JP5917787B2 - Air conditioning system - Google Patents

Description

The present invention relates to an air conditioning system , and more particularly to an air conditioning system using a dehumidifier composed of a total heat exchanger and a desiccant rotor.

  Conventionally, in an air conditioning system (hereinafter sometimes referred to as “air conditioning”) that regulates the temperature and humidity of indoor air, in order to keep indoor air fresh, it is common to take in fresh outside air It has become.

  In such a conventional air conditioning system, one using a desiccant rotor that adsorbs moisture of outside air is known as means for adjusting humidity.

  The desiccant rotor is a honeycomb-shaped rotor that supports a high-regeneration polymer sorbent and silica gel or zeolite, which are known as dehumidifiers, even at low temperatures. The rotor rotates to dehumidify the air. The dehumidifying area is divided into a regenerating area where the adsorbed moisture is released and the desiccant rotor is regenerated. Then, the outside air to be dehumidified is passed through the dehumidifying side flow path, passes through the dehumidifying region of the desiccant rotor, and the moisture in the air is adsorbed by the desiccant rotor, so that it is sent out as air having a low absolute humidity. In addition, since the temperature of the air after passing through the desiccant rotor becomes higher due to the generation of heat of adsorption, the temperature is adjusted as necessary by cooling or passing through a sensible heat exchanger.

  On the other hand, when the desiccant rotor is regenerated, the return air from the room is usually passed through the regeneration side passage and passed through the regeneration region of the desiccant rotor. However, the air for regeneration is high in order to reduce the relative humidity. For this reason, conventionally, heating means for heating the return air is disposed upstream of the regeneration side passage in the desiccant rotor.

  Thus, the return air, which is high-temperature and low-relative-humidity air, takes away moisture from the desiccant rotor and exhausts it, while the dried regeneration region is located in the dehumidification side passage again by the rotation of the desiccant rotor, and the dehumidification region And adsorbs moisture.

  As described above, in order to regenerate the desiccant rotor, a heating means for heating the air is necessary. To date, in order to reduce the cost of such a heating means, a micro gas turbine or a thermal efficiency higher than this is required. The use of exhaust heat, such as a micro gas engine with a high initial cost and a low initial cost, has been attempted. However, there is a strong demand for further reduction of the initial cost from the market, and in order to save energy of the entire system, it has been demanded to reduce the regeneration temperature itself of the desiccant rotor as much as possible.

  Therefore, in order to regenerate the desiccant rotor at a low temperature, it has been considered to cool and dehumidify the outside air in advance before dehumidifying with the desiccant rotor.

  In FIG. 17, the typical block diagram of the conventional air conditioning system which made the desiccant rotor reproducible at the low temperature of about 50 degreeC is shown. In the air conditioning system having such a configuration, when the outside air temperature is about 33 ° C. and the humidity is 60%, the room temperature is about 26 ° C. and the humidity is 50% (absolute humidity is about 10.5 g / kg). FIG. 18 shows a state diagram of the air. It should be noted that the circled numbers shown in FIG. 17 and the circled numbers in FIG. 18 correspond to each other, and the state of air at each position in the system in FIG. 17 can be seen in FIG.

  In FIG. 17, reference numeral 101 denotes an air supply passage that takes in outside air and supplies it into the room, and reference numeral 102 denotes an exhaust passage that exhausts the return air from the room to the outside of the system. The desiccant rotor 200 and the sensible heat exchanger 300 are disposed so as to straddle the supply air flow path 101 that becomes and the supply air flow path 101 that becomes the regeneration side passage. With respect to the positional relationship between the desiccant rotor 200 and the sensible heat exchanger 300, the desiccant rotor 200 is disposed on the upstream side and the sensible heat exchanger 300 is disposed on the downstream side of the supply air flow path 101 as a reference.

  In the air supply flow path 101, a chilled water coil CC for pre-cooling the outside air and an air supply blower S-FAN are disposed on the upstream side of the desiccant rotor 200 in order from the desiccant rotor 200 side. On the downstream side of 300, a cold water coil CC for temperature adjustment is disposed.

  Further, in the exhaust passage 102, a hot water coil HC for heating the return air for desiccant regeneration is disposed between the sensible heat exchanger 300 and the desiccant rotor 200, and on the downstream side of the desiccant rotor 200. A return air blower R-FAN is disposed in the front.

  As shown in the figure, the outside air introduced into the supply air flow channel 101 (temperature approximately 33 ° C., absolute humidity approximately 19.5 g / kg) is cooled to a target temperature (approximately 26 ° C.) by the cold water coil CC, and the absolute humidity. Dehumidified to approximately 18 g / kg (number 2 with o). At this time, cooling energy I1 is required.

  After that, the desiccant rotor 200 dehumidifies to the desired humidity (absolute humidity is approximately 10.5 g / kg) (circled number 3). At this time, heat of adsorption is generated and the temperature of the air rises to about 46 ° C. When this is exchanged with the return air by the sensible heat exchanger 300, the temperature is lowered to about 32 ° C. (number 4 with ○). However, since it does not reach the target temperature (approximately 26 ° C.), it is further cooled to the target temperature by using the cold / hot water coil CC for temperature adjustment (number 5 with ○). At this time, the cooling energy I2 is further required.

  In addition, as an air conditioning system using a desiccant rotor, the total heat exchange rotor (total heat exchanger) is used from the inside of the room so that it is less affected by an increase in the humidity of the outside air, and in particular, it can exert a sufficient effect even with low-temperature regenerated air. Exhaust air with reduced temperature and humidity is dehumidified with a desiccant rotor, and the temperature is adjusted by exchanging sensible heat with the return air from the room. There has been proposed a system in which dry air having a reduced temperature is supplied to a room (see, for example, Patent Document 1).

According to this, the dehumidifying performance is remarkably improved as compared with the case where dehumidification is performed by previously cooling the outside air using a cold / hot water coil or the like, but when this is actually installed, the desiccant rotor, the total heat exchange rotor, This also requires a sensible heat exchanger of the rotor type, and further, a first exhaust fan for passing the return air through the total heat exchange rotor, and a second exhaust for sucking outside air for regenerating the desiccant rotor. Since a fan or the like is necessary, as shown in FIG. 19, it is considered that the system will be a relatively large system that requires a considerable installation volume. In FIG. 19, OA is outside air, SA is supply air, RA is return air, EA is exhaust air, THE is a total heat exchanger, DHE is a desiccant rotor, and SHE is a sensible heat exchanger. Further, HC is a hot water coil, CHC is a cold / hot water coil, and HU is a humidifier.
JP 2003-214654 A

  However, as in the conventional air conditioning system described with reference to FIGS. 17 and 18, even if the air is precooled in advance in order to regenerate the absorbed desiccant rotor at a low temperature, a large amount of cooling energy is required, which saves energy. It is hard to become. Therefore, for example, it is desired that the desiccant rotor can be regenerated by low-temperature exhaust heat generated by exhaust generated in an air conditioning system or the like.

  Moreover, in the structure shown in patent document 1, as above-mentioned, the enlargement of a system cannot be avoided, for example, installing in an existing building etc. becomes very disadvantageous.

  Furthermore, in the configuration shown in FIG. 17 of the above-described prior art, the desiccant rotor straddles the supply passage for supplying outside air into the room and the exhaust passage for exhausting the return air from the room to the outside of the system. Therefore, when it is regenerated with the return air from the room, the odor component in the room of the desiccant rotor is adsorbed, and this gets on the supply air to the room at the time of dehumidification. There is a risk that it will remain forever. Further, in the configuration of Patent Document 1, as shown in FIG. 19, the total heat exchange rotor takes in the outside air and supplies it into the room, and the exhaust path for exhausting the return air from the room to the outside of the system. Since it is disposed across the street, there is no change in that there is a possibility that the odor may remain in the room.

An object of the present invention is to solve the above-mentioned problems and to provide an air conditioning system that is advantageous in terms of initial cost and running cost while effectively utilizing a desiccant rotor.

(1) In the present invention, an air supply passage that takes in outside air and supplies it into the room, a first exhaust passage that introduces return air from the room, and exhausts the return air from the first exhaust passage outside the system. a second exhaust flow path, the sheet while winter seasons are you wet release a stream roadside, winter season in the first exhaust flow path is the total heat exchanger having a rotor you moisture absorption, the first exhaust flow path A desiccant rotor disposed in the middle, and the exhaust flow path and the air supply flow path configured by the first exhaust flow path and the second exhaust flow path have a partition wall in a rectangular box-shaped equipment casing Through which the downstream end of the first exhaust passage and the upstream end of the second exhaust passage are connected by a hairpin curve, and the total heat exchanger The ½ portion faces the upstream side of the air supply flow path, and the other ½ portion is the first exhaust on the upstream side of the hairpin curve through the partition wall. The desiccant rotor is arranged so as to face the flow path, and one half of the desiccant rotor faces the upstream side of the other half of the total heat exchanger located on the first exhaust flow path, and the other 1 / 2 portion is arranged so as to face the downstream side of the second exhaust flow path turned back by the hairpin curve from the first exhaust flow path through the partition wall, and further, the hot water made of a copper tube on the downstream side of the total heat exchanger As a heating means for supplying air, an antifreeze liquid is passed through the hot water coil, and a cold water coil made of a copper tube is provided immediately upstream of the desiccant rotor in the second exhaust flow path to cool the exhaust. The anti-freezing liquid is passed through this cold water coil, and the relative humidity of the exhaust is changed between the dehumidifying area and the regeneration area of the desiccant rotor, and the relative humidity of the exhaust is used in the regeneration area of the desiccant rotor. To humidify the exhaust The moisture in the return air passing through the second exhaust passage is absorbed by the desiccant rotor during heating in winter, and the absorbed moisture is released into the return air passing through the first exhaust passage. In addition, non-feed water humidification is possible without supplying water from outside, and a heat pump using gas as a heat medium is incorporated, and a compressor and a condenser are provided in the supply air flow path, and evaporation is performed in the exhaust flow path. The air conditioning system is characterized in that the low-temperature exhaust heat of the heat pump can be used by disposing a vessel.

(2) In the present invention, in the air conditioning system according to (1), in the total heat exchanger, the outside air of the supply air passage that passes through the rotor is opposed to the return air of the first exhaust passage. The desiccant rotor is disposed so as to straddle the supply air channel and the first exhaust gas channel so as to form a flow, and the desiccant rotor includes return air of the first exhaust gas channel passing through the desiccant rotor. as the second exhaust flow path exhaust to form a counter flow, it is arranged so as to extend in said second exhaust flow path and the first exhaust passage, winter season in the first exhaust flow path is while moisture release, winter season in the second exhaust flow path is characterized by moisture absorption.

( 5 ) The present invention is characterized in that in the air conditioning system according to any one of the above (1) to ( 4 ), a heat pump for temperature adjustment is provided, and the exhaust heat of the heat pump is used as a heat source for regeneration of the desiccant rotor. To do.

  According to the air conditioning method and the air conditioning system of the present invention, it is possible to regenerate the desiccant rotor using low-temperature exhaust heat. Moreover, it is possible to save energy in the entire air conditioning system by using unused energy. Moreover, since it can prevent that the whole system enlarges by setting it as efficient equipment arrangement | positioning, it is easy to employ | adopt this system in a market. Furthermore, according to the present system, the desiccant rotor is arranged in an exhaust flow path that is partitioned from the flow path for supplying air into the room. It can be prevented as much as possible from remaining forever.

  When considering regenerating the desiccant rotor with low-temperature exhaust heat of about 50 ° C, if it is a system that directly dehumidifies the outside air to the optimum absolute humidity, as described in "Background Art", first reduce the cooling. After wetting, it is necessary to dehumidify a large amount with a desiccant rotor, heat exchange with a sensible heat exchanger, and finally cooling.

  In the first place, the conventional desiccant rotor was used to dehumidify “outside air” with almost no exception as in the above-described example. However, if the desiccant rotor is used to dehumidify a large amount, it is obvious that a large amount of energy is required for the regeneration. On the contrary, since the energy can be reduced if the dehumidification amount is made small, the inventor originally focused on utilizing the low indoor absolute humidity. This is because the regeneration (dehumidification performance) of the desiccant rotor depends on the relative humidity of the air for regeneration, and can be sufficiently regenerated even at about 50 ° C. using return air.

  However, even if the room air is further dehumidified, it cannot be ventilated with the outside air, so heat is exchanged between the outside air and the total heat exchanger.

  Therefore, in the air conditioning method according to the present embodiment, the outdoor air and the return air from the room are totally heat-exchanged by the total heat exchanger, and the outdoor air that has been completely heat-exchanged is supplied to the room, The outside air is directly introduced into the total heat exchanger, while the return air is dehumidified in advance using a desiccant rotor and then introduced into the total heat exchanger.

  According to this method, in summer, for example, the desiccant rotor can be regenerated using low-temperature exhaust heat of about 40 to 80 ° C., sufficient dehumidification can be performed, and energy can be saved. .

An air conditioning system (hereinafter referred to as “air conditioning system”) for realizing the above-described air conditioning method has the following configuration.
That is, an air supply passage that takes in outside air and supplies it to the room, an exhaust passage that exhausts the return air from the room to the outside of the system, and stores and absorbs moisture on the air supply passage side, while radiating and releasing heat on the exhaust passage side. A total heat exchanger having a moistening rotor and a desiccant rotor which is disposed in the middle of the exhaust flow path and dehumidifies or humidifies the return air before passing through the total heat exchanger. Yes.

  With this configuration, the entire system can be made compact, and for example, as low-temperature exhaust heat, exhaust generated by an air conditioning system can be used as it is, so that it can be installed in an existing building. Is easy, and the initial cost can be significantly reduced.

As a more specific configuration of the present system, the total heat exchanger is configured so that the outside air of the supply air flow path passing through the rotor and the return air of the exhaust flow path form a counter flow. It arrange | positions so that an air supply flow path and the said exhaust flow path may be straddled, and the said exhaust flow path passes through the said total heat exchanger, the 1st exhaust flow path to the said total heat exchanger, and a flow path consist of a second exhaust flow path toward the end, the desiccant rotor, so that the exhaust of the the air instead of the first exhaust flow path passing through the desiccant rotor second exhaust flow path to form a counter flow The first exhaust flow path and the second exhaust flow path are disposed so as to be absorbed by the first exhaust flow path side, and the second exhaust flow path side is dehumidified. Can do.

By the way, the air conditioning system described above is suitable for use in the summer, but the basic arrangement of the total heat exchanger and the desiccant rotor is not changed, and the following configuration is preferably used in the winter. Can do.
That is, an air supply passage that takes in outside air and supplies it into the room, an exhaust passage that exhausts the return air from the room to the outside of the system, and radiates and releases moisture on the air supply passage side, while storing heat on the exhaust passage side A total heat exchanger having a rotor that absorbs moisture, and a desiccant rotor that is disposed in the middle of the exhaust flow path and humidifies the return air before passing through the total heat exchanger. Out.

As a more specific configuration of such a system, the total heat exchanger may be configured so that the outside air in the supply air passage that passes through the rotor and the return air in the exhaust passage form a counter flow. The exhaust passage is disposed so as to straddle the air supply passage and the exhaust passage, and the exhaust passage passes through the first exhaust passage leading to the total heat exchanger and the total heat exchanger. It consists of a second exhaust flow path toward the flow path end, wherein the desiccant rotor, a gas instead of the first exhaust flow path passing through the desiccant rotor and exhaust of said second exhaust flow path forms a counter current As described above, the first exhaust passage and the second exhaust passage are disposed so as to straddle, and are configured to release moisture on the first exhaust passage side while absorbing moisture on the second exhaust passage side. can do.

  Since the desiccant rotor is disposed in the exhaust flow path of the air conditioning system configured as described above, the desiccant rotor can be regenerated using low-temperature exhaust heat, and sufficient dehumidification and humidification can be performed according to the season. In addition to the effect of being able to save energy, for example, even if a desiccant rotor carrying silica gel is regenerated at a low temperature, the odor adhering to the rotor is only exhausted. Therefore, it is possible to realize a countermeasure against odor which has been a problem in an air conditioning system using a desiccant rotor.

  In particular, it is preferable that the air supply flow path and the exhaust flow path are independent flow paths partitioned from each other, so that the above-described transfer of odor into the room can be further reduced.

  The air conditioning system described above includes a heat pump for temperature adjustment, and the exhaust heat of the heat pump can be used as a heat source for regeneration of the desiccant rotor.

  In recent years, heat pumps have been used in many air conditioning systems as being superior in energy saving energy, and even in the air conditioning system of the present application, it is possible to achieve further energy saving effects by using such heat pumps.

  Hereinafter, the air conditioning system according to the present embodiment will be described more specifically with reference to the drawings.

(First embodiment)
FIG. 1 is an explanatory diagram when the air conditioning system according to the present invention is installed, FIG. 2 is a state diagram of air in the air conditioning system according to the first embodiment, and FIG. 3 is a schematic explanation showing a basic configuration of the air conditioning system. FIG. 2 and the numbers with ○ in FIG. 3 correspond to each other so that the air condition at each position in the system in FIG. 3 can be seen in FIG. . In addition, what is shown in FIG. 2 is the cooling in the summer in which the outside air is 33 ° C. and the absolute humidity is 19.5 g / kg, and the room temperature is about 26 ° C. and the humidity is 50% (the absolute humidity is about 10.5 g / kg) If you are going to.

  As shown in FIG. 1, the basic configuration of the air conditioning system according to the present embodiment is a rectangular box-shaped equipment casing 1 with three upper and lower spaces through partition walls 11, 12, that is, an air supply channel 20 from above. In addition, an outside air introduction duct 13 that is partitioned into a first exhaust passage 21 and a second exhaust passage 22 and communicates with the outside air is provided on one end side (right side in the drawing) of the air supply passage 20 and the other end side (see FIG. Is provided with an outside air delivery duct 14 that communicates with a room to be air-conditioned. An air supply blower S-FAN is disposed in the vicinity of the outside air delivery duct 14 in the air supply flow path 20.

Also, a return air introduction duct 15 is provided on one end side (left side in the figure) of the first exhaust passage 21 to communicate with the room and introduces return air, and the other end side (right side in the figure) of the partition wall 11 is cut away. An exhaust duct 16 communicating with the outside air is provided on one end side (left side in the drawing) of the second exhaust flow path 22 while communicating with the second exhaust flow path 22. Further, a return air blower R-FAN is disposed in the vicinity of the return air introduction duct 15 of the first exhaust passage 21. In this way, the air supply passage 20 independent of each other and the exhaust passage composed of the first exhaust passage 21 and the second exhaust passage 22 are formed in the equipment casing 1. In this embodiment, the outside air that passes through the air supply passage 20 moves substantially linearly, and the return air that passes through the exhaust passage moves so as to draw a hairpin curve.

  Further, in the equipment casing 1, the rotor is such that the upper half faces the upstream side of the air supply passage 20 (the outside air introduction duct 13 side) and the lower half faces the first exhaust passage 21 via the partition wall 11. And the desiccant rotor 4 is arranged so that the upper half faces the first exhaust passage 21 and the lower half faces the second exhaust passage 22 via the partition wall 12. It is installed.

  Further, a cold / hot water coil CHC made of a copper (Cu) tube and a humidifier HU are arranged in order toward the air supply fan F1 on the downstream side of the total heat exchanger 3 in the air supply flow path 20. A hot water coil HC made of a copper tube is disposed immediately upstream of the desiccant rotor 4 in the flow path (second exhaust flow path 22). In the present embodiment, the cold / hot water coil CHC and the hot water coil HC function as a “heat exchanger”.

  The total heat exchanger 3 is capable of exchanging temperature and humidity at the same time, and stores and absorbs moisture in a region facing the air supply channel 20, while the exhaust channel (here, the first exhaust channel 21). It consists of a rotor that can rotate around the central axis so as to dissipate and release moisture in the area facing the surface, and this rotor is formed in a honeycomb shape by supporting a moisture absorbing material such as silica gel on the surface of aluminum foil or the like. Yes. Then, this rotor is rotated so that the outside air is passed through the upper half of the rotor and the room air is passed through the lower half to exchange the total heat.

  During cooling in summer, the rotor material is heated and moisture is absorbed in the upper half of the rotor where high-temperature and high-humidity outdoor air passes. Since the air comes into contact with the outside air, heat and moisture are transferred to the rotor material, and the temperature and humidity are reduced and the room is supplied indoors. Then, the rotor material returns to the lower half again, contacts the low-temperature, low-humidity air that has circulated from the room, receives heat and moisture from the rotor material, and is exhausted.

  The desiccant rotor 4 is a honeycomb-shaped rotor on which a polymer sorbent having high regenerating ability even at low temperatures, silica gel, zeolite, and the like are supported. As described above, the upper half faces the first exhaust passage 21. In addition, the lower half faces the second exhaust passage 22 via the partition wall 12 and is rotatably arranged. Then, when the desiccant rotor 4 rotates, the desiccant rotor 4 becomes a dehumidifying region where the air is dehumidified when positioned on the first exhaust channel 21 side. On the other hand, when the desiccant rotor 4 is positioned on the second exhaust channel 22, the adsorbed moisture is released and the desiccant rotor is released. It becomes a reproduction area for reproducing the rotor 4.

  In the present embodiment, outside air to be dehumidified is passed through the desiccant rotor 4 through the first exhaust flow path 21 serving as the dehumidification side flow path, and the moisture in the air is adsorbed in the dehumidification region, thereby reducing the air with low relative humidity. Is sent to the total heat exchanger 3.

  On the other hand, the return air exchanged through the total heat exchanger 3 flows into the second exhaust passage 22 and passes through the regeneration region of the desiccant rotor 4 to regenerate the desiccant rotor 4. Since the air having undergone total heat exchange by the vessel 3 has a high humidity, it is heated by the hot water coil HC to lower the relative humidity. The regenerated region of the desiccant rotor 4 that has been dried becomes a dehumidifying region when the desiccant rotor 4 rotates and is positioned again in the first exhaust passage 21, and also adsorbs moisture of the return air.

  Here, changes in the temperature and humidity of the air processed by the air conditioning system according to the present embodiment will be described along the numbers with ◯ shown in FIGS. 2 and 3.

First, a description will be given of the period until outside air is introduced into the system and supplied.
(1) When outside air is introduced into the equipment casing 1 (FIG. 1) (number 1 with a circle in FIGS. 2 and 3), the temperature is 33 ° C. and the absolute humidity is 19.5 g / kg.
(2) The outside air that has passed through the total heat exchanger 3 and has undergone total heat exchange is dehumidified to an absolute humidity of 10.5 g / kg (number 2 with a circle). Regarding the return air that is totally heat-exchanged with the outside air, the heat of adsorption is generated when it passes through the desiccant rotor 4 and is substantially the same as the outside air temperature (numbers 4 → 5 with ○). The temperature of the outside air that has passed through the exchanger 3 hardly decreases.
(3) The outside air that has passed through the total heat exchanger 3 is cooled to a target temperature of 26 ° C. by the cold water coil CC (numeral 3 with a circle) and supplied to the room.

Next, a description will be given of how the return air is introduced into the system and exhausted.
(4) The return air flowing into the first exhaust passage 21 from the room is under substantially the same conditions as the supply air, and has a temperature of about 26 ° C. and a humidity of about 50% (absolute humidity of about 10.5 g / kg). It is low-temperature and low-humidity air (number 4 with a circle).
(5) The return air passes through the dehumidifying region of the desiccant rotor 4 and is further dehumidified to become an absolute humidity of approximately 8.5 g / kg (number 5 with a circle), and the first exhaust passage of the total heat exchanger 3 Pass through the area facing 21. As described above, at this time, the temperature of the return air is substantially equal to the outside air temperature due to the heat of adsorption.
(6) The return air that has been totally heat-exchanged with the outside air in the total heat exchanger 3 receives moisture and has an absolute humidity of approximately 17 g / kg (number 6 with a circle).
(7) Since the return air is in a hot and humid state, the relative humidity is lowered to about 28% by heating to about 47 ° C. with the hot water coil HC (number 7 with a circle), and the dehumidifying region of the desiccant rotor 4 Pass through.
(8) Since the dehumidifying performance of the desiccant rotor 4 depends on the relative humidity of the exhaust gas , which is the regeneration air, the desiccant rotor 4 is regenerated by the return air that has passed through the dehumidifying region and has a reduced relative humidity. At this time, the exhaust receives moisture from the desiccant rotor 4 and is discharged as air having substantially the same humidity as the outside air indicated by the numeral 1 with a circle (circled numeral 8).

  As described above, according to the present embodiment, the desiccant rotor 4 itself needs only a small amount of dehumidification, so the temperature of the regenerated air to be regenerated may be as low as about 50 ° C. Further, if the amount of dehumidification by the desiccant rotor 4 is small, the amount of heat of adsorption is naturally reduced, so that the return air that has passed through the dehumidification region of the desiccant rotor 4 rises from about 26 ° C. to about 7 ° C. Since it becomes substantially equal to 33 ° C., as shown by “i” in FIG. 2, the amount of cooling energy is also reduced in the air conditioning system according to the present embodiment. It can be seen that this may be ½ of the conventional cooling energy (I1 + I2) shown in FIG.

  FIG. 4 shows the relationship between the regeneration temperature of the desiccant rotor 4 and the area of the regeneration region. As in the embodiment described above, when the regeneration temperature is 50 ° C. or when the regeneration temperature is 55 ° C. as shown in FIG. 4A, the area ratio of the regeneration region to the dehumidification region is 1: 1, that is, the reproduction area is ½ of the rotor area. However, when the reproduction temperature is set to 80 ° C. by a heating means such as a hot water coil HC, the reproduction area has a rotor area as shown in FIG. There is a possibility that it can be reduced to 1/4.

  In FIG. 4B, the obstacle wall 5 having a predetermined height is erected from the bottom surface of the second exhaust flow path 22 so as to block the front and rear of the lower half of the desiccant rotor 4 facing the second exhaust flow path 22. Thus, the flow path is narrowed, but the desiccant rotor 4 itself can be configured to have a small diameter. If such a small desiccant rotor 4 can be used, the equipment casing 1 can be downsized, and a more compact air conditioning system can be realized.

  That is, in the air conditioning system according to the present embodiment shown in FIGS. 1 and 4A, the dimensions of the equipment casing 1 are 3500 mm in length, 3200 mm in height, and 2000 mm in width, and the total heat exchanger 3 and the desiccant rotor are used. 4 is 1500 mm. However, as shown in FIG. 4B, when the area of the regeneration region of the desiccant rotor 4 is about 1/4 of the rotor area, the dimensions of the casing 1 for equipment are long. The height is 3500 mm, but the height can be reduced to 2750 mm and the width can be reduced to about 1700 mm.

(Second Embodiment)
FIG. 5 is a state diagram of air in the air conditioning system according to the second embodiment, and FIG. 6 is a schematic explanatory diagram showing the basic configuration of the air conditioning system. In this embodiment, the condenser COND, the evaporator EVAP, As an air conditioning system that includes a compressor COMPR and incorporates a heat pump HP that uses gas as a heat medium, the desiccant rotor 4 can be regenerated using the exhaust heat of the heat pump HP. In the air conditioning system according to the second embodiment, as in the first embodiment, each device is disposed in the rectangular box-shaped equipment casing 1, and the evaporator EVAP is disposed in the air supply passage 20. The compressor COMPR and the condenser COND are disposed in the exhaust passage (the first exhaust passage 21 or the second exhaust passage 22). In the first embodiment described above, the cold / hot water coil CHC and the hot water coil HC function as “heat exchangers”, but here, the evaporator EVAP and the condenser COND serve as “heat exchangers”. It is functioning.

  As can be seen from FIG. 5, changes in the temperature and humidity of the air processed by the air conditioning system according to this embodiment are the same as those in the first embodiment (see FIG. 2).

  That is, when the outside air (number 1 with a circle) when introduced into the equipment casing 1 has a temperature of 33 ° C. and an absolute humidity of 19.5 g / kg, the total heat exchange is performed through the total heat exchanger 3. Dehumidified to an absolute humidity of 10.5 g / kg (number 2 with o). And it cools to 26 degreeC which is the target temperature through the evaporator EVAP of heat pump HP (circled number 3), and is supplied indoors through the air blower S-FAN.

On the other hand, the return air flowing into the first exhaust passage 21 from the room is under substantially the same conditions as the supply air, and is a low temperature with an air temperature of about 26 ° C. and a humidity of about 50% (absolute humidity of about 10.5 g / kg). It is low humidity air (circled number 4). The return air passes through the dehumidifying region of the desiccant rotor 4 and is further dehumidified to become an absolute humidity of approximately 8.5 g / kg (number 5 with a circle), and the first exhaust passage 21 of the total heat exchanger 3. Pass through to the area facing you. As described above, at this time, the temperature of the return air is substantially equal to the outside air temperature due to the heat of adsorption.

  The return air that has undergone total heat exchange with the outside air in the total heat exchanger 3 receives moisture and has an absolute humidity of approximately 17 g / kg (number 6 with a circle). The return air is heat-exchanged by the condenser COND by the gas compressed by the compressor COMPR of the heat pump HP and heated to a temperature of about 47 ° C. At this time, the relative humidity is reduced to about 28% (number 7 with a circle), and in that state, the relative humidity is passed through the dehumidifying region of the desiccant rotor 4.

Exhaust that has passed through the desiccant rotor 4 receives water from the desiccant rotor 4, become the air with outside air and substantially the same humidity indicated by ○ subscripts 1 (○ subscripts 8) is discharged. The exhaust temperature is about 41 ° C.

  As described above, the desiccant rotor 4 itself can be dehumidified in this embodiment as well, so that the temperature of the regenerated air to be regenerated can be as low as about 50 ° C., and the amount of cooling energy can be reduced. Thus, the present invention can utilize the low-temperature exhaust heat of the heat pump HP.

(Modification of the second embodiment)
FIG. 7 is a state diagram of air in an air conditioning system according to a modification of the second embodiment, and FIG. 8 is a schematic explanatory diagram showing a basic configuration of the air conditioning system.

  In this modification, the evaporator EVAP of the heat pump HP is arranged in the first exhaust flow path 21 so that the desiccant rotor 4 can be regenerated at a lower temperature.

  Hereinafter, changes in the temperature and humidity of the air processed by the air conditioning system will be described along the numerals with circles shown in FIGS. 7 and 8. In this case as well, the outside air (number 1 with ○) when introduced into the equipment casing 1 has a temperature of 33 ° C. and an absolute humidity of 19.5 g / kg.

The outside air introduced into the equipment casing 1 passes through the total heat exchanger 3 and undergoes total heat exchange to be dehumidified to an absolute humidity of 10.5 g / kg, and is cooled to approximately 26 ° C. (number 2 with a circle). ), And supplied to the room through the air supply fan S-FAN.
At this time, the return air that is totally heat-exchanged with the outside air is cooled to about 17 ° C. by the evaporator EVAP (numbers 3 → 4 with ○), and then passes through the desiccant rotor 4 to rise in temperature to about 24 ° C. (Number 5 with a circle).

  The return air flowing into the first exhaust passage 21 from the room is under substantially the same conditions as the supply air (number 2 with a circle), the temperature is about 26 ° C., the humidity is about 50% (the absolute humidity is about 10.5 g / kg) of low-temperature, low-humidity air (number 3 with a circle).

Then, as described above, the return air is cooled to about 17 ° C. by the evaporator EVAP of the heat pump HP (circled number 4), passes through the dehumidifying region of the desiccant rotor 4, and is dehumidified to have an absolute humidity of about 8 .5 g / kg (circled number 5). At this time, the temperature of the return air becomes approximately 24 ° C. due to the heat of adsorption.

  The return air having an absolute humidity of approximately 8.5 g / kg at approximately 24 ° C. passes through the region facing the first exhaust flow path 21 of the total heat exchanger 3 and is totally heat-exchanged with the outside air to receive moisture. It is about 17 g / kg (number 6 with a circle). At this time, the temperature rises to about 31 ° C.

  Thereafter, the return air is heat-exchanged by the condenser COND by the gas compressed and heated by the compressor COMPR of the heat pump HP, and the temperature rises to about 37 ° C. (number 7 with ○). At this time, the relative humidity is approximately 42%, and the dehumidifying area of the desiccant rotor 4 is passed in this state.

Exhaust that has passed through the desiccant rotor 4 receives water from the desiccant rotor 4, are discharged as air with outside air and substantially the same humidity indicated by ○ subscripts 1 (absolute humidity 19.5 g / kg) (○ Number 8). The exhaust temperature is about 31 ° C.

  As described above, in this modified example, the exhaust heat released into the atmosphere is suppressed to about 31 ° C., which can contribute to the suppression of heat island formation, which is a social problem. In this case, the desiccant rotor 4 can be regenerated at a temperature lower than 40 ° C.

(Third embodiment)
FIG. 9 is an air state diagram in the air conditioning system according to the third embodiment, and FIG. 10 is a schematic explanatory diagram showing a basic configuration of the air conditioning system.
In this embodiment, instead of the heat pump HP used in the modification of the second embodiment described with reference to FIGS. 7 and 8, before introducing the return air from the room into the desiccant rotor 4 and dehumidifying it, While cooling with the cold water coil CC previously, the hot water coil HC is utilized as a heating means at the time of reproducing | regenerating the desiccant rotor 4. FIG. Therefore, as can be seen from FIG. 9, changes in the temperature and humidity of the air processed by the air conditioning system according to the present embodiment are the same as those in FIG. 7.

  That is, when outside air having a temperature of 33 ° C. and an absolute humidity of 19.5 g / kg is introduced into the equipment casing 1 (number 1 with ○), the total heat is exchanged through the total heat exchanger 3 and the absolute humidity is 10 It is dehumidified to 0.5 g / kg, cooled to approximately 26 ° C. (number 2 with ○), and supplied to the room via the air supply fan F1.

  On the other hand, the return air flowing into the first exhaust passage 21 from the room is under substantially the same conditions as the supply air (number 2 with a circle), the temperature is about 26 ° C., the humidity is about 50% (the absolute humidity is about 10.). 5 g / kg) of low-temperature and low-humidity air (number 3 with a circle).

Then, the return air is cooled to about 17 ° C. by the cold water coil CC (number 4 with ○), passes through the dehumidification region of the desiccant rotor 4, and is dehumidified to an absolute humidity of about 8.5 g / kg (○ Number 5). At this time, the temperature of the return air becomes approximately 24 ° C. due to the heat of adsorption.

  The return air having an absolute humidity of approximately 8.5 g / kg at approximately 24 ° C. passes through the region facing the first exhaust flow path 21 of the total heat exchanger 3 and is totally heat-exchanged with the outside air to receive moisture. It is about 17 g / kg (number 6 with a circle). At this time, the temperature rises to about 31 ° C.

  Thereafter, the return air is heated by the hot water coil HC, and the temperature rises to about 37 ° C. (number 7 with ○). At this time, the relative humidity is approximately 42%, and the dehumidifying area of the desiccant rotor 4 is passed in this state.

Exhaust that has passed through the desiccant rotor 4 receives water from the desiccant rotor 4, are discharged as air with outside air and substantially the same humidity indicated by ○ subscripts 1 (absolute humidity 19.5 g / kg) (○ Number 8). The exhaust temperature is about 31 ° C., and in this case as well, it is possible to suppress the increase in the exhaust heat released into the atmosphere.

  As mentioned above, although this invention was demonstrated through each embodiment mentioned above, this invention is not limited to each embodiment, As long as it does not deviate from the summary of invention, you may change a design suitably. As described above, the air conditioning system according to the present invention exhibits a very large energy saving effect during the cooling operation in summer, but the operation of the desiccant rotor 4 necessary for the cooling operation in summer and the desiccant rotor 4 By stopping the operation of the hot water coil HC (see FIG. 3) used for the regeneration, the air conditioning system can be used without any problem even in winter operation.

(Fourth embodiment)
FIG. 11 is a state diagram of air in the air conditioning system according to the fourth embodiment, and FIG. 12 is a schematic explanatory diagram showing a basic configuration of the air conditioning system.
In the present embodiment, each device is disposed in a rectangular box-shaped equipment casing 1, and a hot water coil HC made of a copper tube is disposed on the downstream side of the total heat exchanger 3, and heating means for supplying air is provided. As described above, an antifreeze or brine is passed through the hot water coil HC, and a cold water coil CC made of a copper tube is disposed immediately upstream of the desiccant rotor 4 in the exhaust passage (second exhaust passage 22) to cool the exhaust water. and means, in the cold water coils CC, through antifreeze or brine, with a change in relative humidity between the return air dehumidification area of the desiccant rotor 4 and the exhaust of the reproduction region, the desiccant rotor by utilizing the relative humidity The exhaust gas is humidified in the regeneration region 4.

  As shown in FIG. 11, when the outside air (number 1 with ○) when introduced into the equipment casing 1 is at a temperature of 0 ° C. and an absolute humidity of 2 g / kg, it passes through the total heat exchanger 3 to perform total heat exchange. Then, it is humidified to an absolute humidity of 8 g / kg (number 2 with a circle). And it heats to 22 degreeC which is the target temperature through the hot water coil HC (number 3 with (circle)), and is supplied indoors through the air blower S-FAN.

  On the other hand, the return air that flows into the first exhaust passage 21 from the room is under substantially the same conditions as the supply air, and has a high temperature and high humidity with a temperature of about 22 ° C. and a humidity of about 50% (absolute humidity of about 8 g / kg). (The number 3 with a circle). The return air that has passed through the desiccant rotor 4 receives moisture from the desiccant rotor 4 and has an absolute humidity of approximately 9.5 g / kg (number 4 with a circle), and the first exhaust flow of the total heat exchanger 3 Pass through the area facing the road 21.

  The return air that has undergone total heat exchange with the outside air in the total heat exchanger 3 is dehumidified to an absolute humidity of approximately 3.5 g / kg (number 5 with a circle). And it cools by the cold water coil CC and temperature falls to about 0 degreeC. At this time, the relative humidity rises to about 100% (number 6 with a circle), and passes through the dehumidifying region of the desiccant rotor 4 in this state.

Exhaust gas that has passed through the desiccant rotor 4 is dehumidified by the desiccant rotor 4, and is discharged as air having substantially the same humidity as the outside air indicated by the number 1 with ◯ (number 7 with ◯). The exhaust temperature is about 4 ° C.

  As described above, in the present embodiment, the desiccant rotor 4 humidifies the return air passing through the exhaust passage (first exhaust passage 21), so that the outside air passing through the air supply passage 20 is converted into the total heat exchanger 3. Is humidified. Thus, according to the present embodiment, during the heating in winter, the desiccant rotor 4 can be used to heat the outside air and humidify it.

In particular, by using the desiccant rotor 4, moisture in the exhaust gas passing through the exhaust passage (second exhaust passage 22) is absorbed, and the absorbed moisture is passed through the exhaust passage (first exhaust passage 21). and releases moisture into the return air to pass through. Thus for moisture release and return air and supply air that passes through the exhaust passage (first exhaust passage 21) to the air supply by converting total heat, external Therefore, it is possible to perform humidification without water supply without newly supplying water.

  By the way, when cold water is used as a cooling means in the cold water coil CC when the temperature is low in winter or the like (for example, 0 ° C. or lower), the cold water expands by freezing into ice, and the copper of the cold water coil CC Although the tube may be broken and water leaks, in this embodiment, since the antifreeze or brine is used as the cooling means, the air exchanger without damaging the heat exchanger composed of the copper tube or the like of the cold water coil CC is used. The harmony system can be operated.

In addition, the heat pump HP mentioned above can also be integrated with respect to the air conditioning system of 4th Embodiment. For example, when a heat pump is incorporated into the air conditioning system of the fourth embodiment, the compressor COMPR and the condenser COND are arranged in the air supply passage 20 and the exhaust passage (the first exhaust passage 21 or the second exhaust passage). The evaporator EVAP is arranged in the exhaust passage 22). In this case, it is possible to use the low-temperature exhaust heat of the heat pump HP. In addition, by incorporating a heat pump HP using a gas as a heat medium, even if the temperature is low, heat exchangers such as the evaporator EVAP and the condenser COND are not damaged. without using a cooling means, the exhaust passing through the exhaust passage (the second exhaust passage 22) can be cooled.

  By the way, when the brine is passed through the cooling coil CC, it is necessary to pass the brine not only in the cold water coil CC but also in the piping of the entire air conditioning system such as the hot water coil HC, and further, equipment other than the air conditioning system. Since the brine (for example, heat source) also needs to be specified in order to use the brine, the equipment costs of the air conditioning system and other equipment are increased. Therefore, in this embodiment, since the heat pump HP is incorporated in the air conditioning system, there is no need to pass brine through the piping of the entire air conditioning system or to make the equipment of the air conditioning system to be a brine specification. And the equipment cost of other equipment can be reduced.

(Modification of the fourth embodiment)
FIG. 13 is a state diagram of air in an air conditioning system according to a modification of the fourth embodiment, and FIG. 14 is a schematic explanatory diagram showing a basic configuration of the air conditioning system.

In this modification, each device is disposed in a rectangular box-shaped equipment casing 1, and a hot water coil HC is disposed in an exhaust flow path (first exhaust flow path 21) so that the first exhaust flow path 21 is formed. As heating means for the return air passing therethrough, an antifreeze or brine is passed through the hot water coil HC, and a chilled water coil CC is disposed immediately upstream of the desiccant rotor 4 in the exhaust passage (second exhaust passage 22). As cooling means for exhaust gas passing through the second exhaust flow path 22, antifreeze or brine is passed through the cold water coil CC, and the dehumidification area return air and regeneration area of the desiccant rotor 4 are the same as in the fourth embodiment. with a change in relative humidity between the exhaust, and to perform the humidification of the exhaust in the regeneration zone of the desiccant rotor 4 by utilizing the relative humidity.

  As can be seen from FIG. 13, changes in the temperature and humidity of the air processed by the air conditioning system according to this embodiment are the same as those in the second embodiment (see FIG. 11).

  That is, when the outside air (number 1 with a circle) when introduced into the equipment casing 1 is at a temperature of 0 ° C. and an absolute humidity of 2 g / kg, the absolute humidity is obtained when the total heat is exchanged through the total heat exchanger 3. It is humidified to 8 g / kg (number 2 with a circle). Then, the air is supplied into the room via the air supply fan S-FAN.

  On the other hand, the return air that flows into the first exhaust passage 21 from the room is under substantially the same conditions as the supply air, and has a high temperature and high humidity with a temperature of about 22 ° C. and a humidity of about 50% (absolute humidity of about 8 g / kg). (The number 3 with a circle). The return air is heated to a target temperature of 29 ° C. via the hot water coil HC (numeral 4 with a circle), and the return air that has passed through the desiccant rotor 4 receives moisture from the desiccant rotor 4 and has an absolute humidity. It becomes approximately 9.5 g / kg (number 5 with a circle) and passes through the region facing the first exhaust flow path 21 of the total heat exchanger 3.

  The return air that has undergone total heat exchange with the outside air in the total heat exchanger 3 is dehumidified to an absolute humidity of approximately 3.5 g / kg (number 6 with a circle). And it cools by the cold water coil CC and temperature falls to about 0 degreeC. At this time, the relative humidity rises to about 90% (number 7 with a circle), and in that state, the relative humidity is passed through the dehumidifying region of the desiccant rotor 4.

Exhaust gas that has passed through the desiccant rotor 4 is dehumidified by the desiccant rotor 4 and is discharged as air having substantially the same humidity as the outside air indicated by the number 1 with ◯ (number 8 with ◯). The exhaust temperature is about 4 ° C.

As described above, as in the air conditioning system of the fourth embodiment, in this modified example, the desiccant rotor 4 humidifies the return air passing through the exhaust passage (first exhaust passage 21). The outside air passing through the passage 20 is humidified by the total heat exchanger 3. As described above, according to the present modification, the outside air can be heated and humidified using the desiccant rotor 4 during heating in winter. In particular, by using the desiccant rotor 4, moisture in the exhaust gas passing through the exhaust passage (second exhaust passage 22) is absorbed, and the absorbed moisture is passed through the exhaust passage (first exhaust passage 21). and releases moisture in the return air to pass through. Thus for moisture release and return air and supply air that passes through the exhaust passage (first exhaust passage 21) to the air supply by converting total heat, external Therefore, it is possible to perform humidification without water supply without newly supplying water.

  When the heat pump HP is incorporated into the air conditioning system according to the modification of the fourth embodiment, the compressor COMPR and the condenser COND of the heat pump HP are arranged in the first exhaust passage 21. In this case, it is possible to use the low-temperature exhaust heat of the heat pump HP. Thereby, the same effect as the air conditioning system of the fourth embodiment described above can be obtained.

(Reference example)
As a reference example, the case where the present air conditioning system is used for a heating operation in winter without operating the desiccant rotor 4 will be briefly described with reference to FIGS. 15 and 16. Again, changes in the temperature and humidity of the air will be described along the numbers with a circle in the figure. Here, a cold / hot water coil CHC is disposed downstream of the total heat exchanger 3, and hot water is passed through the cold / hot water coil CHC as heating means for supplying air.

  If the outdoor temperature in winter is approximately 2 ° C. and the absolute humidity is 2.5 g / kg (number 1 with ○), the external air that has been totally heat-exchanged through the total heat exchanger 3 is humidified to an absolute humidity of 7 g / kg. The outside air that has passed through the total heat exchanger 3 is heated to approximately 22 ° C., which is the target temperature, by warm water flowing through the cold / hot water coil CHC. Then, it is supplied into the room as conditioned air humidified to a relative humidity of about 50% (absolute humidity is about 8.5 g / kg) by the humidifier HU (number 4 with a circle).

  On the other hand, the return air flowing into the first exhaust passage 21 from the room is under substantially the same conditions as the supply air (number 5 with a circle), and the return air passes through the dehumidification region of the desiccant rotor 4. Since the desiccant rotor 4 is not operated and the dehumidifying function remains stagnant, the state of the return air after passing through the rotor is not changed from that before passing (number 5 with ○).

  Therefore, the return air having a temperature of about 22 ° C. and an absolute humidity of about 8.5 g / kg passes through the region facing the first exhaust passage 21 of the total heat exchanger 3 and is totally heat-exchanged with the outside air to release moisture. While the absolute humidity is about 4 g / kg, it is cooled to about 7 ° C. (number 6 with ○).

Such return air may be discharged as it is, but as shown in FIG. 16, the second exhaust passage 22 is provided with a hot water coil HC so that it can be used even in the summer. Then, the return air heat-exchanged in the total heat exchanger 3 is exhausted through the desiccant rotor 4 after bypassing the hot water coil HC. Here, since the function of the desiccant roller 4 is also stopped, it is natural that the desiccant rotor 4 may be bypassed and exhausted.

  By the way, as the cold water coil CC used in the embodiment, a cold / hot water coil CHC that passes cold water in the summer and hot water in the winter may be used, or the hot water coil HC used for regeneration of the desiccant rotor 4 is It can be replaced with a steam coil. As described in the second embodiment, when the heat pump HP is used, the cold water coil CC and the cold / hot water coil CHC can be replaced with the evaporator EVAP, and the hot water coil HC can be replaced with the condenser COND.

From the embodiment described above, the following air conditioning method and air conditioning system can be realized.
(1) An air conditioning method in which the outside air and the return air from the room are totally exchanged by the total heat exchanger 3 and the outside air after the total heat exchange is supplied to the room, wherein the outside air is converted into the total heat exchanger. 3. An air conditioning method in which the return air is introduced into the total heat exchanger 3 after being dehumidified in advance using a desiccant rotor 4 while being directly introduced into the air.

  (2) An air supply passage 20 that takes in outside air and supplies it into the room, and an exhaust passage (for example, a first exhaust passage 21 and a second exhaust passage 22) that exhausts the return air from the room to the outside of the system. ), A total heat exchanger 3 having a rotor that stores heat and absorbs moisture on the air supply channel 20 side, and radiates and releases moisture on the exhaust channel side, and is disposed in the middle of the exhaust channel, and the return air And a desiccant rotor 4 that dehumidifies in advance before passing through the total heat exchanger 3.

(3) In the total heat exchanger 3, the outside air of the air supply passage 20 passing through the rotor and the return air of the exhaust passage (for example, the first exhaust passage 21) form a counter flow. As described above, the exhaust passage is disposed so as to straddle the supply passage 20 and the exhaust passage, and the exhaust passage includes the first exhaust passage 21 leading to the total heat exchanger 3 and the entire exhaust passage. consists second exhaust flow path 22 for toward the flow path end through the heat exchanger 3, the desiccant rotor 4, said the air instead of the first exhaust passage 21 passing through the desiccant rotor 4 a as 2 with the exhaust the exhaust passage 22 to form a counter flow, is arranged so as to extend in the first exhaust passage 21 and the second exhaust flow path 22, in the first exhaust passage 21 side An air conditioning system that absorbs moisture while releasing moisture on the second exhaust flow path 22 side.

  (4) The air conditioning system in which the air supply channel 20 and the exhaust channel (for example, composed of the first exhaust channel 21 and the second exhaust channel 22) are independent channels that are partitioned from each other.

  (5) An air-conditioning system including a heat pump HP for temperature control, and using the exhaust heat of the heat pump HP as a heat source for regeneration of the desiccant rotor 4.

It is explanatory drawing at the time of having installed the air-conditioning system of this invention. It is an air state diagram in the air-conditioning system concerning a 1st embodiment. It is a typical explanatory view showing the basic composition of the air-conditioning system. It is explanatory drawing which shows the relationship between the reproduction | regeneration temperature of a desiccant rotor, and the area of a reproduction | regeneration area | region. It is an air state diagram in the air-conditioning system concerning a 2nd embodiment. It is a typical explanatory view showing the composition of the air-conditioning system. It is a state line figure of the air in the air-conditioning system concerning the modification of a 2nd embodiment. It is a typical explanatory view showing the composition of the air-conditioning system. It is an air state diagram in the air-conditioning system concerning a 3rd embodiment. It is a typical explanatory view showing the composition of the air-conditioning system. It is an air state diagram in the air-conditioning system concerning a 4th embodiment. It is a typical explanatory view showing the basic composition of the air-conditioning system. It is a state line figure of air in an air-conditioning system concerning a modification of a 4th embodiment. It is a typical explanatory view showing the basic composition of the air-conditioning system. It is a state line diagram of the air as a reference example which uses the air-conditioning system of this invention in winter. It is a typical explanatory view showing the basic composition of the air-conditioning system. It is a typical block diagram of the conventional air conditioning system. It is a state line diagram of the air in the conventional air conditioning system. It is explanatory drawing which shows the structural example of the conventional air conditioning system.

DESCRIPTION OF SYMBOLS 1 Equipment casing 3 Total heat exchanger 4 Desiccant rotor 20 Supply air flow path 21 1st exhaust flow path 22 2nd exhaust flow path

Claims (2)

An air supply passage for taking in outside air and supplying it into the room;
A first exhaust passage for introducing return air from the room;
A second exhaust passage for exhausting the return air from the first exhaust passage out of the system;
While you winter seasons are wet discharge in the air-supply flow path side, said first winter season in the exhaust flow path is the total heat exchanger having a rotor you moisture absorption,
A desiccant rotor disposed in the middle of the first exhaust flow path,
The exhaust flow path and the air supply flow path configured by the first exhaust flow path and the second exhaust flow path are independent flow paths partitioned from each other through a partition wall in a rectangular box-shaped equipment casing. ,
The downstream end of the first exhaust passage and the upstream end of the second exhaust passage are connected by a hairpin curve,
The total heat exchanger is arranged so that one half of the heat exchanger faces the upstream side of the air supply flow path and the other half of the heat exchanger faces the first exhaust flow path upstream of the hairpin curve via the partition wall. ,
The desiccant rotor has one half portion facing the upstream side of the other half portion of the total heat exchanger located on the first exhaust passage, and the other half portion is the first exhaust passage. Is arranged so as to face the downstream side of the second exhaust flow path folded back by the hairpin curve through the partition wall,
In addition, a hot water coil made of a copper tube is disposed downstream of the total heat exchanger, and antifreeze is passed through the hot water coil as heating means for supplying air, and copper is directly upstream of the desiccant rotor in the second exhaust passage. A chilled water coil consisting of a tube is arranged to serve as a cooling means for exhaust, and is configured to pass antifreeze liquid through the chilled water coil, and the relative humidity of the exhaust is changed between the dehumidifying region and the regeneration region of the desiccant rotor, It is configured to humidify the exhaust in the regeneration region of the desiccant rotor using the relative humidity of the exhaust, and absorbs moisture in the return air passing through the second exhaust channel using the desiccant rotor during heating in winter. The moisture absorbed is released into the return air passing through the first exhaust flow path, enabling non-supply water humidification without supplying water from the outside, and incorporating a heat pump using gas as a heat medium. Air conditioning system, characterized in that the air intake passage to be disposed compressor and a condenser, was it possible to utilize low temperature waste heat of the heat pump by arranging the evaporator in the exhaust passage. The total heat exchanger has the supply air flow path and the first exhaust flow so that the outside air of the supply air flow path passing through the rotor forms a counter flow with the return air of the first exhaust flow path. It is arranged to straddle the road,
The desiccant rotor includes the first exhaust passage and the second exhaust so that the return air of the first exhaust passage passing through the desiccant rotor and the exhaust of the second exhaust passage form a counter flow. is arranged so as to extend in the flow path, winter season in the first exhaust flow path whereas the moisture release, winter season in the second exhaust flow path is an air conditioner according to claim 1, wherein the moisture absorption system.

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