JP2016097368A - Dehumidifier - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dehumidifier which can prevent indoor dew condensation with a less energy.SOLUTION: A dehumidifier is equipped with an indoor air suction part which sucks indoor air in a dehumidification object facility, an ambient air suction part which sucks ambient air outside the facility, and a heat exchanger which brings indoor air and ambient air into thermal contact with each other. The heat exchanger includes: a three-dimensional body part having a first end and a second end which are opposite to each other; plural indoor air passages which move indoor air forward the second end from the first end; and plural ambient air passages which move ambient air towards the first end from the second end. At least a part of each of the plural indoor air passages and at least a part of each of the plural ambient air passages are adjacent to each at at least a part of the body part in a thickness direction and a width direction. Ambient air temperature which is a temperature of ambient air is lower than an indor air temperature which is a temperature of indoor air, and the ambient air temperature cools indoor air, which moves in the plural indoor air passages, to a dew point temperature by ambient air which moves in the ambient air passages.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a dehumidifying device, and preferably relates to a dehumidifying device used for plant growing equipment such as a greenhouse.

  Equipment for growing various plants installed outdoors such as agricultural vinyl houses, glass houses and plant factories is utilized in many places. Such plant growing facilities such as a greenhouse, a glass house, and a plant factory are intended to raise various temperatures and grow various plants.

  For example, in the case of so-called outdoor outdoor cultivation of specific vegetables and fruits, it is necessary to select the season and cultivation place based on the original special products such as vegetables and fruits. For example, salmon and the like require a certain temperature, so it is difficult to grow them in open-air cultivation in the winter or in cold regions. The same applies to other vegetables and fruits. On the other hand, when the population is distributed not only in Japan but also in various regions, the food supply and plant supply may be insufficient when growing only in regions and seasons according to the original special production of these vegetables and fruits. .

  The above-mentioned vinyl house, glass house, plant factory and the like are used so that food supply and plant supply can be controlled without depending on the original characteristics of the plant. These plant growing facilities can take advantage of natural light intake and the accompanying indoor temperature rise to speed up plant growing or to allow growing even in difficult seasons in outdoor cultivation. Of course, not only the temperature can be raised but also the purpose of controlling the temperature to a certain range and protecting against wind and rain can be achieved.

  Plant growing facilities are also used in cold regions and winter (or intermediate periods) for such purposes. Here, the greenhouse effect by natural light such as a vinyl house or a glass house may be insufficient for growing plants and the like. In this case, heating is used to increase the indoor temperature inside the plant growing facility. By this temperature rise, the temperature required for the plant to be grown can be realized.

  However, when heating is used inside the plant breeding facility, the outside air temperature is low (relatively low for plant growth. In other words, the outside air temperature is low based on the room temperature after heating). Due to the temperature difference, condensation may occur inside the plant growing equipment. This is because the inside of a so-called vinyl house or glass house has humidity, but because the temperature difference between the room temperature and the outside air temperature is generated, the room humidity is condensed due to the dew point temperature. This is likely to occur in cold seasons such as in winter and when the temperature drops suddenly even outside the cold season.

  Such condensation adheres to the inner surface of the plant growing facility. The dew that adheres may fall as water droplets and may drop and adhere to growing vegetables and fruits. In this case, the impact of the drop of water drops may cause damage to vegetables and fruits, reducing the value of the product and making shipping impossible.

  Or, the plant itself will be condensed, causing damage to the vegetables, fruits or fresh flowers, or discoloration, resulting in a drop in the commercial value. As described above, when it is necessary to use heating inside the plant growing facility in a cold region, in winter, or in a period of low temperatures before and after that, it is necessary to solve the problem caused by condensation.

  This condensation occurs when the temperature difference between the inside and outside of the plant growing facility is large and the outside air temperature is lower than the inside temperature. For this reason, dew condensation occurs when the internal temperature is raised and the outside air temperature is low and the temperature difference becomes large even outside the winter season. Even in this case, a problem due to condensation occurs.

  Moreover, it is necessary to keep the room temperature constant not only in plant growing facilities such as a vinyl house and a glass house, but also in factories, clean rooms, computer rooms, laboratories, and temperature-controlled rooms. Even in such a room, it may be difficult to keep the room temperature constant because the outside air temperature decreases in winter. In this case, as a matter of course, the room temperature is kept constant so that the room temperature is not dragged by operating the room heating.

  Even in a room where the temperature needs to be kept constant, condensation may occur in the room when the temperature inside the room becomes higher than the outside air temperature and the difference from the outside air temperature becomes large by using heating. Precision equipment and electronic equipment are installed inside factories, clean rooms, computer rooms, laboratories, temperature-controlled rooms, etc., and these may break down or deteriorate due to condensation.

  In this way, in the season when the outside air temperature falls such as in winter, when it is necessary to use heating (a device that raises the temperature) in the room, there are various types based on the fact that condensation occurs due to the temperature difference from the low outside air temperature. There is a problem.

  In order not to cause such condensation, it is conceivable not to increase the difference between the room temperature and the outside temperature. However, the outside air temperature cannot be controlled, and it is difficult to select this method.

  As another method, a method of dehumidifying the room so as not to condense by giving the indoor heating device a dehumidifying function is also conceivable. However, even if a dehumidifying device having a dehumidifying function is operated inside the room, the dehumidifying device does not operate by grasping a dew point that does not cause condensation due to the difference between the room temperature and the outside air temperature. For this reason, the dehumidification may be excessively carried out (naturally, the humidity is too low to reach the dew point so that no dew condensation occurs). In the case of excessive dehumidification, if it is a plant growing facility, the ground may dry or the plant may dry, which may impede the growth. In a factory or a clean room, there may be a problem that the working environment of the worker is deteriorated.

  On the contrary, dehumidification may be insufficient in the dehumidifying device. In this case, even if dehumidification is performed, there is a possibility that dew condensation at the dew point temperature, which eventually occurs based on the difference between the room temperature and the outside temperature, cannot be prevented.

  These dehumidifiers cannot calculate and take into account the dew point temperature due to the difference between the room temperature and the outside air temperature. For this reason, there is no choice but to perform excessive dehumidification in order to prevent the dew point from forming condensation. Conversely, if excessive dehumidification cannot be performed, there remains a problem that condensation occurs even if dehumidification is performed.

  In such a situation, a technique for dehumidification using outside air has been proposed (see, for example, Patent Document 1 and Patent Document 2).

JP2012-30192A Japanese Patent Laid-Open No. 54-60752

  Patent Document 1 is a dehumidifying device 1 that includes a heat exchange element 2 that circulates indoor air and outdoor air to exchange heat and dehumidifies indoor air, and sends indoor air to the heat exchange element 2. An indoor fan 9 is provided on the upstream side of the heat exchange element 2 in the indoor air passage 5, an outdoor fan 10 that sends outdoor air to the heat exchange element 2 is sent to the outdoor fan 10 that sends outdoor air to the outdoor wind. A dehumidifying device provided on the downstream side of the heat exchange element 2 in the path is disclosed.

  Patent Document 1 reduces the humidity of indoor air by using a heat exchange element that cools indoor air containing humidity with outside air having a temperature lower than that of indoor air. The outside air has a low temperature, and the outside air at this low temperature can be dehumidified by changing the room air to a dew point with a heat exchange element, liquefying and dehydrating the humidity contained in the room air.

  Here, as shown in FIG. 1 of Patent Document 1, the heat exchange element disclosed in Patent Document 1 takes in indoor air and outdoor air from directions orthogonal to each other. The indoor air having a high temperature and the outdoor air having a low temperature sent from the orthogonal direction are in contact with each other so as to be orthogonal. As a result of this contact, the room air is cooled by the outside air and falls to the dew point temperature.

  However, when the outside air passes through the heat exchange element 2, the temperature rises from the entrance toward the exit. Due to the orthogonal contact with the indoor air having a high temperature, the temperature starts to move in the vicinity of the entrance, and the temperature of the outside air having a low temperature rises when reaching the exit.

  However, in the heat exchange element of Patent Document 1, room air is sent from a direction orthogonal to the outside air. The room air sent from the orthogonal direction has air passing through the entrance side into which the outside air enters and air passing through the direction close to the exit side of the outside air inside the heat exchange element. At this time, as described above, in the heat exchange element 2 of Patent Document 1, the temperature of the outside air on the outlet side increases. Due to this temperature rise, the indoor air that moves substantially parallel to the outlet side of the outside air cannot reach the dew point due to an insufficient temperature difference.

  As a result, only a part of the room air sent to the heat exchange element 2 reaches the dew point, and the humidity cannot be sufficiently dehumidified. As a result, indoor air that cannot be sufficiently dehumidified is returned to the room again. Here, the standard for sufficient dehumidification is a level at which indoor air does not condense inside due to the outside air temperature. This level is exactly the level at which the heat exchange element uses the outside air temperature to become a dew point and the humidity is liquefied and discharged as water droplets.

  As described above, the heat exchange element of Patent Document 1 cannot reach the dew point in the vicinity of the outlet of the outside air fed orthogonally among the indoor air sent to the heat exchange element (theoretically, the original temperature of the outside air Therefore, the outside air cannot cool the room air to the dew point because the outside air is higher than the original temperature in the vicinity of the outlet), and some of the air sent to the heat exchange element is always at the dew point. Dehumidification is not done.

  The heat exchange element of Patent Literature 1 returns the air to the room without dehumidifying (dehydrating) a part of the air that should reach the dew point at the outside air temperature. Since this is repeated continuously, a part of the indoor air is in a state in which the humidity at which the dew point is always left at the outside temperature remains. After all, the heat exchange element of Patent Document 1 has a problem that it cannot prevent indoor condensation.

  Patent Document 2 describes a dew condensation type dehumidifier connected to a room having high-humidity air through a duct, and a dehumidifying part connected to the duct is layered by stroking a plurality of refrigerant storage chambers, Disclosed is a dehumidifying device characterized in that one end of a dehumidifying duct that insulators each refrigerant storage chamber is connected to the duct, and the other end is connected to a drainage part having a drainage port.

  The dehumidifying device of Patent Document 2 aims to dehumidify the indoor air inside the duct with the refrigerant by exhausting the indoor air through the duct and passing the duct through the refrigerant storage chamber having a plurality of layers. Yes.

  However, the use of a refrigerant increases the cost and makes the apparatus complicated. Due to these complexities, the entire dehumidifier becomes expensive. In addition, there is a problem that indoor dehumidification based on the dew point that is condensed by the outside air cannot be realized by performing heat exchange with the refrigerant. Of course, cooling dehumidification with a refrigerant does not use outside air at all, so there is a problem that energy efficiency for dehumidification is poor.

  As described above, the conventional technology has a problem that the indoor air cannot be reliably dehumidified with energy saving in order to prevent the indoor dew condensation caused by the outside air temperature lower than the room temperature.

  An object of this invention is to provide the dehumidification apparatus which can prevent indoor dew condensation with little energy in view of the said subject.

In view of the above problems, the dehumidifying device of the present invention includes an indoor air suction unit that takes in the indoor air of the facility to be dehumidified,
An outside air suction part that takes in outside air that is outside the equipment;
A heat exchanger for bringing indoor air and outside air into thermal contact with each other,
The heat exchanger
A three-dimensional body having opposing first and second ends;
A plurality of indoor air passages for moving room air from the first end toward the second end;
A plurality of outside air passages for moving outside air from the second end toward the first end,
At least a part of each of the plurality of indoor air passages and at least a part of each of the plurality of outside air passages are adjacent to each other in at least a part in the thickness direction and the width direction of the main body,
The outside air temperature, which is the temperature of the outside air, is lower than the room air temperature, which is the temperature of the room air,
The outside air temperature cools the room air moving through the plurality of room air passages to the dew point temperature by the outside air moving through the outside air passage.

The dehumidifier of the present invention uses the outside air to lower the temperature of the room air to the dew point temperature based on the outside air. Due to the temperature drop to this dew point, the room air is condensed and dehumidification can be realized. By dehumidification based on the dew point in the outside air, the indoor air can be prevented from being condensed by the outside air.
In particular, in a plant growing facility installed outside and exposed to the outside temperature, such as a vinyl house or a glass house, the dew condensation that occurs when the outside temperature is low can be prevented from being generated by using the cool air.

  In addition, the dehumidifying device of the present invention is fed substantially in parallel from the side where the room air and the outside air face each other. As a result, even if the temperature at the outlet of the outside air increases, the variation in the temperature of the outside air due to the position of the indoor air that is sent in is eliminated. As a result, the whole room air to be sent is uniformly cooled by the outside air having no temperature variation, and the whole room air can be dehumidified based on the outside air temperature.

  Since the whole indoor air sent in can be dehumidified uniformly, the indoor air sent back into the room is maintained at a humidity air that has been dehumidified based on the outside air. As a result, it is possible to prevent condensation due to the outside air temperature in the room.

It is a schematic diagram of the heat exchanger in a prior art. It is a schematic diagram of the heat exchanger of this invention. It is a schematic diagram of the dehumidification apparatus at the time of applying to the greenhouse in Embodiment 1 of this invention. It is a schematic diagram of the heat exchanger for dehumidification in Embodiment 1 of this invention. It is a perspective view which shows the dehumidification state in the heat exchanger for dehumidification in Embodiment 1 of this invention. It is a front view of the main-body part in Embodiment 1 of this invention. It is a front view of the main-body part in Embodiment 1 of this invention. It is a perspective view of the heat exchanger for dehumidification in Embodiment 2 of this invention.

A dehumidifying device according to a first aspect of the present invention includes an indoor air suction unit that takes in indoor air of equipment to be dehumidified,
An outside air suction part that takes in outside air that is outside the equipment;
A heat exchanger for bringing indoor air and outside air into thermal contact with each other,
The heat exchanger
A three-dimensional body having opposing first and second ends;
A plurality of indoor air passages for moving room air from the first end toward the second end;
A plurality of outside air passages for moving outside air from the second end toward the first end,
At least a part of each of the plurality of indoor air passages and at least a part of each of the plurality of outside air passages are adjacent to each other in at least a part in the thickness direction and the width direction of the main body,
The outside air temperature, which is the temperature of the outside air, is lower than the room air temperature, which is the temperature of the room air,
The outside air temperature cools the room air moving through the plurality of room air passages to the dew point temperature by the outside air moving through the outside air passage.

  With this configuration, the dehumidifying device can remove excess humidity at the dew point temperature where the room air inside the facility is condensed based on the outside air temperature. As a result, condensation due to outside air inside the facility can be prevented.

  In the dehumidifying device according to the second aspect of the present invention, in addition to the first aspect, the heat exchanger liquefies excess moisture contained in the room air by cooling the room air to the dew point temperature. Discharge.

  With this configuration, the dehumidifying device can generate a state in which the indoor air inside the facility does not condense on the basis of the outside air temperature.

  In the dehumidifying apparatus according to the third aspect of the present invention, in addition to the first or second aspect, the outside air temperature corresponds to the dew point temperature of the room air, and the heat exchanger removes the room air in the whole room air passage. Cool to dew point temperature to liquefy excess water.

  With this configuration, the dehumidifying device can generate a state in which the indoor air inside the facility does not condense on the basis of the outside air temperature.

  In the dehumidifying apparatus according to the fourth invention of the present invention, in addition to the second or third invention, the excess moisture is an amount of room air inside the equipment which is condensed inside the equipment due to the outside air temperature outside the equipment. Corresponding to

  With this configuration, the possibility of condensation can be reduced over the entire indoor air inside the facility.

  In the dehumidifying apparatus according to the fifth invention of the present invention, in addition to any of the first to fourth inventions, the equipment is plant growing equipment such as a plastic house or a glass house, a factory, a clean room, a computer room, a laboratory. And either a constant temperature room.

  With this configuration, it is possible to achieve dehumidification of equipment that is easily exposed to the outside air and that is likely to be adversely affected by condensation.

  In addition to any one of the first to fifth inventions, the dehumidifying device according to the sixth invention of the present invention further includes a housing that houses the indoor air suction unit, the outdoor air suction unit, and the heat exchanger.

  With this configuration, the dehumidifying device can be easily installed outside the facility.

  In the dehumidifying device according to the seventh aspect of the present invention, in addition to the sixth aspect, the second end portion is provided downward of the housing.

  With this configuration, the water that has reached the dew point temperature and is liquefied is easily discharged.

  In the dehumidifying apparatus according to the eighth aspect of the present invention, in addition to the sixth or seventh aspect, an indoor air return unit that returns indoor air cooled to the dew point temperature by the heat exchanger to the inside of the facility, and heat exchange And an outside air discharge unit for discharging outside air that is discharged after cooling the room air to the outside of the housing.

  With this configuration, the dehumidified room air circulates inside the facility.

  In the dehumidifying device pertaining to the ninth aspect of the present invention, in addition to any of the first to eighth aspects of the invention, the room air moving in each of the plurality of room air passages is connected to each of the plurality of adjacent outside air passages. In thermal contact, the outside air cools the room air to the dew point temperature.

  With this configuration, the dehumidifier can perform dehumidification only by using outside air.

  In the dehumidifying device according to the tenth aspect of the present invention, in addition to any of the first to ninth aspects, each of the plurality of indoor air passages and each of the plurality of outside air passages is substantially within the main body. Parallel.

  With this configuration, the thermal contact between the indoor air passage and the outdoor air passage becomes efficient.

  In the dehumidifying device according to the eleventh aspect of the present invention, in addition to any of the first to tenth aspects, each of the plurality of indoor air and each of the plurality of outside air passages has a thickness direction and a width of the main body. They are arranged alternately in at least one of the directions.

  With this configuration, the thermal contact efficiency between the indoor air passage and the outdoor air passage is increased.

  In the dehumidifying device pertaining to the twelfth aspect of the present invention, in addition to any of the first to eleventh aspects of the invention, the outside air that moves through each of the plurality of outside air passages is substantially at the second end that serves as the entrance to the movement. It is the same temperature, and is substantially the same temperature at the first end that becomes the exit of movement.

  With this configuration, there is no variation in temperature rise due to the outside air passage, and cooling to the dew point temperature in each of the indoor air passages that are in thermal contact with each of the outside air passages can be reliably realized.

  In the dehumidifying device according to the thirteenth aspect of the present invention, in addition to any one of the first to twelfth aspects, the room air moving in each of the plurality of room air passages is a second end portion serving as a movement outlet. In this case, the dew point temperature is reached by thermally contacting the lowest temperature of the outside air sent into the plurality of outside air passages.

  With this configuration, the room air becomes the dew point temperature at the outlet of the indoor air passage, and excess moisture is discharged.

  In the dehumidifying device according to the fourteenth aspect of the present invention, in addition to the thirteenth aspect, the indoor air moving in each of the plurality of indoor air passages gradually moves from the first end to the second end. The room air temperature is gradually lowered by continuing the thermal contact with the outside air moving through the outside air passage where the temperature is lowered, and the dew point temperature is lowered near the second end.

  With this configuration, the room air becomes the dew point temperature at the outlet of the indoor air passage, and excess moisture is discharged.

  In the dehumidifying device pertaining to the fifteenth aspect of the present invention, in addition to the fourteenth aspect, the room air that has moved through each of the plurality of room air passages at the second end is equal to the dew point temperature in all the room air passages. Become.

  With this configuration, the heat exchanger can be uniformly condensed in all indoor air passages.

  In the dehumidifying device according to the sixteenth aspect of the present invention, in addition to any one of the first to fifteenth aspects, the rate of taking in indoor air taken into the indoor air passage changes based on the outside air temperature outside the facility. However, when the outside air temperature is relatively high, the intake speed taken into the indoor air passage is slow, and when the outside air temperature is relatively low, the intake speed taken into the indoor air passage is high.

  With this configuration, when the outside air temperature is high, the moving speed of the indoor air in the indoor air passage can be slowed down to reliably cool to the dew point temperature.

  In the dehumidifying device according to the seventeenth aspect of the present invention, in addition to the sixteenth aspect, at least one of the indoor air suction part and the indoor air return part adjusts the intake speed of the indoor air into the indoor air passage.

  With this configuration, the intake speed into the indoor air passage can be easily adjusted.

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

  (Embodiment 1)

  Embodiment 1 will be described.

(Fundamental difference from conventional technology)
First, the problems of the heat exchanger in the prior art as disclosed in Patent Document 1 will be described, and the difference from the heat exchanger of the present invention will be described.

(The fundamental problem of the heat exchanger of the prior art)
FIG. 1 is a schematic diagram of a heat exchanger in the prior art. The heat exchanger 200 of the prior art is sent into the main body 201 from a direction in which room air and outside air are orthogonal to each other. The room air and the outside air sent from each of the orthogonal directions move through respective passages provided in the main body 201.

  That is, in FIG. 1, an indoor air passage 202 through which room air moves is formed in the main body 201 from the room air inlet 210 toward the outlet 211. Similarly, an outside air passage 203 through which outside air moves from the outside air inlet 220 toward the outlet 221 is formed. The room air moves through the room air passage 202 in the direction of arrow A. On the other hand, the outside air moves in the outside air passage 203 in the direction of arrow B. Here, the arrows A and B shown in FIG. 1 indicate that a plurality of indoor air passages 202 and outdoor air passages 203 are provided.

  The room air sent to the inlet 210 of the main body 201 moves along the indoor air passage 202 toward the outlet 211 according to the arrow A. Similarly, the outside air sent into the inlet 220 of the main body 201 moves through the respective outside air passages 203 toward the outlet 221. In this movement, the outside air having a temperature lower than that of the room air makes thermal contact by point contact at each of the intersecting points orthogonal to each other. For example, outside air that moves in a certain outside air passage 203 makes thermal contact only at the intersection of the outside air passage 203 and the indoor air passage 202 that intersects. The same applies when other outside air passages 203 are used as a reference.

  As described above, in the heat exchanger 200 of the prior art, the outside air and the room air are only in a point contact thermal contact only at the intersection point in the main body 201. For this reason, first, the thermal contact efficiency between the outside air and the room air in the entire main body 201 is poor. Here, the room air has a temperature higher than the outside air and is sent from the entrance 210 to the room air passage 202. The temperature of the room air decreases as it approaches the vicinity of the outlet 211 due to thermal contact with the outside air. For this reason, it is required to reach the dew point in a range 212 surrounded by a frame. It is required that a part of the humidity included in the room air is discharged as moisture after reaching the dew point in this range 212 and condensation. This is because the humidity of the indoor air sent to the entrance 210 decreases due to the discharge of moisture.

  However, the outside air repeats the thermal contact with the indoor air that is fed in multiple stages sequentially from the orthogonal direction while moving in the outside air passage 203 from the inlet 220 to the outlet 221. Focusing on a certain outside air passage 203, after entering from the entrance 220, it intersects with the first stage indoor air passage 202, intersects with the next stage indoor air passage 202, and further with the next stage indoor air passage 202. Intersects and repeats thermal point contact with room air in sequence.

  As a matter of course, the temperature of the outside air increases as the temperature approaches the vicinity of the outlet 221 due to the repetition of the thermal point contact. A region 222 surrounded by a frame in FIG. 1 is a region where the temperature of the outside air that has been sent has risen. In this region 222, the temperature of the sent outside air rises, and the indoor air cannot be sufficiently cooled (heat from the indoor air cannot be taken away) due to thermal contact with the indoor air.

  As a result, the indoor air moving through the indoor air passage 202 in the range corresponding to the region 222 is not sufficiently cooled as compared with the indoor air moving through the indoor air passage 202 in the range other than the region 222. End up. As a result, the indoor air moving through the indoor air passage 202 in the range corresponding to this region 222 cannot reach the dew point.

In FIG. 1, the indoor air that has moved through the indoor air passage 202 cannot be condensed at the outlet 211 where the range 212 and the region 222 overlap with each other, and remains dehumidified.
As shown in FIG. 1, the room air reaches the dew point only in a part of the plurality of room air passages 202, and only a part of the room air sent to the main body 201 is dehumidified. The purpose of this dehumidification is to dehumidify the room where dehumidification is intended to a level where no condensation occurs in the room due to outside air. In the situation where only a part of the indoor air sent into the main body 201 is dehumidified by the outside air sent into the outside air passage 203, it is theoretically impossible to prevent the dew condensation in the room.

The orthogonal type heat exchanger 200 according to the prior art has an advantage that each side of the three-dimensional shape can be used for each of the indoor air inlet 210, the outlet 211, the outside air inlet 220, and the outlet 221. For this reason, manufacture is easy. However, as described above, only a part of the room air can be dehumidified, and the object of dewing the inside of the facility with the outside air cannot be achieved.
The heat exchanger 200 in the prior art is aimed at temperature control rather than aimed at dehumidification, and does not take into consideration that dew condensation in the room does not occur as long as a constant dehumidification in the room is possible. For this reason, the problem described with reference to FIG. 1 remains.

  The problem in the heat exchanger 200 of the prior art will be described by taking temperature and dew point as an example. For example, as described above, it is assumed that the initial value of the indoor air has a temperature of 20 ° C. and a humidity of 70%. In the theoretical value in this case, the dew point temperature is 14 ° C., and if the room air is cooled down to 14 ° C. by thermal contact with the outside air in the outside air passage 203 while moving in the indoor air passage 3, the dew point is reached. Can reach and drain humidity as moisture.

  Here, it is assumed that room air having a humidity of 70% at 20 ° C. enters the indoor air passage 202 and outside air having an outside air temperature of 14 ° C. enters the outside air passage 203. The indoor air passage 202 and the outdoor air passage 203 are plural as shown in FIG.

  FIG. 1 shows the outside air temperature. The outside air temperature at the stage of entering from the inlet 220 is 14 ° C. in all the outside air passages 203. However, the outside air temperature rises while moving from the inlet 220 to the outlet 221, and the outside air temperature rises to about 18 ° C. near the outlet 221.

  Here, each of the indoor air passages 202 is a plurality of passages from top to bottom in FIG. That is, even at the outlets 211 of the plurality of indoor air passages 202, the outside air temperature is about 14 ° C. on the upper left side in FIG. 1, but the outside air temperature rises to about 18 ° C. on the lower left side. . That is, at the outlets 211 of the plurality of indoor air passages 202, depending on the location of the outside air passage 203 that is in contact, there is a place where the outside air temperature is 14 ° C. sufficient for the dew point to reach the dew point. There is also a place. This place is a portion where the range 212 and the region 222 described above overlap. In this area, the outside air temperature near the outlet 211 of the indoor air passage 202 rises, and the indoor air cannot reach the dew point.

(The fundamental difference of the heat exchanger of the present invention)
According to the present invention, in the first end and the second end facing each other of the three-dimensional main body, the first end serves as an indoor air inlet and an outdoor air outlet, and the second end serves as an indoor air outlet. Also used as an entrance for outside air.

  FIG. 2 is a schematic diagram of the heat exchanger of the present invention. Unlike the prior art heat exchanger 200 shown in FIG. 1, the heat exchanger 1 of the present invention has a three-dimensional main body portion 2 that has only the first end portion 21 and the second end portion 22 that face each other as room air. It is used for entrances and exits and outside air entrances and exits.

  The room air is sent from the first end 21 to the main body 2 and exits from the second end 22. At this time, the indoor air moves through a plurality of indoor air passages 3 (arrow C schematically shows the plurality of internal air passages 3) provided in the main body 2. On the other hand, outside air is fed from the second end 22 into the main body 2 and exits from the first end 21. At this time, the outside air moves through a plurality of outside air passages 4 (arrow D schematically shows the plurality of outside air passages 4) provided in the main body 2. Here, each of the plurality of indoor air passages 3 and each of the plurality of outside air passages 4 are independent from each other, and the indoor air and the outside air moving through each of them do not mix.

  The indoor air passage 3 and the outside air passage 4 can be thermally contacted indirectly. As a result, the indoor air moving through the indoor air passage 3 is in thermal contact with the outside air moving through the outdoor air passage 4. Arrows C and D indicate thermal contact between the room air and the outside air.

  Here, as is clear from comparison with FIG. 1, the heat exchanger 1 of the present invention shown in FIG. 2 is in linear contact so that the arrow C and the arrow D are adjacent to each other. That is, the indoor air that moves through the indoor air passage 3 and the outside air that moves through the outdoor air passage 4 are linearly and in thermal contact with each other. The thermal contact efficiency between room air and outside air is higher than that of the heat exchanger 200 of the prior art which is only a point contact. As a result, the degree to which the room air is cooled by the outside air is increased, and the room air easily reaches the dew point when it moves through the room air passage 3 and reaches the second end 22 that is the outlet.

  Next, considering the room air as a reference, a region 50 surrounded by a frame in FIG. 2 is a region where the room air reaches the dew point and the humidity is liquefied into moisture. This region 50 is near the outlet of the indoor air passage 3. While the indoor air sent from the first end 21 side serving as the entrance moves through the indoor air passage 3, the outdoor air moves along the outdoor air passage 4 from the second end 22 toward the first end 21. It is gradually cooled by thermal contact.

  In addition, the outlet side of the indoor air passage 3 corresponds to the inlet side of the outside air passage 4 and the temperature of the outside air sent is the lowest. That is, the room air that is gradually cooled and reaches the outlet side of the indoor air passage 3 is cooled by the outside air that has the lowest temperature near the outlet. As a result, it is possible to reliably condense in the region 50 and change the humidity into moisture and discharge the moisture.

  Also in the heat exchanger 1, the outside air moving through the outside air passage 4 gradually increases its temperature as it moves. That is, the temperature of the outside air on the side of the first end 21 that is the outlet rises compared to the side of the second end 22 that is the entrance of the outside air passage 4. However, since the temperature rises uniformly in each of all the outdoor air passages 4, there is no difference in the outside air temperature due to the difference in the position of the indoor air passage 3.

  Naturally, the temperature of the outdoor air in the outdoor air passage 4 is uniform in each of the indoor air passages 3 also on the second end 22 side which is the outlet of the indoor air passage 3.

  As described above, in each of the plurality of indoor air passages 3, the temperature of the outside air in the outside air passage 4 that is in thermal contact does not vary at each position in the movement from the entrance to the exit. As a result, the entire indoor air sent into each of the plurality of indoor air passages 3 provided in the main body 2 uniformly reaches the dew point and is dehumidified. This dehumidifying standard is also based on the dew point at the original temperature of the outside air in the region 50 entering the outside air passage 4. As a result, it is possible to realize theoretical dehumidification that does not cause condensation due to outside air inside the room of the facility.

  In the prior art heat exchanger 200 in FIG. 1, the dew point cannot be reached in the indoor air passage 202 where the range 222 and the region 212 overlap. That is, in the heat exchanger 200 of the prior art, the indoor air passage 202 that cannot reach the dew point and cannot be dehumidified remains, and only a part of the indoor air sent to the main body 201 can be dehumidified based on the dew point due to the outside air. It was.

  On the other hand, the heat exchanger 1 of the present invention reaches the dew point in all of the plurality of indoor air passages 3. As a result, all of the room air sent to the main body 2 is dehumidified based on the dew point due to the outside air. As described above, since all of the indoor air sent to the main body 2 is dehumidified and returned to the interior of the facility, the interior of the facility does not cause condensation due to outside air. That is, the prevention of dew condensation, which is the purpose of dehumidification, can be achieved.

  For example, as described above, it is assumed that the initial value of the indoor air has a temperature of 20 ° C. and a humidity of 70%. In the theoretical value in this case, the dew point temperature is 14 ° C., and if the room air is cooled down to 14 ° C. by thermal contact with the outside air in the outside air passage 4 while moving in the indoor air passage 3, the dew point is reached. Can reach and drain humidity as moisture.

  As shown in FIG. 2, in the vicinity of the outlet of the indoor air passage 3 relating to all of the region 50, the outside air in all of the outside air passages 4 has a temperature of 14 ° C. There is almost no variation in the temperature of 14 ° C. due to the outside air passage 4. As a result, in the vicinity of the outlets of all the indoor air passages 3, the dew point is reached in thermal contact with the outside air at 14 ° C.

  Of course, the outside air moving from the second end 22 to the first end 21 side in the outside air passage 4 gradually increases in temperature, but the temperature rise is also uniform. For example, it is assumed that the outside air temperature at each of the outlets of the plurality of outside air passages 4 has increased to 18 ° C. This is matched with the moving side of the indoor air passage 3. The indoor air sent from the first end 21 side to each of the plurality of indoor air passages 3 is in a state where the temperature is 20 ° C. and the humidity is 70%. The outside air temperature of the outside air passage 4 that is in thermal contact with this stage is 18 ° C., and the temperature difference is 2 ° C. Based on the temperature difference of 2 ° C., in the vicinity of the first end portion 21, the indoor air in the indoor air passage 3 starts to decrease in temperature.

  Next, when the room air that has moved through the plurality of room air passages 3 reaches the vicinity of the middle of the room air passage 3, the room air is lowered to about 17 ° C. The outside air temperature of the outside air passage 4 at the same position at this time is about 15 ° C. to 16 ° C., and also has a temperature difference of about 2 ° C. Due to the temperature difference of about 2 ° C., the indoor air moving around the center is further cooled.

  Further, the indoor air reaches the exit by moving through the plurality of indoor air passages 3. In the vicinity of the region 50. In the vicinity of the outlet, it is immediately after the outside air of 14 ° C. is sent to each of the plurality of outside air passages 4, so that the room air is cooled to around 14 ° C. in accordance with the outside air temperature of 14 ° C. As a result, the indoor air at the outlets of all the indoor air passages 3 can reach the dew point.

  Thus, the heat exchanger 1 of the present invention is fundamentally different in mechanism, structure, and result from the heat exchanger 200 of the prior art. Due to this fundamental difference, the heat exchanger 1 of the present invention can realize dehumidification for suppressing the inside of the facility, which is the original final purpose, to a humidity that does not cause condensation due to outside air. As described above, the heat exchanger 200 according to the prior art cannot theoretically realize dehumidification for suppressing the inside of the facility to a humidity that does not cause condensation due to the outside air.

(Overview)
First, an overall outline of the dehumidifying device of Embodiment 1 will be described. FIG. 3 is a schematic diagram of a dehumidifying device when applied to the greenhouse in the first embodiment of the present invention. In FIG. 3, the state where the dehumidifier 11 is used for the greenhouse 110 is shown.

  The dehumidifying device 11 includes an indoor air suction unit 330 that takes in indoor air of the equipment to be dehumidified (in FIG. 3, the greenhouse 110), an outdoor air suction unit 430 that takes in external air that is outside the equipment, and indoor air and outdoor air. And a heat exchanger 1 that is in thermal contact with each other. Further, a blower fan 320 that returns the indoor air dehumidified by the heat exchanger 1 to the greenhouse 110 that is a facility, and a discharge fan 420 that exhausts outside air used for dehumidification by the heat exchanger 1 to the outside may be provided. .

  As shown in FIG. 3, the dehumidifying device 11 is installed outside the facility to be dehumidified, and dehumidifies the indoor air inside the facility using outside air outside the facility. As will be described later, in the facility itself, room air reaches the dew point due to the outside air outside, and condensation occurs. In order to prevent this dew condensation, indoor air is guided to the dew point by the heat exchanger 1 using the outside air temperature. If the heat exchanger 1 leads to the dew point with the outside air temperature as a reference, the indoor air in the heat exchanger 1 can discharge excess moisture that can be condensed with the outside air temperature as a reference.

  With this heat exchanger 1, the indoor air of the facility can discharge excess moisture at a level that causes condensation at the outside air temperature by cooling to the dew point temperature in contact with the outside air. Due to the dehumidification due to the discharge of excess water, the room air returned from the dehumidifying device 11 to the facility is not condensed due to the outside air temperature outside the facility. By preventing this dew condensation, various problems due to dew condensation in the facility can be solved.

  The greenhouse 110 is an example of equipment to be dehumidified. Plant growing facilities such as a plastic house and a glass house are installed outside and directly exposed to the outside air. In addition, since the outer wall is made of vinyl or glass instead of the outer wall of concrete or the like, the inside tends to condense when the outside air temperature is low. In particular, in cold districts and cold seasons, heating such as heating is performed internally for plant growth. This heating raises the temperature of the indoor air inside the greenhouse 110. Due to this rise, the difference between the outside air temperature and the room air temperature becomes large, and condensation due to outside air tends to adhere to the inner surface of the greenhouse 110.

  The greenhouse 110 is provided with a delivery path for sending room air to the dehumidifier 11 and a return path for returning room air from the dehumidifier 11. According to this route, room air is exchanged with the dehumidifier 11 from the greenhouse 110 as shown in FIG.

  The dehumidifying device 11 includes a heat exchanger 1 for dehumidification inside. For this reason, the dehumidifying device 11 includes a case 500, and the dehumidifying heat exchanger 1 may be accommodated in the case 500. Further, the case 500 may accommodate the blower fan 320 and the exhaust fan 420. Furthermore, the indoor air suction part 330 and the outdoor air suction part 430 may be accommodated. Here, the blower fan 320, the exhaust fan 420, the indoor air suction unit 330, and the outside air suction unit 430 do not need to be completely stored in the case 500 for connection to the outside. For example, necessary openings provided in the case 500 are connected to these elements.

  The indoor air suction unit 330 is connected to the greenhouse 110 and takes the indoor air of the greenhouse 110 into the dehumidifier 11. In particular, the indoor air suction unit 330 takes the indoor air of the greenhouse 110 into the heat exchanger 1 for dehumidification. At this time, the indoor air suction unit 330 may continuously take in indoor air into the dehumidifying heat exchanger 1 or may intermittently take in indoor air.

  The indoor air suction unit 330 may be a fan or a pressure pump.

  Similarly, the outside air suction unit 430 is connected to the outside, and takes outside outside air into the dehumidifier 11. In particular, the outside air suction unit 430 takes outside air into the dehumidifying heat exchanger 1. At this time, the outside air suction unit 430 may continuously take outside air into the dehumidifying heat exchanger 1 or may intermittently take outside air. However, the heat exchanger 1 for dehumidification makes the indoor air and the outside air that enter from the opposite direction come into thermal contact with each other through a passage. This thermal contact reduces the room air to the dew point temperature. For this reason, it is appropriate that the indoor air suction unit 330 and the outside air suction unit 430 have the same intake operation. If the indoor air suction unit 330 operates continuously, it is appropriate that the outdoor air suction unit 430 also operate continuously.

  As shown in FIG. 4, the dehumidifying heat exchanger 1 includes a main body 2, an indoor air passage 3, and an outside air passage 4. FIG. 4 is a schematic diagram of the heat exchanger for dehumidification according to Embodiment 1 of the present invention.

  The indoor air suction part 330 sends the indoor air of the greenhouse 110 into the indoor air passage 3 provided in the main body part 2. The outside air suction part 430 sends outside air into the outside air passage 4 provided in the main body part 2. Here, the indoor air passage 3 moves the indoor air from the first end 21 toward the second end 22, so the indoor air suction unit 330 feeds the indoor air from the first end 21. In the outside air passage 4 that moves outside air in the opposite direction, the outside air suction unit 430 sends outside air from the second end 22. In this way, indoor air and outside air are fed into each of the indoor air passage 3 and the outside air passage 4 provided in the main body 2 so that the inside thereof can move in a predetermined direction.

  The dehumidifying heat exchanger 1 includes a plurality of indoor air passages 3 that move room air from the first end 21 toward the second end 22, and outside air from the second end 22 toward the first end 21. And a plurality of outside air passages 4 for moving the air. At least a part of each of the plurality of indoor air passages 3 and at least a part of each of the plurality of outside air passages 4 are adjacent to each other in at least a part in the thickness direction and the width direction of the main body 2.

  Due to this adjacency, at least a part of each of the indoor air passages 3 and at least a part of each of the outdoor air passages 4 are in thermal contact. In other words, the indoor air moving through the indoor air passage 3 and the outside air moving through the outdoor air passage 4 are in thermal contact.

  Here, the outside air temperature of the outside air sent into the outside air passage 4 is lower than the temperature of the room air sent into the indoor air passage 3. Due to this low outside air temperature, the room air moving through the indoor air passage 3 reaches the dew point temperature based on the outside air temperature. By reaching this dew point temperature, the room air can be liquefied and discharged with excess water at a level at which dew condensation occurs in the outside air.

  In other words, the outside air temperature corresponds to the dew point temperature of the indoor air, and the heat exchanger 1 for dehumidification cools the room air to the dew point temperature by the outside air in the entire indoor air passage 3 to liquefy excess moisture. This excess moisture corresponds to the amount of room air inside the equipment that is dewed inside the equipment due to the outside air temperature of the equipment.

  As described above, the dehumidifying device 11 can dehumidify the indoor air with the outside air. As described above, the dehumidified level is a level at which the indoor air of the greenhouse 110, which is a facility, is not condensed by the outside air. The room air dehumidified by the dehumidifier 11 is returned to the inside of the greenhouse 110 by the blower fan 320. As a result, the humidity at the level at which dew condensation occurs in the greenhouse 110 due to outside air is reduced, and dew condensation can be prevented.

  By repeating the dehumidification in the above dehumidifying apparatus 11, it is possible to continuously prevent the indoor air of the greenhouse 110 from being condensed by the outside air. As a result, adverse effects on plants and the like caused by condensation within the greenhouse 110 can be prevented.

  In addition, in FIG. 3, although demonstrated using the greenhouse 110 as an example of equipment, the equipment used as a dehumidification object is either plant growing equipment, such as a glass house, a factory, a clean room, a computer room, a laboratory, and a temperature-controlled room. It may be.

  Next, details and operations of each unit will be described.

(Indoor air suction part)
As shown in FIG. 3, the indoor air suction unit 330 takes in the indoor air of the facility to be dehumidified into the dehumidifying heat exchanger 1. Here, the indoor air suction unit 330 connects the opening of the facility and the opening of the case 500 (housing), and takes in the indoor air of the facility with a suction fan, a suction pump, or the like. Here, the indoor air is taken in from an indoor air passage entrance 31 provided on the first end 21 side of the main body 2. For this reason, the indoor air suction part sucks indoor air in a direction connected to the indoor air passage entrance 31.

  The indoor air suction part 330 may be provided inside the case 500 or inside the facility. Alternatively, it may be provided inside a delivery path that connects the equipment and the case 500. The delivery path only needs to be formed by a pipeline, and the indoor air suction part 330 is provided inside the pipeline.

(Outside air suction part)
As shown in FIG. 3, the outside air suction unit 430 takes outside air outside the equipment into the heat exchanger 1 for dehumidification. Since the case 500 is exposed to the outside, the outside air suction part 430 may be provided in the outside air intake opening provided in the case 500.

  As with the indoor air suction unit 330, the outside air suction unit 430 uses a suction fan or a suction pump. Here, the indoor air suction unit 330 and the outdoor air suction unit 430 are operated in accordance with their operating times. It is preferred that both operate at the same time. This is because this simultaneous operation introduces cooling outside air to dehumidify the indoor air to be dehumidified.

(Heat exchanger for dehumidification)
The dehumidifying heat exchanger 1 dehumidifies the indoor air using the outside air in the dehumidifying device 11. The dehumidifying heat exchanger 1 includes a main body 2, an indoor air passage 3, and an outdoor air passage 4.

  The main body 2 has a three-dimensional shape (a three-dimensional shape) having a first end 21 and a second end 22 facing each other. The main body 2 forms a basic skeleton of the heat exchanger 1 for dehumidification. The main body 2 may be formed of a metal, alloy, resin, wood, ceramics, reinforced paper material, or a combination thereof. In FIG. 4, the main body 2 has a rectangular parallelepiped outer shape, but may be a cube or another three-dimensional shape. The main body 2 has end portions corresponding to respective inlets and outlets of an indoor air passage 3 and an outdoor air passage 4 described later as a first end portion 21 and a second end portion 22. The first end 21 and the second end 22 oppose each other. That is, as described in FIGS. 1 and 2, the main body 2 of the dehumidifying heat exchanger 1 according to the first embodiment exchanges heat between the first end 21 and the second end 22 that face each other. realizable.

  The indoor air passage 3 is a passage that takes in indoor air inside the facility to be dehumidified and moves the indoor air from the first end portion 21 toward the second end portion 22. In FIG. 4, a plurality of indoor air passages 3 are provided inside the main body 2 from the first end 21 to the second end 22. That is, each of the plurality of indoor air passages 3 is an internal through passage provided from the first end 21 of the main body 2 toward the second end 22.

  Each of the plurality of indoor air passages 3 takes in indoor air from the facility and moves it from the first end 21 toward the second end 22. Therefore, the indoor air passage 3 has an indoor air passage inlet 31 on the first end portion 21 side and an indoor air passage outlet 32 on the second end portion 22 side. The indoor air passage 3 moves the indoor air from the indoor air passage entrance 31 toward the indoor air passage outlet 32. At this time, all of the plurality of indoor air passages 3 may not be able to move the indoor air. Depending on the intake state of the room air, any of the plurality of indoor air passages 3 may be in a state where the room air is not moved.

  The plurality of outside air passages 4 are passages that take in outside air that is air outside the facility to be dehumidified and move the outside air from the second end 22 toward the first end 21. In FIG. 4, a plurality of outside air passages 4 are provided inside the main body 2 from the second end 22 to the first end 21. That is, each of the plurality of outside air passages 4 is an internal through passage provided from the second end 22 of the main body 2 toward the first end 21.

  Each of the plurality of outside air passages 4 takes outside air from the outside of the facility and moves it from the second end 22 toward the first end 21. That is, the movement is in the direction opposite to the moving direction of the indoor air in the indoor air passage 3. Each of the plurality of outside air passages 4 has an outside air passage inlet 41 on the second end portion 22 side and an outside air passage outlet 42 on the first end portion 21 side for the movement of the outside air. Each of the plurality of outside air passages 4 can discharge the outside air taken in from the outside air passage inlet 41 from the outside air passage outlet 42 by moving the inside through passage.

  Of course, as in the case of the indoor air passage 3, all of the plurality of outside air passages 4 may not be able to move the outside air depending on the intake state of the outside air.

  In FIG. 4, the state of passing through the inside of the main body 2 in either the indoor air passage 3 or the outdoor air passage 4 is omitted for the sake of easy viewing.

  Here, at least a part of each of the plurality of indoor air passages 3 and at least a part of each of the plurality of outside air passages 4 are adjacent to each other in at least a part in the thickness direction and the width direction of the main body 2. In FIG. 4, each of the indoor air passages 3 and each of the outside air passages 4 are adjacent to each other in the width direction in the direction from the first end portion 21 to the second end portion 22. In particular, each of the plurality of indoor air passages 3 and each of the plurality of outside air passages 4 are alternately arranged. By arranging these alternately, one of the plurality of indoor air passages 3 and one of the plurality of outside air passages 4 are adjacent to each other along the second end 22 from the first end 21.

  By this adjacency, the indoor air passage 3 and the outside air passage 4 can be in thermal contact. In other words, the indoor air moving through the indoor air passage 3 and the outside air moving through the outdoor air passage 4 can be in thermal contact. As shown in FIG. 4, each of the plurality of indoor air passages 3 and each of the plurality of outside air passages 4 are alternately arranged. In the case of such a structure, each of the indoor air passages 3 can be in thermal contact with each of the outdoor air passages 4. As a result, the room air and the outside air can be in thermal contact with each other at the boundary between the alternately arranged passages.

  Here, the outside air temperature that is the temperature of the outside air entering the outside air passage entrance 41 of the outside air passage 4 is lower than the indoor air temperature that is the temperature of the room air entering the indoor air passage entrance 31 of the indoor air passage 3. As described with reference to FIG. 1 and FIG. 2, the dehumidifying heat exchanger 1 in the first embodiment is efficient and uses the outside air when the temperature of the room air inside the facility is higher than the outside air. The purpose is low-cost dehumidification. From this, naturally, the outside temperature used in the heat exchanger 1 for dehumidification is lower than the room air temperature in the above state.

  Due to this temperature difference, the outside air moving in the outside air passage 4 cools the indoor air moving in the indoor air passage 3 to the dew point temperature. Due to the cooling to the dew point temperature, the indoor air that moves through the indoor air passage 3 and reaches the indoor air passage outlet 32 is condensed, and excess moisture at a level that causes condensation based on the outside air is liquefied and discharged. The

  As shown in FIG. 5, excess water 100 cooled to the dew point temperature and liquefied is discharged from the indoor air passage outlet 32. FIG. 5 is a perspective view showing a dehumidified state in the dehumidifying heat exchanger according to Embodiment 1 of the present invention. The state where the liquefied water 100 is discharged at the indoor air passage outlet 32 is shown.

  An arrow α in FIG. 5 indicates the moving direction of room air in the room air passage 3. Similarly, an arrow β in FIG. 5 indicates the direction of movement of outside air in the outside air passage 4. The room air and the outside air move in parallel while facing each other as indicated by arrows α and β.

  Here, the indoor air is indoor air inside the facility that may be condensed by the outside air of the facility as described above. Outside air is air existing outside the facility. The dehumidifying heat exchanger 1 takes in the room air and the outside air from different ends of the main body 2 and removes excess moisture from the room air using the outside air to dehumidify.

(Main body)
Details of the main body 2 will be described. The main body 2 is a basic element of the heat exchanger 1 for dehumidification that includes an indoor air passage 3 and an outdoor air passage 4 that are through-holes. Here, the main body 2 includes a first end 21 and a second end 22 that face each other. For this reason, it can have the 1st end part 21 and the 2nd end part 22 which oppose, and it has the solid | 3D shape which can contain the indoor air passage 3 and the outdoor air passage 4 which are a penetration path inside. Is preferred.

  Here, the fact that the first end 21 and the second end 22 are opposed to each other is not limited to being opposed substantially in parallel, but is opposed in a state where the respective extension lines intersect. Including. That is, the main body 2 may have a three-dimensional shape in a curved state from the first end 21 to the second end 22.

  Each of the first end portion 21 and the second end portion 22 has an indoor air passage entrance 31, an indoor air outlet 32, an outdoor air passage entrance 41, and an outdoor air passage outlet 42. For this reason, the main-body part 2 needs to be a three-dimensional shape which has the 1st end part 21 and the 2nd end part 22 which oppose at least as mentioned above.

  Since the main body 2 includes an indoor air passage 3 and an outdoor air passage 4 that are through-holes, the interior of the integrally formed solid body is hollowed out later, and the indoor air passage 3 and the outdoor air passage 4 May be provided. Alternatively, it may be formed as a three-dimensional shape including the indoor air passage 3 and the outdoor air passage 4 by combining the parts of the members so that these which are through passages are formed.

  It is also preferable that the main body 2 has a shape corresponding to the shape, number, or arrangement of the indoor air passage 3 and the outdoor air passage 4 provided therein. For this reason, a height, a width, etc. should just be defined by the structure, arrangement | positioning, etc. of the indoor air passage 3 and the outdoor air passage 4.

  In addition, although the main-body part 2 should just be formed with various raw materials, it is preferable that it is a raw material with high heat conductivity in the part which the indoor air passage 3 and the outdoor air passage 4 contact thermally. Conversely, a material with low thermal conductivity may be used on the outer periphery so that the outside air temperature of the taken-in outside air does not rise too much.

(Indoor air passage and outdoor air passage)
Each of the plurality of indoor air passages 3 is a passage that penetrates through the inside of the main body portion 2 from the first end portion 21 toward the second end portion 22. The indoor air passage 3 has an indoor air passage inlet 31 on the first end portion 21 side and an indoor air passage outlet 32 on the second end portion 22 side. The room air inside the facility to be dehumidified is sent to the room air passage entrance 31. The sent indoor air moves from the indoor air passage inlet 31 toward the indoor air passage outlet 32.

  An arrow α in FIG. 5 is the indoor air movement path. In order to assist this movement, it is also preferable that a blower fan, a pressurizer, or the like that sends room air near the room air passage entrance 31 is provided. This may be provided as a member integrated with or continuous with the indoor air suction unit 330.

  In addition, in order to promote the movement of the indoor air passage along the arrow α in the indoor air passage 3, it is also preferable that an exhaust fan, a pressurizer, or the like is provided in the vicinity of the indoor air passage outlet 32. These may be provided outside the main body 2 or outside the heat exchanger 1 for dehumidification.

  Each of the plurality of outside air passages 4 is a passage that penetrates the inside of the main body portion 2 from the second end portion 22 toward the first end portion 21. That is, each of the outdoor air passages 4 is a passage that penetrates in a direction along the indoor air passage 3, and the movement path of the outdoor air is opposite to the movement path of the indoor air as indicated by an arrow β.

  The outside air passage 4 includes an outside air passage inlet 41 on the second end portion 22 side and an outside air passage outlet 42 on the first end portion 21 side. The outside air passage entrance 41 takes in outside air that cools the room air that moves through the inside air passage 3 to the dew point temperature. The taken outside air moves through the outside air passage 4 and is discharged from the outside air passage outlet 42. With the movement of the outside air inside the outside air passage 4, the room air moving in the room air passage 3 that is in thermal contact with the outside air passage 4 is cooled.

  Here, outside air outside the facility is taken into the outside air passage 4. In order to assist this intake, it is also preferable that a blower fan, a pressurizer, or the like for sending outside air near the outside air passage entrance 41 is provided. These may be provided as a member integrated with or connected to the outside air suction unit 430.

  Similarly, in order to promote the movement of the outside air along the arrow β in the outside air passage 4, it is preferable that an exhaust fan, a pressurizer, or the like is provided in the vicinity of the outside air passage outlet. These may be provided outside the main body 2 or outside the heat exchanger 1 for dehumidification.

(Configuration of indoor air passage and outdoor air passage)
It is also preferable that each of the plurality of indoor air passages 3 and each of the plurality of outside air passages 4 are substantially parallel inside the main body 2. For example, in the dehumidifying heat exchanger 1 shown in FIGS. 4 and 5, each of the plurality of indoor air passages 3 and each of the plurality of outside air passages 4 are substantially parallel inside the main body 2.

  By being substantially parallel, there is an advantage that manufacturing of the main body 2 including the indoor air passage 3 and the outdoor air passage 4 is easy. Further, there is an advantage that the indoor air movement in the indoor air passage 3 and the outdoor air movement in the outdoor air passage 4 are smooth.

  Further, the indoor air passage 3 and the outdoor air passage 4 are in thermal contact. Since the indoor air passage 3 and the outdoor air passage 4 are substantially parallel, the distance between each of the indoor air passage 3 and each of the outdoor air passages 4 tends to be constant in the moving direction. Since the interval is substantially constant, the interval between the indoor air passage 3 and the outdoor air passage 4 that are adjacent to each other tends to be constant over the entire movement path. As a result, thermal contact between room air and outside air occurs over the entire movement path.

  The thermal contact over the entire path increases the cooling efficiency by which the room air is cooled by the outside air.

  Here, it is appropriate that each of the plurality of indoor air passages 3 and each of the plurality of outside air passages 4 are alternately arranged in at least one of the thickness direction and the width direction of the main body 2. FIG. 6 is a front view of the main body according to the first embodiment of the present invention. The state which looked at the main-body part 2 from either the 1st end part 21 or the 2nd end part 22 is shown.

  Each of the plurality of indoor air passages 3 provided in the main body 2 and each of the plurality of outside air passages 4 are alternately arranged in the width direction, and is one row in the height direction. By arranging them alternately in this way, it is possible to realize that all the indoor air passages 3 are in thermal contact with one indoor air passage 3. For this reason, the cooling energy of the room air by the outside air that moves through one outside air passage 4 is distributed substantially uniformly, and the cooling mechanism to the dew point temperature described with reference to FIG. 2 is easily exhibited.

  Of course, for example, the two indoor air passages 3 and the two outside air passages 4 may be arranged side by side, or may be another configuration.

  Further, as shown in FIG. 7, the indoor air passage 3 and the outdoor air passage 4 may be configured in two rows (or more) in the height direction. In this case, there is an advantage that the unit amount of indoor air that can be dehumidified in the dehumidifying heat exchanger 1 is increased. FIG. 7 is a front view of the main body according to the first embodiment of the present invention.

  When arranged in two rows as shown in FIG. 7, each of the indoor air passages 3 and each of the outdoor air passages 4 are alternately arranged in the width direction, and each of the indoor air passages 3 and the outdoor air in the height direction. Each of the passages 4 may be arranged alternately. By doing so, the outdoor air passage 4 is arranged in each of the height direction and the width direction of a certain indoor air passage 3. With this arrangement, the indoor air moving through a certain indoor air passage 3 is efficiently cooled by the outside air passage 4 arranged around the width and height directions.

(Cooling indoor air to dew point temperature)
The dehumidifying heat exchanger 1 reliably cools the room air that moves through all of the plurality of room air passages 3 to the dew point temperature by the outside air that moves through the outside air passage 4 by the mechanism described with reference to FIG.

  As shown in FIGS. 4 and 5, the room air of the facility to be dehumidified is sent to each of the indoor air passage entrances 31. Outside air outside the facility is sent to each of the outside air passage entrances 41. The room air and the outside air are fed from the opposite sides of the first end 21 and the second end 22, respectively.

  Outside air moves in each of the outside air passages 4 along the arrow β. Each of the outdoor air passages 4 is in thermal contact with each of the adjacent indoor air passages 3 as shown in FIG. Due to this thermal contact, the outside air moving in each of the outside air passages 4 has a temperature higher than the outside air temperature when entering the outside air passage entrance 41, depending on the room air temperature when entering the indoor air passage entrance 31. The temperature gradually increases.

  However, the outside air that moves through the outside air passage 4 and reaches the outside air passage outlet 42 does not rise above the room air temperature of the room air at the room air passage entrance 31. With the configuration of the dehumidifying heat exchanger 1 corresponding to the mechanism described in FIG. 2, all of the plurality of outside air passages 4 are along the indoor air passage 3. As a result, the temperature of each of the plurality of outdoor air passages 4 rises due to thermal contact with each of the plurality of adjacent indoor air passages 3.

  For this reason, as above-mentioned, outside air is settled in the temperature rise to the room air temperature of the room air passage entrance 31 in the same end surface as the outside air passage exit 42. In particular, the same applies to all outside air passages 4. In other words, the outside air that has moved through the plurality of outside air passages 4 and reached the outside air passage outlet 42 has a temperature substantially equal to or lower than the room air temperature at the room air passage entrance 31.

  As a result, the temperature rise of the outside air in each of the plurality of outside air passages 4 does not cause any one of the outside air passages 4 to exceed the room air temperature. As a result, the variation in the degree of cooling of the indoor air in each of the outdoor air passages 4 is reduced. Eventually, all of the room air moving through each of the plurality of room air passages 3 is cooled to the dew point temperature.

  The indoor air sent from the indoor air passage inlet 31 is cooled by thermal contact with the outside air moving through the outdoor air passage 4 while moving to the indoor air passage outlet 32. The outside air that comes into contact with the indoor air passage outlet 32 at the end of the movement has a dew point temperature that causes the room air of the equipment to be dehumidified to condense (that is, the outside air has the lowest temperature at the second end portion 22). Since this second end corresponds to the indoor air passage outlet 32, the indoor air reaches the dew point in thermal contact with the lowest temperature outside air at the indoor air passage outlet 32). By the thermal contact with the outside air having the dew point temperature, the indoor air is reliably cooled to the dew point temperature at the indoor air passage outlet 32 together with the previous cooling.

  By this cooling, excess moisture based on the dew point temperature due to the outside air is liquefied and removed from the indoor air at the indoor air outlet 32. By this removal, the room air of the facility to be dehumidified is dehumidified according to a standard that does not condense. In particular, cooling to the dew point temperature and dehumidification are realized in all indoor air passages 3 provided in the main body 2.

  This solves the problem in the configuration of FIG. This is as described in the mechanism in FIG.

  As mentioned above, the heat exchanger 1 for dehumidification of Embodiment 1 can dehumidify by using outside air to the level which does not condense indoor air with outside air. Since outside air is used for dehumidification, useless energy is not required. In addition, the configuration of the heat exchanger 1 makes it difficult for the temperature rise of the outside air to be uneven, and the indoor air can be uniformly cooled and dehumidified.

  As described above, the dehumidifying apparatus according to Embodiment 1 can realize dehumidification to a level where condensation does not occur by cooling the indoor air of the facility to be dehumidified to the dew point temperature using the outside air. This dehumidification makes it difficult for the inside of the facility to cause dew condensation due to the outside air, and it is difficult to cause various problems based on the dew condensation inside the facility.

  In addition, the intake speed of the indoor air into the indoor air passage 3 may be changed based on the outside air temperature that is the temperature of the outside air of the facility. For example, when the outside air temperature is relatively high (for example, when the outside air temperature is higher than a predetermined value or in proportion to the temperature curve of the outside air temperature), the intake speed of the indoor air into the indoor air passage 3 is relatively high. Be late. At this time, the intake speed into the indoor air passage 3 may be decreased in proportion to the value of the outside air temperature.

  On the contrary, when the outside air temperature is relatively low, the intake speed of the indoor air into the indoor air passage 3 is relatively increased. In either case, the outside air temperature may be divided by a predetermined value, and the indoor air intake speed may be changed stepwise, or the indoor air intake speed may be changed continuously in proportion to the outside air temperature. Also good.

  These are for surely cooling the indoor air to the dew point temperature by the thermal contact between the indoor air passage 3 and the outdoor air passage 4.

  Here, the indoor air intake speed into the indoor air passage 3 may be adjusted by the indoor air suction unit 330. Or you may adjust with the ventilation fan 320 which returns the indoor air after dehumidification to an installation.

  Further, the dehumidifying device 11 may include an outside air temperature measurement unit that measures the outside air temperature that is a reference for adjusting the speed of taking in indoor air into the indoor air passage 3 (inflow rate). For example, a thermometer may be installed in a place where it comes into contact with the outside air, and this thermometer may be handled as the outside air temperature measuring unit. In addition, the outside air temperature measurement unit outputs the measurement result to the indoor air suction unit 330 and the blower fan 320. In response to this output, the indoor air suction unit 330 and the blower fan 320 can change the intake speed of the indoor air into the indoor air passage 3.

  The blower fan 320 is an indoor air return unit that returns indoor air after dehumidification to the inside of the facility, and the exhaust fan is an example of an external air discharge unit that discharges the external air used for cooling to the outside.

  (Embodiment 2)

  Next, a second embodiment will be described. In the second embodiment, various additional devices will be described.

(Water drop outlet)
It is also preferable that the dehumidifying heat exchanger 1 includes a water droplet discharge port for discharging water droplets generated by condensation of room air by the outside air.

  In FIG. 5, it is appropriate that a water droplet discharge port is provided at the indoor air passage outlet 32. For example, the water droplet discharge port may include a structure that guides the water droplet to the tip so that the water droplet is not easily clogged in the indoor air passage 3. For example, it is preferable that a dew-like derivative is provided at the indoor air passage outlet 32 so that condensed water droplets are easily discharged.

  Moreover, the water droplet discharge port may be provided in each of the plurality of indoor air passage outlets 32 or may be provided collectively.

(Entrance and exit of indoor air passage and outdoor air passage)
The main body 2 includes a plurality of indoor air passages 3 and an outdoor air passage 4. Here, as shown in FIG. 5, the indoor air passage 3 and the outdoor air passage 4 are formed substantially in parallel from opposite directions. That is, the indoor air moving through the indoor air passage 3 and the outdoor air moving through the outdoor air passage 4 move while facing each other.

  Here, as shown in FIG. 4, in the dehumidifying heat exchanger 1, indoor air passage inlets 31 that are entrances of the plurality of indoor air passages 3 are arranged at the first end portion 21, and the second end portion 22. Alternatively, the outside air passage entrances 41 that are the entrances of the plurality of outside air passages 4 may be arranged side by side.

  That is, as shown in FIG. 5, all of the indoor air passage inlet 31 and the outdoor air passage outlet 42 are arranged in the first end portion 21. Similarly, the indoor air passage outlet 32 and the outdoor air passage entrance 41 are all lined up at the second end portion 22.

  On the other hand, indoor air is sent from the facility to be dehumidified to the indoor air passage entrance 31 and sent back to the equipment from the indoor air passage outlet 32. The main body 2 is placed at a position based on the equipment. For this reason, the 1st edge part 21 thru | or 2nd edge part 22 of the main-body part 2 will be located in the reverse side of the near side and the far side with respect to an installation.

  Thus, it may be inconvenient for the indoor air to enter and exit at each of the first end portion 21 and the second end portion 22 that are at positions opposite to the facility. This is because it is appropriate for the room air to enter and exit the room as long as the room air reaches the body 2 from the facility and returns from the body 2 to the facility.

  The same applies to the relationship between the outside air passage 4 and outside air. Outside air is taken in and discharged from a different direction from the facility. For this reason, it is appropriate that the outside air passage entrance 41 and the outside air passage outlet 42 are also aligned in the same direction.

  FIG. 8 is a perspective view of a heat exchanger for dehumidification according to Embodiment 2 of the present invention. Inside the main body 2, room air moves along the indoor air passage 3 as indicated by an arrow α. Similarly, outside air moves along the outside air passage 4 inside the main body 2 as indicated by an arrow β. The movement path between the room air and the outside air is as described in the first embodiment.

  Here, the dehumidifying heat exchanger 1 shown in FIG. 8 includes an indoor air introduction part 300 connected to the indoor air passage inlet 31 and an indoor air discharge part 310 connected to the indoor air passage outlet 32. By providing these, in the heat exchanger 1 for dehumidification, the indoor air introduction unit 300 that actually sends room air to the indoor air passage 3 on the direction side of the equipment, and the room air that returns the room air after dehumidification to the equipment The discharge unit 310 can be arranged.

  Similarly, the dehumidifying heat exchanger 1 shown in FIG. 7 includes an outside air introduction part 400 connected to the outside air passage inlet 41 and an outside air discharge part 410 connected to the outside air passage outlet 42. By providing these, in the heat exchanger 1 for dehumidification, on the side opposite to the equipment, an outside air introduction unit 400 that actually sends outside air to the outside air passage 4, and an outside air discharge unit 410 that discharges the outside air after use to the outside, Can be arranged.

  Furthermore, the introduction and discharge of indoor air can be concentrated on one side (equipment side) of the heat exchanger 1 for dehumidification, and the introduction and discharge of outside air can be concentrated on the opposite side of the heat exchanger 1 for dehumidification. On the other hand, inside the body part 2 of the heat exchanger 1 for dehumidification, as indicated by arrows α and β, movement of room air in the room air passage 3 as described in the first embodiment, The movement of the outside air in the outside air passage 4 is performed.

  In FIG. 8, the room air taken out from the facility is sent from the room air introduction part 300 to the main body part 2 according to the arrow F. The room air introduction part 300 distributes and sends the room air into the plurality of room air passages 3 inside the main body part 2. Thereafter, each of the indoor air passages 3 moves the indoor air along the arrow α. In this movement, it is cooled by the outside air that moves in the opposite direction in parallel. Thereafter, the room air moves from the outlet of the room air passage 3 to the room air discharge unit 310. The room air discharge unit 310 discharges room air after dehumidification along the arrow G.

  At the time of this discharge, the condensed water may be discharged from the indoor air discharge unit 310.

  On the other hand, in FIG. 8, outside air is sent to the outside air introduction unit 400 according to the arrow H from the opposite side of the facility. The outside air introduction unit 400 sends outside air into the main body 2. The outside air sent into the main body 2 moves through the plurality of outside air passages 4 inside the main body 2 along the arrow β. After this movement, the outside air is gathered from each of the outside air passages 4 and is discharged from the outside air discharge unit 410 to the outside. Finally, the outside air is discharged from the outside air discharge unit 410 along the arrow I.

  With such an air moving path, the function of the dehumidifying heat exchanger 1 described in the first embodiment can be realized, and the introduction and discharge of indoor air and outside air with reference to the facility can be made more efficient. In particular, due to intensive introduction and discharge, air movement in the indoor air passage 3 and the outside air passage 4 can be made smooth.

  Note that each of the indoor air introduction unit 300, the indoor air discharge unit 310, the outside air introduction unit 400, and the outside air discharge unit 410 is in a spatially separated state.

(Relationship between main unit and case)
As described with reference to FIG. 3, it is also preferable that the dehumidifying device 11 has a case 500 (housing). This is because the case 500 is provided, and the case 500 accommodates the dehumidifying heat exchanger 1 and the like, so that installation outside the facility becomes easy.

  Here, it is appropriate that the main body portion 2 is accommodated in the case 500 so that the second end portion 22 faces downward. This is because the second end portion 22 is a portion corresponding to the indoor air passage outlet 32 and is liable to discharge liquefied water droplets by being located downward.

  Further, the case 500 may include a drainage channel that guides water droplets discharged from the second end 22 to the outside and drains them to the ground. By this drainage channel, the liquefied water droplets are discharged from the dehumidifying device 11 to the outside.

  As described above, the dehumidifying device according to Embodiment 2 can facilitate the discharge of liquefied water droplets, and facilitate the intake of indoor air into the indoor air passage 3 and the intake of outside air into the outdoor air passage 4.

  As described above, the dehumidifying device described in the first and second embodiments is an example for explaining the gist of the present invention, and includes modifications and alterations without departing from the gist of the present invention.

DESCRIPTION OF SYMBOLS 1 Heat exchanger for dehumidification 2 Main-body part 21 1st end part 22 2nd end part 3 Indoor air passage 31 Indoor air passage entrance 32 Indoor air passage exit 4 Outside air passage 41 Outside air passage entrance 42 Outside air passage exit 11 Dehumidifier 100 Moisture 110 Greenhouse 300 Indoor air introduction part 310 Indoor air discharge part 320 Blower fan 330 Indoor air suction part 400 Outside air introduction part 410 Outside air discharge part 420 Exhaust fan 430 Outside air suction part 500 Case

Claims (17)

An indoor air suction section for taking in indoor air of the equipment to be dehumidified;
An outside air suction unit that takes in outside air that is outside the equipment;
A heat exchanger for bringing the indoor air and the outside air into thermal contact with each other,
The heat exchanger is
A three-dimensional body having opposing first and second ends;
A plurality of indoor air passages for moving room air from the first end toward the second end;
A plurality of outside air passages for moving outside air from the second end toward the first end,
At least a part of each of the plurality of indoor air passages and at least a part of each of the plurality of outside air passages are adjacent to each other in at least a part in the thickness direction and the width direction of the main body part,
The outside air temperature that is the temperature of the outside air is lower than the room air temperature that is the temperature of the room air,
The dehumidifying device, wherein the outside air temperature cools the room air that moves through the plurality of room air passages to a dew point temperature by the outside air that moves through the outside air passages.   The dehumidifier according to claim 1, wherein the heat exchanger liquefies and discharges excess moisture contained in the room air by cooling the room air to a dew point temperature.   The dehumidification according to claim 3, wherein the outside air temperature corresponds to a dew point temperature of the room air, and the heat exchanger cools the room air to a dew point temperature throughout the indoor air passage to liquefy excess moisture. apparatus.   4. The dehumidifying device according to claim 2, wherein the excess moisture corresponds to an amount of condensation of the room air inside the equipment by the outside air temperature outside the equipment inside the equipment.   The dehumidifying apparatus according to any one of claims 1 to 4, wherein the facility is any one of a plant growing facility such as a vinyl house and a glass house, a factory, a clean room, a computer room, a laboratory, and a temperature-controlled room.   The dehumidifier according to any one of claims 1 to 5, further comprising a housing that houses the indoor air suction unit, the outside air suction unit, and the heat exchanger.   The dehumidifying device according to claim 6, wherein the second end portion is provided toward a lower side of the housing. An indoor air return unit for returning the indoor air cooled to the dew point temperature by the heat exchanger to the inside of the facility;
The dehumidifying device according to claim 6, further comprising: an outside air discharge unit that discharges the outside air that is cooled and discharged by the heat exchanger to the outside of the housing.   The room air moving through each of the plurality of room air passages is in thermal contact with each of the plurality of adjacent outside air passages, and the outside air cools the room air to a dew point temperature. The dehumidifying device according to any one of 8.   10. The dehumidifying device according to claim 1, wherein each of the plurality of indoor air passages and each of the plurality of outside air passages are substantially parallel inside the main body portion.   The dehumidification according to any one of claims 1 to 10, wherein each of the plurality of indoor air and each of the plurality of outside air passages are alternately arranged in at least one of a thickness direction and a width direction of the main body. apparatus.   The outside air that moves in each of the plurality of outside air passages has substantially the same temperature at a second end that serves as an entrance of movement, and substantially the same temperature at the first end that serves as an exit of movement. Item 12. The dehumidifying device according to any one of Items 1 to 11.   The room air that moves through each of the plurality of indoor air passages is in thermal contact with the lowest temperature state of the outside air that is fed into the plurality of outside air passages at a second end that serves as an outlet for movement. The dehumidifying device according to any one of claims 1 to 12, wherein the dew point temperature is obtained.   The indoor air that moves through each of the plurality of indoor air passages is in thermal contact with the outside air that moves through the outdoor air passage, where the temperature gradually decreases as it moves from the first end to the second end. The dehumidifying device according to claim 13, wherein the dehumidifying device gradually reduces the indoor air temperature by continuing to lower the dew point temperature in the vicinity of the second end.   The dehumidifying device according to claim 14, wherein the indoor air that has moved through each of the plurality of indoor air passages at the second end has a dew point temperature in all of the indoor air passages. Based on the outside air temperature outside the equipment, the intake speed of the indoor air taken into the indoor air passage changes,
When the outside air temperature is relatively high, the intake speed taken into the indoor air passage becomes slow,
The dehumidifying device according to any one of claims 1 to 15, wherein when the outside air temperature is relatively low, an intake speed taken into the indoor air passage is increased.   The dehumidifying device according to claim 16, wherein at least one of the indoor air suction part and the indoor air return part adjusts the intake speed of indoor air into the indoor air passage.