the condensed water droplets to drip smoothly. In addition, high-efficiency heat exchange is performed in the heat exchanger to reduce the saturated water vapor content of the regeneration air and return it to the heater, thereby increasing the amount of moisture released from the dehumidification rotor and the recovery of condensed water in the heat exchanger, and suppressing the air The amount of dehumidification caused by leakage is reduced, and the dehumidification efficiency (condensation latent heat of dehumidified moisture/energy required for dehumidification) is improved. the

The dehumidification device of the present invention has: a dehumidification rotor that absorbs moisture from supplied air and releases moisture to heated air to regenerate; a moisture absorption path that supplies air to the dehumidification rotor to absorb moisture; and circulates regeneration air to the dehumidification rotor. and a circulation path for releasing moisture; a heater for heating regeneration air supplied to the dehumidification rotor; and a heat exchanger having a regeneration air path forming a part of the circulation path and a cooling air path through which cooling air flows, wherein the The heat exchanger has a structure in which a plurality of thin plate-shaped heat transfer plates are stacked at predetermined intervals, and reconditioning air and cooling air are alternately flowed into the lamination gaps of the heat transfer plates to form the reconditioning air passage and the cooling air. passage, the end faces of the heat conduction plates other than the passage opening are welded adjacent to each other to ensure the airtightness of the regeneration air passage and the cooling air passage, and the regeneration air and the cooling air are heated through each of the heat conduction plates. exchange to condense the moisture in the regeneration air. the

According to such a configuration, the following effects are obtained. That is, the airtightness of the reconditioning air passage and the cooling air passage is ensured by welding adjacent end faces of the heat transfer plates other than the passage openings, and the laminated state of the heat transfer plates can be firmly fixed without using an adhesive. , and make sure to ensure the airtightness of the regeneration air passage and the cooling air passage. In addition, the reconditioning air and the cooling air can exchange heat through only one of the heat transfer plates, thereby suppressing thermal resistance and improving heat exchange efficiency. In addition, the heat transfer surface is compactly formed without providing other components such as an adhesive or a spacer plate, and the size and weight of the heat exchanger can be reduced. In addition, it is possible to suppress the stagnation of water droplets due to surface tension without providing a corner portion such as a partition plate or a passage dividing plate, and allow the condensed water droplets to drip smoothly. In addition, high-efficiency heat exchange is performed in the heat exchanger to reduce the saturated water vapor content of the regeneration air and return it to the heater, thereby increasing the amount of moisture released from the dehumidification rotor and the recovery of condensed water in the heat exchanger, and suppressing the air The amount of dehumidification caused by leakage is reduced, and the dehumidification efficiency (condensation latent heat of dehumidified moisture/energy required for dehumidification) is improved. the

The dehumidification device of the present invention has: a dehumidification rotor that absorbs moisture from supply air and releases moisture to heated air to regenerate; a moisture absorption path that supplies air to the dehumidification rotor to absorb moisture; and circulates regenerated air to the dehumidification rotor. a circulation path for releasing moisture; a heater for heating regeneration air supplied to the dehumidification rotor; and a heat exchanger having a regeneration air path forming a part of the circulation path and a cooling air path through which cooling air flows, wherein the heat The exchanger has a structure in which a plurality of thin plate-shaped heat conduction plates are stacked at different intervals, and reconditioning air and cooling air alternately flow into the lamination gaps of the heat conduction plates to form the reconditioning air passage and the reconditioning air passage. The cooling air passage is used to exchange heat between the reconditioning air and the cooling air through each of the heat conduction plates, so as to condense moisture in the reconditioning air. the

According to such a configuration, the following effects are obtained. That is, by stacking a plurality of thin plate-shaped heat transfer plates at different intervals, the reconditioning air and cooling air can be appropriately adjusted according to the respective air conditions of the reconditioning air and cooling air, such as the state of water drop generation or the state of impurity content. In addition, the reconditioning air and the cooling air can exchange heat through only one of the heat transfer plates, thereby suppressing thermal resistance and improving heat exchange efficiency. In addition, the heat transfer surface is compactly formed without providing other parts such as a partition plate, and the size and weight of the heat exchanger can be reduced. In addition, it is possible to suppress the stagnation of water droplets due to surface tension without providing a corner portion such as a partition plate or a passage dividing plate, and allow the condensed water droplets to drip smoothly. In addition, high-efficiency heat exchange is performed in the heat exchanger to reduce the saturated water vapor content of the regeneration air and return it to the heater, thereby increasing the amount of moisture released from the dehumidification rotor and the recovery of condensed water in the heat exchanger, and suppressing the air The amount of dehumidification caused by leakage is reduced, and the dehumidification efficiency (condensation latent heat of dehumidified moisture/energy required for dehumidification) is improved. the

The dehumidification device of the present invention has: a dehumidification rotor that absorbs moisture from supply air and releases moisture to heated air to regenerate; a moisture absorption path that supplies air to the dehumidification rotor to absorb moisture; and circulates regenerated air to the dehumidification rotor. a circulation path for releasing moisture; a heater for heating regeneration air supplied to the dehumidification rotor; and a heat exchanger having a regeneration air path forming a part of the circulation path and a cooling air path through which cooling air flows, wherein the heat The exchanger has a structure in which a plurality of thin plate-shaped heat transfer plates are stacked at predetermined intervals, and reconditioning air and cooling air are alternately flowed into the lamination gaps of the heat transfer plates to form the reconditioning air passage and the cooling air passage. , press each of the heat conducting plates from the stacking direction to improve the airtightness of the reconditioning air passage and the cooling air passage, make the reconditioning air and cooling air exchange heat through each of the heat conducting plates, and make the reconditioning air moisture condensation. the

According to such a configuration, the following effects are obtained. That is, the airtightness of the reconditioning air passage and the cooling air passage is improved by pressing each of the heat conduction plates from the stacking direction without using an adhesive. In addition, the reconditioning air and the cooling air can exchange heat through only one of the heat transfer plates, thereby suppressing thermal resistance and improving heat exchange efficiency. In addition, the heat transfer surface is compactly formed without providing other components such as an adhesive or a spacer plate, and the size and weight of the heat exchanger can be reduced. In addition, it is possible to suppress the stagnation of water droplets due to surface tension without providing a corner portion such as a partition plate or a passage dividing plate, and allow the condensed water droplets to drip smoothly. In addition, high-efficiency heat exchange is performed in the heat exchanger to reduce the saturated water vapor content of the regeneration air and return it to the heater, thereby increasing the amount of moisture released from the dehumidification rotor and the recovery of condensed water in the heat exchanger, and suppressing the air The amount of dehumidification caused by leakage is reduced, and the dehumidification efficiency is improved (condensation latent heat of dehumidified moisture/energy required for dehumidification). the

The dehumidification device of the present invention has: a dehumidification rotor that absorbs moisture from supply air and releases moisture to heated air to regenerate; a moisture absorption path that supplies air to the dehumidification rotor to absorb moisture; and circulates regenerated air to the dehumidification rotor. a circulation path for releasing moisture; a heater for heating regeneration air supplied to the dehumidification rotor; The regenerating air flowing in the passage is cooled by the cooling air flowing in the cooling air passage, and the heat exchanger condenses the moisture in the regenerating air, wherein the heat exchanger is formed in such a structure that the thin plate-shaped Each heat conduction plate is stacked at predetermined intervals by spacer ribs integrally formed with the plurality of heat conduction plates, and cooling air and regeneration air alternately flow into the gaps between the plurality of heat conduction plates to form a cooling air passage and a regeneration air passage, It has a head frame fitted into the upper peripheral part of the heat exchanger to form a part of the circulation path, and a foot frame fitted into the lower surface peripheral part of the heat exchanger to form a part of the circulation path, and is provided to seal the upper surface. The peripheral portion and the sealing portion of the lower peripheral portion. the

According to such a configuration, the following effects are obtained. That is, since the spacer ribs for maintaining the lamination intervals of the heat transfer plates are integrally formed with each heat transfer plate, the passage intervals between the reconditioning air passage and the cooling air passage can be appropriately ensured, and the structure can be simplified. In addition, since the intervals between the reconditioning air passage and the cooling air passage are alternately formed in multiple layers via only one of the heat transfer plates, the thermal resistance can be reduced and the heat exchange efficiency can be improved. In addition, since the heat transfer surfaces are closely formed, it is possible to reduce the size of the heat exchanger. In addition, since there is no corrugated plate or channel dividing plate for maintaining intervals in the reconditioning air channel, surface tension is less likely to act on the dew condensation water droplets generated on the channel surface, and the water droplets drip smoothly. Therefore, the increase in the passage resistance caused by the stagnation of water droplets in the passage disappears, and a predetermined reconditioning air volume can be maintained. In addition, the regenerating air with a small amount of saturated water vapor becomes a further low-humidity state, and the amount of water released in the regenerating area also increases. Accompanied by the increase in the amount of released water, the amount of moisture absorbed in the moisture absorption region of the desiccant rotor also increases. The synergistic effect of each increase in the water recovery amount, the water release amount, and the moisture absorption amount can improve the dehumidification efficiency (the latent heat of condensation of the dehumidified water/the energy required for dehumidification). In addition, since the decrease in the amount of saturated water vapor in the regeneration air can be reduced, even if the circulation path and the outside air move in the regeneration area, the difference in the amount of saturated water vapor can be reduced. Therefore, the amount of water vapor discharged to the outside is reduced, and performance degradation due to air leakage can be suppressed. In addition, since the airtightness of the circulation path can be ensured by increasing the head frame, the foot frame, and the sealing part, and at the same time, a heat exchanger can be installed in the circulation path with a relatively simple structure, so it is possible to suppress air leakage with an inexpensive structure. Reduced performance. the

Description of drawings

Fig. 1 is a schematic cross-sectional view of a dehumidifier according to Embodiment 1 of the present invention. the

2 is a schematic exploded perspective view of a dehumidification rotor mounted on the dehumidification device according to Embodiment 1 of the present invention. the

3 is a schematic exploded perspective view of a heat exchanger mounted on the dehumidifier according to Embodiment 1 of the present invention. the

Fig. 4 is a schematic perspective view showing a fixed holding state of a heat exchanger mounted on the dehumidifier according to Embodiment 1 of the present invention. the

5 is a schematic exploded perspective view showing a fixed and held state of a heat exchanger mounted on the dehumidifier according to Embodiment 1 of the present invention. the

6A is a schematic molding process diagram of a heat transfer plate of a heat exchanger mounted on the dehumidifier according to Embodiment 1 of the present invention. the

6B is a schematic molding process diagram of the heat transfer plate of the heat exchanger mounted on the dehumidifier according to Embodiment 1 of the present invention. the

6C is a schematic molding process diagram of the heat transfer plate of the heat exchanger mounted on the dehumidifier according to Embodiment 1 of the present invention. the

Fig. 7 is a hygroscopic diagram (湿り空気気図図) showing state changes of reconditioning air in the dehumidifier according to Embodiment 1 of the present invention. the

Fig. 8 is a schematic cross-sectional view of a dehumidifier according to Embodiment 2 of the present invention. the

9 is a schematic exploded perspective view of a dehumidification rotor mounted on a dehumidification device according to Embodiment 2 of the present invention. the

Fig. 10 is a schematic exploded perspective view of a heat exchanger mounted on a dehumidifier according to Embodiment 2 of the present invention. the

Fig. 11 is a schematic exploded perspective view showing a fixed holding state of a heat exchanger mounted on a dehumidifier according to Embodiment 2 of the present invention. the

Fig. 12 is a schematic perspective view showing a water droplet promoting unit mounted on the head frame of the dehumidifier according to Embodiment 2 of the present invention. the

13 is a schematic exploded perspective view showing a heat exchanger deterioration prevention unit mounted on a head frame of a dehumidifier according to Embodiment 2 of the present invention. the

Fig. 14 is a schematic cross-sectional view showing a regeneration air rectifying unit mounted on a head frame and a foot frame of a dehumidifier according to Embodiment 2 of the present invention. the

15 is a schematic cross-sectional view showing rectifying plates mounted on the head frame and the foot frame of the dehumidifier according to Embodiment 2 of the present invention. the

16 is a schematic cross-sectional view showing an impurity mixing prevention unit mounted on a head frame of a dehumidifier according to Embodiment 2 of the present invention. the

Fig. 17 is a schematic cross-sectional view showing the structure of a head frame of a dehumidifier according to Embodiment 2 of the present invention when dividing ribs are provided. the

Fig. 18 is a schematic exploded perspective view showing a fixed and held state of the heat exchanger when the head frame and the foot frame of the dehumidifier according to Embodiment 2 of the present invention are integrally formed. the

Fig. 19 is a hygroscopic diagram showing state changes of reconditioning air in the dehumidifier according to Embodiment 2 of the present invention. the

Symbol Description

2. 102 dehumidification rotor

6. 106 moisture absorption path

8. 108 cycle paths

9, 109 heaters

10, 110 heat exchanger

11. 111 regeneration air channel

12, 112 cooling air passages

23a, 23b, 125a, 125b heat conduction plate

24a, 24b, 126a, 126b spacer ribs

27a, 27b guide ribs

28 rectifying ribs

30 rotunda

32 storage department

35 sheets

113 head frame

114 foot frame

131 upper peripheral part

Peripheral part below 132

137 sealing department

138 flange part

139 elastic sealing material

140 Droplet Promotion Department

141 Drip Promotion Department

142 Heat Exchange Promotion Department

143 drops promote dimples

144 Heat Exchanger Deterioration Prevention Department

145 protective film

146 regeneration air inlet end face

148 Regenerative air rectification unit

149 wind direction board

150 rectifier plate

151 through holes

152 Impurity Mixture Prevention Department

153 split ribs

157 heat exchange department

Detailed ways

(implementation mode 1)

Embodiment 1 of the present invention will be described with reference to FIGS. 1 to 7 . the

Fig. 1 is a schematic cross-sectional view of a dehumidifier according to Embodiment 1 of the present invention. As shown in FIG. 1, a dehumidification rotor 2 that absorbs moisture from the air is rotatably erected inside the main body 1, and a moisture absorption path 6 is provided. 3 Suction air is supplied to the dehumidification rotor 2, and is discharged from the suction port 5 opened on the upper part of the main body 1. In addition, a circulation path 8 is formed in which regeneration air supplied by the regeneration fan 7 circulates through the dehumidification rotor 2, and a heater 9 for heating the regeneration air is arranged near the wind upstream side of the dehumidification rotor 2 in the circulation path 8. As the heater 9, as long as it is capable of exothermic operation, for example, a nickel-chrome heat-resistant alloy (nickel), a halogen lamp heater, a carbon heater (carbon heater), a PTC heater, etc. can be used. In addition, a substantially trapezoidal heat exchanger 10 is arranged on the wind downstream side of the desiccant rotor 2 of the circulation path 8 and the wind upstream side of the moisture absorption path 6, and a part of the circulation path 8 is provided on the heat exchanger 10 through which reconditioning air passes. The regeneration air passage 11 and the cooling air passage 12 through which the air flowing in the moisture absorption passage 6 passes. The reconditioning air passage 11 is vertically arranged so that the reconditioning air inlet side is located at the upper part and the reconditioning air outlet side is located at the lower part, and the air inlet side of the reconditioning air passage 11 is from the front side to the rear side with respect to the supply direction of the reconditioning air. The reconditioning air supplied to the reconditioning air passage 11 can flow in with an inclination of about 10° upslope (上り接) without changing direction. In addition, the reconditioning air outlet side of the reconditioning air passage 11 has an angle of about 10° relative to the horizontal direction. The inclination enables smooth movement of water droplets reaching the outlet of the passage. These inclination angles can be appropriately set depending on the structure, but are preferably set to an inclination angle of at least 5° or more in order to satisfy the effect of uniforming the wind speed distribution on the passage inlet side and the water droplet movement on the passage outlet side described later. Also, the cooling air passage 12 through which the cooling air that exchanges heat with the reconditioning air flowing in the reconditioning air passage 11 flows is arranged in a substantially horizontal direction, and the reconditioning air and the cooling air cross each other in a substantially vertical direction to perform heat exchange. Moreover, a drain port 13 for discharging condensed water from the circulation path 8 is provided on the path connecting the outlet side of the regeneration air passage 11 and the regeneration fan 7, and a drain port 13 is detachably arranged below the drain port 13 for receiving the condensed water. Shrunken drain tank14. the

In the above structure, in the moisture absorption path 6, the dehumidification rotor 2 absorbs moisture from the air supplied by the processing fan 4, and the dry air from which the moisture has been absorbed by the dehumidification rotor 2 is supplied to the outside of the main body 1 through the outlet 5. The desiccant rotor 2 that absorbs moisture in the moisture absorption path 6 discharges the moisture into the high-temperature regeneration air that rotates on the circulation path 8 and is heated by the heater 9 to perform regeneration. The desiccant rotor 2 is continuously rotated straddling the moisture absorption path 6 and the circulation path 8 , and continuously absorbs moisture in the moisture absorption path 6 and discharges and regenerates in the circulation path 8 . On the other hand, reconditioning air containing moisture discharged from the dehumidification rotor 2 and forming high humidity is supplied to the reconditioning air passage 11 of the heat exchanger 10 . The inlet of the reconditioning air passage 11 forms an upward slope from the front side to the rear side relative to the supply direction of the reconditioning air, so the reconditioning air supplied into the reconditioning air passage 11 flows into the reconditioning air passage 11 without changing direction, and realizes uniform wind speed distribution change. The reconditioning air supplied to the reconditioning air passage 11 exchanges heat with the cooling air supplied from the suction port 3 to the cooling air passage 12 by the processing fan 4. During this heat exchange process, the reconditioning air is cooled, the saturated water vapor content decreases, and the moisture is saturated. The saturated moisture condenses in the reconditioning air passage 11 , and drips down smoothly due to the wind pressure of the reconditioning air flowing downward in the reconditioning air passage 11 and the weight of the water droplets themselves. The water droplets falling in the reconditioning air passage 11 and reaching the passage outlet move to the lowermost apex 15 along the inclined portion formed at the passage outlet, so that the stagnation of the water droplets due to the surface tension of the passage outlet can be suppressed. The water droplets that successively moved to the lowermost apex portion 15 become large particles, are separated from the passage by their own weight, drop to the drain tank 4, and are recovered as condensed water. The regeneration air cooled and dehydrated by the heat exchanger 10 is sucked into the regeneration fan 7 , supplied to the heater 9 again, and circulated through the circulation path 8 . the

2 is a schematic exploded perspective view of a dehumidification rotor mounted on the dehumidification device according to Embodiment 1 of the present invention. The desiccant rotor 2 is a circular KORUGETO structure made of inorganic fibers such as ceramic fibers and glass fibers, or plain paper made by mixing these inorganic fibers and pulp, and KORUGETO (コルゲ一ト (transliteration: Colgate)) processed corrugated paper. One or two types of hygroscopic agents such as silica gel, ORAITO (オゼライト (transliteration: Ou Ze Laite)) and other inorganic adsorption-type hygroscopic agents, organic polymer electrolytes, ion exchange resins and other hygroscopic agents, Lithium chloride and other absorbent moisture absorbents form a ventilated structure in the axial direction. The dehumidification rotor 2 is sandwiched and accommodated from both shaft sides by the frame A17 with the gear part 16 on the outer periphery and the frame B18 with a plurality of radial ribs erected, and the frame A17 and the frame B18 are fixed with a plurality of bolts from the outer periphery, and inserted into the frame. The bearing part 20 of the center hole 19 of the desiccant rotor 2 and the center part of the frame B18 are bolted, and the desiccant rotor 2 is fixed and held. And the gear part 16 of the frame A17 meshes with the gear 22 of the drive motor 21, and the rotation operation of the dehumidification rotor 2 is performed by rotating the drive motor 21. At this time, the rotation speed of the dehumidification rotor 2 is set to about 10 to 40 rotations per hour. In addition, the height of the ribs formed on the frame B18 determines the volume of the space formed between the surface of the desiccant rotor 2 and the front end of the ribs. The ribs are formed by pressing and bending a thin material that can ensure the strength of the ribs, for example, a stainless steel plate with a thickness of about 0.4 to 1.0 mm. In this way, air leakage from the moisture absorption path 6 and the circulation path 8 can be suppressed. In addition, the rotation method of the desiccant rotor 2 is not limited to the above-mentioned structure, for example, it may also be a structure in which the drive motor 21 is connected to the center of the desiccant rotor 2 to make it rotate directly, or it may be hung on a gear provided on the outer periphery of the desiccant rotor 2. A pulley is provided, and the driving motor 21 is connected via the pulley to rotate. the

Fig. 3 is a schematic exploded perspective view of a heat exchanger mounted on the dehumidifier according to Embodiment 1 of the present invention. The heat exchanger 10 is formed by alternately laminating a plurality of heat transfer plates 23a formed with concavo-convex portions in a predetermined pattern on a thin plate such as a sheet with a thickness of 0.05 to 0.5 mm, and forming a pattern of concavo-convex portions different from the heat conduction plate 23a on the same thin plate. The heat conduction plate 23b is formed. The plate thickness of the heat conduction plate 23a and heat conduction plate 23b is preferably 0.05 mm or more from the viewpoint of formability, strength, and shape retention of the concave-convex portion described later, and is preferably 0.5 mm or less from the viewpoint of ensuring thermal conductivity. In addition, the gaps between the stacked heat conduction plates 23a and 23b are formed by alternately flowing regeneration air and cooling air so that the regeneration air passage 11 and the cooling air passage 12 are formed every other layer, and the regeneration air flowing in the regeneration air passage 11 and the The cooling air flowing in the cooling air passage 12 exchanges heat via the respective heat transfer plates 23a and 23b. Thereby, the cause of heat exchange hindrance is only the thermal resistance of one sheet of the heat transfer plate 23 a and the heat transfer plate 23 b , and efficient heat exchange between the reconditioning air and the cooling air can be performed. Actually, 20 to 60 heat transfer plates 23a and 23b are stacked in total, but for the sake of simplicity, two heat transfer plates 23a and 23b are disassembled and shown in the stacking direction. the

The heat conduction plate 23a and the heat conduction plate 23b have a substantially trapezoidal planar shape, and the approximately trapezoid has two sets of opposite sides of a long side and a short side, the opposite sides of the long sides form a vertically parallel state, and the opposite sides of the short sides face each other. Tilted approximately 10° from the horizontal. On the heat conduction plate 23a, hollow convex spacer ribs 24a with a width of about 4 mm protrude along each opposite side of the long side. The hollow convex-shaped spacer rib 24b having a width of about 4 mm. The spacer ribs 24a of the heat conduction plate 23a are formed at about 3mm, and the protruding surface of the spacer ribs 24a is in contact with the heat conduction plate 23b in the stacked state, so that the passage interval of the reconditioning air passage 11 is maintained at a predetermined size of about 3mm. On the other hand, the convex height of the spacer ribs 24b of the heat transfer plate 23b is formed to be about 2mm, and the protruding surface of the spacer ribs 24b is in contact with the heat transfer plate 23a in the laminated state, so that the passage interval of the cooling air passage 12 is maintained in a prescribed manner. The specified size is about 2mm. In addition, the corners 25 at both ends of the spacer ribs 24a that overlap with the spacer ribs 24b protruding from the heat conduction plate 23b in the stacked state are further protruded by about 2 mm, which is the height of the spacer ribs 24b. The inner hollow concave part of the rib part 24b fits, and the entire protruding surface is in contact with the heat conducting plate 23b. Similarly, the corners 26 at both ends of the spacer ribs 24b that overlap with the spacer ribs 24a protruding from the heat conduction plate 23a in the stacked state are further protruded by the height of the spacer ribs 24a, that is, about 3mm, and the corners 26 are in contact with the spacer ribs 24a. The inner hollow concave part of spacer rib 24a cooperates, and the protruding set surface is all in contact with heat conducting plate 23a. In this way, the entire protruding surfaces of the spacer ribs 24a and 24b are in contact with the adjacent heat transfer plates 23b and 23a, whereby the passage intervals of the reconditioning air passages 11 in the stacked state are maintained at an appropriate predetermined size. That is, about 3 mm, and the passage interval of the cooling air passage 12 is similarly maintained at about 2 mm, which is an appropriate predetermined size. In this way, the stacking interval on the reconditioning air passage 11 side is defined by the rib height of the spacer rib 24a protruding from the heat conduction plate 23a, and the cooling air passage is defined by the rib height of the space rib 24b protruding from the heat conduction plate 23b. 12-sided stack spacing. the

As described above, the stacking interval on the reconditioning air passage 11 side is defined by the rib height of the spacer ribs 24a protruding from the heat conduction plate 23a, and the cooling is regulated by the rib height of the spacer ribs 24b protruding from the heat conduction plate 23b. Lamination interval on the air passage 12 side. Also, the rib height of the spacer ribs 24 a is set to about 3 mm, and the rib height of the spacer ribs 24 b is set to about 2 mm, so the passage interval of the reconditioning air passage 11 is wider than that of the cooling air passage 12 . If set in this way, the bridging phenomenon of dew-condensed water droplets on the regeneration air passage 11 can be suppressed, the water droplets can drip smoothly, and the increase of ventilation resistance caused by the stagnation of water droplets can be suppressed, and the cooling air passage 12 does not leave redundant passage intervals. On the other hand, it can be compactly formed, and the miniaturization of the heat exchanger 10 and the improvement of heat exchange efficiency can be aimed at. In addition, when using air containing a large amount of impurities as the cooling air passing through the cooling air passage 12, for example, if the passage interval of the cooling air passage 12 is about 2mm, the impurities accumulate in the passage intervals, the passage resistance increases, and the heat is generated. hindrance to exchange. In this case, the rib height of the spacer ribs 24b is higher than that of the spacer ribs 24a, for example, set to about 4mm, and by widening the passage interval of the cooling air passage 12, accumulation of impurities can be suppressed. In this way, the rib heights of the spacer ribs 24a and 24b are preferably adjusted appropriately according to the respective states of the reconditioning air and the cooling air, for example, the state of water drop generation and the state of impurity content. the

In addition, a hollow convex guide rib 27a with a width of about 2 mm is continuously formed in the horizontal central portion of the heat conduction plate 23a in the same direction as the spacer rib 24a, and two facing spacer ribs 24b are continuously formed in the vertical direction of the heat conduction plate 23b. A hollow convex guide rib 27b with a width of about 2 mm protrudes in the opposite direction. The guide rib 27b is provided on the center portion of the spacer rib 24a and the guide rib 27a in a laminated state. Thus, in the stacked state, the guide ribs 27a and 27b protrude so that the ribs on both sides of the reconditioning air passage 11 are at approximately equal intervals, and in the stacked state, the guide ribs 27a and the guide ribs 27b The protruding arrangement is continuous with respect to the blowing direction of the reconditioning air, so that the water droplets condensed in the reconditioning air passage 11 drip quickly along the guide ribs 27a and 27b, and the retention of water droplets in the reconditioning air passage 11 is suppressed. The rib heights of the guide ribs 27a and 27b can be appropriately set as long as they are equal to or less than the spacer ribs 24a, but are preferably set according to the state of keeping the space between the reconditioning air passages 11 and the state of dripping water. For example, if the rib height of the guide rib 27a is set to be about 3mm the same as that of the spacer rib 24a, and the rib height of the guide rib 27b is set to be about 1mm lower than the guide rib 27a, then the regeneration air passage 11 The channel gap can also be appropriately maintained in the central portion, and the channel cross-sectional area of the reconditioning air channel 11 can also be widened to reduce the channel impedance, and the dew condensation in the channel can drip smoothly without bridging. the

In addition, a plurality of hollow convex rectifying ribs 28 with a width of about 1 mm at approximately equal intervals in the horizontal direction protrude from the heat conducting plate 23b in the same direction as the spacer ribs 24b. The hollow concave part of the guide rib 27b protruding from the reverse surface of the heat conducting plate 23b is discontinuous. As a result, the rectification ribs 28 protrude from the heat transfer plate 23b side into the cooling air passage 12 in the stacked state of the heat transfer plates, and are discontinuous with respect to the blowing direction of the cooling air, so that the cooling air of each cooling air passage 12 flows along the rectification direction. The ribs 28 flow uniformly, and the discontinuous parts of the rectifying ribs 28 have uniform pressure (equalized pressure), and the wind speed distribution is averaged, enabling efficient heat exchange with the reconditioning air. The rib height of the rectifying ribs 28 can be appropriately set as long as it is equal to or less than the spacer ribs 24b. The wind velocity distribution of the cooling air can be uniformed, and the cooling air passage 12 can also be used to maintain passage intervals. the

In addition, the heat conduction plate 23a is formed with a melting portion 29a covered by the spacer rib 24b formed on the heat conduction plate 23b when stacked, and the spacer rib 23b formed on the heat conduction plate 23a when stacked is formed on the heat conduction plate 23b. The melting part 29b on. In addition, in the laminated state in which the heat conduction plate 23a and the heat conduction plate 23b are stacked in a predetermined number, heat is applied to the melting portion 29a covered by the spacer rib 24b by a heater or the like to melt the spacer rib 24b and the fusion portion 29a. If joined, the end surfaces of the cooling air passage 12 other than the passage opening are welded, thereby ensuring the airtightness of the cooling air passage 12 . Also in the stacked state, heat is applied by a heater or the like to the melting portion 29b covered by the spacer rib portion 24a, and the spacer rib portion 24a and the fusion portion 29b are melted and bonded, and the end faces of the cooling air passage 11 other than the passage opening are welded. , thereby ensuring the airtightness of the cooling air passage 11. In this way, the heat conduction plate 23a and the heat conduction plate 23b are welded to the end faces other than the passage openings adjacent to each other, and the laminated state of the heat conduction plate 23a and the heat conduction plate 23b can be firmly fixed without using an adhesive, and the regeneration air can also be ensured. The airtightness of passage 11 and cooling air passage 12. the

As described above, the heat exchanger 10 has a substantially trapezoidal shape formed with concave and convex portions such as the spacer rib 24a and the spacer rib 24b, the guide rib 27a and the guide rib 27b, the rectification rib 28, the melting portion 29a, and the melting portion 29b. The heat conduction plates 23a are alternately stacked with heat conduction plates 23b, the reconditioning air passage 11 is arranged on the opposite side of the short side of the trapezoid, and the cooling passage 12 is arranged on the opposite side of the long side substantially perpendicular to the reconditioning air passage 11. Accordingly, the passage cross-sectional area of the cooling air passage 12 is formed wider than the passage cross-sectional area of the reconditioning air passage 11, the ventilation resistance of the cooling air passage 12 is formed lower than the ventilation resistance of the reconditioning air passage 11, and it is possible to easily supply more air than the reconditioning air. of cooling air. As a result, the reconditioning air can be cooled by a large amount of cooling air, so that the temperature of the reconditioning air can be further lowered during the cooling process, and the amount of saturated water vapor can be reduced. In addition, the cross-sectional area of the reconditioning air passage 11 and the cooling air passage 12 is appropriately set according to the structure of the device by changing the planar shape of the heat transfer plate 23a and the heat transfer plate 23b. For example, in the case of a device structure in which the cooling air cannot flow, the cooling air passage 12 is arranged on the short side of the trapezoid, and the regeneration air passage 11 is arranged on the long side, so that the cross-sectional area of the cooling air passage 12 is larger than that of the regeneration air. The cross-sectional area of the passage 11 is narrow, and the passage resistances of the cooling air passage 12 and the reconditioning air passage 11 can be adjusted to the ventilation resistance corresponding to the air volumes of the cooling air and the reconditioning air. the

In addition, in the heat exchanger 10, the arrangement of the reconditioning air passage 11 and the cooling air passage 12 can be adjusted according to the device structure by the lamination pattern of the heat conduction plate 23a and the heat conduction plate 23b. For example, assuming that the protruding surface side of the spacer rib 24a and the spacer rib 24b is stacked in sequence, then as shown in FIG. The reconditioning air passages 11 are arranged at both ends in the stacking direction. The heat exchanger 10 is constituted by such an arrangement pattern, and the device is configured such that gas flows in the outer periphery of the heat exchanger 10 in the stacking direction, then the regeneration air flowing in the regeneration air passages 11 arranged at both ends of the stacking direction and the outer periphery of the heat exchanger 10 Heat exchange is performed between the flowing air, and both the heat conduction plate 23a and the heat conduction plate 23b function as heat conduction surfaces. On the contrary, starting from the heat conduction plate 23b, the heat conduction plates 23a and the heat conduction plates 23b are alternately laminated in the same number, and the cooling air passages 12 are arranged on both ends of the stacking direction. The heat exchanger 10 is constituted by such an arrangement pattern, and the outer periphery of the heat exchanger 10 in the lamination direction is provided with a fixing part or the like for maintaining the lamination state of the heat exchanger 10 or the heat conduction plate 23a and the heat conduction plate 23b. The cooling air passage 12 thermally insulates (thermally insulates) the fixing portion arranged outside it from the reconditioning air flowing in the reconditioning air passage 11 arranged inside it, and suppresses thermal deformation of the fixing portion due to high-temperature reconditioning air. the

4 is a schematic perspective view showing a fixed and held state of the heat exchanger mounted on the dehumidifier according to Embodiment 1 of the present invention, and shows a configuration in which the heat exchanger 10 is fixed and held using a ring body 30 . In FIG. 4 , the heat exchanger 10 is laminated with a predetermined number of heat transfer plates 23 a and 23 b in total of 40 sheets. The stacked state is fixed and maintained by the tight binding of the wheel-shaped bodies 30 arranged at the upper and lower positions. As the wheel-shaped body 30, as long as the stacked heat conduction plates 23a and heat conduction plates 23b can be tightly bound and fixed, and each heat conduction plate 23a and heat conduction plate 23b can be pressed against the stacking direction, for example, by applying Wheel rubber (wheel ゴム) or knot-shaped materials such as wire or tires are bound to form a wheel shape. The tight binding force of the wheel 30 acts on the stacked heat conduction plates 23a and 23b as pressure from the stacking direction. For example, when a wheel rubber is used as the wheel 30 , the elastic force of the wheel rubber can press each heat transfer plate 23a and heat transfer plate 23b against each other from the stacking direction. This pressing force increases the contact force between the protruding surface of the partition rib 24a formed on the heat conducting plate 23a and the heat conducting plate 23b connected to the protruding surface, thereby improving the airtightness of the reconditioning air passage 11 . In addition, similarly, the contact force between the protruding surface of the spacer rib 24b formed on the heat conducting plate 23b and the heat conducting plate 23a connected to the protruding surface is increased, and the airtightness of the cooling air passage 12 is improved. In this way, by pressing the heat conduction plates 23a and heat conduction plates 23b from the lamination direction by the tight binding force of the wheel-shaped body 30, the contact force between the spacer ribs 24a and the heat conduction plates 23b, and the spacer ribs 24b and the heat conduction plates 23a is realized. Fixed maintenance of the laminated state and improvement of the airtightness of the reconditioning air passage 11 and the cooling air passage 12 . the

The ring-shaped body 30 is preferably set to have a ring-shaped peripheral length shorter than the outer peripheral length of the stacked heat transfer plates, in the range of 1 to 12 mm. Its reason is: the difference between the perimeter of the ring-shaped body 30 and the outer perimeter of the heat-conducting plate in the stacked state is less than 1 mm, and when the ring-shaped body 30 is additionally provided, the pressure acting on each heat-conducting plate 23a and the heat-conducting plate 23b from the stacking direction Due to insufficient pressure, the airtightness of the regeneration air passage 11 and the cooling air passage 12 is reduced. In addition, if the difference between the circumference of the wheel-shaped body 30 and the outer circumference of the heat conduction plate in the stacked state exceeds 12 mm, not only the additional setting of the ring-shaped body 30 The operation is difficult, and the working pressure on each heat transfer plate 23a and heat transfer plate 23b from the stacking direction becomes too large, and the passage gap between the reconditioning air passage 11 and the cooling air passage 12 cannot be properly maintained. In this way, the shorter the difference between the circumference of the wheel-shaped body 30 and the outer circumference of the heat conduction plates in the stacked state, the lower the airtightness of the regeneration air passage 11 and the cooling air passage 12. On the contrary, the circumference of the wheel-shaped body 30 and the stacked The longer the difference between the outer peripheral lengths of the heat conduction plate in the state, the more difficult it is to maintain the passage interval between the reconditioning air passage 11 and the cooling air passage 12. Therefore, in order to properly ensure the airtightness and passage interval of the regeneration air passage 11 and the cooling air passage 12, the difference between the circumference of the ring body 30 and the outer circumference of the heat conduction plate in the stacked state is preferably in the range of 1 to 12 mm, more preferably 2 to 12 mm. 8mm range. the

Fig. 5 is a schematic exploded perspective view showing a fixed and held state of the heat exchanger mounted on the dehumidifier according to Embodiment 1 of the present invention, showing a configuration in which the heat exchanger 10 is housed in the storage section and fixed and held. The heat exchanger 10 has the same structure as that shown in FIG. 4 , and heat transfer plates 23 a and 23 b are formed by alternately stacking a predetermined number of sheets, that is, a total of 40 sheets. The lamination completion dimension A at this time is 60 mm, which is a value obtained by multiplying the rib height dimension 3 mm of the spacer rib 24 a formed on the heat conduction plate 23 a by the number of heat conduction plates 23 a , and the spacer rib 24 b formed on the heat conduction plate 23 b The rib height dimension 2mm multiplied by the number of heat conduction plates 23b is 40mm, the thickness of heat conduction plate 23a and heat conduction plate 23b, for example 0.25mm, is multiplied by the total number of heat conduction plates ie 10mm, which is 110mm. A housing portion 32 having a width B smaller than the lamination completion dimension A, for example, 105 mm, is formed on the case 31 that accommodates and holds the heat exchanger 10 in a fixed manner. The heat exchanger 10 in the state where the heat transfer plates are stacked is inserted into the housing portion 32 as indicated by a hollow arrow. An engaging portion 33 is formed on the casing 31 in the storage direction of the heat exchanger 10 , and the inserted heat exchanger 10 comes into contact with the engaging portion 33 to complete storage in the accommodating portion 32 . In this stored state, the width dimension B of the storage portion 32 is 5 mm smaller than the stacked dimension A, so the heat transfer plates 23a and 23b in each stacked state act on the pressing force corresponding to this 5 mm from the stacking direction. The contact force between the protruding surface of the spacer rib 24a formed on the heat conduction plate 23a and the heat conduction plate 23b connected to the protruding surface is increased by this pressure, thereby improving the airtightness of the reconditioning air passage 11. The contact force between the protruding surface of the spacer rib 24b formed on the heat conducting plate 23b and the heat conducting plate 23a connected to the protruding surface is increased, and the airtightness of the cooling air passage 12 is improved. Then, in this storage-completed state, the heat exchanger 10 is fixedly held by fixing the lid portion 34 fitted to the case 31 and the case 31 with bolts. The casing 31 and the cover 34 are provided with openings communicating with the inlets and outlets of the regeneration air passages 11 and the cooling air passages 12 of the heat exchanger 10, and the regeneration air and the cooling air can be communicated to the heat exchanger 10 through these openings. . the

In this way, the heat exchanger 10 is housed in the storage portion 32 in which the width dimension B is smaller than the dimension A at which the heat conduction plates are stacked in the stacked state of the heat conduction plates, and each heat conduction plate 23a and heat conduction plate 23b are pressed against each of the heat conduction plates 23b from the stacking direction, thereby realizing the reconditioning air passage 11 And the improvement of the airtightness of the cooling air passage 12. In addition, the difference between the lamination end dimension A and the width dimension B is 5 mm in the above structure, but the difference is preferably set within the range of 1 to 12 mm. The reason is that if it is less than 1mm, the pressure acting on each heat transfer plate 23a and heat transfer plate 23b from the stacking direction is insufficient in the state of completion of storage in the storage portion 32, and the airtightness of the regeneration air passage 11 and the cooling air passage 12 is insufficient. In addition, if it exceeds 12mm, the storage operation in the storage part 32 will become difficult, and the pressure acting on each heat transfer plate 23a and heat transfer plate 23b from the stacking direction will be too large, and the reconditioning air passage 11 and the cooling system will not be properly maintained. The passage interval of the air passage 12. In this way, the smaller the difference between the lamination end dimension A and the width dimension B, the lower the airtightness of the regeneration air passage 11 and the cooling air passage 12, and on the contrary, the larger the difference between the lamination completion dimension A and the width dimension B, the lower the airtightness of the regeneration air passage 11 and the cooling air passage 12. 11 and cooling air passage 12, the more difficult it is to maintain the passage interval. Therefore, in order to properly ensure the airtightness and passage gap between the reconditioning air passage 11 and the cooling air passage 12, the difference between the lamination completion dimension A and the width dimension B is preferably in the range of 1 to 12 mm, more preferably in the range of 2 to 8 mm. the

6A, 6B, and 6C are schematic molding process drawings showing the heat transfer plate of the heat exchanger mounted on the dehumidifier according to Embodiment 1 of the present invention, and show how the heat transfer plate 23a and the heat transfer plate 23b are formed. As shown in FIG. 6A , the flat sheet 35 is heated to soften it, mounted on a vacuum forming metal mold 36 forming concave and convex portions, and the sheet 35 is bonded and formed on the vacuum forming metal mold by a vacuum pump not shown. 36 on. Thereby, the sheet 35 is formed on the concavo-convex portion as shown in FIG. 6B . Two types of concavo-convex patterns are formed on the vacuum formed metal mold 36: concavo-convex patterns 37a corresponding to the concavo-convex shapes of the spacer ribs 24a, guide ribs 27a, and melting portions 29a integrally formed on the heat conducting plate 23a; The concavo-convex pattern 37b corresponding to the concavo-convex pattern 37b formed on the spacer rib 24b, the guide rib 27b, the rectifying rib 28, and the melting portion 29b on the heat conduction plate 23b is formed simultaneously by one forming operation. And, as shown in Fig. 6C, the sheet material 35 forming the concave-convex portion 38a and the concave-convex 38b is pressed and cut out by a die 40 having a stamping knife 39 having a shape equal to the outer peripheral shape of each heat-conducting plate 23a and the heat-conducting plate 23b, thereby forming the concave-convex. The heat conduction plate 23a of the portion 38a and the heat conduction plate 23b of the formed concavo-convex portion 38b are cut at the same time. This cutting process is performed on a plurality of sheets 35 formed with concavo-convex portions, and a predetermined number of heat conduction plates 23 a and heat conduction plates 23 b are produced respectively. the

It is preferable to use a material having a thickness in the range of 0.05 to 0.5 mm for the sheet 35 . The reason is: if the thickness is less than 0.05 mm, the sheet 35 is likely to be damaged due to expansion and contraction during forming of the concavo-convex part and the strength of the formed sheet 35 is reduced, and the formed heat conduction plates 23a, 23b are also fragile at the waist, and the shape It is difficult to maintain the shape. In addition, if the thickness exceeds 0.5mm, the thermal conductivity will be greatly reduced due to the increase of thermal resistance. In this way, the thinner the sheet 35 is, the lower the formability, strength, and shape retention are, and conversely, the thicker the sheet 35 is, the lower the thermal conductivity is. Therefore, in order to satisfy formability, strength, shape retention, and thermal conductivity, the range of 0.05 to 0.5 mm is preferable, and the range of 0.1 to 0.3 mm is more preferable. the

In addition, it is preferable to use a thermoplastic resin material as the raw material of the sheet 35 . If such a material is used, the sheet 35 is heated during vacuum forming due to its thermoplasticity, becomes very soft, and smoothly adheres to the vacuum forming metal mold 36, and the forming of the concave-convex portion 37a and the concave-convex portion 37b becomes easy. the

In addition, the sheet 35 may be a material in which rubber particles are dispersed on a thermoplastic resin material. Forming such a raw material, in addition to having the ease of molding of thermoplastic resins, since the rubber dispersed on the sheet 35 has elastic properties, when it is stuck on the vacuum forming metal mold 36, the sheet 35 is difficult to split or crack, The airtightness of the heat transfer plate 23a and the heat transfer plate 23b is ensured. For example, when an impact-resistant polystyrene sheet is used as the sheet 35, in addition to having the ease of molding of thermoplastic resin, due to the dimensional stability of polystyrene resin, there is less dimensional shrinkage after molding, and the concave and convex portions 38a, The dimensional accuracy of the concavo-convex portion 38b is improved, and further, due to the elastic properties of the rubber particles contained in the impact-resistant polystyrene, the occurrence of cracks or cracks during vacuum forming is suppressed. the

In this way, when polystyrene resin is used as the thermoplastic resin material of the sheet 35, the dimensional shrinkage after vacuum forming is reduced, and the dimensional accuracy of the concave-convex portion 38a and the concave-convex portion 38b is improved. Therefore, the spacing ribs 24 a and the spacing ribs 24 b are formed with good precision, and the passage gap between the reconditioning air passage 11 and the cooling air passage 12 is appropriately maintained. the

In addition, polypropylene may be used as the thermoplastic resin material of the sheet 35 . Using such a raw material, due to the strength of the waist of polypropylene, when the sheet 35 is taken out from the vacuum forming die 36, the sheet 35 is less likely to be broken or bent, and when the heat conduction plate 23a and the heat conduction plate 23b are laminated, it is less likely to be broken or bent. Improves handleability due to sheet breakage or bending due to poor handling. the

In addition, polycarbonate can also be used as the thermoplastic resin material of the sheet|seat 35. Using this raw material, due to the shape retention of polycarbonate, the strength of the spacer ribs 24a and 24b, the guide ribs 27a and 27b, and the rectification ribs 28 is improved, and the adjacent gaps in the stacked state can be ensured. The strength of each contact position of the heat transfer plate 23a and the heat transfer plate 23b is such that the passage gap between the reconditioning air passage 11 and the cooling air passage 12 is reliably maintained. the

In addition, polyethylene terephthalate can also be used as the thermoplastic resin material of the sheet 35 . Using this raw material, due to the heat resistance of polyethylene terephthalate, the heat resistance of the heat transfer plate 23a and the heat transfer plate 23b is improved, and even if the temperature of the air supplied to the heat exchanger 10 rises during abnormal operation, the heat transfer plate can be suppressed. 23a and thermal deformation of the heat conducting plate 23b. the

In addition, acrylonitrile-butadiene-styrene can also be used as the thermoplastic resin material of the sheet 35 . Using such raw materials, due to the impact resistance of acrylonitrile-butadiene-styrene, when the sheet 35 is taken out from the vacuum forming metal mold 36, it is difficult for the sheet 35 to be chapped or split. Even in the handling of the plate 23b, cracks and splits are less likely to occur, and the airtightness of the heat conduction plate 23a and the heat conduction plate 23b can be ensured. the

In addition, antibacterial agents, antistatic agents, flame retardants, deodorants, and the like may be added singly or in combination to the sheet 35 made of the above-mentioned raw materials. Add antibacterial agent in sheet 35, such as natural antibacterial agent such as allyl isocyanate, phosphatol, chitosan, metal antibacterial agent such as silver, photocatalyst antibacterial agent such as titanium oxide photocatalyst antibacterial agent etc. In the case of this type, the heat conduction plate 23a and heat conduction plate 23b formed from the sheet 35 are subjected to antibacterial treatment to suppress the generation of bacteria and fine dust caused by water droplets remaining in the heat exchanger 10 . In addition, when an anionic, cationic, nonionic low-molecular antistatic agent or metal filler is added as the sheet 35, the heat conduction plate 23a and the heat conduction plate 23b formed from the sheet 35 are subjected to antistatic treatment to suppress The condensed water recovered by the heat exchanger 10 is charged, and discharge phenomenon hardly occurs during drainage operation. In addition, when a flame retardant, such as a halogen-based, phosphorus-based, inorganic-based flame retardant, is added to the sheet 35, the heat-conducting plate 23a and the heat-conducting plate 23b formed from the sheet 35 are subjected to a flame-retardant treatment to suppress abnormalities. The thermal deformation of the heat transfer plate 23a and the heat transfer plate 23b caused by the temperature rise of the supply air supplied to the heat exchanger 10 at the time. In addition, when a deodorant such as activated carbon or photocatalyst is added to the sheet 35, the heat conduction plate 23a and the heat conduction plate 23b formed by the sheet 35 are subjected to deodorization treatment to suppress residual water droplets mixed into the heat exchanger 10 or heat exchange. Impurities in the container 10 produce odor. the

In addition, the surface of the sheet 35 is preferably treated with hydrophobicity or hydrophilicity to suppress retention of water droplets. For example, even if the sheet 35 made of thermoplastic resin material is not specially treated, the surface of the sheet 35 has hydrophobicity, and the surface is further improved by coating a fluorine-based hydrophobic material or the like. Using such a sheet 35 to form the heat conduction plate 23a and the heat conduction plate 23b, the surfaces of the formed heat conduction plate 23a and the heat conduction plate 23b also have hydrophobicity, and the water droplets that condense on the surface of the regeneration air passage 11 have a lower contact angle due to the hydrophobic effect of the surface. become larger and drop rapidly in the regeneration air passage 11. In addition, the sheet 35 is coated with a hydrophilic coating, such as a fluorine-based hydrophilic coating, so that the surface of the sheet 35 is hydrophilic. In this way, the surfaces of the heat conduction plate 23a and heat conduction plate 23b formed from the sheet 35 are also hydrophilic, and the water droplets condensed on the surface of the reconditioning air passage 11 expand into a liquid film through the hydrophilic effect, and the bridging phenomenon of water droplets is suppressed. the

7 is a hygroscopic diagram showing state changes of reconditioning air in the dehumidifier according to Embodiment 1 of the present invention, showing state changes of reconditioning air circulating through the circulation path 8 of the dehumidifier. In FIG. 7 , the solid line connecting points 41, 42, and 43 represents the state change of the regeneration air in the dehumidifier of this embodiment, and the dotted line connecting points 44, 45, and 46 represents the regeneration of the conventional dehumidifier. The state of the air changes. Here, points 41 and 44 represent the air states at the outlet of the heat exchanger 10 , and points 42 and 45 represent the air states at the outlet of the heater 9 . In addition, points 43 and 46 represent the air conditions at the inlet of the heat exchanger 10 which is the outlet of the dehumidification rotor 2 . In the dehumidifier of the present embodiment, since the heat exchanger 10 efficiently exchanges heat between the reconditioning air and the cooling air, the reconditioning air can be further cooled to a lower temperature than conventional dehumidifiers. Therefore, the temperature Ta at the outlet of the heat exchanger 10 indicated at the point 41 in the present embodiment takes a lower value than the temperature Tb at the outlet of the heat exchanger 10 indicated at the conventional point 44 . For example, when cooling air at 20°C is used, the outlet temperature Tb of the conventional heat exchanger 10 is only cooled to about 35°C, but in this embodiment, the temperature Ta at the outlet of the heat exchanger 10 can be cooled to 30°C or less. In addition, the air at the outlet of the heat exchanger 10 is water-saturated saturated air after being cooled, so the amount of saturated water vapor is equal to the absolute humidity. Therefore, the temperature of the outlet of the heat exchanger 10 which is the saturated air can be lower than before, and accordingly the absolute humidity can also be lowered. That is, the absolute humidity Xa at the outlet of the heat exchanger 10 indicated at the point 41 in the present embodiment has a lower value than the absolute humidity Xb at the outlet of the heat exchanger 10 indicated at the conventional point 44 . Specifically, the absolute humidity Xa at the outlet of the heat exchanger 10 according to the present embodiment is reduced to about 3 g/kg (DA) relative to the absolute humidity Xb at the outlet of the heat exchanger 10 of the conventional technology being about 5 g/kg (DA). The regeneration air having a small absolute humidity, that is, a saturated water vapor content, is supplied to the heater 9, so that the relative humidity of the air heated by the heater 9 is sufficiently lowered to become drier air. That is, the relative humidity at the outlet of the heater 9 according to the present embodiment indicated by the point 42 is a lower value than the relative humidity at the outlet of the conventional heater 9 indicated by the point 45 . This sufficiently dry air is supplied to the dehumidification rotor 2, so the amount of moisture released from the dehumidification rotor 2 increases, and the amount of condensed water recovered by the heat exchanger 10, that is, the dehumidification amount also increases. In addition, since the saturated water vapor amount of the regeneration air leaked from the gap between the dehumidification rotor 2 and the heater 9, etc. is also reduced, the leakage amount of water vapor accompanying the air leakage is also reduced, and the amount of dehumidification caused by the leakage of water vapor can be suppressed. reduce. Through such combined action, the dehumidification device of this embodiment improves the dehumidification efficiency (condensation latent heat of dehumidified moisture/energy required for dehumidification). In this way, the dehumidification efficiency can be increased to about 40%. the

The dehumidifier of the present embodiment described above has the following effects. the

That is, by the spacer ribs 24a formed integrally with the heat transfer plate 23a and the spacer ribs 24b formed integrally with the heat transfer plate 23b, the passage interval between the reconditioning air passage 11 and the cooling air passage 12 can be appropriately ensured, and an increase in ventilation resistance can be suppressed. the

In addition, by exchanging heat between the reconditioning air and the cooling air via only one of the heat conduction plates 23a and 23b, heat exchange efficiency can be improved by suppressing thermal resistance. the

In addition, since the heat transfer surface is compactly formed without providing other components such as a partition plate, it is possible to reduce the size and weight of the heat exchanger 10 . the

In addition, without providing corner members such as partition plates and passage dividing plates, it is possible to suppress the stagnation of water droplets due to surface tension and allow the condensed water droplets to drip smoothly. the

In addition, high-efficiency heat exchange is performed in the heat exchanger 10 to reduce the saturated water vapor content of the regeneration air and return it to the heater 9, thereby increasing the amount of water released from the dehumidification rotor 2 and the recovery of condensed water in the heat exchanger 10 , and suppress the reduction of dehumidification caused by air leakage, and improve the dehumidification efficiency (condensation latent heat of dehumidified moisture/energy required for dehumidification). the

In addition, the adjacent end faces of the heat conduction plate 23a and the heat conduction plate 23b other than the passage openings are welded together, that is, the spacer ribs 24a and the melting portion 29b are welded, and the spacer ribs 24b and the fusion portion 29a are welded, which can be eliminated. The laminated state of the heat conduction plate 23a and the heat conduction plate 23b is firmly fixed by using an adhesive, and the airtightness of the reconditioning air passage 11 and the cooling air passage 12 can be ensured. the

In addition, the reconditioning air passages 11 and the cooling air passages 12 are alternately formed in multiple layers at different intervals, so the passage intervals can be appropriately adjusted according to the respective air states of the reconditioning air and cooling air, such as the state of water drop generation or the state of impurity content. the

In addition, when the passage interval of the reconditioning air passage 11 is wider than that of the cooling air passage 12 , bridging phenomenon of water droplets condensed in the reconditioning air passage 11 can be suppressed, and the water droplets can drip smoothly. the

In addition, when the passage interval of the cooling air passage 12 is wider than the passage interval of the reconditioning air passage 11, it is possible to suppress accumulation of impurities in the cooling air in the cooling air passage 12. the

In addition, the airtightness of the reconditioning air passage 11 and the cooling air passage 12 can be improved by pressing the respective heat transfer plates 23a and 23b from the stacking direction without using an adhesive. the

In addition, when the thermally conductive plates 23a and 23b in the stacked state are tightly bound by the wheel-shaped body 29, the tight force of the wheel-shaped body 30 acts as a pressing force on each of the heat-conductive plates 23a and 23b, and the thermal conductivity can be maintained. The laminated state of the plate 23a and the heat transfer plate 23b can also improve the airtightness of the reconditioning air passage 11 and the cooling air passage 12 . the

In addition, when the accommodating part 32 is stored in the heat conduction plate 23a and the heat conduction plate 23b in a stacked state, it is possible to conduct heat conduction to each of the heat conduction plates stored in the stacked state by the accommodating part 32 having a width dimension smaller than the stack reduction dimension of the heat conduction plate 23a and the heat conduction plate 23b. The plate 23a and the heat conduction plate 23b apply pressure to improve the airtightness of the reconditioning air passage 11 and the cooling air passage 12, and maintain the laminated state of the heat conduction plate 23a and the heat conduction plate 23b. the

In addition, water droplets condensed in the reconditioning air passage 11 drip smoothly along the guide ribs 27a and 27b, and stagnation of water droplets in the reconditioning air passage 11 can be suppressed. the

Since the guide rib 27a and the guide rib 27b are continuously formed in the blowing direction of the reconditioning air, stagnation of water droplets at discontinuous parts of the ribs is suppressed, and water droplets condensed in the reconditioning air passage 11 can be quickly dropped. the

In addition, the cooling air supplied to the cooling air passage 12 flows along the rectification ribs 28 with equal pressure, so that the heat exchange efficiency with the reconditioning air can be improved. the

In addition, the cooling air flowing along the rectifying ribs 28 forms an equalized pressure at the discontinuous part of the rectifying ribs 28, so that the dispersion distribution is averaged, and the heat exchange efficiency is further improved. the

In addition, since the reconditioning air passage 11 is arranged on the long side of the heat transfer plate 23a and the heat transfer plate 23b, and the cooling air passage 12 is arranged on the short side, the passage sectional area of the cooling air passage 12 can be made wider than the passage sectional area of the reconditioning air passage 11. By making the ventilation resistance of the cooling air passage 12 smaller than the ventilation resistance of the reconditioning air passage 11, it is possible to easily supply more cooling air than the reconditioning air. the

In addition, when the cooling air passage 12 is arranged on the long side of the heat conduction plate 23a and the heat conduction plate 23b, and the reconditioning air passage 11 is arranged on the short side, the passage sectional area of the reconditioning air passage 11 is made larger than the passage sectional area of the cooling air passage 12. Wider, the ventilation resistance of the reconditioning air passage 11 is made smaller than the ventilation resistance of the cooling air passage 12, and more reconditioning air than cooling air can be easily supplied. the

In addition, the heat conduction plate 23a and heat conduction plate 23b are arranged so that the reconditioning air in the reconditioning air passage 11 flows vertically downward, so the dew condensation water droplets in the reconditioning air passage 11 are due to the weight of the water droplet itself and the reconditioning air flowing vertically downward. Rapid dripping due to high wind pressure can suppress the increase in ventilation resistance caused by the stagnation of water droplets. the

In addition, since the side corresponding to the outlet side of the reconditioning air passage 11 of the heat transfer plate 23a and the heat transfer plate 23b is inclined relative to the horizontal direction, the water droplets that condense in the reconditioning air passage 11 and drop to the outlet of the passage are along the side corresponding to the outlet side. The inclined part on one side moves to the lowermost apex 15 to form large particles, which can be easily separated from the outlet part due to its own weight, and can reduce the retention of water droplets caused by surface tension and prevent the passage from being blocked. the

In addition, the side corresponding to the inlet side of the reconditioning air passage 11 of the heat transfer plate 23a and the heat transfer plate 23b is inclined relative to the horizontal direction, and the inlet side of the reconditioning air passage 11 is formed from the front side to the rear side with respect to the supply direction of the reconditioning air. Therefore, the wind speed distribution of the reconditioning air flowing into the reconditioning air passage 11 can be uniformed, and the heat exchange efficiency can be improved. the

In addition, when the reconditioning air passages 11 are arranged at both ends of the stacking direction of the heat transfer plates 23a and 23b, the reconditioning air flowing in the reconditioning air passages 11 arranged at both ends of the stacking direction and the outer periphery of the heat exchanger 10 can be realized. The heat exchange between the air can make the heat transfer plate 23a and the heat transfer plate 23b all function effectively as a heat transfer surface. the

In addition, when the cooling air passages 12 are arranged at both ends of the stacking direction of the heat conduction plate 23a and the heat conduction plate 23b, the heat exchanger 10 disposed on the outer side can be fixed through the cooling air passages 12 arranged at both ends of the stacking direction. The heat insulation between the fixing part and the reconditioning air arranged inside the reconditioning air passage 11 suppresses the thermal deformation of the fixing part caused by the high-temperature reconditioning air. the

In addition, the heat conduction plate 23a and the heat conduction plate 23b are formed by the sheet 35 made of thermoplastic resin material, so the ease of molding of the thermoplastic resin material can improve the spacer ribs 24a and guide ribs 27a integrally formed with the heat conduction plate 23a, The formability of the concavo-convex parts such as the spacer ribs 24b, the guide ribs 27b, and the straightening ribs 28 formed integrally with the heat transfer plate 23b. the

In addition, when the rubber particles are dispersed in the sheet 35 , due to the elastic properties of the rubber particles dispersed on the sheet 35 , it is possible to suppress the occurrence of chapping or splitting during the molding of the concavo-convex portion. the

In addition, when polystyrene is used as the thermoplastic resin material of the sheet 35, due to the dimensional stability of polystyrene, the dimensional shrinkage of the concave-convex portion after molding can be suppressed, and the precision of the spacer ribs 24a and the spacer ribs 24b can be improved. Formed in such a way that the passage interval between the reconditioning air passage 11 and the cooling air passage 12 is properly maintained. the

In addition, when polypropylene is used as the thermoplastic resin material of the sheet 35, the strength of the waist portion of the polypropylene prevents the sheet from breaking or bending when the sheet 35 is formed and when the heat conduction plate 23a and the heat conduction plate 23b are stacked. It occurs and improves handling characteristics. the

In addition, when polycarbonate is used as the thermoplastic resin material of the sheet 35, due to the shape retention of polycarbonate, the strength of each contact position between the adjacent heat conduction plates 23a and 23b in the stacked state is ensured, and reliable The passage interval between the reconditioning air passage 11 and the cooling air passage 12 is maintained accurately. the

In addition, when polyethylene terephthalate is used as the thermoplastic resin material of sheet 35, the heat resistance of heat conduction plate 23a and heat conduction plate 23b can be improved due to the heat resistance of polyethylene terephthalate. Thermally, thermal deformation of the heat conduction plate 23a and the heat conduction plate 23b caused by the temperature rise at the time of abnormality is suppressed. the

In addition, when acrylonitrile-butadiene-styrene is used as the thermoplastic resin material of sheet 35, the impact resistance of acrylonitrile-butadiene-styrene can improve the resistance of heat conduction plate 23a and heat conduction plate 23b. Shock resistance suppresses the occurrence of cracks and cracks during forming and lamination of the concavo-convex part, and ensures the airtightness of the heat conduction plate 23a and the heat conduction plate 23b. the

In addition, when the sheet material 35 adopts an impact-resistant polystyrene sheet, the dimensional stability of the impact-resistant polystyrene can suppress the dimensional shrinkage of the concave-convex portion after molding, and the spacer ribs 24a and the spacer ribs 24b is formed with high precision, the passage interval between the regeneration air passage 11 and the cooling air passage 12 is maintained appropriately, and the elastic properties of the rubber particles contained in the impact-resistant polystyrene suppress cracks or cracks during the molding of the concave and convex parts. the

In addition, since the thickness of the sheet 35 is in the range of 0.05 to 0.5 mm, it is possible to prevent cracks during molding of the concave-convex portion, reduce the thermal resistance of the heat conduction plate 23a and the heat conduction plate 23b, and improve heat exchange efficiency. the

In addition, when the antibacterial agent is added to the sheet 35, the heat conduction plate 23a and the heat conduction plate 23b are subjected to antibacterial treatment, so the generation of bacteria and dust caused by the water droplets in the heat exchanger 10 can be suppressed. the

In addition, when an antistatic agent is added to the sheet 35, antistatic treatment is performed on the heat conduction plate 23a and the heat conduction plate 23b, so the condensed water recovered by the heat exchanger 10 is less likely to be charged, and the discharge phenomenon during the drainage operation can be suppressed. the

In addition, when the flame retardant is added to the sheet 35, the heat conduction plate 23a and the heat conduction plate 23b are subjected to flame retardant treatment, so the thermal deformation of the heat conduction plate 23a and the heat conduction plate 23b caused by the temperature rise during abnormality can be suppressed. the

In addition, when a deodorant is added to the sheet 35, deodorization treatment is performed on the heat transfer plate 23a and the heat transfer plate 23b, so it is possible to suppress the odor from the water droplets in the heat exchanger 10 and the impurities mixed into the heat exchanger 10. occur. the

In addition, when the surface of the sheet 35 is hydrophobic, the surfaces of the heat transfer plate 23a and the heat transfer plate 23b formed from the sheet 35 are also hydrophobic, so the contact angle of the dew-condensed water droplets in the reconditioning air passage 11 increases, Water droplets are able to drip quickly. the

In addition, when the surface of the sheet 35 is made hydrophilic, the surfaces of the heat transfer plate 23a and the heat transfer plate 23b formed from the sheet 35 are also hydrophilic, so the water droplets condensed in the reconditioning air passage 11 spread into a liquid film. shape, which can suppress the bridging phenomenon of water droplets. the

In the above description, only one example for implementing the present invention has been described, and the present invention is not limited to the first embodiment. the

For example, in the above-mentioned Embodiment 1, the cooling air supplied to the cooling air passage 12 of the heat exchanger 10 uses the air supplied to the moisture absorption path 6 by the processing fan 4, as long as the cooling air can cool the regeneration air, it may also be the same as the moisture absorption path 6. The air in other separate paths may also be supplied by using other fans separate from the processing fan 4 . the

In addition, in the above-mentioned first embodiment, the outer shapes of the heat transfer plate 23a and the heat transfer plate 23b are trapezoidal, but as long as the heat transfer plate 23a and the heat transfer plate 23b can form the regeneration air passage 11 and the cooling air passage 12 and have at least two sets of opposite sides Any shape may be sufficient, and it may be a rectangle, a parallelogram, a right-angled trapezoid, or the like. In addition, an n-sided shape may be formed as a quadrangle or more, and sides other than the sides opposite to the opening of the reconditioning air passage 11 and the opening of the cooling air passage 12 may be formed as sealing surfaces. the

In the first embodiment, the protrusions of the spacer ribs 24a have a width of about 4mm and a height of about 3mm, but these dimensions can also be set according to usage conditions and dew condensation of reconditioning air. Similarly, the dimensions of the protrusions of the spacer ribs 24b are set to about 4mm in width and 2mm in height, but these dimensions can be appropriately set according to usage conditions, impurity-containing state of cooling air, and the like. the

In addition, in Embodiment 1, the guide ribs 27a with a width of about 2 mm and a height of about 3 mm protrude from the heat transfer plate 23a side in the regeneration air passage 11, and two guide ribs 27a with a width of about 2 mm and a height of about 1 mm protrude from the heat transfer plate 23b side. However, the number, position, width dimension, and rib height dimension of the guide ribs are not limited thereto. For example, it is also possible to form a structure in which ribs protrude from either side of the heat conduction plate 23a or the heat conduction plate 23b in the reconditioning air passage 11, and the number of ribs or the width of the ribs can also be adjusted according to the size of the reconditioning air passage 11. Passage width etc. are set appropriately. In addition, as long as the rib height dimension is equal to or less than the spacer rib 24 a that defines the passage interval of the reconditioning air passage 11 , it can be appropriately set according to the passage interval of the reconditioning air passage 11 and the like. the

In addition, in the above-mentioned first embodiment, a plurality of rectification ribs 28 with a width of about 1 mm and a height of about 2 mm protrude from the side of the heat transfer plate 23b in the cooling air passage 12, but the number, position, width dimension, and rib width of the rectification ribs The part height dimension is not limited to this. For example, it is also possible to protrude ribs from both sides of the heat conduction plate 23a side and the heat conduction plate 23b side in the cooling air passage 12. Width and other designs. In addition, the rib height dimension should just be below the space|interval rib 24b which defines the passage interval of the cooling air passage 12, and can be set suitably according to the passage interval of the cooling air passage 12, etc. FIG. the

In addition, in the first embodiment described above, as the arrangement pattern of the reconditioning air passages 11 and the cooling air passages 12, the case where the reconditioning air passages 11 are arranged on both ends of the lamination direction or the case where the cooling air passages 12 are arranged on both ends of the lamination direction is described. circumstances, but not limited to this. That is, the reconditioning air passage 11 may be arranged at one of the two ends in the stacking direction, and the cooling air passage 12 may be arranged at the other end. These arrangement patterns can be set according to device configuration settings. the

In addition, in the above-mentioned first embodiment, the structure in which the stacked state of the heat conduction plate 23a and the heat conduction plate 23b is fixed and held by the rings 30 provided at two places up and down is formed. The outer shape and the number of laminated sheets of the heat conduction plate 23b are appropriately set. the

In addition, in the above-mentioned first embodiment, as a method of ensuring the fixation of the heat transfer plate 23a and the heat transfer plate 23b and the airtightness of the reconditioning air passage 11 and the cooling air passage 12, welding the spacer rib 24a and the melting portion 29b and separating them are adopted. The method of welding the ribs 24b and the fused portions 29a is not limited thereto, and any structure may be used as long as the end faces of the heat transfer plates other than the passage openings can be welded in a laminated state. the

In addition, in the first embodiment described above, as a method of integrally forming concavo-convex portions such as spacer ribs, guide ribs, rectifying ribs, and melted portions with the heat transfer plate, vacuum forming is used to form concavities and convexities on the flat sheet 35. However, the forming method is not limited thereto. For example, a structure in which concave and convex portions are formed on the sheet 35 by pressure forming, ultra-high pressure forming, or press forming may be used. the

In addition, in the above-mentioned first embodiment, two types of concave-convex patterns, the concave-convex pattern 37a and the concave-convex pattern 37b, are formed on the vacuum forming mold 36, and the concave-convex portion 38a and the concave-convex portion 38a and As the method of the uneven portion 38b of the heat conduction plate 23b, the forming method is not limited thereto, and the uneven portion 38a and the uneven portion 38b may be formed separately, or a plurality of uneven portions 38a and the uneven portion 38b may be formed simultaneously. Vacuum forming metal mold 36 . These can be appropriately set according to the molding time and the number of moldings. the

In addition, in the above-mentioned first embodiment, the die 40 having the punching blade 39 having a shape equal to the outer peripheral shape of each heat conduction plate 23a and heat conduction plate 23b is pressed against the sheet 35 formed with the concave and convex portions 38a and the concave and convex portions 38b to cut, and The method of forming the heat conduction plate 23a and the heat conduction plate 23b is not limited thereto, and the sheet 35 may be cut into a predetermined shape by an ultrasonic cutter or a laser, for example. the

(implementation mode 2)

Embodiment 2 of the present invention will be described with reference to FIGS. 8 to 19 . the

Fig. 8 is a schematic cross-sectional view of a dehumidifier according to Embodiment 2 of the present invention. As shown in FIG. 8 , a dehumidification rotor 102 that absorbs moisture from the air is erected in a rotatable manner inside the main body 101, and a moisture absorption path 106 is provided. The suction port 103 sucks air, supplies it to the dehumidification rotor 102 , and discharges it from the suction port 105 opened at the upper part of the main body 101 . In addition, a circulation path 108 is formed in which the regeneration air supplied by the regeneration fan 107 circulates through the dehumidification rotor 102, and a heater 109 for heating the regeneration air is arranged near the wind upstream side of the dehumidification rotor 102 in the circulation path 108. As the heater 109, as long as it is capable of exothermic operation, for example, a nickel-chrome heat-resistant alloy (nickel), a halogen lamp heater, a carbon heater (carbon heater), a PTC heater, etc. can be used. In addition, a substantially trapezoidal heat exchanger 110 is arranged on the wind downstream side of the dehumidification rotor 102 of the circulation path 108 and on the wind upstream side of the moisture absorption path 106. The heat exchanger 110 is provided to form a part of the circulation path 108 so that reconditioning air passes. The regeneration air passage 111 and the cooling air passage 112 through which the air flowing in the moisture absorption passage 106 passes. The reconditioning air passage 111 is vertically arranged such that the reconditioning air inlet side is located at the upper part and the reconditioning air outlet side is located at the lower part. On the other hand, since the cooling air passage 112 is arranged in the horizontal direction, the reconditioning air flowing through the reconditioning air passage 111 and the cooling air flowing through the cooling air passage 112 cross each other in a substantially vertical direction to exchange heat. In addition, the reconditioning air outlet side of the reconditioning air passage 111 has an inclination of about 10° with respect to the horizontal direction so that water droplets reaching the passage outlet can move smoothly. These inclination angles can be appropriately set depending on the structure, but are preferably set to an inclination angle of at least 5° or more in order to satisfy the water droplet moving action on the outlet side of the passage described later. The heat exchanger 110 is connected to the circulation path 108 by fitting the upper part into the head frame 113 and fitting the lower part into the foot frame 114 . The head frame 113 connects the upper portion of the reconditioning air passage 111 of the heat exchanger 110 to the circulation path 108 , and the foot frame 114 connects the lower portion of the reconditioning air passage 111 to the circulation path 108 . In addition, a drain port 115 for discharging condensed water from the circulation path 108 is opened in the path connecting the outlet side of the regeneration air passage 111 of the heat exchanger 110 to the regeneration fan 107 . In addition, a drain tank 116 for receiving and storing condensed water is detachably provided below the drain port 115 . the

In the above structure, in the moisture absorbing path 106, the dehumidifying rotor 102 absorbs moisture from the air supplied by the processing fan 104, and the dry air dehumidified by the dehumidifying rotor 102 is supplied from the outlet 105 to the outside of the main body 101. The desiccant rotor 102 that absorbs moisture in the moisture absorption path 106 releases moisture into the high-temperature regeneration air that rotates and moves on the circulation path 108 and is heated by the heater 109 to perform regeneration, and moves to the moisture absorption path 106 to repeatedly perform moisture absorption and regeneration. On the other hand, reconditioning air containing moisture released from the dehumidification rotor 102 and forming high humidity is supplied to the reconditioning air passage 111 of the heat exchanger 110 . The reconditioning air supplied to the reconditioning air path 111 exchanges heat with the cooling air supplied from the suction port 103 to the cooling air path 112 by the processing fan 104 . The saturated moisture condenses in the reconditioning air passage 111 , and drips down smoothly due to the wind pressure of the reconditioning air flowing downward in the reconditioning air passage 111 and the weight of the water droplets themselves. The water droplets falling in the reconditioning air passage 111 and reaching the outlet of the passage move to the lowermost apex 117 along the inclined portion at the outlet of the passage, so that the stagnation of the water droplets due to the surface tension of the outlet of the passage can be suppressed. The water droplets that successively moved to the lowermost apex portion 117 become large particles, are separated from the passage by their own weight, drop to the drain tank 116, and are recovered as condensed water. The regeneration air cooled and dehydrated by the heat exchanger 110 is sucked into the regeneration fan 107 , supplied to the heater 109 again, and circulated through the circulation path 108 . the

9 is a schematic exploded perspective view of a dehumidification rotor mounted on a dehumidification device according to Embodiment 2 of the present invention. The dehumidification rotor 102 is a circular KORUGETO structure formed by wrapping flat paper made of inorganic fibers such as ceramic fibers and glass fibers or a mixture of these inorganic fibers and pulp, and KORUGETO (コルゲ一ト (transliteration: Colgate)) processed corrugated paper. One or two types of hygroscopic agents such as silica gel, ORAITO (オゼライト (transliteration: Ou Ze Laite)) and other inorganic adsorption-type hygroscopic agents, organic polymer electrolytes, ion exchange resins and other hygroscopic agents, Lithium chloride and other absorbent moisture absorbents form a ventilated structure in the axial direction. The dehumidification rotor 102 is clamped and accommodated from both shaft sides by the frame A119 with the gear part 118 on the outer periphery and the frame B120 with a plurality of radial ribs erected, and the frame A119 and the frame B120 are fixed with a plurality of bolts from the outer periphery, and inserted into the frame. The bearing part 122 of the center hole 121 of the desiccant rotor 102 and the center part of the frame B120 are bolted, and the desiccant rotor 102 is fixed and held. And the gear part 118 of the frame A119 meshes with the gear 124 of the drive motor 123, and the rotation operation of the dehumidification rotor 102 is performed by rotating the drive motor 123. At this time, the rotation speed of the dehumidification rotor 102 is set to about 10 to 42 rotations per hour. In addition, the height of the ribs formed on the frame B120 determines the volume of the space formed between the surface of the desiccant rotor 102 and the front end of the ribs. The ribs are formed by pressing and bending a thin material that can ensure the strength of the ribs, for example, a stainless steel plate with a thickness of about 0.4 to 1.0 mm. In this way, air leakage from the moisture absorption path 106 and the circulation path 108 can be suppressed. In addition, the rotation method of the dehumidification rotor 102 is not limited to the above-mentioned structure, for example, it may also be a structure in which the drive motor 123 is connected to the center of the dehumidification rotor 102 to make it rotate directly, or it may be hung on a gear provided on the outer periphery of the dehumidification rotor 102. A pulley is provided, and the driving motor 123 is connected to the drive motor 123 via the pulley to perform a rotation operation. the

Fig. 10 is a schematic exploded perspective view of a heat exchanger mounted on a dehumidifier according to Embodiment 2 of the present invention. In the heat exchanger 110, a plurality of heat transfer plates 125a formed with concavo-convex portions in a predetermined pattern on a thin plate such as a sheet with a thickness of 0.05 to 0.5 mm are alternately laminated, and a pattern of concavo-convex portions different from that of the heat conduction plate 125a is formed on the same thin plate. The heat conduction plate 125b is formed. The thickness of the heat conduction plate 125a and heat conduction plate 125b is preferably 0.05 mm or more from the viewpoint of the formability, strength, and shape retention of the concave-convex portion described later, and is preferably 0.5 mm or less from the viewpoint of ensuring thermal conductivity. In addition, the gaps between the stacked heat conduction plates 125a and 125b alternately flow in regeneration air and cooling air so that every other layer of regeneration air passages 111 and cooling air passages 112, the regeneration air flowing in the regeneration air passages 111 and cooling The cooling air flowing in the air passage 112 exchanges heat through each of the heat conduction plates 125a and 125b. Thus, the cause of heat exchange obstruction is only the thermal resistance of one sheet of the heat transfer plate 125a and the heat transfer plate 125b, and efficient heat exchange can be performed between the reconditioning air and the cooling air. Each heat transfer plate 125a and heat transfer plate 125b are actually stacked in a total of about 20 to 60 sheets, but for the sake of simplicity, two heat transfer plates 125a and 125b are illustrated in the stacking direction. the

The heat conduction plate 125a and the heat conduction plate 125b have a substantially trapezoidal planar shape, and the approximately trapezoid has two sets of opposite sides on a long side and a short side, the opposite sides of the long sides are formed in a vertically parallel state, and the opposite sides of the short sides are The upper side is parallel to the horizontal direction, and the lower side is inclined at about 10° with respect to the horizontal direction. Hollow convex spacer ribs 126a with a width of about 4mm protrude along each opposite side of the long side on the heat conducting plate 125a. The hollow convex-shaped spacer rib 126b having a width of about 4 mm. The convex height of the spacer ribs 126a of the heat transfer plate 125a is formed to be about 3mm, and the protruding surface of the spacer ribs 126a is in contact with the heat transfer plate 125b in the stacked state, so that the passage interval of the reconditioning air passage 111 is regulated and maintained at a predetermined size, that is, About 3mm. On the other hand, the convex height of the spacer ribs 126b of the heat transfer plate 125b is about 2 mm, and the protruding surface of the spacer ribs 126b is in contact with the heat transfer plate 125a in the laminated state, so that the passage interval of the cooling air passage 112 is maintained in a prescribed manner. The specified size is about 2mm. In addition, the corners 127 at both ends of the spacer ribs 126a that overlap with the spacer ribs 126b protruding from the heat conduction plate 125b in the stacked state are further protruded by the height of the spacer ribs 126b, that is, about 2 mm. The inner hollow concave part of the rib 126b fits, and the entire protruding surface is in contact with the heat conducting plate 125b. Similarly, the corners 128 at both ends of the spacer ribs 126b that overlap with the spacer ribs 126a protruding from the heat conduction plate 125a in the laminated state are further protruded by the height of the spacer ribs 126a, that is, about 3mm. Cooperating with the inner hollow concave part of the spacer rib 126a, the entire protruding surface is in contact with the heat conducting plate 125a. In this way, the entire protruding surfaces of the spacer ribs 126a and 126b are in contact with the adjacent heat transfer plates 125b and 125a, whereby the channel intervals of the reconditioning air channels 111 in the stacked state are maintained at an appropriate predetermined size. That is, about 3 mm, and the passage interval of the cooling air passage 112 is similarly maintained at about 2 mm, which is an appropriate predetermined size. In this way, the stacking interval on the regeneration air passage 111 side is defined by the rib height of the spacer ribs 126a protruding from the heat conduction plate 125a, and the cooling air passage is defined by the rib height of the spacer ribs 126b protruding from the heat conduction plate 125b. 112 side stack spacing. the

In addition, a hollow convex guide rib 129a with a width of about 2 mm is continuously formed in the same direction as the spacer rib 126a at the central portion of the heat conduction plate 125a in the horizontal direction, and two spacer ribs 126b are continuously formed in the vertical direction of the heat conduction plate 125b. A hollow convex guide rib 129b with a width of about 2mm protrudes in the opposite direction. The guide rib 129b is provided on the center portion of the spacer rib 126a and the guide rib 129a in a laminated state. Thus, in the stacked state, the guide ribs 129a and the guide ribs 129b protrude so that the intervals between the ribs on both sides of the reconditioning air passage 111 are approximately equal, and in the stacked state, the guide ribs 129a and the guide ribs 129b The protruding arrangement is continuous with respect to the blowing direction of the reconditioning air, so that the water droplets condensed in the reconditioning air passage 111 drip quickly along the guide ribs 129a and 129b, and the stagnation of water droplets in the reconditioning air passage 111 is suppressed. The rib heights of the guide ribs 129a and 129b can be appropriately set as long as they are equal to or less than the spacer ribs 126a, but are preferably set according to the state of maintaining the interval of the reconditioning air passage 111 and the state of dripping water. For example, if the rib height of the guide rib 129a is set to be about 3mm the same as that of the spacer rib 126a, and the rib height of the guide rib 129b is set to be about 1mm lower than that of the guide rib 129a, then the regeneration air passage 111 The channel gap can also be appropriately maintained in the central part, and the channel cross-sectional area of the reconditioning air channel 111 can also be widened to reduce the channel impedance, and the dew condensation in the channel can drip smoothly without bridging. the

In addition, a plurality of hollow convex rectifying ribs 130 with a width of about 1 mm at approximately equal intervals in the horizontal direction protrude from the heat conducting plate 125b in the same direction as the spacer ribs 126b. The protruding surfaces of the rectifying ribs 130 are formed on The hollow concave part of the guiding rib 129b protruding from the reverse surface of the heat conducting plate 125b is discontinuous. As a result, the rectification ribs 130 protrude from the heat transfer plate 125b side into the cooling air passage 112 in the stacked state of the heat transfer plates, and are discontinuous with respect to the blowing direction of the cooling air, so the cooling air supplied to the cooling air passage 112 rectifies The ribs 130 flow uniformly, and the discontinuities of the rectifying ribs 130 have uniform pressure (equalized pressure), and the wind speed distribution is averaged, enabling efficient heat exchange with the regeneration air. The rib height of the rectifying ribs 130 can be appropriately set as long as it is equal to or less than the spacer ribs 126b. The wind speed distribution of the cooling air can be uniformed, and the cooling air passage 112 can also be used to maintain passage intervals. the

As described above, the heat exchanger 110 is composed of substantially trapezoidal heat transfer plates 125a formed with the spacer ribs 126a and 126b, the guide ribs 129a and 129b, the rectification ribs 130 and other concavo-convex parts, and the heat conduction plates 125b are alternately stacked. The reconditioning air passage 111 is arranged on the opposite side of the short side of the trapezoid, and the cooling passage 12 is arranged on the opposite side of the long side substantially perpendicular to the reconditioning air passage 111 . Accordingly, the passage cross-sectional area of the cooling air passage 112 is formed wider than the passage cross-sectional area of the reconditioning air passage 111, the ventilation resistance of the cooling air passage 112 is formed lower than that of the reconditioning air passage 111, and it is possible to easily supply more air than the reconditioning air. of cooling air. As a result, the reconditioning air can be cooled by a large amount of cooling air, so that the temperature of the reconditioning air can be further lowered during the cooling process, and the amount of saturated water vapor can be reduced. In addition, the passage sectional area of the reconditioning air passage 111 and the cooling air passage 112 is appropriately set according to the structure of the device by changing the planar shape of the heat transfer plate 125a and the heat transfer plate 125b. For example, in the case of a device structure in which the cooling air cannot flow, the cooling air passage 112 is arranged on the short side of the trapezoid, and the reconditioning air passage 111 is arranged on the long side, so that the cross-sectional area of the cooling air passage 112 is relatively large compared to the reconditioning air. The passage 111 has a narrow cross-sectional area, and the passage resistances of the cooling air passage 112 and the reconditioning air passage 111 can be adjusted to the ventilation resistance corresponding to the air volumes of the cooling air and the reconditioning air. the

In addition, in the heat exchanger 110, the arrangement of the reconditioning air passage 111 and the cooling air passage 112 can be adjusted according to the device structure by the lamination pattern of the heat conduction plate 125a and the heat conduction plate 125b. For example, assuming that the protruding surface side of the spacer rib 126a and the spacer rib 126b is stacked sequentially, as shown in FIG. The reconditioning air passages 111 are arranged at both ends in the stacking direction. The heat exchanger 110 is constituted by such an arrangement pattern, and the device is configured such that air flows in the outer periphery of the heat exchanger 110 in the stacking direction, then the regeneration air flowing in the regeneration air passages 111 arranged at both ends of the stacking direction and the outer periphery of the heat exchanger 110 Heat is exchanged between the flowing air, and both the heat conduction plate 125a and the heat conduction plate 125b function as heat conduction surfaces. On the contrary, starting from the heat conduction plate 125b, the heat conduction plates 125a and the heat conduction plates 125b are alternately laminated in the same number, and the cooling air passages 112 are arranged on both ends of the stacking direction. The heat exchanger 110 is constituted by such an arrangement pattern, and the outer periphery of the heat exchanger 110 in the lamination direction is arranged to maintain the heat exchanger 110 or the heat conduction plate 125a and the heat conduction plate 125b. The cooling air passage 112 thermally isolates (thermally insulates) the fixing portion arranged outside it from the reconditioning air flowing in the reconditioning air passage 111 arranged inside it, and suppresses thermal deformation of the fixing portion due to high-temperature reconditioning air. the

The heat conduction plate 125a and the heat conduction plate 125b are formed by heating a flat sheet to soften it, placing it on a vacuum forming die, and forming from the direction of the die by so-called vacuum forming of adhering the sheet by vacuum suction. . It is preferable to use a material having a thickness in the range of 0.05 to 0.5 mm for the sheet 35 . The reason is that if the thickness is less than 0.05 mm, the sheet is prone to breakage due to expansion and contraction at the time of forming the concavo-convex part and a decrease in the strength of the formed sheet, and the formed heat conduction plates 125a and 125b are also fragile at the waist, making it difficult to maintain the shape. , In addition, if the thickness exceeds 0.5mm, due to the increase of thermal resistance, the thermal conductivity is greatly reduced. In this way, the thinner the sheet, the lower the formability, strength, and shape retention, and conversely, the thicker the sheet, the lower the thermal conductivity. Therefore, in order to satisfy formability, strength, shape retention, and thermal conductivity, the range of 0.05 to 0.5 mm is preferable, and the range of 0.1 to 0.3 mm is more preferable. the

Moreover, it is preferable to use a thermoplastic resin material as a raw material of a sheet. Using such a material, since the sheet is thermoplastic, it is heated during vacuum forming, becomes very soft, and smoothly adheres to the vacuum forming die, and the forming of the concave and convex portions of the heat conduction plates 125a, 125b becomes easy. the

In addition, the sheet may be a raw material in which rubber particles are dispersed on a thermoplastic resin material. Forming such a raw material, in addition to the ease of molding of thermoplastic resin, since the rubber dispersed on the sheet has elastic properties, it will make the sheet difficult to split or crack when it is glued to the vacuum forming metal mold, ensuring that the heat conduction plate 125a and the airtightness of the heat conducting plate 125b. For example, when an impact-resistant polystyrene sheet is used as a sheet material, in addition to the ease of molding of thermoplastic resin, the dimensional stability of polystyrene resin reduces the dimensional shrinkage after molding, and the heat conduction plate 125a and the heat conduction plate The dimensional accuracy of the concavo-convex portion of the plate 125b is improved, and the occurrence of cracks or cracks during vacuum forming is suppressed due to the elastic properties of the particles contained in the impact-resistant polystyrene. the

In this way, when polystyrene resin is used as the thermoplastic resin material of the sheet, the dimensional shrinkage after vacuum forming is reduced, and the dimensional accuracy of the concavo-convex portions of the heat transfer plate 125 a and the heat transfer plate 125 b is improved. Therefore, the spacing ribs 126a and the spacing ribs 126b are formed with good precision, and the passage gap between the reconditioning air passage 111 and the cooling air passage 112 is maintained appropriately. the

In addition, polypropylene can also be used as the thermoplastic resin material of the sheet. Using such a raw material, due to the strength of the waist of polypropylene, it is difficult to break or bend the sheet when the sheet is taken out from the vacuum forming die, and when the heat conduction plate 125a and the heat conduction plate 125b are laminated, it is difficult to cause damage due to poor handling. The resulting sheet breaks or bends, improving handling. the

In addition, polycarbonate can also be used as the thermoplastic resin material of the sheet. Using this raw material, due to the shape retention of polycarbonate, the strength of the spacer ribs 126a and 126b, the guide ribs 129a and 129b, and the rectification ribs 130 is improved, and the adjacent parts in the stacked state can be ensured. The strength of each contact position of the heat transfer plate 125a and the heat transfer plate 125b is such that the passage gap between the reconditioning air passage 111 and the cooling air passage 112 is reliably maintained. the

In addition, polyethylene terephthalate can also be used as the thermoplastic resin material of the sheet. Using this raw material, due to the heat resistance of polyethylene terephthalate, the heat resistance of the heat transfer plate 125a and the heat transfer plate 125b is improved, and even if the temperature of the air supplied to the heat exchanger 110 rises during abnormal operation, the heat transfer plate can be suppressed. 125a and thermal deformation of the heat conducting plate 125b. the

In addition, acrylonitrile-butadiene-styrene can also be used as the thermoplastic resin material of the sheet. Using such raw materials, due to the impact resistance of acrylonitrile-butadiene-styrene, when the sheet is taken out from the vacuum forming metal mold, it is difficult to crack or split the sheet. Even during the processing, cracking or splitting hardly occurs, and the airtightness of the heat conduction plate 125a and the heat conduction plate 125b can be ensured. the

In addition, antibacterial agents, antistatic agents, flame retardants, deodorants, etc. may be added singly or in combination to the sheet made of the above-mentioned raw materials. Add any antibacterial agent to the sheet, such as natural antibacterial agents such as allyl isocyanate, patina alcohol, and chitosan, metal antibacterial agents such as silver, and photocatalyst antibacterial agents such as titanium oxide. In the case of the heat exchanger 110, the heat conduction plate 123a and the heat conduction plate 123b formed from the sheet 135 are subjected to antibacterial treatment to suppress the occurrence of bacteria and fine dust caused by water droplets remaining in the heat exchanger 110. In addition, when an anionic, cationic, nonionic low-molecular antistatic agent or metal filler is added as the sheet 135, the heat conduction plate 123a and the heat conduction plate 123b formed from the sheet 135 are subjected to antistatic treatment to suppress The condensed water recovered by the heat exchanger 110 is charged, and discharge phenomenon hardly occurs during drainage operation. In addition, when a flame retardant, such as a halogen-based, phosphorus-based, inorganic-based flame retardant, is added to the sheet 135, the heat-conducting plate 123a and the heat-conducting plate 123b formed from the sheet 135 are subjected to a flame-retardant treatment to suppress abnormalities. The thermal deformation of the heat conduction plate 123a and the heat conduction plate 123b caused by the temperature rise of the supply air supplied to the heat exchanger 110 at the time. In addition, when a deodorant such as activated carbon or photocatalyst is added to the sheet 135, the heat conduction plate 123a and the heat conduction plate 123b formed by the sheet 135 are deodorized to suppress residual water droplets mixed into the heat exchanger 110 or heat exchange. Impurities in the container 110 generate odor. the

In addition, the surface of the sheet is preferably treated with hydrophobicity or hydrophilicity to suppress retention of water droplets. For example, the surface of a sheet made of a thermoplastic resin material is hydrophobic even without special treatment, and the surface can be coated with a fluorine-based hydrophobic material to increase the hydrophobicity. If such a sheet is used to form the heat conduction plate 125a and the heat conduction plate 125b, the surfaces of the formed heat conduction plate 125a and the heat conduction plate 125b also have hydrophobicity, and the contact angle of the water droplets condensed on the surface of the regeneration air passage 111 changes due to the hydrophobic effect of the surface. Large, dripping rapidly in the regeneration air passage 111. In addition, the sheet is coated with a hydrophilic coating such as a fluorine-based hydrophilic coating to make the surface of the sheet hydrophilic. In this way, the surfaces of the heat conduction plate 125a and heat conduction plate 125b formed from the sheets are also hydrophilic, and the water droplets condensed on the surface of the reconditioning air passage 111 expand into a liquid film through the hydrophilic effect, and the bridging phenomenon of water droplets is suppressed. the

In addition, as the heat transfer plate, a thin-plate-like sheet material formed by molding metal can also be used. As the sheet material, since the heat exchanger 110 is exposed to high temperature and high humidity, a stainless steel or aluminum thin plate is used, preferably with a thickness of 0.05 to 0.5 mm, in consideration of heat resistance and corrosion resistance. If the thickness is less than 0.05 mm, the sheet is likely to be damaged due to expansion and contraction during the forming of the concavo-convex part and a decrease in the strength of the formed sheet, and the formed heat conduction plates 125a, 125b are also fragile at the waist, making it difficult to maintain the shape. If the thickness exceeds 0.5mm, the thermal conductivity will be greatly reduced due to the increase of thermal resistance, and the use of metal materials may also cause the disadvantage of increased weight. In this way, the thinner the sheet, the lower the formability, strength, and shape retention, and conversely, the thicker the sheet, the lower the thermal conductivity and the heavier the weight. Therefore, in order to satisfy formability, strength, shape retention and thermal conductivity, the sheet thickness is preferably in the range of 0.05 to 0.5 mm, more preferably in the range of 0.1 to 0.3 mm. In this way, the metal material is used as the heat conduction plate, and the metal material generally has a thermal conductivity several ten times higher than that of the resin material, so the heat exchange efficiency per unit heat conduction plate can be greatly improved. That is, as long as it is a heat exchanger made of a metal material with the same capacity as a heat exchanger made of a resin material, it can be expected that the dehumidification efficiency can be improved by improving the heat exchange efficiency, and the reduction in power consumption can be expected. On the other hand, when considering the same heat exchange efficiency, the capacity of the heat exchanger can be reduced, and a compressed dehumidifier can be obtained. the

11 is a schematic exploded perspective view of a heat exchanger mounted on a dehumidifier according to Embodiment 2 of the present invention in a fixed state, showing a structure in which a heat exchanger 110 is connected to a head frame 113 and a foot frame 114 . In FIG. 11 , the heat exchanger 110 has a body shape by alternately stacking a predetermined number of heat transfer plates 125 a and 125 b in total, 42 sheets. The heat exchanger 110 inserts the upper peripheral portion 131 of the four sides of the surface of the body shape into which the regeneration air flows into the head frame 113, and inserts the lower periphery of the four sides of the body shape of the lower surface of the heat exchanger 110 into which the regeneration air flows. The portion 132 is fitted into the foot frame 114 to be fixed. The head frame 113 forms a case in which a head inlet 133 through which reconditioning air flows in and a head connection port 134 connected to the heat exchanger 110 are opened. The head frame 114 also forms a box in which a foot outlet 135 through which reconditioning air flows in and a foot connection port 136 connected to the heat exchanger 110 are opened. The head connection port 134 is provided with a flange portion 138 as a sealing portion 137 in order to prevent leakage of regenerated air and condensed water from the connection portion between the heat exchanger 110 and the upper peripheral portion 131, so that the upper peripheral portion 131 of the heat exchanger 110 is separated from the upper peripheral portion 131. The upper direction and the side direction constitute a contact surface to match the heat exchanger 110 , and the elastic sealing material 139 is attached to the flange portion 138 . The flange part 138 contacts the upper surface peripheral part 131 of the heat exchanger 110 through the elastic sealing material 139, and the elastic sealing material 139 deforms to fill the gap, thereby preventing leakage of reconditioning air and condensed water. In addition, the foot connection port 136 of the foot frame 114 is similarly provided with a flange portion 138 as a seal portion 137, and an elastic seal material 139 is attached to prevent leakage of regeneration air and condensed water. When the condensed water leaks from the heat exchanger 110, the leaked condensed water evaporates again, adsorbs on the desiccant rotor 102 again, or is released into the city as water vapor, resulting in a loss of dehumidification capacity. In addition, when the leaked condensed water stays in the main body 101 other than the drain tank 116, there is a possibility of leaking from the main body 101. In the above structure, leakage of these condensed waters is prevented, and a dehumidification device with reduced dehumidification capacity or no leakage of water can be formed. Moreover, the head frame 113 and the foot frame 114 are fixed to the partition plate which comprises the dehumidifier main body which is not shown in figure. As the elastic sealing material 139, a raw material that has elasticity and can prevent the penetration of air and water under pressure is used. In the present embodiment, EPUTOSHIRA (エプトシララ) is independently foamed, but rubber, polyester, etc. can also be used. For raw materials such as ethylene, there is no difference in the above-mentioned effects. the

In addition, on the inner wall surfaces of the head frame 113 and the foot frame 114 , drip promoting ribs 141 are provided as water drop promoting portions 140 that promote dripping of attached water droplets. In the head frame 113 and the foot frame 114, heat exchange also takes place between regeneration air and cooling air. In this case, the amount of saturated water vapor in the regenerating air decreases and becomes saturated with water, and the water on the inner wall surface condenses to form water droplets. The water droplet stays at this position until it reaches a certain size, and the water droplet falls vertically downward against the adhesion force to the wall due to its own weight. In the state where the water droplets are stagnant on the wall, the water droplets themselves act as thermal resistance and hinder the heat exchange between the head frame 113 and the foot frame 114 . As mentioned above, by providing the dripping promotion rib 141, the condensed water droplets are collected by the concave and convex shape, and the growth of the water droplets is promoted, so that the water droplets drop from the wall surface as soon as possible. In this way, the stagnation of water droplets on the wall surface is reduced, heat exchange is promoted, and the recovery amount of condensed water is increased. Furthermore, by forming the concavo-convex shape, the area for heat exchange, that is, the heat conduction area can be increased compared with the planar shape, so heat exchange can also be promoted. The dripping promotion rib 141 needs to be formed in a shape that prevents water droplets from stagnating and dripping, and may be formed in a straight line from above to below. Moreover, the height and pitch of the dripping promotion ribs 141 are set according to the water droplet hydrophobicity of the wall surface of the head frame 113 and the foot frame 114, but the size of the dripping water drop can also be considered, and the height can be set to 0.5mm-52mm and the pitch 1.0mm. mm to 10 mm, but in this embodiment, the height is 2.0 mm and the pitch is 2.0 mm. In addition, in this embodiment, it is arranged on the side wall surface, but it is also possible to make the top surface of the head frame 113 and the bottom surface of the foot frame 114 inclined from the horizontal plane, and provide ribs from the high position to the low position to promote adhesion. drops of water dripping down. the

In addition, in FIG. 11 , the top surface of the head frame 113 is formed as another component, and the heat exchange promotion part 142 for heat exchange between the cooling air and the reconditioning air of the head frame 113 is made of a high thermal conductivity material. In this embodiment, the top plate is made of stainless steel plate gold with high thermal conductivity. In addition, metallic substances are considered as highly heat-conductive substances, but stainless steel, aluminum, etc. are preferably used in consideration of corrosion and the like because the reconditioning air passage has a relatively high temperature and high humidity compared to indoor conditions. Moreover, in this way, a part of the head frame 113 is constituted by a material with high thermal conductivity, so that the heat exchange of the head frame 113 can be promoted, and the recovery amount of condensed water can be increased. In FIG. 11 , only the head frame 113 uses a highly thermally conductive material, but the foot frame 114 can also be used, and a further improvement in heat exchange efficiency can be expected. the

12 is a schematic perspective view showing a water drop promoting unit mounted on a head frame of a dehumidifier according to Embodiment 2 of the present invention, showing a structure in which a drip promoting dimple 143 is provided as a water drip promoting unit 140 on a head frame 113 . The drip promotion dimple 143 is formed by arranging a plurality of hemispherical protrusions on the inner wall surface of the head frame 113 . The water droplets condensed on the wall surface are collected by the small steep slope formed by the dripping promotion dimples 143, which promotes the combination of surrounding small water droplets and becomes larger, so that the water droplets can drip from the wall surface as soon as possible. In order to have such an effect, the dripping promotion dimples 143 need to form the diameter and pitch of the hemispherical convex part to a predetermined size according to its system, but the diameter may be 1.0 mm to 52 mm, and the pitch may be 2.0 mm to 10 mm. In this embodiment, In , the diameter of the convex portion is 2.0 mm, and the pitch to the adjacent convex portion is 52 mm. In the present embodiment, the head frame 113 is described, but the same applies to the foot frame 114 , and the heat exchange efficiency can be improved by providing the drip promotion dimple 143 . In addition, in FIG. 12 , the drip promotion dimple 143 is provided on the inner wall surface, but it can also be provided on the top surface of the head frame 113 or the bottom surface of the foot frame 114 , and there is no difference in the effect of promoting the dripping of water droplets. the

13 is a schematic exploded perspective view showing a heat exchanger deterioration prevention unit mounted on the head frame of the dehumidifier according to Embodiment 2 of the present invention, showing a heat exchanger as a heat exchanger for preventing the heat exchanger 110 from deteriorating due to the heat of reconditioning air. The deterioration prevention unit 144 is configured in a case where the protective sheet 145 is disposed on the head frame 113 . The protection sheet 145 is arranged on the head frame 113 to cover the regeneration air inlet end surface 146 of the heat exchanger 110 when the head frame 113 is mated with the heat exchanger 110 . The temperature of the regenerated air at the regenerated air inlet end face 146 is higher than that of the ambient air, usually about 42°C to 60°C. Adsorption can be fully performed, so the release of moisture in the regeneration part of the dehumidification rotor 102 becomes less, and the heat consumed by the latent heat of vaporization of the heat given by the heater 109 becomes less, and when the high temperature is maintained, it flows into the head frame 113 and flows into the heat exchanger. 110. In addition, when the rotational drive of the dehumidification rotor 102 is stopped due to any abnormality, or when the processing fan 104 is stopped due to any abnormality, etc., the moisture absorption and release of the dehumidification rotor 102 can be performed normally, and the regeneration air flowing into the heat exchanger 110 The temperature rose sharply. At this time, when the heat exchanger 110 is made of a resin with a relatively low heat-resistant temperature, there is a possibility of deterioration such as deformation due to the heat of the reconditioning air. Therefore, as described above, the protective sheet 145 is arranged to cover the reconditioning air inlet end surface 146, and the reconditioning air flowing in at a high temperature can first hit the protection sheet 145 and then flow into the reconditioning air passage 111 of the heat exchanger 110, so that high temperature can be prevented. The air directly hits the reconditioning air inlet end surface 146 of the heat exchanger 110 to prevent deterioration due to the heat of the heat exchanger 110 . Since the protection sheet 46 needs to cover the reconditioning air inlet end surface 146 of the heat exchanger 110 and allow the reconditioning air to pass through, as shown in FIG. The inlet of the reconditioning air passage 111 of 110 approximately coincides with each other. In addition, since the protection sheet 145 is exposed to high temperature and high humidity by the reconditioning air, dew may condense on the surface, so it is necessary to use a material having heat resistance and corrosion resistance. For example, it is preferable to use polyethylene terephthalate resin, polyphenylene sulfide, syndiotactic polystyrene resin, polycarbonate resin in consideration of heat resistance among resin materials, and it is preferable to use Stainless steel, aluminum and other materials. In addition, when a resin material is used, the head frame 113 is made of the same material and integrally molded, thereby reducing the number of parts and realizing an inexpensive structure. the

14 is a schematic cross-sectional view showing the reconditioning air rectifying unit mounted on the head frame and the foot frame of the dehumidifier according to Embodiment 2 of the present invention, showing that the heat exchanger 142 as the promotion heat exchanger 110 is connected between the head frame 113 and the foot frame. 114 is provided with the structure of the case where the reconditioning air rectification part 148 is provided. In FIG. 14 , louvers 149 are disposed on the head frame 113 and the foot frame 114 as the reconditioning air straightening unit 148 . In this embodiment, the reconditioning air flowing into the head frame 113 from the lateral direction changes its flow direction by approximately 90° in the head frame 113 , and flows into the heat exchanger 110 downward. The wind direction plate 149 is configured to equalize the flow (fluid) of the above-mentioned reconditioning air. In FIG. 14 , the fluids are stagnated in parts A and B in the figure, and flow into the heat exchanger 110 in a state where the wind speed distribution is large. The wind direction plate 149 has a shape of a combination of a straight line and an arc to smoothly change the flow direction of the regeneration air to reduce the ventilation resistance, so that the regeneration air flows without omission over the entire area of the A part and the B part where the fluid stagnates. By arranging the wind direction plate 149 as described above, the flow can be made uniform and the wind velocity distribution can be made uniform. Accordingly, the heat exchange efficiency between the reconditioning air and the cooling air in the heat exchanger 110 is improved, and condensation of moisture can be promoted. On the other hand, the louver 149 arranged on the foot frame 114 also has the same effect as the louver 149 arranged on the head frame 113 described above, and can improve the heat exchange efficiency of the heat exchanger 110 . The wind direction plate 149 may also be provided with other components separate from the head frame 113 and the foot frame 114, but the integral formation can reduce the number of components and form an inexpensive structure. the

15 is a schematic cross-sectional view showing rectifying plates mounted on the head frame and the foot frame of the dehumidifier according to Embodiment 2 of the present invention. In FIG. 15 , straightening plates 150 are disposed on the head frame 113 and the foot frame 114 as the reconditioning air straightening portion 148 . The rectifying plate 150 is configured as a plate-shaped body in which a plurality of through-holes 151 are opened. A pressure loss is formed with respect to the fluid of the reconditioning air, which can function to make the wind velocity distribution at the inlet of the heat exchanger 110 uniform. The through-holes 151 with a plurality of openings are arranged uniformly with respect to the regeneration air path of the heat exchanger 110 to reduce the wind speed distribution of the regeneration air to the heat exchanger 110 . In addition, when the wind velocity distribution of the reconditioning air is preliminarily biased and flows into the heat exchanger 110, the diameter, shape, and pitch of the through-holes 151 can be changed according to the location in accordance with the flow, so that the heat exchanger 110 can be adjusted. The fluid inside the regeneration air passage 111 is homogenized. Thereby, the heat exchange efficiency of the reconditioning air and cooling air in the heat exchanger 110 can be improved, and the condensation of moisture can be accelerated. On the other hand, the rectifying plate 150 offset on the foot frame 114 also has the same effect as that of the rectifying plate 150 disposed on the head frame 113 described above, and can improve the heat exchange efficiency of the heat exchanger 110 . The rectifying plate 150 may also be configured with other components that are separate from the head frame 113 and the foot frame 114, or may be integrally formed to reduce the number of components and form an inexpensive structure. the

16 is a schematic cross-sectional view showing an impurity prevention unit mounted on a head frame of a dehumidifier according to Embodiment 2 of the present invention, showing a configuration of an impurity prevention unit 152 that prevents impurities from entering a heat exchanger 110 . The impurity mixing prevention part 152 is provided near the reconditioning air inlet of the head frame 113, and is formed in a porous shape in which a plurality of small holes are provided in the flow direction of the reconditioning air to capture impurities. In order to capture impurities, it is good to form small holes, but if the ventilation resistance of the regeneration air is too large, the capacity of the regeneration fan 107 needs to be increased, and for such reasons, the dehumidifier will become larger. Therefore, as the impurity mixing prevention part 152, it is suitable to use a material with small pores and low ventilation resistance, such as a mesh material made of heat-resistant resin or a grid-shaped material woven with metal fibers. Most of the impurities mixed into the cooling air enter the main body, which can be removed by the filter, and since the circulation path 108 of the regeneration air is basically a closed circuit, no impurities are mixed into the circulation path 108 at all. However, some impurities that cannot be caught by the filter adhere to the treatment area of the desiccant rotor 102 , and some of the impurities attached when the shape of the treatment area of the desiccant rotor 102 is driven to the regeneration area enter the circulation path 108 . Impurities mixed into the circulation path 108 accumulate in the path, and may also accumulate in the air path of the heat exchanger 110 . In this case, a part of the reconditioning air passage 111 of the heat exchanger 110 is clogged due to the accumulation of impurities, resulting in a decrease in the reconditioning air volume, which may lower the heat exchange efficiency and reduce the dehumidification capacity. As described above, by providing the impurity incorporation prevention unit 152 , it is possible to suppress intrusion of impurities into the reconditioning air passage 111 of the heat exchanger 110 , and dehumidify stably without reducing the heat exchange efficiency of the heat exchanger 110 . In addition, by disposing the impurity prevention part 152 in a detachable manner, the user can regularly clean the impurity prevention part 152 without worrying about the increase of the ventilation resistance due to the impurities in the impurity prevention part 152, and can obtain sufficient dehumidification capacity. Dehumidifiers that will degrade. The mechanism for disposing the impurity prevention part 152 in a detachable manner is not shown, but may be, for example, a mechanism in which the foreign matter prevention part 152 can be slid and removed along the guide. At this time, it is important that there is no leakage of reconditioning air or water droplets in the state where the foreign matter mixing prevention part 152 is removed, and it is necessary to provide a leakage prevention part provided with a fitting part or the like. When the condensed water leaks, the leaked condensed water evaporates again, is adsorbed on the dehumidification rotor 102 again, or is released as water vapor in the room, thereby constituting a loss of dehumidification capacity. In addition, even if the leaked condensed water stagnates in the main body 101 other than the drain tank 116, water leakage from the main body 101 may occur. the

17 is a schematic cross-sectional view showing the structure of the case where the head frame of the dehumidifier according to Embodiment 2 of the present invention is provided with split ribs, showing that the head frame 113 is provided with split ribs 153 that are divided into a plurality of passages along the stacking direction. structure of the situation. As shown in the figure, the head frame 113 is provided with a head connection port 134 and a split rib 153 , and the split rib 153 is divided into two head connection ports 134 to divide the head frame 113 into two rooms. The reconditioning air inlet 154 and the reconditioning air outlet 155 are respectively disposed in each room divided by the dividing rib 153 to introduce and discharge reconditioning air. The foot frame 114 has a foot frame connecting port 136 connected to the heat exchanger 110 and a water pumping hole 156 for discharging condensed water. In the heat exchanger 110 , the upper part of the reconditioning air passage 111 is inserted and fixed to the head frame 113 , and the lower part thereof is inserted and fixed to the foot frame 114 . The reconditioning air introduced into the head frame 113 from the reconditioning air inlet 154 flows downward in the reconditioning air passage 111 of the heat exchanger 110. The dividing rib 153 of the head frame 113 extends to the end surface of the reconditioning air passage 111 of the heat exchanger 110 to divide the reconditioning air passage. The reconditioning air flows vertically downward in the reconditioning air passage 111 on the divided side. Then, the flow direction is changed by approximately 180° by the foot frame 114, so that the reconditioning air passage 111 on the other side of the heat exchanger 110 flows vertically upward. Then, the air flows into the head frame 113 and flows out through the reconditioning air outlet 155 . By forming the above structure, with the same volume of the heat exchanger, it is also possible to increase the flow path of the reconditioning air inside the heat exchanger 110 and increase the heat exchange distance between the reconditioning air and the cooling air, thus improving the cooling efficiency of the reconditioning air. In addition, the foot frame 114 temporarily diffuses the reconditioning air, and reintroduces the reconditioning air passage 111, so that the temperature boundary layer growing on the wall surface of the reconditioning air passage 111 is temporarily eliminated, and a decrease in heat exchange efficiency can be suppressed. In addition, in the present embodiment, the cross-sectional area of the flow passage where the reconditioning air flows upward in the reconditioning air passage 111 is larger than that of the flow passage that flows downward. With such a structure, the wind speed of the reconditioning air becomes faster in the passage flowing below, so that the water droplets adhering to the wall surface are pressed by the wind speed to promote the dripping of the water droplets. On the other hand, in the passage flowing upward, the wind speed of the reconditioning air is slowed down, so that the wind speed of the reconditioning air prevents the water droplets adhering to the wall surface from dripping. The stagnation of water droplets on the wall surface is reduced, so it is possible to suppress a decrease in heat exchange efficiency due to water droplets becoming thermal resistance, and it is possible to obtain the heat exchanger 110 with high heat exchange efficiency. In addition, it is also possible to provide a heat exchange unit 157 that performs a heat exchange between the reconditioning air flowing into the heat exchanger 110 and the reconditioning air flowing out. In the heat exchanger 157, the split ribs 153 are made of a material with high thermal conductivity. Thereby, before flowing into the heat exchanger 110, the temperature can be lowered in advance by exchanging heat with the reconditioning air after passing through the heat exchanger 110, and the reconditioning air can be cooled to a lower temperature. In addition, the reconditioning air passing through the heat exchanger 110 can exchange heat with the reconditioning air before flowing into the heat exchanger 110 to increase its temperature and flow out. The regeneration air flowing out of the heat exchanger 110 is guided to the regeneration fan 107 and introduced into the heater 109 to raise the temperature in advance, thereby reducing the power consumption of the heater 109 . In this embodiment, the divided ribs 153 are used as the heat exchange portion 157, but the heat exchange portion 157 may be additionally provided to form a structure in which the regeneration air flowing into the heat exchanger 110 exchanges heat with the regeneration air flowing out of the heat exchanger 110. , there is no difference in effect. In addition, in the present embodiment, the passage of the heat exchanger 110 is divided into two, and the reconditioning air is turned back once, but by adding the dividing ribs 153 of the head frame 113 and the foot frame 114, it can be obtained. The switching times of the system balance can further improve the above-mentioned effect. the

Fig. 18 is a schematic exploded perspective view showing a fixed holding state of a heat exchanger in a case where a head frame and a foot frame of the dehumidifier according to Embodiment 2 of the present invention are integrally formed. In FIG. 18 , the head frame 113 and the foot frame 114 are integrally formed via a joint frame portion 158 . A flange portion 138 is provided as a sealing portion 137 on the head connection port 134 and the foot connection port 136 of the integrally formed head frame 113 and foot frame 114 , and an elastic sealing material 139 is attached thereto. Insert the heat exchanger 110 from the direction of the arrow in the figure, so that the upper part and the lower part are embedded and fixed in the connecting ports of the head frame 113 and the foot frame 114 respectively. In addition, the heat exchanger 110 is fixedly held by screwing the cover part 159 to the integrally formed head frame 113 and foot frame 114 . With such a structure, since the positional relationship between the head frame 113 and the foot frame 114 relative to the heat exchanger 110 can be restricted, the heat exchanger 110 can be assembled into the head frame 113 and the foot frame without damaging the sealing performance of the sealing portion 38. In 114, it is possible to suppress a reduction in dehumidification performance due to air leakage with an inexpensive structure. the

Fig. 19 is a hygroscopic air diagram showing the state of reconditioning air in the dehumidifier according to Embodiment 2 of the present invention. In FIG. 19 , the solid line connecting points a, b, and c represents the state change of the reconditioning air in the dehumidifier of this embodiment, and the dotted line connecting points d, e, and f represents the reconditioning air of the conventional dehumidification device. status change. Here, points a and d represent the air state at the outlet of the heat exchanger 110, and points b and e represent the air state at the outlet of the heater 109. In addition, point c and point f show the state of the air at the inlet of the heat exchanger 110 which is the outlet of the dehumidification rotor 102 . In the dehumidifier of this embodiment, since the heat exchanger 110 efficiently exchanges heat between the reconditioning air and the cooling air, the reconditioning air can be further cooled to a lower temperature than conventional dehumidifiers. Therefore, the temperature Ta at the outlet of the heat exchanger 110 shown at the point a in this embodiment takes a lower value than the temperature Td at the outlet of the heat exchanger 110 shown at the conventional point d. For example, when cooling air at 20°C is used, the outlet temperature Td of the conventional heat exchanger 110 is only cooled to about 37°C, but in this embodiment, the temperature Ta at the outlet of the heat exchanger 110 can be cooled to 30°C or less. In addition, the air at the outlet of the heat exchanger 110 is water-saturated saturated air after being cooled, so the amount of saturated water vapor is equal to the absolute humidity. Therefore, the temperature at the outlet of the heat exchanger 110 which is the saturated air can be lower than before, and accordingly the absolute humidity can also be lowered. That is, the absolute humidity Xa at the outlet of the heat exchanger 110 shown at the point a in this embodiment becomes a lower value than the absolute humidity Xd at the outlet of the heat exchanger 110 shown at the conventional point d. Specifically, relative to the absolute humidity Xd at the outlet of the conventional heat exchanger 110 being about 5 g/kg (DA), the absolute humidity Xa at the outlet of the heat exchanger 110 of the present embodiment is reduced to about 3 g/kg (DA). The reconditioning air having a low absolute humidity, that is, the amount of saturated water vapor is supplied to the heater 109, so that the relative humidity of the air heated by the heater 109 is sufficiently lowered to become drier air. That is, the relative humidity at the outlet of the heater 109 of the present embodiment shown at the point b is a lower value than the relative humidity at the outlet of the conventional heater 109 shown at the point e. This sufficiently dry air is supplied to the dehumidification rotor 102, so the amount of moisture released from the dehumidification rotor 102 increases, and the amount of condensed water recovered by the heat exchanger 110, that is, the dehumidification amount also increases. In addition, since the amount of saturated water vapor in the reconditioning air leaking from the gap between the dehumidification rotor 102 and the heater 109 is also reduced, the leakage amount of water vapor accompanying this air leakage is also reduced, and the decrease in the dehumidification amount caused by the leakage of water vapor can be suppressed. . Through such composite action, the dehumidification device of the present embodiment improves dehumidification efficiency (condensation latent heat of dehumidified moisture/energy required for dehumidification). the

The content described above is a description of an example for implementing the present invention, and the present invention is not limited to the above-mentioned second embodiment. the

For example, in the above-mentioned second embodiment, the cooling air supplied to the cooling air passage 112 of the heat exchanger 110 uses the air supplied to the moisture absorption path 106 by the processing fan 104, as long as the cooling air can cool the regeneration air, it may also be the same as the moisture absorption path 106. The air in other separate paths may also be supplied by using another fan separate from the processing fan 104 . the

In addition, in the above-mentioned second embodiment, the outer shapes of the heat transfer plate 125a and the heat transfer plate 125b are trapezoidal, but as long as the heat transfer plate 125a and the heat transfer plate 125b can form the regeneration air passage 111 and the cooling air passage 112 and have at least two sets of opposite sides Any shape may be sufficient, and it may be a rectangle, a parallelogram, a right-angled trapezoid, or the like. the

In Embodiment 2, the protrusions of the spacer ribs 126a have a width of about 4mm and a height of about 3mm, but these dimensions can also be set according to usage conditions and dew condensation of reconditioning air. Similarly, the dimensions of the protrusions of the spacer ribs 126b are set to about 4mm in width and 2mm in height, but these dimensions can also be appropriately set according to usage conditions, impurities contained in cooling air, and the like. the

In addition, in the above-mentioned second embodiment, the guide ribs 129a with a width of about 2 mm and a height of about 3 mm protrude from the side of the heat transfer plate 125a in the reconditioning air passage 111, and two guide ribs 129a with a width of about 2 mm and a height of about 1 mm are protruded from the side of the heat transfer plate 125b. The guide ribs 129b, but the number, position, width dimension, and rib height dimension of the guide ribs are not limited thereto. For example, it is also possible to form a structure in which ribs protrude from either side of the heat conduction plate 125a side or the heat conduction plate 125b side in the reconditioning air passage 111, and the number of ribs or the width of the ribs can also be determined according to the reconditioning air passage 111. Passage width etc. are set appropriately. In addition, as long as the rib height dimension is equal to or less than the spacer rib 126 a that defines the passage interval of the reconditioning air passage 11 , it can be appropriately set according to the passage interval of the reconditioning air passage 111 and the like. the

In addition, in the above-mentioned second embodiment, a plurality of rectifying ribs 130 with a width of about 1 mm and a height of about 2 mm protrude from the side of the heat transfer plate 125b in the cooling air passage 112, but the number, position, width dimension, and rib of the rectifying ribs The part height dimension is not limited to this. For example, it is also possible to protrude ribs from both sides of the heat conduction plate 125a side and the heat conduction plate 125b side in the cooling air passage 112. Width and other designs. In addition, the rib height dimension should just be below the space|interval rib 126b which defines the passage interval of the cooling air passage 112, and can be set suitably according to the passage interval of the cooling air passage 112, etc. FIG. the

In the second embodiment described above, as the arrangement pattern of the reconditioning air passages 111 and the cooling air passages 12, the case where the reconditioning air passages 111 are arranged on both ends of the stacking direction or the case where the cooling air passages 112 are arranged on both ends of the lamination direction is described. circumstances, but not limited to this. That is, the reconditioning air passage 111 may be arranged at one end of both ends in the stacking direction, and the cooling air passage 112 may be arranged at the other end. These arrangement patterns can be set according to device configuration settings. the

In addition, in the above-mentioned second embodiment, as a method of integrally forming concavo-convex portions such as spacer ribs, guide ribs, rectifying ribs, and melted portions with the heat transfer plate, the concavo-convex portions are formed on the flat sheet 35 by vacuum forming. method, but the forming method is not limited thereto, for example, a structure in which concave and convex portions are formed on the sheet 35 by pressure forming, ultra-high pressure forming, press forming, etc. may be used. the

Industrial Applicability: As mentioned above, the dehumidifier of the present invention can improve heat exchange efficiency, realize small size and light weight, reduce ventilation resistance, and can also reduce water drop retention in the regeneration air passage. The airtightness of the regeneration air passage and the cooling air passage can be equipped with a heat exchanger that can be adjusted to the passage interval suitable for the state of the regeneration air and cooling air, and the dehumidification efficiency can be improved (condensation latent heat of dehumidified moisture / dehumidification required Energy), suitable for high-efficiency dehumidification functions such as dehumidifiers, dryers, clothes dryers, clothes drying washing machines, bathroom dryers, air conditioners, or solvent recovery devices. the

Claims (25)

1. dehydrating unit, it has:

Carry out moisture absorption and to adding that hot-air is emitted moisture and the dehumidifying rotor of regenerating from air supply;

To described dehumidifying rotor air supply and the moisture absorption path of hygroscopic moisture;

Make regeneration air be recycled to described dehumidifying rotor and emit the circulating path of moisture;

The heater that adds the regeneration air of the described dehumidifying rotor of heat supply; And

Have the regeneration air path of a part that forms described circulating path and the heat exchanger of the path of cool air that the cooling air flows, wherein,

Described heat exchanger forms such structure: laminal heat-conducting plate is stacked a plurality of with the interval of regulation, in the stacked gap of described heat-conducting plate, alternately flow into regeneration air and cooling air and form described regeneration air path and described path of cool air, by the stacked interval that keeps described heat-conducting plate with the integrally formed interval flank of described heat-conducting plate, make regeneration air and the heat exchange of cooling air via each described heat-conducting plate, make the moisture in the regeneration air condensing

Be integrally formed in the prominent rectification flank of establishing in the described path of cool air with described heat-conducting plate,

Described rectification flank is in the discontinuous formation of air supply direction of cooling air.

2. dehydrating unit as claimed in claim 1 is characterized in that, is integrally formed in the prominent guiding flank of establishing in the described regeneration air path with described heat-conducting plate.

3. dehydrating unit as claimed in claim 2 is characterized in that, described guiding flank forms continuously at the air supply direction of regeneration air.

4. dehydrating unit as claimed in claim 1, it is characterized in that, the profile of described heat-conducting plate is formed the polygon of the opposite side of opposite side with long side and short brink, dispose described path of cool air, dispose described regeneration air path at short brink at long side.

5. dehydrating unit as claimed in claim 1, it is characterized in that, the profile of described heat-conducting plate is formed the polygon of the opposite side of opposite side with long side and short brink, dispose described regeneration air path, dispose described path of cool air at short brink at long side.

6. as claim 4 or 5 described dehydrating units, it is characterized in that described heat-conducting plate is configured to make regeneration air to flow downward along vertical direction in described regeneration air path.

7. dehydrating unit as claimed in claim 6 is characterized in that, one side that described heat-conducting plate is corresponding with the outlet side of described regeneration air path tilts with respect to horizontal direction.

8. dehydrating unit as claimed in claim 6 is characterized in that, one side that described heat-conducting plate is corresponding with the entrance side of described regeneration air path tilts with respect to horizontal direction.

9. dehydrating unit as claimed in claim 1 is characterized in that, arranges described regeneration air path at the stacked direction two ends of described heat-conducting plate.

10. dehydrating unit as claimed in claim 1 is characterized in that, arranges described path of cool air at the stacked direction two ends of described heat-conducting plate.

11. dehydrating unit as claimed in claim 1 is characterized in that, described heat-conducting plate is shaped by the sheet material that is made of thermoplastic resin material.

12. dehydrating unit as claimed in claim 1 is characterized in that, described heat-conducting plate is shaped by the sheet material of dispersion rubber particle on thermoplastic resin material.

13., it is characterized in that the thermoplastic resin material of described sheet material is a polystyrene as claim 11 or 12 described dehydrating units.

14., it is characterized in that the thermoplastic resin material of described sheet material is a polypropylene as claim 11 or 12 described dehydrating units.

15., it is characterized in that the thermoplastic resin material of described sheet material is a Merlon as claim 11 or 12 described dehydrating units.

16., it is characterized in that the thermoplastic resin material of described sheet material is a PETG as claim 11 or 12 described dehydrating units.

17., it is characterized in that the thermoplastic resin material of described sheet material is an acrylonitrile-butadiene-styrene (ABS) as claim 11 or 12 described dehydrating units.

18., it is characterized in that described sheet material is the impact resistant polystyrene sheet as claim 11 or 12 described dehydrating units.

19., it is characterized in that the thickness of described sheet material is 0.05～0.5mm scope as claim 11 or 12 described dehydrating units.

20. as claim 11 or 12 described dehydrating units, it is characterized in that, in described sheet material, add antiseptic.

21. as claim 11 or 12 described dehydrating units, it is characterized in that, in described sheet material, add charged preventor.

22. as claim 11 or 12 described dehydrating units, it is characterized in that, in described sheet material, add incombustible agent.

23. as claim 11 or 12 described dehydrating units, it is characterized in that, in described sheet material, add deodorizer.

24., it is characterized in that the surface of described sheet material has hydrophobicity as claim 11 or 12 described dehydrating units.

25., it is characterized in that the surperficial possess hydrophilic property of described sheet material as claim 11 or 12 described dehydrating units.

Images