Individual distributed air conditioning system

Abstract

This invention provides an individual distributed air conditioning system that controls the temperature and humidity of the incoming outside air by combining total heat exchange, cooling dehumidification, and dry dehumidification in an individual distributed air conditioning system. [Solution] Each indoor unit 21a, 21b, and 21c of the multi-air conditioning unit 2 performs individual air conditioning for each corresponding area of ​​the target space 4. The ventilation unit 3 has a total heat exchange element 34, a heat exchanger 39, and a desiccant unit 56. The heat exchanger 39 is the cooling unit, and the desiccant unit 56 is the dry dehumidification unit. The return air RA from the target space 2 passes through the exhaust side of the total heat exchange element 34 and the regeneration side of the desiccant unit 56 to become exhaust air EA to the outside. The outside air OA passes through the supply side of the total heat exchange element 34, passes through the heat exchanger 39, and passes through the processing side of the desiccant unit 56 to become temperature and humidity regulated supply air SA to the target space 4.

Description

Technical Field

[0001] The present invention relates to an individual decentralized air conditioning system and pertains to an energy-saving technology for suppressing excessive temperature adjustment.

Background Art

[0002] Conventionally, for example, the dehumidification system described in Patent Document 1 includes a ventilation device and a dehumidification device. The ventilation device includes a total heat exchanger, and the total heat exchanger exchanges the total heat between the outside air OA and the air RA. Thereafter, the outside air OA flows in as the first supply air SA1 without passing through the dehumidification device, and the indoor air RA flows into the dehumidification device. The dehumidification device includes a stationary desiccant, a cooler, and a heater. In the stationary desiccant, the air RA that has passed through the heater flows into the first dehumidification element and flows out to the outside as the exhaust air EA, and the air RA cooled by the cooler passes through the second dehumidification element, is dehumidified, and returns to the room as the second supply air SA2. The stationary desiccant alternately dries the first dehumidification element and the second dehumidification element.

[0003] Patent Document 2 describes a desiccant block device. In this device, a plurality of desiccant parts are interposed between the dehumidification target air path and the regeneration air path in the air conditioner, and the plurality of desiccant parts are integrally turned by a rotational operation around the axis. When one desiccant part is in the first posture state, the other desiccant parts are in the second posture state, and dehumidification and regeneration are performed alternately.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

[0005]

Patent Document 2

Disclosure of the Invention

Problems to be Solved by the Invention

[0006] As described in Patent Document 1 above, when a ventilation device and a dehumidifier are used in combination, outside air OA flows into the room as supply air SA1 without passing through the dehumidifier, a portion of the indoor air RA is dehumidified by the stationary desiccant of the dehumidifier and flows into the room as a second supply air SA, and the remaining portion of the air RA passes through the ventilation device, regenerates the stationary desiccant, and flows out to the outside as exhaust air EA.

[0007] Therefore, since the air supply to the room was carried out independently from each of the two systems, there was a structural factor that could lead to uneven humidity levels in the room due to the supply of air with different humidity levels.

[0008] Furthermore, in Patent Document 1, since the outside air volume and the indoor return air volume are controlled individually, the air volume passing through the total heat exchanger may be lower than the air volume passing through the dehumidifier, potentially leading to an extreme shortage of regeneration air volume for regenerating the static desiccant in the dehumidifier.

[0009] Incidentally, there are two methods of dehumidification: dry dehumidification and cooling dehumidification. Cooling dehumidification cools the air using a heat exchanger such as a direct expansion coil or a chilled water coil, and removes moisture by condensation at the dew point temperature. In this method, if humidity is prioritized over temperature as the control target, the air is cooled excessively, so it is necessary to heat the air to return it to the target temperature, which is a factor that worsens energy efficiency.

[0010] Dry dehumidification uses a stationary desiccant or desiccant rotor to remove moisture. While it requires a heat source for desiccant regeneration, it is more energy-efficient than cooling dehumidification because it directly adsorbs moisture from the air.

[0011] Furthermore, there are two types of air conditioning systems for buildings: the central system, also known as central air conditioning, and the individual system, also known as multi-unit air conditioning for buildings.

[0012] Central air conditioning systems cool or heat the indoor air by passing chilled or hot water, generated by chillers, boilers, and heat pumps installed in the building's machine room, through heat exchangers in air conditioners installed in individual rooms.

[0013] Building multi-zone air conditioning, also known as individual distributed air conditioning, involves distributing air conditioners to each room. Outdoor units, typically installed on the roof, and indoor units, installed on the ceiling, are connected by refrigerant piping. This allows for different air conditioning conditions depending on the area the air conditioner is assigned to; for example, heating near windows in winter and cooling near heat-generating equipment such as computers.

[0014] The present invention aims to provide an individual distributed air conditioning system that can maintain an appropriate temperature and humidity in the indoor environment by controlling the temperature and humidity of the incoming outside air by combining total heat exchange, cooling dehumidification, and dry dehumidification in an individual distributed air conditioning system. [Means for solving the problem]

[0015] To solve the above problems, the individual distributed air conditioning system of the present invention comprises a multi-air conditioning unit responsible for air conditioning of a target space and a ventilation unit responsible for ventilation of the target space and temperature and humidity adjustment of incoming outside air. The multi-air conditioning unit has indoor units distributed to each corresponding area of ​​the target space and an outdoor unit that circulates a heat transfer medium between the indoor units, with each indoor unit performing individual air conditioning for each corresponding area of ​​the target space. The ventilation unit has a total heat exchange element, a heat exchanger, and a desiccant unit, and the return air from the target space passes through the total heat exchange element and the desiccant unit to be exhausted to the outside, while the outside air passes through the total heat exchange element, the heat exchanger, and the desiccant unit to become temperature and humidity regulated supply air to the target space.

[0016] The present invention relates to an individual distributed air conditioning system characterized in that the heat exchanger consists of a chilled / hot water coil or a direct expansion coil.

[0017] The present invention provides a distributed air conditioning system characterized by having a humidifier downstream of the heat exchanger in the direction of outside airflow.

[0018] The present invention provides an individual distributed air conditioning system characterized by having a humidifier downstream of the desiccant rotor in the direction of outside airflow.

[0019] In the individual distributed air conditioning system of the present invention, the heat exchanger serves as both a cooling unit during cooling and a heating unit during heating, and the desiccant unit serves as both a dry dehumidifying unit during cooling and a humidifying unit during heating.

[0020] The individual distributed air conditioning system of the present invention is characterized in that the return air from the target space passes through the exhaust side of the total heat exchange element and through the regeneration side of the desiccant rotor to be exhausted to the outside, the outside air passes through the supply air side of the total heat exchange element, is cooled by passing through the heat exchanger, is dry dehumidified by passing through the processing side of the desiccant rotor to become temperature and humidity regulated supply air to the target space.

[0021] In the individual distributed air conditioning system of the present invention, the ventilation equipment section consists of an outside air processing unit and a humidity control unit, the outside air processing unit has a total heat exchange element and a heat exchanger, the humidity control unit has a desiccant section, the desiccant section consists of a desiccant rotor, the return air from the target space passes through the exhaust side of the total heat exchange element of the outside air processing unit, exits the outside air processing unit and passes through the regeneration side of the desiccant rotor of the humidity control unit to be exhausted to the outside, the outside air passes through the supply air side of the total heat exchange element of the outside air processing unit, is cooled by passing through the heat exchanger, exits the outside air processing unit and passes through the processing side of the desiccant rotor of the humidity control unit to be dry dehumidified and supplied to the target space with temperature and humidity regulated.

[0022] In the individual decentralized air conditioning system of the present invention, the ventilation equipment unit consists of an outdoor air treatment unit and a humidity control unit. The outdoor air treatment unit has a total heat exchange element, and the humidity control unit has a heat exchanger and a desiccant section. The desiccant section consists of a desiccant rotor. The return air of the target space passes through the exhaust side of the total heat exchange element of the outdoor air treatment unit, exits the outdoor air treatment unit, passes through the regeneration side of the desiccant rotor of the humidity control unit, and becomes exhaust to the outside. The outdoor air passes through the supply side of the total heat exchange element of the outdoor air treatment unit, exits the outdoor air treatment unit, is cooled by passing through the heat exchanger of the humidity control unit, and is dried and dehumidified by passing through the treatment side of the desiccant rotor to become supply air with adjusted temperature and humidity to the target space.

[0023] In the individual decentralized air conditioning system of the present invention, the ventilation equipment unit has a regeneration heat exchanger on the upstream side of the desiccant section in the air flow direction of the return air. The heat exchanger and the regeneration heat exchanger consist of direct expansion coils. The multi-air conditioning equipment unit has indoor units for cooling operation and indoor units for heating operation that can operate simultaneously, and has a heat medium circuit in which a heat medium for cooling and a heat medium for heating circulate between the indoor unit and the outdoor unit. The heat medium for cooling flows into the direct expansion coil of the heat exchanger, and the heat medium for heating flows into the direct expansion coil of the regeneration heat exchanger.

[0024] In the individual decentralized air conditioning system of the present invention, the ventilation equipment unit has a regeneration heat exchanger on the upstream side of the desiccant section in the air flow direction of the return air. The heat exchanger consists of a direct expansion coil, and the regeneration heat exchanger consists of a hot water coil. The multi-air conditioning equipment unit has indoor units for cooling operation and indoor units for heating operation that can operate simultaneously, and has a heat medium circuit in which a heat medium for cooling and a heat medium for heating circulate between the indoor unit and the outdoor unit. The heat medium for cooling flows into the direct expansion coil of the heat exchanger, and between the heat medium circuit and the hot water coil, there is a heating heat exchanger for heating the hot water flowing through the hot water coil of the regeneration heat exchanger by the heat medium for heating.

Effect of the Invention

[0025] According to the present invention as described above, while individual air conditioning is performed for each corresponding area of the target space by each indoor unit of the multi-air conditioning equipment unit distributed in the target space, total heat exchange between the return air and the outside air of the target space is performed by the total heat exchange element of the ventilation equipment unit, the outside air is cooled by the heat exchanger, and further the outside air is dried and dehumidified by the desiccant unit, and the introduced outside air is supplied to the target space as supply air whose temperature and humidity are appropriately adjusted.

[0026] Therefore, in the present invention, the indoor air of the target space is not dehumidified, and the ventilation equipment unit only adjusts the temperature and humidity of the outside air and supplies it to the target space, and the supply air is performed in one system. Thus, it is possible to eliminate the structural factor in which air of different humidities is supplied into the room by two systems of supply air as in the prior art, resulting in humidity unevenness in the room.

[0027] And, it is possible to suppress the influence exerted on the target space by the temperature change and humidity change of the outside air, which are disturbance factors in the air conditioning of the target space. By appropriately adjusting the temperature and humidity of the introduced outside air and supplying it as supply air, the indoor temperature and indoor humidity, which are the basis of air conditioning in the target space, can be controlled to appropriate temperatures and humidities. Therefore, when individual air conditioning is performed by each indoor unit of the multi-air conditioning equipment unit, an appropriate temperature environment and humidity environment can be realized without excessively cooling the indoor air, and energy saving can be achieved.

[0028] Also, by combining cooling and dehumidification and dry dehumidification to dehumidify the outside air, it is possible to limit the dehumidification to condensation due to dew at an appropriate cooling temperature without excessively cooling the temperature of the outside air in cooling and dehumidification, and suppress the energy loss associated with excessive cooling. Furthermore, when dehumidifying in subsequent dry dehumidification, the latent heat change due to dehumidification shifts to sensible heat and the air is heated, so that while achieving energy saving, the temperature of the air reduced by cooling and dehumidification can be brought close to the temperature of the indoor air and supplied as supply air.

[0029] Furthermore, by arranging the total heat exchange element, heat exchanger, and desiccant section in series, and controlling the intake and exhaust airflow rates (return air exhaust and outside air supply) while maintaining a constant ratio, the airflow rate of return air passing through the regeneration side of the desiccant section does not decrease drastically compared to the airflow rate of outside air passing through the processing side of the desiccant section. This balances the regeneration load and dehumidification load of the desiccant section, suppressing a decrease in dehumidification performance. [Brief explanation of the drawing]

[0030] [Figure 1] A schematic diagram showing an individual distributed air conditioning system in an embodiment of the present invention. [Figure 2] A schematic diagram showing an individual distributed air conditioning system in another embodiment of the present invention. [Figure 3] A schematic diagram showing an individual distributed air conditioning system in yet another embodiment of the present invention. [Figure 4] A schematic diagram showing the configuration of the heat source of an individual distributed air conditioning system in an embodiment of the present invention. [Figure 5] A schematic diagram showing the configuration of other heat sources in the individual distributed air conditioning system according to an embodiment of the present invention. [Figure 6] A psychrometric chart showing the movement of temperature and humidity in the configuration of this embodiment. [Figure 7] A psychrometric chart showing temperature and humidity movement in the comparative example's individual distributed air conditioning system. [Figure 8] Schematic diagram showing an individual distributed air conditioning system as a comparative example. [Best Mode for Carrying Out the Invention]

[0031] Hereinafter, embodiments of the present invention will be described based on the drawings. (Example 1) In Figure 1, the individual distributed air conditioning system 1 according to this embodiment comprises a multi-air conditioning unit 2 and a ventilation unit 3. The multi-air conditioning unit 2 is responsible for air conditioning of the target space 4, and the ventilation unit 3 is responsible for ventilation of the target space 4 and temperature and humidity control of the incoming outside air.

[0032] The multi-air conditioning unit 2 has multiple indoor units 21a, 21b, and 21c distributed across the ceiling 5 of the target space 4, and each indoor unit 21a, 21b, and 21c can perform individual air conditioning for each corresponding area of ​​the target space 4.

[0033] The ventilation equipment section 3 has an outside air processing unit 31 and a humidity control unit 51 arranged in series, and it is also possible to configure the ventilation equipment section 3 of this embodiment by adding a humidity control unit 51 to an existing facility that has an outside air processing unit 31.

[0034] The outside air treatment unit 31 is a direct expansion type total heat exchange unit, and has a partition wall 33 that forms two passages through which return air RA and outside air OA flow inside the casing 32, and a total heat exchange element 34 that separates the two passages into an upstream side and a downstream side. The two passages intersect via the total heat exchange element 34, forming an exhaust side passage 35 through which return air RA flows and a supply side passage 36 through which outside air OA flows.

[0035] A return air fan 37 is located downstream of the total heat exchange element 34 in the exhaust passage 35 in the direction of the return air RA airflow, and an outside air fan 38 is located downstream of the total heat exchange element 34 in the supply passage 36 in the direction of the outside air OA airflow. A heat exchanger 39 and an evaporative humidifier 40 are sequentially arranged downstream of the outside air fan 38.

[0036] The heat exchanger 39 of the outside air processing unit 31 consists of a direct expansion coil, serving as a cooling section during cooling and a heating section during heating. The evaporative humidifier 40 is for humidification during winter heating. The heat exchanger 39 can also be replaced with a hot / cold water coil.

[0037] The humidity control unit 51 has a partition wall 55 that forms two passages inside the casing 52: a desiccant regeneration side passage 53 through which return air RA flows and a desiccant processing side passage 54 through which outside air OA flows, and a desiccant section 56 that separates the two passages into an upstream side and a downstream side. In this case, the desiccant section 56 consists of a desiccant rotor that forms a dry dehumidification section, and the desiccant rotor rotates between a position corresponding to the desiccant regeneration side passage 53 and a position corresponding to the desiccant processing side passage 54.

[0038] In the airflow direction of the return air RA, upstream of the desiccant section 56 of the desiccant regeneration side passage 53, there is a regeneration heat exchanger 57 consisting of a direct expansion coil, and downstream of the desiccant section 56 of the desiccant regeneration side passage 53, there is an exhaust fan 58. In the airflow direction of the outside air OA, downstream of the desiccant section 56 of the desiccant processing side passage 54, there is a supply air fan 59.

[0039] A return air duct 61 connected to a return air port 6 opening in the ceiling 5 of the target space 4 is connected to the return air upstream port 62 of the exhaust side passage 35 of the outside air processing unit 31. A return air relay duct 64 connected to the return air downstream port 63 of the exhaust side passage 35 is connected to the regeneration upstream port 65 of the desiccant regeneration side passage 53 of the humidity control unit 51. An exhaust duct 67 connected to the regeneration downstream port 66 of the desiccant regeneration side passage 53 is connected to the external exhaust system.

[0040] An outside air duct 68 connected to the external outside air system is connected to the outside air upstream port 69 of the supply air passage 36 of the outside air processing unit 31, an outside air relay duct 71 connected to the outside air downstream port 70 of the supply air passage 36 is connected to the processing upstream port 72 of the desiccant processing passage 54 of the humidity control unit 51, and a supply air duct 74 connected to the processing downstream port 73 of the desiccant processing passage 54 is connected to the supply air port 7 which opens into the ceiling 5 of the target space 4.

[0041] As shown in Figure 4, a medium piping 23 for circulating the heat transfer medium is provided between each indoor unit 21a, 21b, 21c and the outdoor unit 22, and the indoor units 21a, 21b, 21c, the outdoor unit 22, and the medium piping 23 constitute a heat transfer medium circuit. Each indoor unit 21a, 21b, 21c, the heat exchanger 39 of the outdoor air processing unit 31, and the regenerative heat exchanger 57 of the humidity control unit 51 are connected to the heat transfer medium circuit via a branching unit 24.

[0042] In this configuration, the multi-air conditioning unit 2 allows for simultaneous operation of indoor units 21b and 21c for cooling and indoor unit 21a for heating, with cooling and heating heat transfer fluids circulating in the heat transfer fluid circuit. Heating heat transfer fluid circulates through the regenerative heat exchanger 57 of the humidity control unit 51.

[0043] The operation of the above configuration will be explained below. The outside air processing unit 31 drives the return air fan 37 and draws in indoor air as return air RA from the return air port 6 in the ceiling 5 of the target space 4 through the return air duct 61. In the outside air processing unit 31, the return air RA passes through the total heat exchange element 34 from the upstream side to the downstream side of the exhaust side passage 35 and exchanges total heat with the outside air OA. The return air RA that has passed through the total heat exchange element 34 enters the desiccant regeneration side passage 53 of the humidity control unit 51 via the return air relay duct 64.

[0044] The humidity control unit 51 drives the exhaust fan 58 to draw in the return air RA, which passes through the regenerative heat exchanger 57 to become heated regenerative air. This regenerative air then passes from the upstream side to the downstream side of the desiccant regeneration passage 53, through the regeneration side of the desiccant rotor in the desiccant section 56, and desorbs moisture adsorbed on the desiccant rotor, thus regenerating the desiccant rotor. The regenerative air that has passed through the desiccant section 56, along with the desorbed moisture, is exhausted to the outside through the exhaust duct 67 by the exhaust fan 58.

[0045] The outdoor air processing unit 31 drives the outdoor air fan 38 and draws in outdoor air OA through the outdoor air duct 68. In the outdoor air processing unit 31, the outdoor air OA passes through the total heat exchange element 34 from the upstream side to the downstream side of the supply side passage 36 and exchanges total heat with the return air RA. After passing through the total heat exchange element 34, the outdoor air OA passes through the heat exchanger 39, which cools the outdoor air OA. The outdoor air OA passes through the non-operating evaporative humidifier 40 for winter heating and enters the desiccant processing side passage 54 of the humidity control unit 51 via the outdoor air relay duct 71.

[0046] The humidity control unit 51 drives the supply fan 59 to draw in outside air OA, and the outside air OA passes from the upstream side to the downstream side of the desiccant processing side passage 54 through the processing side of the desiccant rotor of the desiccant section 56, where the desiccant rotor dry-dehumidifies the outside air OA. The outside air OA that has passed through the desiccant section 56 is supplied to the target space 4 as temperature and humidity regulated supply air SA through the supply duct 74 by the supply fan 59.

[0047] As described above, in this embodiment, the indoor units 21a, 21b, and 21c of the multi-air conditioning unit 2, which are distributed throughout the target space 4, perform individual air conditioning for each corresponding area of ​​the target space 4. The total heat exchange element 34 of the ventilation unit 3 performs total heat exchange between the return air RA of the target space 4 and the outside air OA, the heat exchanger 39 cools the outside air OA, and the desiccant unit 56 further dehumidifies the outside air OA using a dry method, and the introduced outside air is supplied to the target space 4 as supply air SA with appropriately adjusted temperature and humidity.

[0048] Therefore, the indoor air in the target space 4 is not dehumidified, and the ventilation equipment unit 3 adjusts the temperature and humidity of only the outside air OA and supplies it to the target space 4. Since the supply air SA is performed in a single system, it is possible to eliminate the structural factor that causes humidity unevenness in the room, as in the conventional system where air with different humidity levels is supplied to the room by two supply air SA systems.

[0049] Furthermore, the influence of temperature and humidity changes in the outside air OA, which are disturbances in the air conditioning of the target space 4, on the target space 4 can be suppressed. By appropriately adjusting the temperature and humidity of the incoming outside air before supplying it, the indoor temperature and humidity, which serve as the basis for air conditioning in the target space 4, can be controlled to appropriate levels. Therefore, when individual air conditioning is performed by each indoor unit 21a, 21b, and 21c of the multi-air conditioning system 2, an appropriate temperature and humidity environment can be achieved without excessively cooling the indoor air, thereby saving energy. (See the psychrometric chart in Figure 6.) Furthermore, by combining cooling dehumidification and dry dehumidification to dehumidify the outside air (OA), it is possible to limit dehumidification to condensation at an appropriate cooling temperature without excessively cooling the outside air (OA) during cooling dehumidification, thereby suppressing energy loss associated with excessive cooling.

[0050] Furthermore, during subsequent dry dehumidification, the latent heat change due to dehumidification is converted into sensible heat, warming the air. This allows for energy savings while bringing the temperature of the air, which has been lowered by cooling dehumidification, closer to the room air temperature before supplying it to the room.

[0051] Furthermore, by arranging the total heat exchange element 34, the heat exchanger 39, and the desiccant unit 56 in series, and controlling the intake and exhaust airflow rates of the return air RA and the outside air OA while maintaining a constant ratio, the airflow rate of the return air RA passing through the regeneration side of the desiccant unit 56 does not decrease drastically compared to the airflow rate of the outside air OA passing through the processing side of the desiccant unit 56. This balances the regeneration load and dehumidification load of the desiccant unit 56, suppressing a decrease in dehumidification performance.

[0052] Here, the advantages of this embodiment will be explained by comparing the temperature and humidity transfer in the configuration of this embodiment with the temperature and humidity transfer in the configuration shown in Figure 8 as a comparative example, that is, a configuration in which the outside air processing unit 31 is not provided with a cooling heat exchanger 39. Each component shown in Figure 8 is denoted by the same reference numerals as the components of this embodiment, and its description is omitted.

[0053] Figure 6 is a psychrometric chart showing the temperature and humidity changes in the configuration of this embodiment, and Figure 7 is a psychrometric chart showing the temperature and humidity changes in the configuration shown in Figure 8.

[0054] In both Figures 6 and 7, the outside air has a dry-bulb temperature of 35°C (DB), an absolute humidity of 0.0197 kg / kg (DA), and a specific enthalpy of 85 kJ / kg (DA), while the return air has a dry-bulb temperature of 27°C (DB), an absolute humidity of 0.0105 kg / kg (DA), and a specific enthalpy of 54 kJ / kg (DA).

[0055] In the configuration shown in Figure 8, as shown in the psychrometric chart in Figure 7, the outside air OA, after passing through the supply air side of the total heat exchange element 34, has a dry-bulb temperature of 29.8°C (DB), an absolute humidity of 0.0139 kg / kg (DA), and a specific enthalpy of 65 kJ / kg (DA) at the outlet. It then passes through the processing side of the desiccant section and is dry-dehumidified to become the supply air SA. The supply air SA has a dry-bulb temperature of 37.5°C (DB), an absolute humidity of 0.0105 kg / kg (DA), and a specific enthalpy of 65 kJ / kg (DA).

[0056] The return air RA, after passing through the exhaust side of the total heat exchange element 34, has a dry-bulb temperature of 32°C (DB), an absolute humidity of 0.0165 kg / kg (DA), and a specific enthalpy of 74 kJ / kg (DA) at the outlet. It is then heated in the regenerative heat exchanger 57 to become regenerative air with a dry-bulb temperature of 45°C (DB), an absolute humidity of 0.0165 kg / kg (DA), and a specific enthalpy of 87 kJ / kg (DA). This regenerative air then passes through the regeneration side of the desiccant section 56, regenerating the desiccant section 56 and becoming exhaust air EA. The exhaust air EA has a dry-bulb temperature of 37°C (DB), an absolute humidity of 0.0195 kg / kg (DA), and a specific enthalpy of 87 kJ / kg (DA).

[0057] Therefore, the absolute humidity of the exhaust air EA and the outside air OA becomes almost the same, the absolute humidity of the return air RA and the supply air SA becomes almost the same, and the supply air SA is supplied to the room at a temperature higher than the temperature of the return air RA, i.e., the room temperature. Therefore, this becomes a factor that strengthens the cooling by each indoor unit 21b and 21c during the cooling operation of the multi-air conditioning unit 2.

[0058] In contrast, in this embodiment, as shown in the psychrometric chart of Figure 6, the outside air OA, after passing through the supply air side of the total heat exchange element 34, has a dry-bulb temperature of 29.8°C (DB), an absolute humidity of 0.0137 kg / kg (DA), and a specific enthalpy of 65 kJ / kg (DA). It is then cooled in the heat exchanger 39, becoming a dry-bulb temperature of 14.5°C (DB), an absolute humidity of 0.0095 kg / kg (DA), and a specific enthalpy of 38 kJ / kg (DA). It then passes through the processing side of the desiccant section 56 and is dry-dehumidified to become the supply air SA. The supply air SA has a dry-bulb temperature of 23°C (DB), an absolute humidity of 0.0063 kg / kg (DA), and a specific enthalpy of 38 kJ / kg (DA).

[0059] At this time, the latent heat change due to dehumidification on the processing side of the desiccant unit 56 is converted to sensible heat, and the air is heated, thereby saving energy while bringing the temperature of the air that has been lowered by cooling and dehumidification closer to the temperature of the room air before supplying it as air.

[0060] The return air RA, after passing through the exhaust side of the total heat exchange element 34, has a dry-bulb temperature of 32.2°C (DB), an absolute humidity of 0.0165 kg / kg (DA), and a specific enthalpy of 74 kJ / kg (DA) at the outlet. It is then heated in the regenerative heat exchanger 57 to become regenerative air with a dry-bulb temperature of 39°C (DB), an absolute humidity of 0.0165 kg / kg (DA), and a specific enthalpy of 82 kJ / kg (DA). This regenerative air then passes through the regeneration side of the desiccant section 56, regenerating the desiccant section 56 and becoming exhaust air EA. The exhaust air EA has a dry-bulb temperature of 30.5°C (DB), an absolute humidity of 0.0195 kg / kg (DA), and a specific enthalpy of 82 kJ / kg (DA).

[0061] Therefore, the absolute humidity of the exhaust air EA and the outside air OA becomes almost the same, and the supply air SA is supplied to the room as air with lower absolute humidity and dry-bulb temperature compared to the return air RA. Consequently, there is no need to increase the cooling power of each indoor unit 21b and 21c during the cooling operation of the multi-air conditioning system unit 2. (Example 2) In Example 1, an evaporative humidifier 40 for winter heating was provided in the outside air processing unit 31, but as shown in Figure 2, it is also possible to place the evaporative humidifier 40 in the humidity control unit 51. The evaporative humidifier 40 is installed downstream of the supply air fan 59 in the direction of the outside air OA airflow. Other effects are the same as in Example 1, and the same reference numerals are used for the components, and their explanation is omitted. (Example 3) In Example 1, the outside air processing unit 31 was equipped with a heat exchanger 39 and an evaporative humidifier 40 for winter heating. However, as shown in Figure 3, it is also possible to omit the evaporative humidifier 40 and equip the humidity control unit 51 with the heat exchanger 39. In this case, the heat exchanger 39 functions to cool the outside air OA during cooling and to heat the outside air OA during heating. The desiccant unit 56 functions to perform dry dehumidification during cooling and to humidify during heating. In other words, during heating, the heated outside air OA adsorbs moisture from the desiccant unit 56, becoming humidified supply air SA. Other effects are the same as in Example 1, and the same reference numerals are used for the components, and their explanation is omitted. (Example 4) In Example 1, the regenerative heat exchanger 57 of the humidity control unit 51 was a direct expansion coil, but as shown in Figure 5, it is also possible to use a hot water coil for the regenerative heat exchanger 57 of the humidity control unit 51.

[0062] In this case, in order to supply hot water to the regenerative heat exchanger 57, a heating heat exchanger 25 is provided between the heat transfer medium circuit and the hot water coil of the regenerative heat exchanger 57 of the humidity control unit 51. The heating heat transfer medium is circulated from the heat transfer medium circuit of the multi-air conditioning unit 2 to the heating heat exchanger 25 via the branching unit 24, thereby heating the hot water flowing through the hot water coil of the humidity control unit 51. [Explanation of Symbols]

[0063] RA return air OA outside air EA exhaust SA Air Intake 1. Individual distributed air conditioning system 2. Multi-air conditioning system section 3. Ventilation Equipment Department 4. Target space 5. Ceiling 6 Return air port 7 Air supply port 21a, 21b, 21c indoor unit 22 Outdoor unit 23 Media piping 24 Branch Unit 25 Heating heat exchanger 31. Outdoor air treatment unit 32 Casing 33 Partition wall 34 Total heat exchange element 35 Exhaust side passage 36 Air supply side passage 37. Return air fan 38 Outdoor fan 39 Heat exchanger 40 Evaporative Humidifiers 51 Humidity Control Unit 52 Casing 53 Desiccant Regeneration Sidewalk 54 Desiccant treatment side passage 55 Partition wall 56 Desiccant section 57 Regeneration heat exchanger 58 Exhaust fan 59 Intake fan 61 Return air duct 62 Upstream return air port 63 Return air downstream port 64. Return air relay duct 65 Regeneration upstream outlet 66 Regeneration downstream outlet 67 Exhaust duct 68 Outdoor air duct 69 Outdoor air upstream outlet 70 Outdoor air outlet 71 Outdoor air relay duct 72 Upstream processing port 73 Downstream processing port 74. Air supply duct

Claims

1. It comprises a multi-air conditioning unit responsible for air conditioning of the target space, and a ventilation unit responsible for ventilation of the target space and temperature and humidity control of the incoming outside air. The multi-air conditioning system unit comprises indoor units distributed in each corresponding area of ​​the target space, and an outdoor unit that circulates a heat transfer medium between the indoor units, with each indoor unit performing individual air conditioning for each corresponding area of ​​the target space. The ventilation equipment section comprises a total heat exchange element, a heat exchanger, and a desiccant section. An individual distributed air conditioning system characterized in that the return air from the target space passes through the total heat exchange element and the desiccant section to be exhausted to the outside, and the outside air passes through the total heat exchange element, the heat exchanger, and the desiccant section to become temperature and humidity regulated supply air to the target space.

2. The individual distributed air conditioning system according to claim 1, characterized in that the heat exchanger consists of a chilled / hot water coil or a direct expansion coil.

3. The individual distributed air conditioning system according to claim 1, characterized in that a humidifier is provided downstream of the heat exchanger in the direction of outside airflow.

4. The individual distributed air conditioning system according to claim 1, characterized in that a humidifier is provided downstream of the desiccant rotor in the direction of outside airflow.

5. The individual distributed air conditioning system according to claim 1, characterized in that the heat exchanger serves as both a cooling section during cooling and a heating section during heating, and the desiccant section serves as both a dry dehumidifying section during cooling and a humidifying section during heating.

6. The individual distributed air conditioning system according to claim 1, characterized in that the return air from the target space passes through the exhaust side of the total heat exchange element and the regeneration side of the desiccant rotor to be exhausted to the outside, outside air passes through the supply side of the total heat exchange element, is cooled by passing through the heat exchanger, is dry dehumidified by passing through the processing side of the desiccant rotor to become temperature and humidity regulated supply air to the target space.

7. The aforementioned ventilation system consists of an outside air processing unit and a humidity control unit. The outside air processing unit has the total heat exchange element and the heat exchanger, The humidity control unit has the desiccant section, and the desiccant section consists of a desiccant rotor. The individual distributed air conditioning system according to claim 1, characterized in that the return air from the target space passes through the exhaust side of the total heat exchange element of the outside air processing unit, exits the outside air processing unit, passes through the regeneration side of the desiccant rotor of the humidity control unit, and becomes exhaust to the outside; the outside air passes through the supply air side of the total heat exchange element of the outside air processing unit, is cooled by passing through the heat exchanger, exits the outside air processing unit, passes through the processing side of the desiccant rotor of the humidity control unit, is dry dehumidified, and becomes temperature and humidity regulated supply air to the target space.

8. The aforementioned ventilation system consists of an outside air processing unit and a humidity control unit. The aforementioned outside air processing unit has the total heat exchange element, The humidity control unit comprises the heat exchanger and the desiccant section, the desiccant section consisting of a desiccant rotor, The individual distributed air conditioning system according to claim 1, characterized in that the return air from the target space passes through the exhaust side of the total heat exchange element of the outside air processing unit, exits the outside air processing unit, passes through the regeneration side of the desiccant rotor of the humidity control unit, and becomes exhaust to the outside; outside air passes through the supply air side of the total heat exchange element of the outside air processing unit, exits the outside air processing unit, is cooled by passing through the heat exchanger of the humidity control unit, passes through the processing side of the desiccant rotor, is dry dehumidified, and becomes temperature and humidity regulated supply air to the target space.

9. The ventilation equipment section has a regenerative heat exchanger upstream of the desiccant section in the direction of the return airflow, and the heat exchanger and the regenerative heat exchanger are made of direct expansion coils. The multi-air conditioning system unit is capable of simultaneously operating the indoor unit for cooling and the indoor unit for heating, and has a heat transfer medium circuit between the indoor unit and the outdoor unit through which a heat transfer medium for cooling and a heat transfer medium for heating are circulated. The individual distributed air conditioning system according to claim 1, characterized in that the heat transfer medium for cooling flows to the direct expansion coil of the heat exchanger, and the heat transfer medium for heating flows to the direct expansion coil of the regenerative heat exchanger.

10. The ventilation equipment section has a regenerative heat exchanger upstream of the desiccant section in the direction of the return airflow, the heat exchanger consists of a direct expansion coil, and the regenerative heat exchanger consists of a hot water coil. The multi-air conditioning system unit is capable of simultaneously operating the indoor unit for cooling and the indoor unit for heating, and has a heat transfer medium circuit between the indoor unit and the outdoor unit through which a heat transfer medium for cooling and a heat transfer medium for heating are circulated. The individual distributed air conditioning system according to claim 1, characterized in that the heat transfer medium for cooling flows to the direct expansion coil of the heat exchanger, and a heating heat exchanger is provided between the heat transfer medium circuit and the hot water coil, which heats the hot water flowing through the hot water coil of the regenerative heat exchanger with the heat transfer medium for heating.

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