JPH10197010A - Air conditioner and air conditioning system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioning system in which fresh air is processed with sharp energy saving and the running cost is reduced by employing a heat pump, a desiccant, and a whole heat exchanger. SOLUTION: In a first air passage A, air on the first air passage introduced from a first space into an air conditioner and a desiccant 103 are brought into contact for dehumidification and is then whole heat exchanged with air on a second air passage B in a whole heat exchanger 153. Further, the air on the first air passage after the whole heat exchange is heated with a high heat source 220 of a heat pump 200 and is then passed through the desiccant 103 for dehumidification and regeneration of the desiccant, and is released from the air conditioner into a second space.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioning system, and more particularly to an air conditioning system that uses an air conditioner that circulates and processes indoor air and an air conditioner (external air conditioner) that processes outside air and guides the air into the room. About.

[0002]

2. Description of the Related Art FIG. 6 shows an example of a conventional air conditioning system, which includes an air conditioner 3 which circulates and processes indoor air and an air conditioner (an external conditioner) which processes outside air and guides it to a room. ) 11
This is an air conditioning system that uses both. The external conditioner is a total heat exchanger (enthalpy heat exchanger), and simultaneously exchanges the humidity and sensible heat between the outside air and the indoor air. On the other hand, the air-conditioning load generated inside the air-conditioned space is taken out by an indoor air conditioner (air conditioner using a heat pump) and discarded outside the room.

[0003]

The operation of the total heat exchanger as described above will be described with reference to a psychrometric chart shown in FIG. 7, in which the outside air (state K) and the indoor air (state Q) are enthalpy during cooling. After the replacement, the processing outside air becomes the state L and the indoor exhaust becomes the state T, so that the air is supplied to the room and the air is exhausted to the outside. At this time, the enthalpy exchange efficiency of the current product is practically low at 60 to 70% with the current product, so an enthalpy difference ΔH occurs between the supply air (state L) and the room (state Q), and as a result, the air Air having a difference in absolute humidity (moisture difference ΔX) is supplied into the room, and 30 to 40% of the moisture difference between the untreated outside air and the room enters the room. Since this moisture must be dehumidified by an air conditioner, it is necessary to cool the room air to a dew point temperature (15 to 16 ° C.) of about 5 to 10 ° C. to dehumidify the air.

Among the air conditioning loads, the latent heat load required for dehumidification accounts for 10 to 15% of the total air conditioning load when a total heat exchanger is used, and the remaining 85 to 90% is a sensible heat load. This sensible heat air conditioning load does not need to be cooled to the dew point,
It is enough air-conditioning load if cooled to the extent. However, in the conventional air conditioning system, the sensible heat and the latent heat are collectively processed by mixing the introduced outside air with the room air, so that all the heat is cooled at a temperature level below the dew point temperature of about 10 ° C. It is necessary to set the difference (temperature head) between the evaporation temperature and the condensation temperature of the air conditioner the same as when the total heat exchanger is not used, and the air conditioning load can be reduced, but the temperature head for pumping up the heat cannot be reduced.

As described above, in the prior art, since the high temperature head is pumped up and discarded outside, the driving energy of the heat pump for the sensible heat load processing is wasted and the energy consumption rate is large. In addition, in an air conditioner, it is necessary to provide a drain in order to treat dew condensation for dehumidification, which has led to complication of the equipment.

[0006]

Means for Solving the Problems The present invention has been made to solve the above-mentioned problems, and the invention according to claim 1 is a first air path from a first space to a second space. A second air path extending from the second space to the first space; a desiccant disposed in the first air path to repeat adsorption of moisture in flowing air and regeneration by air after heating; A heat pump for providing a high heat source for desiccant regeneration in the first air path and a low heat source for cooling air in the second air path; and a heat source for the heat pump in each of the first air path and the second air path. A total heat exchanger for exchanging heat between air before contacting the air, and the first air path connects the air in the first air path introduced from the first space to the air conditioner with the desiccant. After contact and dehumidification, The heat exchanger performs total heat exchange with the air in the second air path, and further heats the air in the first air path after the total heat exchange by the high heat source of the heat pump, and then passes through the desiccant to remove the desiccant. The air conditioner is configured to perform wet regeneration and discharge the moisture from the air conditioner to a second space.

In such a configuration, during cooling, the first space is used as an air-conditioned space, the indoor air is used as a first air path, the second space is used as an outdoor space, and outside air is used as a second air path. In this case, the air (processed outside air) supplied into the room from the second air path can be made to have an absolute humidity lower than that of the room air, so that moisture does not have to be brought into the room. Therefore, there is no need to dehumidify with an air conditioner,
The operating temperature head of the heat source refrigeration cycle of the air conditioner (air conditioner) can be reduced, and significant energy savings can be achieved. In addition, since it is not necessary to dehumidify in an air conditioner, a drain for dew condensation is not required.

According to a second aspect of the present invention, the desiccant and the total heat exchanger are integrally formed by using the same desiccant to form a desiccant assembly, and the desiccant assembly and air in the first and second air paths. Contacting the desiccant assembly with air of a first air path introduced from a first space; and air and desiccant assembly of a second air path introduced from a second space. A third step of bringing the air of the first air path into contact with the desiccant assembly after the first step, and a step of bringing the air of the first air path after the third step into contact with the heat pump. After heating by a high heat source, passing through the desiccant assembly to perform a dehumidifying regeneration of the desiccant assembly in the fourth step, and then returning to the first step again, a cycle is constituted. Claims Is an air-conditioner as set forth in.

In such a configuration, the contact between the desiccant and the first and second air paths can be performed as a continuous cycle, smooth operation can be performed, and the invention according to claim 1 can be realized. Similar effects can be obtained.

According to a third aspect of the present invention, the desiccant assembly has a rotor shape, and the desiccant assembly circulates in each air path by rotating the rotor. The air conditioner according to the above.

The invention according to a fourth aspect is the air conditioner according to any one of the first to third aspects, wherein a vapor compression heat pump is used as the heat pump.

The invention according to claim 5 is the air conditioner according to any one of claims 1 to 3, wherein an absorption heat pump is used as the heat pump.

According to a sixth aspect of the present invention, when the air conditioner according to any one of the first to fifth aspects is used for cooling,
Is used as an air-conditioning room, and the second space is used as an external space.

According to a seventh aspect of the present invention, when the air conditioner according to any one of the first to fifth aspects is used during heating,
An air-conditioning system is characterized in that the first space is used as an external space and the second space is used as an air-conditioning room.

An eighth aspect of the present invention is an air conditioning system characterized in that the air conditioner according to any one of the first to fifth aspects is used as an external controller, and an air conditioner for sensible heat treatment is additionally provided. In such a configuration, the outside air is introduced by the external air conditioner at the time of cooling, and the absolute humidity can be made lower than the indoor air that discharges the air supplied to the room from the second air path. No need to bring in. Therefore, there is no need to dehumidify the air conditioner as an air conditioning system, and the operating temperature head of the air conditioner can be reduced,
Significant energy savings are achieved. In addition, since it is not necessary to dehumidify in an air conditioner, a drain for dew condensation is not required.

The invention according to claim 9 is the air conditioner according to any one of claims 1 to 5, wherein the heat pump has a function of cooling a sensible heat load of the air-conditioned space. . In such a configuration, the sensible heat load of the air-conditioned space is recovered during cooling to perform desiccant dehumidification regeneration,
Since the desiccant enhances the dehumidifying effect and performs the latent heat treatment, a high cooling effect with energy saving can be obtained.

[0017]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of an air conditioning system according to the present invention will be described below with reference to FIGS. FIG. 1 shows a basic configuration of an air conditioning system according to the present invention. An air conditioner 3 circulates and processes air in a room 2 to be air conditioned, and an air conditioner (outside air conditioner) that processes outside air and guides the air into the room. This is an air-conditioning system that uses the air conditioning system 1 and the air conditioning system 1 in combination. The air conditioner 3 may be an ordinary air conditioner that switches between a refrigerator and a heat pump, but any other air conditioner may be used.

FIG. 2 is a first embodiment showing the configuration of the external tone controller of the present invention. The air conditioner 1 is a desiccant external air conditioner that uses the desiccant rotor 103, the total heat exchanger 153, and the heat pump 200, which repeats adsorption and release (regeneration) of moisture. That is, the desiccant external air conditioner 1 has a discharge path A (first air path) for discharging indoor air to the outside of the room.
And an introduction path B (second air path) for introducing outside air into the room. The total heat exchanger 153 and the desiccant rotor 1 extend between the indoor air discharge path A and the outside air introduction path B over both paths.
And a heat pump 200 serving as a heat source of the desiccant external controller 1. As the heat pump, an arbitrary one may be employed. For example, a vapor compression heat pump proposed by the present applicant in Japanese Patent Application No. 8-22313 may be used.

The discharge path A (first air path) for discharging indoor air to the outside of the room is formed by a path 124 between an exhaust outlet (shown as a symbol RA) of the indoor space (first space) and a suction port of the blower 140. The outlet of the blower 140 is connected to the dehumidified air (process air) side of the desiccant rotor 103 via a path 125, and the outlet of the desiccant rotor 103 of the discharge path A on the dehumidified air side is connected via a path 126. To the total heat exchanger 153, and the total heat exchanger 153 of the discharge path A
The outlet is connected to a heater (high heat source) 220 of the heat pump via a path 127, and the outlet of the heater 220 of the discharge path A is connected to the regeneration air side of the desiccant rotor 103 via a path 128. The outlet of the desiccant rotor 103 on the regeneration air side is connected to the external space (second
The space is connected to an exhaust port (shown as EX). Thus, a cycle is formed in which room air is taken in and exhausted to the outside.

On the other hand, the outside air introduction route B is
Is connected to the suction port of the blower 102 for introducing outside air via the path 107, and the discharge port of the blower 102 is connected to the total heat exchanger 153 via the path 108, so that the total heat exchange of the introduction path B is performed. The outlet of the heater 153 is connected to the cooler (low heat source) 210 of the heat pump via the path 109, and the outside air introduction path
The outlet of the cooler (low heat source) 210 of B is connected to a supply port (shown as SA) to the indoor space (first space) via the path 110. This forms a cycle in which outside air is taken in, processed, and introduced into the room.

The heat medium (hot water or refrigerant) inlet of the heater 220 is connected to the heat medium path outlet of the heat pump 200 via a path 221, and the hot water outlet of the heater 220 is connected to the heat medium path of the heat pump via a path 222. Connect to the entrance. The heat medium path entrance of the cooler 210 is a path 2
11, connected to the heat medium path outlet of the heat pump,
The cold water outlet of the cooler 210 is connected to the heat medium path inlet of the heat pump via the path 212. In the figure, circled alphabets K to V are symbols indicating the state of air corresponding to FIG. 3, where SA is supply air (processed outside air), RA is return air (exhausted indoor air). ), OA represents outside air, and EX represents exhaust.

FIG. 3 is a psychrometric chart showing the operation of the desiccant external air conditioner using the heat pump constructed as described above as a heat source at the time of cooling, showing the operating state of the air conditioner of the embodiment of FIG. This will be described with reference to FIG.

The air released from the room (RA: state Q) is sucked into the blower 140 via the path 124, pressurized and flows into the desiccant rotor 103, where water is adsorbed in the isenthalpy process and the absolute humidity decreases (state). R). The discharged air with reduced humidity reaches the total heat exchanger 153, where it exchanges total heat with the outside air (state K), and connects the state K and the state R according to a known state change process of the total heat exchanger. The state changes along the top, the enthalpy rises, and the temperature and the absolute humidity increase (state S). The discharged air that has exited the total heat exchanger 153 is sent to a heater (high heat source) 220 of a heat pump,
Heated to 60 ° C., the relative humidity decreases (state U).
The discharge air having a decreased relative humidity is supplied to the desiccant rotor 103.
To remove water from the desiccant rotor (dehumidification regeneration: state V). The discharged air that has passed through the desiccant rotor 103 passes through a path 129 and is discarded outside as exhaust gas.

The introduced outside air (introduced air OA: state K) is sucked into the blower 102 via the path 107, and is boosted to reach the total heat exchanger 153 via the path 108, where the discharged air (state R) After the total heat exchange, the state changes along the straight line connecting the state K and the state R according to the known state change process of the total heat exchanger, the enthalpy decreases, and the temperature and the absolute humidity decrease (state L). . Air with reduced enthalpy and dehumidified and cooled (state L) is used as a heat pump cooler (low heat source) 2
10 and cooled to 15-20 ° C (state M).
The cooled discharged air is supplied to the indoor space via the path 110. The introduced air (supply air SA: state M) obtained in this way can make the enthalpy and the absolute humidity lower than those of the indoor space. That is, an enthalpy difference Δh and an absolute humidity difference Δx can be generated between the introduced air (air supply: state M) and the indoor space (state Q), thereby preventing moisture from being brought into the indoor space. At the same time, a cooling effect can be exerted by the enthalpy difference Δh.

The operation of the heat pump of the desiccant external regulator having the above-described structure will be described. The cooler 210 uses the heat pump to cool the introduced air and remove the sensible heat of the introduced air to reduce the enthalpy.
Further, the heater 220 has the function of heating the released air to lower the relative humidity and dehumidifying and regenerating the desiccant 103. By this dehumidifying and regenerating action, the desiccant restores the moisture absorbing ability, and causes the action of dehumidifying the discharged air in the state Q taken out of the room to the state R. ) Can be changed to lower temperature and lower humidity than in the room (state L).

Thus, by the action of the heat pump,
Since the heat removed by cooling the introduced air is heated and used again for desiccant regeneration, a significant energy saving effect can be obtained as compared with the case where separate cooling heat sources and heating sources are used. In the external air conditioner 1 of the present invention, the heat pump having a refrigeration effect of the amount of heat obtained by multiplying the enthalpy difference between the state L and the state M by the air flow rate can remove all the external air load into the room. If outside air is introduced without using the external air conditioner 1, a refrigerator having a cooling effect of calorific value obtained by multiplying the enthalpy difference between the state K and the state M by the air flow rate is required. A significant energy saving effect can be obtained.

Now, when the state M is designed to be equal to the state Q and the efficiency of the total heat exchanger is 70%, the line segment QR becomes parallel to the isenthalpy line. Therefore, the enthalpy of the point Q is the point R
Therefore, the enthalpy differences K to Q can be replaced by enthalpy differences K to R, and the enthalpy differences L to M can be replaced by enthalpy differences L to R. Therefore, enthalpy difference (K to Q): enthalpy difference (L to M) = enthalpy difference (K to R): enthalpy difference (L to R) = 10: 3. That is, the refrigerating capacity of the heat pump is 3/10 of the refrigerating capacity that covers the outside air load when the external air conditioner 1 is not used.
, And 70% energy saving.

On the other hand, also in the air conditioner 3, an energy saving effect can be obtained. That is, the desiccant external air conditioner 1 allows the air SA to be supplied to the room to have an absolute humidity lower than that of the return air RA, so that moisture does not have to be brought into the room. Therefore, it is not necessary to dehumidify in the air conditioner 3, and it is sufficient only to perform the sensible heat treatment of the air. Therefore, the air conditioner 3
The air may be cooled to about 20 ° C., and the evaporation temperature can be raised by about 10 ° C.

As a result, the temperature head becomes smaller (for example, from 40 ° C. to 30 ° C.). Since the energy saving rate is ΔT1 / ΔT2 = 30/40 = 0.75, the energy saving is about 25%. Therefore, the energy saving rate of the entire system is 0.3 × 0.3 + 0.7 × 0.75 = 0.615, considering that the ratio of the outside air load to the average air conditioning load is about 30%. Therefore, energy saving is about 38%.

In addition, since it is not necessary to dehumidify the air conditioner 3, and no drain is required, it is possible to reduce equipment cost and operation time. In this embodiment,
Although a vapor compression heat pump is used as the heat pump 200, any heat source unit having a heat pump function may be used according to the above-described contents.
The same effect can be obtained by adopting an absorption heat pump as proposed in 3053. Further, in the present embodiment, an example in which cold and hot water is used as the heat transfer medium has been described. However, instead of the cold and hot water, direct evaporation and condensation of the refrigerant may be used.

In order to prevent the noise and vibration of the compressor of the vapor compression heat pump from being transmitted to the room, for example, as proposed by the inventor of the present invention in Japanese Patent Application No. 8-195732, an assembly accommodating a desiccant and a heat exchanger of the heat pump. The assembly and the assembly that houses the heat pump compressor may be separated.

In this embodiment, the operation of the cooling operation has been described. However, in the heating operation, the state of the room and the state of the outside air are switched in FIG. 3, and the outside air has a low temperature and a low humidity, and the room has a high temperature and a high humidity. Therefore, in the case of heating, the first air path is set to outside air (introduced air), and the second air path is set to exhaust air (released air) from the room. Is exhausted to the outside of the room, the moisture of the outside air can be collected and humidified in the room, and the heating load of the air conditioner 3 can be reduced. The operation in this case is the same as that in the case of cooling, and thus the description is omitted.

FIG. 4 is a second embodiment showing the configuration of an air conditioner according to the present invention. The air conditioner 1 includes a desiccant assembly 103 'in which a desiccant rotor and a total heat exchanger that repeat adsorption and release (regeneration) of moisture are integrated, and a heat pump 200.
It is a desiccant external control machine using As shown in the detailed view, the desiccant assembly has a rotor shape, and a portion where the desiccant and the air contact is divided into four parts. As a first step, each of these parts is air (released air) in a first air path taken out of a room (first space).
A second air path (introduced air) taken in from an external space (second space: outside air) and pressurized by the blower 102 as a second step of bringing the desiccant assembly 103 ′ into contact with the desiccant assembly 103 ′.
A step of bringing the desiccant assembly into contact with the air of the first step, a step of bringing the desiccant assembly into contact with the air (discharged air) in the first air path after the first step, and a fourth step as the third step. The air (released air) in the first air path after the step 3 is supplied to the heater (high heat source) 220 of the heat pump 200.
After the heating, the process of passing through the desiccant assembly to perform the dehumidification regeneration of the desiccant assembly is performed in this order, and then returns to the first process again.

The correspondence between the present embodiment and the previous embodiment is that the first step and the fourth step of the present embodiment correspond to the desiccant rotor 103 of the embodiment of FIG. 2, and the second step and the third step Figure 2
Corresponds to the total heat exchanger 153 of the embodiment. The connection of each air path is the same as in the embodiment of FIG. In the figure, circled alphabets K to V are symbols indicating the state of air corresponding to FIG. 3, where SA is supply air (processed outside air), RA is return air (exhausted indoor air). ), OA represents outside air, and EX represents exhaust.

Next, a description will be given with reference to FIG. 3 which is a psychrometric chart showing an operation state of the air conditioning part of the embodiment of FIG. The air released from the room (RA: state Q) is sucked into the blower 140 via the path 124, is pressurized, passes through the section of the first process of the desiccant assembly 103 ', adsorbs water in the isenthalpy process, and is absolutely absorbed. Humidity decreases (condition
R). The discharged air with reduced humidity is supplied to the desiccant assembly 10.
3 ', passing through the third step section, where the outside air (state
K) and the total heat exchange, the state changes along a straight line connecting the state K and the state R according to the known state change process of the total heat exchanger, the enthalpy rises, and the temperature and the absolute humidity increase ( State S). The air discharged from the third step section of the desiccant assembly 103 'is heated by a heat pump heater (high heat source).
It is sent to 220 and heated to 45-60 ° C., and the relative humidity decreases (state U). The discharged air having the reduced relative humidity flows into the fourth step section of the desiccant assembly 103 'to remove the moisture of the desiccant assembly (dehumidification regeneration: state
V). The discharged air that has passed through the fourth step section of the desiccant assembly 103 ′ is discarded as exhaust air through a path 129.

On the other hand, outside air to be introduced (introduced air: state
K) is sucked into the blower 102 via the path 107 and is pressurized to reach the second step section of the desiccant assembly 103 ′ via the path 108, where the heat is completely exchanged with the released air (state R). According to the known state change process of the total heat exchanger, the state changes along a straight line connecting the state K and the state R, and the enthalpy decreases, and the temperature and the absolute humidity decrease (state
L). Air with reduced enthalpy and dehumidified cooling (state L)
Is sent to the heat pump cooler (low heat source) 210 and
Cool to ２０20 ° C. (state M). The cooled introduced air is supplied to the indoor space via the path 110. In this way, even when the external control device of the second embodiment is used, the same operation as that of the first embodiment can be performed, and therefore, the same effect can be obtained.

FIG. 5 is a third embodiment showing the configuration of the air conditioning system of the present invention. The heat pump 200 connected to the air conditioner (external air conditioner) 1 is connected to an air conditioner (sensible heat treatment machine) 4 in the air-conditioned space via paths 41 and 42. In the present system, the heat pump of the external air conditioner 1 also serves as the heat source of the air conditioner 4, so that the sensible heat recovered in the air-conditioned space can be heated and used for heating the heat pump. As a result, the amount of heat used for desiccant dehumidification regeneration increases, the desiccant dehumidifying effect increases, the humidity of the air supply to the room decreases, and the processing capacity of the sensible heat load and, consequently, the cooling load increases. Power consumption is suppressed and an energy saving effect is obtained. Further, the capacity of the heat pump can be relatively reduced.

[0038]

As described above, according to the present invention,
At the time of cooling, after the air released from the room and the desiccant are brought into contact with each other, the whole air is exchanged with the outside air introduction air, and the air after the total heat exchange is further cooled by the low heat source of the heat pump and discharged into the room. A hybrid external air conditioner having a heat pump, a desiccant and a total heat exchanger configured to heat the discharged air after the total heat exchange by the high heat source of the heat pump and then pass the desiccant to perform dehumidification regeneration of the desiccant. The use of the air conditioning system in the air conditioning system greatly reduces external air treatment, provides an air conditioning system with reduced running costs, and eliminates the need for a drain such as an air conditioner used in combination, thereby reducing costs. be able to.

[Brief description of the drawings]

FIG. 1 is an explanatory diagram showing a basic configuration of an embodiment of an air conditioning system according to the present invention.

FIG. 2 is an explanatory diagram showing a basic configuration of the air conditioner of the embodiment of FIG.

FIG. 3 is an explanatory diagram showing a desiccant air-conditioning cycle of air of the air conditioner of FIG. 2 in a psychrometric chart.

FIG. 4 is an explanatory diagram showing a configuration of an air conditioner of another embodiment.

FIG. 5 is an explanatory diagram showing a basic configuration of another embodiment of the air conditioning system according to the present invention.

FIG. 6 is an explanatory diagram showing a basic configuration of a conventional air conditioning system.

FIG. 7 is an explanatory diagram showing a desiccant air-conditioning cycle of air in a conventional desiccant air-conditioning in a psychrometric chart.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 desiccant outside air conditioner 2 indoor space 3 air conditioner (air conditioner) 200 heat pump 102, 140 blower 103 desiccant rotor 103 'desiccant assembly 153 total heat exchanger 210 cooler (low heat source) 220 heater (high heat source) A release path B introduction route SA air supply RA return air EX exhaust OA outside air Δx moisture difference Δh enthalpy difference

Claims (9)

[Claims] A first space extending from the first space to the second space;
Air path and a second space from the second space to the first space
An air path, a desiccant that is disposed in the first air path and repeats adsorption of moisture in the flowing air and regeneration by air after heating, and a high heat source for desiccant regeneration in the first air path, A heat pump for providing a low heat source for cooling air in a second air path; and a total heat for exchanging heat between air in the first air path and the second air path before contacting the heat source of the heat pump. The first air path is dehumidified by contacting the air of the first air path introduced into the air conditioner from the first space with the desiccant and then dehumidifying the second air path in the total heat exchanger. After the total heat exchange with the air in the air path, the air in the first air path after the total heat exchange is heated by the high heat source of the heat pump, and then passes through the desiccant to perform dehumidification regeneration of the desiccant. The air conditioner is configured to discharge air from the air conditioner to the second space. 2. The step of integrally forming a desiccant and a total heat exchanger using the same desiccant to form a desiccant assembly, wherein the step of contacting the desiccant assembly with air of first and second air systems includes: A first step of bringing the air of the first air system introduced from the first space into contact with the desiccant assembly, and a second step of bringing the air of the second air system introduced from the second space into contact with the desiccant assembly , The first after the first step
Contacting the desiccant assembly with the air of the air system of the third
And the fourth step of heating the air of the first air system after the third step by the high heat source of the heat pump and passing the air through the desiccant assembly to dehumidify and regenerate the desiccant assembly. The air conditioner according to claim 1, wherein a cycle is configured to return to the first step again. 3. The air conditioner according to claim 1, wherein the desiccant assembly has a rotor shape, and the desiccant assembly flows through each air path by rotating the rotor. 4. The air conditioner according to claim 1, wherein a vapor compression heat pump is used as the heat pump. 5. The air conditioner according to claim 1, wherein an absorption heat pump is used as the heat pump. 6. The air conditioner according to claim 1, wherein the first space is an air conditioning room, and
An air-conditioning system characterized by using a space as an external space. 7. An air conditioning system, wherein the air conditioner according to claim 1 is used as an external space and the second space is used as an air conditioning room during heating. 8. An air conditioning system comprising the air conditioner according to claim 1 as an external controller and an air conditioner for sensible heat treatment. 9. The heat pump according to claim 1, wherein the heat pump has a function of cooling a sensible heat load in the air-conditioned space.
The air conditioner according to any one of claims 1 to 5.