JP3742864B2 - Air conditioning system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent the cost-up and the increase of maintenance parts in a case when a plurality of air conditioners using adsorption heat exchangers are installed or when air conditioner using the adsorption heat exchanger is installed together with an air conditioner using an air heat exchanger. <P>SOLUTION: This air conditioning system 1 comprises a plurality of latent heat system use-side refrigerant circuits 10a, 10b connected with each other in parallel, and a plurality of sensible system use-side refrigerant circuits 10c, 10d connected with each other in parallel. The latent heat system use-side refrigerant circuits 10a, 10b have the adsorption heat exchangers 22, 23, 32, 33 provided with adsorbent on their surfaces. The sensitive heat system use-side refrigerant circuits 10c, 10d have the air heat exchangers 42, 52 and performs the heat exchange between the refrigerant and air. <P>COPYRIGHT: (C)2006,JPO&amp;NCIPI

Description

  The present invention relates to an air conditioning system, and more particularly to an air conditioning system that processes indoor latent heat load and sensible heat load by performing a vapor compression refrigeration cycle operation.

  Conventionally, an air conditioner that performs indoor cooling and dehumidification is known (see, for example, Patent Document 1). Such an air conditioner includes a vapor compression refrigerant circuit having an outdoor heat exchanger as a heat source side heat exchanger and an indoor heat exchanger as an air heat exchanger, and the refrigerant circuit includes a refrigerant. Refrigeration cycle operation by circulating The air conditioner dehumidifies indoors by setting the evaporation temperature of the refrigerant in the indoor heat exchanger to be lower than the dew point temperature of the indoor air and condensing moisture in the indoor air.

On the other hand, a dehumidifying device including a heat exchanger having an adsorbent on the surface is also known (see, for example, Patent Document 2). Such a dehumidifying apparatus includes two heat exchangers provided with an adsorbent, and performs an adsorption operation in which moisture in the air is adsorbed and dehumidified in one of the two heat exchangers. A regenerating operation for desorbing moisture adsorbed on the other side of the vessel is performed. At that time, water cooled by the cooling tower is supplied to the heat exchanger that adsorbs moisture, and hot waste water is supplied to the regenerated heat exchanger. And this dehumidification apparatus supplies the air dehumidified by adsorption | suction operation | movement and reproduction | regeneration operation | movement indoors.
International Publication No. 03/029728 Pamphlet JP-A-7-265649

  In the former air conditioner, the evaporation temperature of the refrigerant in the indoor heat exchanger is set lower than the dew point temperature of indoor air, and the indoor latent heat load is processed by condensing moisture in the air. In other words, even if the evaporation temperature of the refrigerant in the indoor heat exchanger is higher than the dew point temperature of the indoor air, the sensible heat load can be processed. The evaporation temperature has to be set to a low value. For this reason, there is a problem that the difference between high and low pressures of the vapor compression refrigeration cycle is increased, the power consumption in the compressor is increased, and only a low COP (coefficient of performance) can be obtained.

In the latter dehumidifier, the cooling water cooled by the cooling tower, that is, the cooling water having a temperature not much lower than the indoor temperature is supplied to the heat exchanger. Therefore, this dehumidifying apparatus has a problem that it can not process the sensible heat load even though it can process the indoor latent heat load.
In contrast, the inventor of the present application has invented an air conditioner including a vapor compression refrigerant circuit having a heat source side heat exchanger and an adsorption heat exchanger as a use side heat exchanger (for example, (See Japanese Patent Application No. 2003-351268.) This air conditioner performs adsorption heat exchange by alternately performing an adsorption operation for adsorbing moisture in the air to an adsorption heat exchanger with an adsorbent on the surface and a regeneration operation for desorbing moisture from the adsorption heat exchanger. The air that has passed through the vessel can be supplied indoors to handle indoor sensible heat loads and latent heat loads. That is, instead of condensing moisture in the air and dehumidifying the air as in the former air conditioner, the moisture in the air is adsorbed by the adsorbent to dehumidify the air. It is not necessary to set the temperature lower than the dew point temperature of the air, and the air can be dehumidified even if the evaporation temperature of the refrigerant is set to be higher than the dew point temperature of the air. For this reason, according to this air conditioning apparatus, even when air is dehumidified, the evaporation temperature of the refrigerant can be set to a higher temperature than before, and the high / low pressure difference of the refrigeration cycle can be reduced. As a result, power consumption in the compressor can be reduced, and COP can be improved. In addition, when air is dehumidified, the indoor sensible heat load can also be processed by setting the temperature lower than the evaporation temperature of the refrigerant necessary in the adsorption heat exchanger.

  Next, the inventor of the present application is trying to apply an air conditioning apparatus using the above-described adsorption heat exchanger to an air conditioning system (a so-called multi-air conditioning system) installed in a building or the like. In a large-scale air conditioning system, it may be necessary to install multiple air conditioning units that use adsorption heat exchangers, so a compressor or the like as a heat source is installed according to the number of adsorption heat exchangers. This causes a problem that the cost increases and the number of maintenance points increases. Further, even when an air conditioner using an adsorption heat exchanger is installed together with an air conditioner having a normal air heat exchanger, a compressor as a heat source separately from the air conditioner having an air heat exchanger Etc. have to be installed, resulting in a problem of increased costs and increased maintenance points.

  An object of the present invention is to install a plurality of air conditioners using an adsorption heat exchanger or install an air conditioner using an adsorption heat exchanger together with an air conditioner using an air heat exchanger. Is to suppress the increase in cost and the increase in maintenance parts.

An air conditioning system according to a first aspect of the present invention is an air conditioning system that processes an indoor latent heat load and a sensible heat load by performing a vapor compression refrigeration cycle operation. A first usage side refrigerant circuit, a plurality of second usage side refrigerant circuits connected to each other in parallel, and a heat source side refrigerant circuit are provided. The first usage-side refrigerant circuit has an adsorption heat exchanger having an adsorbent provided on the surface thereof, and makes the adsorption heat exchanger function as a refrigerant evaporator to adsorb moisture in the air to the adsorbent. It is possible to alternately perform an operation and a regeneration operation in which the adsorption heat exchanger functions as a refrigerant condenser to desorb moisture from the adsorbent. The 2nd utilization side refrigerant circuit has an air heat exchanger, and can perform heat exchange with a refrigerant and air. The heat source side refrigerant circuit has a compression mechanism and a heat source side heat exchanger, and only the compression mechanism of the compression mechanism and the heat source side heat exchanger is common to the first usage side refrigerant circuit and the second usage side refrigerant circuit. Used. The first usage side refrigerant circuit is connected to a discharge gas communication pipe connected to the discharge side of the compression mechanism and an intake gas communication pipe connected to the suction side of the compression mechanism. The air conditioning system can supply the air that has passed through the adsorption heat exchanger indoors, and can supply the air that has passed through the air heat exchanger indoors.

  This air conditioning system is capable of mainly handling indoor latent heat loads by dehumidifying or humidifying the air passing through the adsorption heat exchanger by alternately performing the adsorption operation and the regeneration operation of the adsorption heat exchanger. A first usage-side refrigerant circuit and a plurality of second usage-side refrigerant circuits capable of mainly processing indoor sensible heat loads by exchanging heat with air passing through the air heat exchanger. This constitutes a multi-type air conditioning system. Here, the plurality of first usage-side refrigerant circuits are connected to each other in parallel. The plurality of second usage-side refrigerant circuits are connected to each other in parallel. That is, at least for each system including the first usage-side refrigerant circuit (hereinafter referred to as a latent heat load processing system) or each system including the second usage-side refrigerant circuit (hereinafter referred to as a sensible heat load processing system), The heat source for performing the compression refrigeration cycle operation is integrated. Thereby, it is possible to suppress an increase in cost and an increase in maintenance locations that occur when a plurality of air conditioners using an adsorption heat exchanger are installed.

Further, in this air conditioning system, since both the first use side refrigerant circuit and the second use side refrigerant circuit are connected to one heat source side refrigerant circuit, the heat sources are combined into one and the cost is increased. And the number of maintenance points is further suppressed.

Teeth may, in this air conditioning system, the connection has been latent heat load treatment system via the discharge side and the discharge gas connection pipe and the intake gas connection pipe to the intake side of the compression mechanism of the first use-side refrigerant circuit is the heat source side refrigerant circuit Therefore, in each of the plurality of first usage-side refrigerant circuits, the adsorption heat exchanger functions as an evaporator or a condenser so that dehumidification is performed in an indoor air-conditioned space while other It is possible to perform dehumidification or humidification according to the needs of each indoor air-conditioned space, such as humidification in an air-conditioned space. Moreover, since the compression mechanism can be installed in a place different from the first and second usage-side refrigerant circuits such as outdoors, it is possible to reduce indoor sound and vibration. Here, the compression mechanism includes not only one compressor but also one in which two or more compressors are connected in parallel.

An air conditioning system according to a second aspect of the present invention is an air conditioning system that processes an indoor latent heat load and a sensible heat load by performing a vapor compression refrigeration cycle operation. There comprises a plurality of second utilization side refrigerant circuits are connected in parallel, and a heat source side refrigerant circuit. The first usage-side refrigerant circuit has an adsorption heat exchanger having an adsorbent provided on the surface thereof, and makes the adsorption heat exchanger function as a refrigerant evaporator to adsorb moisture in the air to the adsorbent. It is possible to alternately perform an operation and a regeneration operation in which the adsorption heat exchanger functions as a refrigerant condenser to desorb moisture from the adsorbent. The 2nd utilization side refrigerant circuit has an air heat exchanger, and can perform heat exchange with a refrigerant and air. The heat source side refrigerant circuit has a compression mechanism and a heat source side heat exchanger, and only the compression mechanism of the compression mechanism and the heat source side heat exchanger is common to the first usage side refrigerant circuit and the second usage side refrigerant circuit. Used . The first usage-side refrigerant circuit is connected to a discharge gas communication pipe connected to the discharge side of the compression mechanism and a suction gas communication pipe connected to the suction side of the compression mechanism. The air conditioning system can supply the air that has passed through the adsorption heat exchanger indoors, and can supply the air that has passed through the air heat exchanger indoors.

  In this air-conditioning system, the indoor latent heat load can be mainly processed by dehumidifying or humidifying the air passing through the adsorption heat exchanger by alternately performing the adsorption operation and the regeneration operation of the adsorption heat exchanger. A multi-type equipped with a plurality of second usage-side refrigerant circuits capable of mainly treating indoor sensible heat loads by exchanging heat with air passing through an air heat exchanger. The air conditioning system is configured. Here, in this air conditioning system, since both the first usage side refrigerant circuit and the plurality of second usage side refrigerant circuits are connected to one heat source side refrigerant circuit, the heat sources are combined into one. Cost increase and increase in maintenance points are suppressed. That is, an increase in cost and an increase in maintenance points that occur when an air conditioner using an adsorption heat exchanger is installed together with an air conditioner using an air heat exchanger are suppressed. In addition, in this air conditioning system, the first usage side refrigerant circuit is connected to the discharge side and the suction side of the compression mechanism of the heat source side refrigerant circuit via the discharge gas communication pipe and the suction gas communication pipe to constitute a latent heat load processing system. Therefore, in each of the plurality of first usage-side refrigerant circuits, by making the adsorption heat exchanger function as an evaporator or function as a condenser, dehumidification is performed in an indoor air-conditioned space, while other air conditioning is performed. It is possible to perform dehumidification or humidification according to the needs of each indoor air-conditioned space, such as humidification in a space. Moreover, since the compression mechanism can be installed in a place different from the first and second usage-side refrigerant circuits such as outdoors, it is possible to reduce indoor sound and vibration. Here, the compression mechanism includes not only one compressor but also one in which two or more compressors are connected in parallel.

Air conditioning system according to a third aspect of the present invention is the air conditioning system according to the first or second invention, the second use-side refrigerant circuit is connected to the liquid connecting pipe connected to the liquid side of the heat source-side heat exchanger In addition, the discharge gas communication pipe and the intake gas communication pipe are switchably connected via a switching mechanism.
In this air conditioning system, the second usage side refrigerant circuit is connected to the liquid side of the heat source side heat exchanger of the heat source side refrigerant circuit via a liquid communication pipe, and the discharge gas is communicated to the discharge side and the suction side of the compression mechanism. Since the sensible heat load processing system is configured by being connected via the piping and the suction gas communication piping, and the connection state between the discharge side and the suction side of the compression mechanism can be switched by the switching mechanism, By switching the switching mechanism so that it is connected via the gas communication piping, the air heat exchanger functions as a condenser for indoor heating, or the switching mechanism so that it is connected via the intake gas communication piping By switching the, it is possible to cause the air heat exchanger to function as an evaporator and perform indoor cooling. In addition, in each of the plurality of second usage-side refrigerant circuits, the air heat exchanger functions as an evaporator or a condenser, so that cooling is performed in an indoor air-conditioned space while heating is performed in another air-conditioned space. It is possible to configure an air conditioning system capable of performing cooling or heating at the same time, that is, so-called simultaneous cooling and heating, according to the needs of each indoor location.

Air conditioning system according to a fourth aspect of the present invention is the air conditioning system according to the first or second invention, the second use-side refrigerant circuit, the liquid connection pipe and the intake gas which is connected to the liquid side of the heat source-side heat exchanger Connected to communication piping.
In this air conditioning system, the second usage side refrigerant circuit is connected to the liquid side of the heat source side heat exchanger of the heat source side refrigerant circuit via a liquid communication pipe, and to the suction side of the compression mechanism via an intake gas communication pipe. Therefore, the air heat exchanger can function as an evaporator to cool indoors.

Air conditioning system according to a fifth aspect of the present invention, first to fourth one in accordance keep the air conditioning system of the invention, the first utilization side refrigerant circuit and the second utilization side refrigerant circuit, an integral utilization unit is doing.
In this air conditioning system, the first usage-side refrigerant circuit and the second usage-side refrigerant circuit constitute an integrated usage unit, and therefore the unit including the first usage-side refrigerant circuit indoors and the second usage-side refrigerant Compared with the case where the unit provided with the circuit is installed separately, the unit size can be reduced and the labor for installing the unit can be reduced.

An air conditioning system according to a sixth aspect is the air conditioning system according to the fifth aspect , wherein the utilization unit can supply the air dehumidified or humidified in the adsorption heat exchanger indoors.
In this air conditioning system, air that has been dehumidified or humidified (that is, subjected to latent heat treatment) in the adsorption heat exchanger, that is, the first usage-side refrigerant circuit, can be supplied indoors. Only the operation of dehumidifying or humidifying can be performed.

An air conditioning system according to a seventh aspect is the air conditioning system according to the fifth aspect , wherein the utilization unit allows the air dehumidified or humidified in the adsorption heat exchanger to exchange heat with the refrigerant in the air heat exchanger. Is possible.
In this air conditioning system, the adsorption heat exchanger, that is, the air that has been dehumidified or humidified (that is, subjected to latent heat treatment) in the first usage-side refrigerant circuit can be further subjected to sensible heat treatment. Even if some sensible heat load is processed together with the latent heat load due to the change to a temperature that is not suitable for the indoor target air temperature, this air is not blown out indoors, but air heat exchange is also performed. After performing the sensible heat treatment with the vessel to a temperature suitable for the indoor target air temperature, the operation of blowing out indoors can be performed.

Air conditioning system according to the eighth invention, in any one of the air conditioning system according to a seventh invention, is connected to the gas side of the air heat exchanger, to function air heat exchanger as an evaporator of refrigerant A pressure adjusting mechanism for controlling the evaporation pressure of the refrigerant in the air heat exchanger.
An air conditioning system according to a ninth aspect of the present invention is the air conditioning system according to the eighth aspect of the present invention, wherein the air heat exchanger is made to function as an evaporator by the pressure adjustment mechanism based on the dew point temperature of indoor air. To control the evaporation pressure.

  In this air conditioning system, based on the dew point temperature of indoor air, for example, by controlling the pressure adjusting mechanism so that the evaporation temperature of the refrigerant in the air heat exchanger does not become the dew point temperature or less, the air heat exchanger The generation of drain water in the air heat exchanger can be suppressed by preventing moisture in the air from condensing on the surface. Thereby, a drain pipe is not required for the unit having the second usage-side refrigerant circuit, and labor saving in the installation work of the unit having the second usage-side refrigerant circuit can be achieved.

  Here, the dew point temperature of indoor air can be measured, for example, by measuring the dew point temperature of indoor air sucked into this unit using a dew point sensor provided in the unit having an air heat exchanger, A temperature / humidity sensor provided in a unit having a heat exchanger may be used to actually measure the temperature and humidity of indoor air sucked into the unit and calculate the dew point temperature from these measured values. If the unit with an air heat exchanger does not have a dew point sensor or temperature / humidity sensor, use the measured values of the dew point sensor and temperature / humidity sensor provided on the unit with an adsorption heat exchanger. Also good.

An air conditioning system according to a tenth aspect of the present invention is the air conditioning system according to the ninth aspect of the present invention, further comprising a pressure detection mechanism that detects a refrigerant pressure in the air heat exchanger. The air conditioning system calculates a target evaporation pressure value from the dew point temperature of indoor air, and adjusts the refrigerant evaporation pressure detected by the pressure detection mechanism to be equal to or higher than the target evaporation pressure value by the pressure adjustment mechanism.

In this air conditioning system, the control value of the refrigerant evaporation pressure in the air heat exchanger by the pressure adjustment mechanism uses the evaporation pressure of the refrigerant in the air heat exchanger measured by the pressure detection mechanism instead of the dew point temperature. Control responsiveness can be improved compared to the case where the evaporation pressure of the refrigerant is controlled using the dew point temperature.
An air conditioning system according to an eleventh aspect of the invention is the air conditioning system according to the tenth aspect of the invention, further comprising a condensation detection mechanism that detects the presence or absence of condensation in the air heat exchanger. The air conditioning system changes the target evaporation pressure value when dew condensation is detected by the dew condensation detection mechanism.

In this air conditioning system, the dew condensation detection mechanism reliably detects dew condensation in the air heat exchanger, and when dew condensation is detected, for example, by making a change to increase the target evaporation pressure value, the air heat exchanger The evaporating temperature of the refrigerant in can be increased, and condensation in the air heat exchanger can be reliably prevented.
An air conditioning system according to a twelfth aspect of the present invention is the air conditioning system according to the tenth aspect of the present invention, further comprising a dew condensation detection mechanism that detects the presence or absence of dew condensation in the air heat exchanger. The air conditioning system stops the compression mechanism when condensation is detected by the condensation detection mechanism.

In this air conditioning system, the condensation detection mechanism reliably detects condensation in the air heat exchanger, and when the condensation is detected, the compression mechanism is stopped so that condensation in the air heat exchanger is ensured. Can be prevented.
An air conditioning system according to a thirteenth aspect of the present invention is the air conditioning system according to the tenth aspect of the present invention, further comprising a dew condensation detection mechanism that detects the presence or absence of dew condensation in the air heat exchanger. The 2nd utilization side refrigerant circuit is provided with the utilization side expansion valve connected to the liquid side of the air heat exchanger. The air conditioning system closes the use side expansion valve when dew condensation is detected by the dew condensation detection mechanism.

  In this air conditioning system, the dew condensation detection mechanism reliably detects dew condensation in the air heat exchanger and closes the user side expansion valve when dew condensation is detected. Can be surely prevented.

As described above, according to the present invention, the following effects can be obtained.
In 1st invention, the increase in cost and the increase in a maintenance location which arise when installing two or more air conditioning apparatuses using an adsorption heat exchanger can be suppressed. Moreover, since both the 1st utilization side refrigerant circuit and the 2nd utilization side refrigerant circuit are connected with respect to one heat source side refrigerant circuit, a heat source is put together into one and the cost increase and the increase in a maintenance location increase. It is further suppressed.

In 2nd invention, the increase in the cost which arises when installing the air conditioning apparatus using an adsorption heat exchanger with the air conditioning apparatus using an air heat exchanger, and the increase in a maintenance location can be suppressed.
In the third invention, in each of the plurality of second usage-side refrigerant circuits, the air heat exchanger is allowed to function as an evaporator or a condenser so that cooling is performed in an indoor air-conditioned space, It is possible to configure an air conditioning system that can perform cooling and heating simultaneously, that is, cooling or heating at the same time according to the needs of each indoor air-conditioned space, such as heating in an air-conditioned space. is there.

In the fourth aspect of the invention, it is possible to perform indoor cooling by causing the air heat exchanger to function as an evaporator.
In the fifth aspect of the invention, the unit size is reduced and the unit installation work is performed as compared with the case where the unit having the first usage-side refrigerant circuit and the unit having the second usage-side refrigerant circuit are separately installed indoors. Can be saved.

In 6th invention, only the driving | operation which dehumidifies or humidifies indoors can be performed by one unit.
In the seventh aspect of the invention, for example, even when the sensible heat load is somewhat processed by the adsorption heat exchanger and the air temperature is changed to a temperature not suitable for the indoor target air temperature, In addition, it is possible to perform an operation of blowing out indoors after sensible heat treatment is performed with an air heat exchanger to achieve a temperature suitable for the indoor target air temperature.

In the eighth and ninth inventions, a drain pipe is not required for the unit having the second usage side refrigerant circuit, labor saving of the installation work of the unit having the second usage side refrigerant circuit, and further, the first usage side refrigerant circuit Labor saving can be achieved in the installation work of all the units having both the first and second usage-side refrigerant circuits.
In the tenth invention, as the control value of the refrigerant evaporation pressure in the air heat exchanger by the pressure adjustment mechanism, the evaporation pressure of the refrigerant in the air heat exchanger measured by the pressure detection mechanism is used instead of the dew point temperature. Control responsiveness can be improved compared to the case where the evaporation pressure of the refrigerant is controlled using the dew point temperature.

In the eleventh invention, the dew condensation detection mechanism reliably detects dew condensation in the air heat exchanger, and when dew condensation is detected, for example, the air heat exchanger is changed by increasing the target evaporation pressure value. The evaporating temperature of the refrigerant in can be increased, and condensation in the air heat exchanger can be reliably prevented.
In the twelfth invention, the dew condensation detection mechanism reliably detects dew condensation in the air heat exchanger, and when dew condensation is detected, the second compression mechanism is stopped. Condensation can be reliably prevented.

In the thirteenth invention, the dew condensation detection mechanism reliably detects dew condensation in the air heat exchanger and closes the use side expansion valve when dew condensation is detected. Can be surely prevented.

Hereinafter, an embodiment of an air conditioning system according to the present invention will be described based on the drawings.
[First Embodiment]
(1) Configuration of Air Conditioning System FIG. 1 is a schematic refrigerant circuit diagram of an air conditioning system 1 according to a first embodiment of the present invention. The air conditioning system 1 is an air conditioning system that processes an indoor latent heat load and a sensible heat load such as a building by performing a vapor compression refrigeration cycle operation. The air conditioning system 1 is a so-called separate type multi-air conditioning system, and mainly includes a plurality of (in this embodiment, two) latent heat system utilization units 2 and 3 connected in parallel with each other, A plurality of (in this embodiment, two) sensible heat system utilization units 4 and 5, a heat source unit 6, latent heat system utilization units 2 and 3, and a sensible heat system utilization unit 4 and 5 and a heat source connected in parallel Connecting pipes 7, 8, 9 for connecting the unit 6 are provided. In the present embodiment, the heat source unit 6 functions as a heat source common to the latent heat system use units 2 and 3 and the sensible heat system use units 4 and 5. In this embodiment, only one heat source unit 6 is provided. However, when there are a large number of latent heat system use units 2, 3 and sensible heat system use units 4, 5, etc., a plurality of units are connected in parallel. It may be.

<Latent heat system use unit>
The latent heat system utilization units 2 and 3 are installed in an indoor ceiling of a building or the like by being hung or suspended, by a wall or the like, or in a space behind the ceiling. The latent heat system use units 2 and 3 are connected to the heat source unit 6 via the connection pipes 8 and 9, and constitute a refrigerant circuit 10 with the heat source unit 6. The latent heat system use units 2 and 3 perform a vapor compression refrigeration cycle operation by circulating the refrigerant in the refrigerant circuit 10 to mainly process a latent heat load indoors (also in the following description). When the term “latent heat load processing system” is used, it functions as a combination of the latent heat system use units 2 and 3 and the heat source unit 6).

  Next, the configuration of the latent heat system use units 2 and 3 will be described. Since the latent heat system utilization unit 2 and the latent heat system utilization unit 3 have the same configuration, only the configuration of the latent heat system utilization unit 2 will be described here. The configuration of the latent heat system utilization unit 3 will be described below. Reference numerals in the 30th order are assigned instead of reference numerals in the 20th order indicating the respective parts of 2, and description of each part is omitted.

The latent heat system utilization unit 2 mainly constitutes a part of the refrigerant circuit 10 and includes a latent heat system utilization side refrigerant circuit 10a capable of dehumidifying or humidifying air. This latent heat system utilization side refrigerant circuit 10a mainly includes a latent heat system utilization side four-way switching valve 21, a first adsorption heat exchanger 22, a second adsorption heat exchanger 23, and a latent heat system utilization side expansion valve 24. I have.
The latent heat system use side four-way switching valve 21 is a valve for switching the flow path of the refrigerant flowing into the latent heat system use side refrigerant circuit 10a, and the first port 21a thereof is connected to the heat source unit 6 via the discharge gas communication pipe 8. The second port 21b is connected to the suction side of the compression mechanism 61 of the heat source unit 6 via the suction gas communication pipe 9, and the third port 21b is connected to the discharge side of the compression mechanism 61 (described later). 21 c is connected to the gas side end of the first adsorption heat exchanger 22, and the fourth port 21 d is connected to the gas side end of the second adsorption heat exchanger 23. The latent heat system use side four-way switching valve 21 connects the first port 21a and the third port 21c and connects the second port 21b and the fourth port 21d (first state, using the latent heat system of FIG. 1). 1), the first port 21a and the fourth port 21d are connected, and the second port 21b and the third port 21c are connected (second state, latent heat system of FIG. 1). It is possible to perform switching that refers to the broken line of the use side four-way switching valve 21).

  The first adsorption heat exchanger 22 and the second adsorption heat exchanger 23 are cross fin type fin-and-tube heat exchangers configured by heat transfer tubes and a large number of fins. Specifically, the first adsorption heat exchanger 22 and the second adsorption heat exchanger 23 include a large number of aluminum fins formed in a rectangular plate shape, and a copper heat transfer tube penetrating the fins. Yes. The first adsorption heat exchanger 22 and the second adsorption heat exchanger 23 are not limited to cross fin type fin-and-tube type heat exchangers, but other types of heat exchangers, for example, corrugated fin type It may be a heat exchanger or the like.

  In the first adsorption heat exchanger 22 and the second adsorption heat exchanger 23, an adsorbent is supported on the surface of the fin by dip molding (immersion molding). The method for supporting the adsorbent on the surfaces of the fins and the heat transfer tubes is not limited to dip molding, and the adsorbent may be supported on the surface by any method as long as the performance as the adsorbent is not impaired. . As this adsorbent, functionalities such as zeolite, silica gel, activated carbon, organic polymer polymer material having hydrophilicity or water absorption, ion exchange resin material having carboxylic acid group or sulfonic acid group, thermosensitive polymer, etc. A polymer material or the like can be used.

  The first adsorption heat exchanger 22 and the second adsorption heat exchanger 23 function as a refrigerant evaporator while allowing air to pass outside thereof, so that moisture in the air is adsorbed by the adsorbent supported on the surface of the first adsorption heat exchanger 22 and the second adsorption heat exchanger 23. Can be made. In addition, the first adsorption heat exchanger 22 and the second adsorption heat exchanger 23 function as a refrigerant condenser while allowing air to pass through the outside of the first adsorption heat exchanger 22 and the second adsorption heat exchanger 23. Can be desorbed.

The latent heat system use side expansion valve 24 is an electric expansion valve connected between the liquid side end of the first adsorption heat exchanger 22 and the liquid side end of the second adsorption heat exchanger 23, and serves as a condenser. Depressurizing the refrigerant sent from one of the functioning first adsorption heat exchanger 22 and the second adsorption heat exchanger 23 to the other of the first adsorption heat exchanger 22 and the second adsorption heat exchanger 23 functioning as an evaporator. Can do.
Further, although not shown in detail, the latent heat system utilization unit 2 is configured to suck outside air (hereinafter referred to as “outdoor air OA”) into the unit, and to discharge the air from inside the unit to the outside. , An indoor air inlet for sucking indoor air (hereinafter referred to as indoor air RA) into the unit, and air blown indoors from the unit (hereinafter referred to as supply air SA) The air flow path for switching the air flow path, the exhaust fan disposed in the unit so as to communicate with the exhaust port, the air supply fan disposed in the unit so as to communicate with the air inlet, And a switching mechanism including a damper or the like. Thereby, the latent heat system utilization unit 2 sucks the outdoor air OA from the outside air inlet into the unit and passes it through the first or second adsorption heat exchangers 22 and 23, and then supplies the air SA supplied indoors from the inlet. Or the outdoor air OA is sucked into the unit from the outside air inlet and passed through the first or second adsorption heat exchangers 22, 23, and then discharged as exhaust air EA from the outlet to the outside. The air RA is sucked into the unit from the inside air suction port, passed through the first or second adsorption heat exchangers 22 and 23, and then supplied indoors as the supply air SA from the air supply port, or the indoor air RA is sucked into the inside air After being sucked into the unit from the mouth and passed through the first or second adsorptive heat exchangers 22 and 23, the air can be discharged from the exhaust port to the outside as exhaust air EA.

  Furthermore, the latent heat system utilization unit 2 includes an RA intake temperature / humidity sensor 25 that detects the temperature and relative humidity of the indoor air RA sucked into the unit, and the temperature and relative humidity of the outdoor air OA sucked into the unit. OA intake temperature / humidity sensor 26 to detect, SA supply temperature sensor 27 to detect the temperature of supply air SA supplied indoors from within the unit, and latent heat system to control the operation of each part constituting the latent heat system utilization unit 2 And a use side control unit 28. The latent heat system use side control unit 28 includes a microcomputer and a memory provided for controlling the latent heat system use unit 2, and passes through the remote controller 11 and a heat source side control unit 65 of the heat source unit 6 described later. In addition, it is possible to exchange input signals for the target temperature and humidity of the indoor air, and to exchange control signals and the like with the heat source unit 6.

<Sensible heat system use unit>
The sensible heat system utilization units 4 and 5 are installed in a ceiling or the like by embedding or hanging in an indoor ceiling of a building or the like, or by hanging on a wall or the like. The sensible heat system utilization units 4, 5 are connected to the heat source unit 6 via the connection pipes 7, 8, 9 and the connection units 14, 15, and constitute a refrigerant circuit 10 with the heat source unit 6. . The sensible heat system use units 4 and 5 function as a sensible heat load processing system that mainly processes indoor sensible heat loads by circulating a refrigerant in the refrigerant circuit 10 and performing a vapor compression refrigeration cycle operation. (In the following description, the term “latent heat load processing system” refers to a combination of the latent heat system utilization units 2 and 3 and the heat source unit 6). The sensible heat system utilization unit 4 is installed in the same conditioned space as the latent heat system utilization unit 2, and the sensible heat system utilization unit 5 is installed in the same conditioned space as the latent heat system utilization unit 3. That is, the latent heat system utilization unit 2 and the sensible heat system utilization unit 4 are paired to process a latent heat load and a sensible heat load in a certain air-conditioned space. Are paired to process the latent heat load and sensible heat load of another air-conditioned space.

  Next, the structure of the sensible heat system utilization units 4 and 5 will be described. In addition, since the sensible heat system utilization unit 4 and the sensible heat system utilization unit 5 have the same configuration, only the configuration of the sensible heat system utilization unit 4 will be described here. The reference numerals in the 50s are attached instead of the reference numerals in the 40s indicating the respective parts of the sensible heat system utilization unit 4, and the description of each part is omitted.

  The sensible heat system utilization unit 4 mainly constitutes a part of the refrigerant circuit 10, and the sensible heat system utilization side refrigerant circuit 10c capable of dehumidifying or humidifying the air (in the sensible heat system utilization unit 5, the sensible heat system utilization unit 5 A heat system utilization side refrigerant circuit 10d) is provided. The sensible heat system use side refrigerant circuit 10 c mainly includes a sensible heat system use side expansion valve 41 and an air heat exchanger 42. In the present embodiment, the sensible heat system utilization side expansion valve 41 is an electric expansion valve connected to the liquid side of the air heat exchanger 42 in order to adjust the refrigerant flow rate. In the present embodiment, the air heat exchanger 42 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and performs heat exchange between the refrigerant and the indoor air RA. Equipment. In the present embodiment, the sensible heat system utilization unit 4 includes a blower fan (not shown) for supplying indoor air RA as supply air SA after sucking indoor air RA into the unit and exchanging heat. It is possible to exchange heat between the indoor air RA and the refrigerant flowing through the air heat exchanger 322.

  The sensible heat system utilization unit 4 is provided with various sensors. A liquid side temperature sensor 43 that detects the temperature of the liquid refrigerant is provided on the liquid side of the air heat exchanger 42, and a gas side temperature sensor 44 that detects the temperature of the gas refrigerant on the gas side of the air heat exchanger 42. Is provided. Further, the sensible heat system utilization unit 4 is provided with an RA suction temperature sensor 55 for detecting the temperature of the indoor air RA sucked into the unit. In addition, the sensible heat system utilization unit 4 includes a sensible heat system utilization side control unit 48 that controls the operation of each part constituting the sensible heat system utilization unit 4. The sensible heat system use side control unit 48 includes a microcomputer and a memory provided for controlling the sensible heat system use unit 4, and the target temperature and target humidity of the indoor air through the remote controller 11. It is also possible to exchange input signals and the like, and exchange control signals and the like with the heat source unit 6.

<Heat source unit>
The heat source unit 6 is installed on the rooftop of a building or the like, and is connected to the latent heat system use units 2 and 3 and the sensible heat system use units 4 and 5 via the connecting pipes 7, 8, and 9. A refrigerant circuit 10 is configured between the use units 2 and 3 and the sensible heat system use units 4 and 5.

Next, the configuration of the heat source unit 6 will be described. The heat source unit 6 mainly constitutes a part of the refrigerant circuit 10 and includes a heat source side refrigerant circuit 10e. The heat source side refrigerant circuit 10e mainly includes a compression mechanism 61, a three-way switching valve 62, a heat source side heat exchanger 63, a heat source side expansion valve 64, and a receiver 68.
In the present embodiment, the compression mechanism 61 is a positive displacement compressor capable of changing the operation capacity by inverter control. In the present embodiment, the compression mechanism 61 is a single compressor, but is not limited to this, and two or more compressors are connected in parallel according to the number of units used. May be.

  The three-way switching valve 62 connects the discharge side of the compression mechanism 61 and the gas side of the heat source side heat exchanger 63 when the heat source side heat exchanger 63 functions as a condenser (hereinafter referred to as a condensation operation state). When the heat source side heat exchanger 63 functions as an evaporator (hereinafter referred to as an evaporation operation state), the heat source is connected so that the suction side of the compression mechanism 61 and the gas side of the heat source side heat exchanger 63 are connected. This is a valve for switching the flow path of the refrigerant in the side refrigerant circuit 10e. The first port 62a is connected to the discharge side of the compression mechanism 61, and the second port 62b is connected to the suction side of the compression mechanism 61. The third port 62 c is connected to the gas side end of the heat source side heat exchanger 63. As described above, the three-way switching valve 62 connects the first port 62a and the third port 62c (corresponding to the condensation operation state, see the solid line of the three-way switching valve 62 in FIG. 1), It is possible to perform switching to connect the 2-port 62b and the third port 62c (corresponding to the evaporation operation state, see the broken line of the three-way switching valve 62 in FIG. 1). A discharge gas communication pipe 8 is connected between the discharge side of the compression mechanism 61 and the three-way switching valve 62. Accordingly, the high-pressure gas refrigerant compressed and discharged by the compression mechanism 61 can be supplied to the latent heat system use units 2 and 3 and the sensible heat system use units 4 and 5 regardless of the switching operation of the three-way switching valve 62. It has become. The suction side of the compression mechanism 61 is connected to a suction gas communication pipe 9 through which a low-pressure gas refrigerant returning from the latent heat system use units 2 and 3 and the sensible heat system use units 4 and 5 flows.

  In this embodiment, the heat source side heat exchanger 63 is a cross-fin type fin-and-tube heat exchanger constituted by heat transfer tubes and a large number of fins, and exchanges heat with refrigerant using air as a heat source. Equipment. In the present embodiment, the heat source unit 6 includes an outdoor fan (not shown) for taking outdoor air into the unit and sending it out, and heats the outdoor air and the refrigerant flowing through the heat source side heat exchanger 63. It is possible to exchange.

  In the present embodiment, the heat source side expansion valve 64 can adjust the flow rate of the refrigerant flowing between the heat source side heat exchanger 63 and the air heat exchangers 42 and 52 via the liquid communication pipe 7. It is an electric expansion valve. The heat source side expansion valve 64 is used in a substantially fully open state when the heat source side heat exchanger 63 is in the condensing operation state, and the opening degree is adjusted when the heat source side heat exchanger 63 is in the condensing operation state and communicates with the liquid from the air heat exchangers 42 and 52. It is used to decompress the refrigerant flowing into the heat source side heat exchanger 63 via the pipe 7.

The receiver 68 is a container for temporarily storing the refrigerant flowing between the heat source side heat exchanger 63 and the air heat exchangers 42 and 52. In the present embodiment, the receiver 68 is connected between the heat source side expansion valve 64 and the liquid communication pipe 7.
The heat source unit 6 is provided with various sensors. Specifically, the heat source unit 6 performs the operation of the suction pressure sensor 66 that detects the suction pressure of the compression mechanism 61, the discharge pressure sensor 67 that detects the discharge pressure of the compression mechanism 61, and the operation of each part of the heat source unit 6. The heat source side control part 65 to control is provided. The heat source side control unit 65 includes a microcomputer and a memory provided to control the heat source unit 6, and the latent heat system use side control units 28 and 38 of the latent heat system use units 2 and 3 Control signals can be transmitted between the sensible heat system use side control units 48 and 58 of the heat system use units 4 and 5. In addition, the heat source side control unit 65 can exchange control signals and the like with the heat source side control unit 65.

  In the air conditioning system 1 of the present embodiment, the high-pressure gas refrigerant compressed and discharged by the compression mechanism 61 of the heat source unit 6 is supplied to the adsorption heat exchangers 22 of the latent heat system utilization units 2 and 3 via the discharge gas communication pipe 8. 23, 32, 33, and return to the suction side of the compression mechanism 61 of the heat source unit 6 from the adsorption heat exchangers 22, 23, 32, 33 of the latent heat system utilization units 2, 3 through the suction gas communication pipe 9. Can be done. For this reason, indoor dehumidification or humidification can be performed regardless of the operation of the sensible heat system utilization units 4 and 5.

  The sensible heat system utilization units 4 and 5 are connected to the gas side of the air heat exchangers 42 and 52 so as to be switchable to the discharge gas communication pipe 8 and the suction gas communication pipe 9 via the connection units 14 and 15. The connection units 14 and 15 mainly include cooling / heating switching valves 71 and 81 and connection unit control units 72 and 82 for controlling operations of the respective parts constituting the connection units 14 and 15. When the sensible heat system utilization units 4 and 5 perform the cooling operation, the cooling / heating switching valves 71 and 81 are connected to the gas side of the air heat exchangers 42 and 52 of the sensible heat system utilization units 4 and 5 and the intake gas communication pipe 9. When the sensible heat system use units 4 and 5 perform the heating operation, the gas side of the air heat exchangers 42 and 52 of the sensible heat system use units 4 and 5 is connected. Is a valve that functions as a switching mechanism for switching between a state (hereinafter referred to as a heating operation state) for connecting the discharge gas communication pipe 8 and the discharge gas communication pipe 8, and the first ports 71 a and 81 a are connected to the air heat exchangers 42 and 52. The second ports 71 b and 81 b are connected to the intake gas communication pipe 9, and the third ports 71 c and 81 c are connected to the discharge gas communication pipe 8. As described above, the cooling / heating switching valves 71, 81 connect the first ports 71a, 81a and the second ports 71b, 81b (corresponding to the cooling operation state, the solid lines of the cooling / heating switching valves 71, 81 in FIG. 1). Or the first port 71a, 81a and the third port 71c, 81c can be switched (corresponding to the heating operation state, see the broken line of the cooling / heating switching valves 71, 81 in FIG. 1). is there. The connection unit control units 72 and 82 include a microcomputer and a memory provided for controlling the connection units 14 and 15, and the sensible heat system use side control unit 48 of the sensible heat system use units 4 and 5. , 58 can transmit a control signal. As a result, the sensible heat system utilization units 4 and 5 can perform so-called simultaneous cooling and heating operations such as heating the sensible heat system utilization unit 5 while cooling the sensible heat system utilization unit 4. It has become.

(2) Operation | movement of an air conditioning system Next, operation | movement of the air conditioning system 1 of this embodiment is demonstrated. The air conditioning system 1 can process an indoor latent heat load with a latent heat load processing system, and can process an indoor sensible heat load mainly with a sensible heat load processing system. Prior to the description of the various operation operations, first, the operation during the independent operation of the latent heat load processing system of the air conditioning system 1 (that is, when the sensible heat system utilization units 4 and 5 are not operated) will be described.

The air conditioning system 1 can perform various dehumidifying operations and humidifying operations as described below by an independent operation of only the latent heat load processing system.
<All ventilation modes>
First, the dehumidifying operation and the humidifying operation in the full ventilation mode will be described. In the full ventilation mode, when the air supply fan and the exhaust fan of the latent heat system utilization units 2 and 3 are operated, the outdoor air OA is sucked into the unit through the outside air inlet and supplied indoors as the supply air SA through the air inlet. Then, an operation is performed in which the indoor air RA is sucked into the unit through the inside air suction port and is discharged to the outside as exhaust air EA through the exhaust port.

The operation during the dehumidifying operation in the full ventilation mode will be described with reference to FIGS. 2, 3, and 4. Here, FIGS. 2 and 3 are schematic refrigerant circuit diagrams showing the operation during the dehumidifying operation in the full ventilation mode when only the latent heat load processing system of the air conditioning system 1 is operated. FIG. 4 is a control flow diagram when only the latent heat load processing system of the air conditioning system 1 is operated.
2 and 3, during the dehumidifying operation, for example, in the latent heat system use unit 2, the first adsorption heat exchanger 22 becomes a condenser and the second adsorption heat exchanger 23 becomes an evaporator. And the second operation in which the second adsorption heat exchanger 23 serves as a condenser and the first adsorption heat exchanger 22 serves as an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated.

In the following description, the operations of the two latent heat system use units 2 and 3 will be described together.
In the first operation, the regeneration operation for the first adsorption heat exchangers 22 and 32 and the adsorption operation for the second adsorption heat exchangers 23 and 33 are performed in parallel. During the first operation, as shown in FIG. 2, the latent heat system use-side four-way switching valves 21 and 31 are in the first state (see the solid line of the latent heat system use-side four-way switching valves 21 and 31 in FIG. 2). Is set. In this state, the high-pressure gas refrigerant discharged from the compression mechanism 61 flows into the first adsorption heat exchangers 22 and 32 through the discharge gas communication pipe 8 and the latent heat system use-side four-way switching valves 21 and 31, and the first It condenses while passing through the adsorption heat exchangers 22 and 32. The condensed refrigerant is depressurized by the latent heat system use side expansion valves 24 and 34 and then evaporated while passing through the second adsorption heat exchangers 23 and 33, and the latent heat system use side four-way switching valve 21. , 31 is again sucked into the compression mechanism 61 through the suction gas communication pipe 9 (see the arrow attached to the refrigerant circuit 10 in FIG. 2). At this time, since the sensible heat system utilization side expansion valves 41 and 51 of the sensible heat system utilization units 4 and 5 are closed, the refrigerant does not flow into the sensible heat system utilization units 4 and 5.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is discharged to the outdoors as exhaust air EA through the exhaust port accompanying the indoor air RA. In the second adsorption heat exchangers 23 and 33, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the adsorption heat generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the outdoor air OA dehumidified by the second adsorption heat exchangers 23 and 33 is supplied indoors as supply air SA through the air supply port (adsorption heat exchangers 22, 23, 32 and 33 in FIG. 2). (See arrows on both sides of the).

  In the second operation, the adsorption operation for the first adsorption heat exchangers 22 and 32 and the regeneration operation for the second adsorption heat exchangers 23 and 33 are performed in parallel. During the second operation, as shown in FIG. 3, the latent heat system use-side four-way switching valves 21, 31 are in the second state (see the broken lines of the latent heat system use-side four-way switching valves 21, 31). Is set. In this state, the high-pressure gas refrigerant discharged from the compression mechanism 61 flows into the second adsorption heat exchangers 23 and 33 through the discharge gas communication pipe 8 and the latent heat system use side four-way switching valves 21 and 31, and the second It condenses while passing through the adsorption heat exchangers 23 and 33. The condensed refrigerant is depressurized by the latent heat system use side expansion valves 24 and 34, and then evaporated while passing through the first adsorption heat exchangers 22 and 32, and the latent heat system use side four-way switching valve 21. , 31 is again sucked into the compression mechanism 61 through the suction gas communication pipe 9 (see the arrow attached to the refrigerant circuit 10 in FIG. 3).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the second adsorption heat exchangers 23, 33 is discharged to the outdoors as exhaust air EA through the exhaust port accompanying the indoor air RA. In the first adsorption heat exchangers 22 and 32, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the outdoor air OA dehumidified by the first adsorption heat exchangers 22 and 32 is supplied indoors as supply air SA through the air supply port (adsorption heat exchangers 22, 23, 32, and 33 in FIG. 3). (See arrows on both sides of the).

Here, the system control performed at the time of the independent operation of only the latent heat load processing system of the air conditioning system 1 will be described.
First, when the indoor air target temperature and target relative humidity are set by the remote controllers 11 and 12, the latent heat system use side control units 28 and 38 of the latent heat system use units 2 and 3 receive these target temperature values and targets. Along with the relative humidity value, the temperature value and relative humidity value of the indoor air sucked into the unit detected by the RA suction temperature / humidity sensors 25, 35, and the unit detected by the OA suction temperature / humidity sensors 26, 36 The temperature value and the relative humidity value of the outdoor air sucked in are input.

  Then, in step S1, the latent heat system use side control units 28 and 38 calculate the target value of enthalpy or the target value of absolute humidity from the target temperature value and target relative humidity value of indoor air, The current value of enthalpy of air sucked into the unit from the indoor or the current value of absolute humidity is calculated from the temperature value and the relative humidity value detected by the humidity sensors 25 and 35, and the difference between the two values (hereinafter referred to as necessary latent heat capacity). Value Δh). Here, the necessary latent heat capacity value Δh is the difference between the target value of the indoor air enthalpy or the target value of absolute humidity and the current enthalpy value or absolute humidity value of the indoor air, as described above. This corresponds to the latent heat load that must be processed in the system 1. Then, the value of the necessary latent heat capacity value Δh is converted into a capacity UP signal K1 for notifying the heat source side controller 65 whether or not the processing capacity of the latent heat system utilization units 2 and 3 needs to be increased. For example, when the absolute value of Δh is smaller than a predetermined value (that is, when the humidity value of indoor air is close to the target humidity value and there is no need to increase or decrease the processing capacity), the capability UP signal K1 is set to “ 0, and when the absolute value of Δh is larger than the predetermined value in the direction in which the processing capacity must be increased (that is, in the dehumidifying operation, the humidity value of indoor air is higher than the target humidity value and the processing capacity needs to be increased) If the capacity UP signal K1 is “A” and the absolute value of Δh is larger than the predetermined value in the direction in which the processing capacity must be reduced (that is, in the dehumidifying operation, the humidity value of the indoor air is If the humidity is lower than the target humidity value and the processing capacity needs to be lowered, the capacity UP signal K1 is set to “B”.

  Next, in step S2, the heat source side control unit 65 uses the capability UP signal K1 of the latent heat system utilization units 2 and 3 transmitted from the latent heat system utilization side control units 28 and 38, and uses the target condensation temperature value TcS1 and the target condensation temperature value TcS1. An evaporation temperature value TeS1 is calculated. For example, the target condensation temperature value TcS1 is calculated by adding the capability UP signal K1 of the latent heat system use units 2 and 3 to the current target condensation temperature value. Further, the target evaporation temperature value TeS1 is calculated by subtracting the capability UP signal K1 of the latent heat system use units 2 and 3 from the current target evaporation temperature value. Thereby, when the value of the capability UP signal K1 is “A”, the target condensing temperature value TcS1 becomes high and the target evaporation temperature value TeS1 becomes low.

  Next, in step S3, a system condensing temperature value Tc1 and a system evaporating temperature value Te1 which are values corresponding to actual measured values of the condensing temperature and the evaporating temperature of the entire air conditioning system 1 are calculated. For example, the system condensing temperature value Tc1 and the system evaporation temperature value Te1 are the suction pressure value of the compression mechanism 61 detected by the suction pressure sensor 66 and the discharge pressure value of the compression mechanism 61 detected by the discharge pressure sensor 67. It is calculated by converting into the refrigerant saturation temperature at the pressure value. Then, the temperature difference ΔTc1 of the target condensation temperature value TcS1 with respect to the system condensation temperature value Tc1 and the temperature difference ΔTe1 of the target evaporation temperature value TeS1 with respect to the system evaporation temperature value Te1 are calculated, and by dividing these temperature differences, the compression mechanism 61 Determine whether the operating capacity needs to be increased or decreased and the range of increase or decrease.

  By controlling the operation capacity of the compression mechanism 61 using the operation capacity of the compression mechanism 61 determined in this way, system control is performed so as to approach the target temperature and target relative humidity of indoor air. For example, when the value obtained by subtracting the temperature difference ΔTe1 from the temperature difference ΔTc1 is a positive value, the operating capacity of the compression mechanism 61 is increased. Conversely, when the value obtained by subtracting the temperature difference ΔTe1 from the temperature difference ΔTc1 is a negative value Controls to reduce the operating capacity of the compression mechanism 61.

  Here, the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 adsorb moisture in the air and desorb the adsorbed moisture into the air by the adsorption operation and the regeneration operation. In addition to the separation process (hereinafter referred to as latent heat treatment), a process of changing the temperature by cooling or heating the passing air (hereinafter referred to as sensible heat treatment) is also performed. FIG. 5 shows a graph in which the latent heat treatment capability and the sensible heat treatment capability obtained in the adsorption heat exchanger are displayed with the horizontal axis indicating the switching time interval between the first operation and the second operation, that is, the adsorption operation and the regeneration operation. According to this, when the switching time interval is shortened (time C in FIG. 5 is set to the latent heat priority mode), the latent heat treatment, that is, the process of adsorbing or desorbing moisture in the air is preferentially performed. When the switching time interval is increased (time D in FIG. 5, the sensible heat priority mode is selected), it is understood that sensible heat treatment, that is, processing for changing the temperature by cooling or heating the air is preferentially performed. . For example, when air is brought into contact with the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 functioning as an evaporator, moisture is first adsorbed mainly by an adsorbent provided on the surface. This is because the heat of adsorption generated at this time is processed, but if moisture is adsorbed to the vicinity of the moisture adsorption capacity of the adsorbent, air is mainly cooled thereafter. In addition, when air is brought into contact with the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 that function as condensers, the adsorbent is initially treated mainly by heat treatment of the adsorbent provided on the surface. This is because the moisture adsorbed on the air is desorbed in the air, but when the water adsorbed on the adsorbent is almost desorbed, the air is mainly heated thereafter. The ratio of the sensible heat treatment capacity to the latent heat treatment capacity (hereinafter referred to as the sensible heat treatment capacity ratio) can be changed by changing the switching time interval according to a command from the latent heat system utilization side control units 28 and 38. It is like that. As will be described later, the latent heat load processing system of the air conditioning system 1 is operated together with the sensible heat load processing system (that is, when the sensible heat system utilization units 4 and 5 are operated, hereinafter referred to as normal operation). In order to mainly perform the latent heat treatment, the switching time interval is set to time C, that is, the latent heat priority mode.

As described above, in the air conditioning system 1, in the dehumidifying operation only in the latent heat load processing system, the outdoor air is dehumidified and cooled by the sensible heat treatment capability obtained according to the switching time interval. The cooling operation to supply to can be performed.
The operation during the humidifying operation in the full ventilation mode will be described with reference to FIGS. 6 and 7. Here, FIGS. 6 and 7 are schematic refrigerant circuit diagrams showing the operation during the humidification operation in the full ventilation mode only in the latent heat load processing system of the air conditioning system 1. In addition, about the system control currently performed in the air conditioning system 1, since it is the same as that of the above-mentioned dehumidification operation of all ventilation modes, description is abbreviate | omitted.

  6 and 7, during the humidification operation, for example, in the latent heat system use unit 2, the first adsorption heat exchanger 22 becomes a condenser and the second adsorption heat exchanger 23 becomes an evaporator. And the second operation in which the second adsorption heat exchanger 23 serves as a condenser and the first adsorption heat exchanger 22 serves as an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated. Hereinafter, the flow of the refrigerant in the refrigerant circuit 10 during the first operation and the second operation is the same as the dehumidifying operation in the above-described all-ventilation mode. Only the air flow will be described.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is supplied indoors as supply air SA through the air supply port along with the outdoor air OA. In the second adsorption heat exchangers 23 and 33, the moisture in the indoor air RA is adsorbed by the adsorbent to dehumidify the indoor air RA, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the indoor air RA dehumidified by the second adsorption heat exchangers 23 and 33 is discharged to the outside as exhaust air EA through the exhaust port (of the adsorption heat exchangers 22, 23, 32, and 33 in FIG. 6). See arrows on both sides).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet. Is done. The moisture desorbed from the second adsorption heat exchangers 23 and 33 is supplied indoors as supply air SA through the air supply port along with the outdoor air OA. In the first adsorption heat exchangers 22 and 32, the moisture in the indoor air RA is adsorbed by the adsorbent to dehumidify the indoor air RA, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the indoor air RA dehumidified by the first adsorption heat exchangers 22 and 32 is discharged to the outside as exhaust air EA through the exhaust port (of the adsorption heat exchangers 22, 23, 32, and 33 in FIG. 7). See arrows on both sides).

Here, the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 perform not only the latent heat treatment but also the sensible heat treatment, as in the above-described dehumidifying operation in the full ventilation mode.
As described above, in the air conditioning system 1, in the humidification operation only in the latent heat load processing system, the outdoor air is humidified and heated by the sensible heat treatment capability obtained according to the switching time interval. Humidification operation can be performed.

<Circulation mode>
Next, the dehumidifying operation and the humidifying operation in the circulation mode will be described. In the circulation mode, when the air supply fan and the exhaust fan of the latent heat system utilization units 2 and 3 are operated, the indoor air RA is sucked into the unit through the internal air inlet and supplied indoors as the supply air SA through the air inlet. An operation is performed in which the outdoor air OA is sucked into the unit through the outside air inlet and discharged to the outside as exhaust air EA through the exhaust port.

  The operation during the dehumidifying operation in the circulation mode will be described with reference to FIGS. Here, FIG. 8 and FIG. 9 are schematic refrigerant circuit diagrams showing the operation during the dehumidifying operation in the circulation mode in only the latent heat load processing system of the air conditioning system 1. In addition, about the system control currently performed in the air conditioning system 1, since it is the same as that of the above-mentioned dehumidification operation of all ventilation modes, description is abbreviate | omitted.

  During the dehumidifying operation, as shown in FIGS. 8 and 9, for example, in the latent heat system use unit 2, the first adsorption heat exchanger 22 becomes a condenser and the second adsorption heat exchanger 23 becomes an evaporator. And the second operation in which the second adsorption heat exchanger 23 serves as a condenser and the first adsorption heat exchanger 22 serves as an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated. Hereinafter, the flow of the refrigerant in the refrigerant circuit 10 during the first operation and the second operation is the same as the dehumidifying operation in the above-described all-ventilation mode. Only the air flow will be described.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is discharged to the outdoors as exhaust air EA through the exhaust port accompanying the outdoor air OA. In the second adsorption heat exchangers 23 and 33, the moisture in the indoor air RA is adsorbed by the adsorbent to dehumidify the indoor air RA, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the indoor air RA dehumidified by the second adsorption heat exchangers 23 and 33 is supplied indoors as supply air SA through the air supply port (adsorption heat exchangers 22, 23, 32, and 33 in FIG. 8). (See arrows on both sides of the).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet. Is done. The moisture desorbed from the second adsorption heat exchangers 23 and 33 is accompanied by the outdoor air OA and discharged to the outdoors as exhaust air EA through the exhaust port. In the first adsorption heat exchangers 22 and 32, the moisture in the indoor air RA is adsorbed by the adsorbent, the indoor air is dehumidified, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. And the indoor air RA dehumidified by the 1st adsorption heat exchangers 22 and 32 is supplied indoors as supply air SA through an air supply opening (Adsorption heat exchangers 22, 23, 32, and 33 of FIG. 9). (See arrows on both sides of the).

Here, the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 perform not only latent heat treatment but also sensible heat treatment.
As described above, in the air conditioning system 1, in the circulation mode dehumidifying operation of only the latent heat load processing system, the indoor air is dehumidified and cooled by the sensible heat treatment ability obtained according to the switching time interval. The supplied dehumidifying operation can be performed.

  The operation during the humidification operation in the circulation mode will be described with reference to FIGS. 10 and 11. Here, FIG. 10 and FIG. 11 are schematic refrigerant circuit diagrams showing the operation during the dehumidifying operation in the circulation mode only in the latent heat load processing system of the air conditioning system 1. In addition, about the system control currently performed in the air conditioning system 1, since it is the same as that of the above-mentioned dehumidification operation of all ventilation modes, description is abbreviate | omitted.

  During the humidification operation, as shown in FIGS. 10 and 11, for example, in the latent heat system utilization unit 2, the first adsorption heat exchanger 22 becomes a condenser and the second adsorption heat exchanger 23 becomes an evaporator. And the second operation in which the second adsorption heat exchanger 23 serves as a condenser and the first adsorption heat exchanger 22 serves as an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated. Hereinafter, the flow of the refrigerant in the refrigerant circuit 10 during the first operation and the second operation is the same as the dehumidifying operation in the above-described all-ventilation mode. Only the air flow will be described.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is supplied indoors as the supply air SA through the air supply port along with the indoor air RA. In the second adsorption heat exchangers 23 and 33, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the adsorption heat generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the outdoor air OA dehumidified by the second adsorption heat exchangers 23 and 33 is discharged outdoors as exhaust air EA through the exhaust port (of the adsorption heat exchangers 22, 23, 32, and 33 in FIG. 10). See arrows on both sides).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the second adsorption heat exchangers 23 and 33 is supplied indoors as the supply air SA through the air supply port along with the indoor air RA. In the first adsorption heat exchangers 22 and 32, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the outdoor air OA dehumidified by the first adsorption heat exchangers 22 and 32 is discharged to the outdoors as exhaust air EA through the exhaust port (of the adsorption heat exchangers 22, 23, 32, and 33 in FIG. 11). (See arrows on both sides.)

Here, the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 perform not only the latent heat treatment but also the sensible heat treatment, as in the above-described dehumidifying operation in the full ventilation mode.
As described above, in the air conditioning system 1, in the humidification operation in the circulation mode of only the latent heat load treatment system, the indoor air is humidified and heated by the sensible heat treatment ability obtained according to the switching time interval. The humidification heating operation to supply can be performed.

<Air supply mode>
Next, the dehumidifying operation and the humidifying operation in the air supply mode will be described. In the air supply mode, when the air supply fan and the exhaust fan of the latent heat system utilization units 2 and 3 are operated, the outdoor air OA is sucked into the unit through the outside air inlet and supplied indoors as the supply air SA through the air inlet. Then, an operation is performed in which the outdoor air OA is sucked into the unit through the outside air inlet and is discharged to the outdoors as exhaust air EA through the outlet.

  The operation during the dehumidifying operation in the air supply mode will be described with reference to FIGS. Here, FIGS. 12 and 13 are schematic refrigerant circuit diagrams showing the operation during the dehumidifying operation in the air supply mode in only the latent heat load processing system of the air conditioning system 1. In addition, about the system control currently performed in the air conditioning system 1, since it is the same as that of the above-mentioned dehumidification operation of all ventilation modes, description is abbreviate | omitted.

  During the dehumidifying operation, as shown in FIGS. 12 and 13, for example, in the latent heat system use unit 2, the first adsorption heat exchanger 22 becomes a condenser and the second adsorption heat exchanger 23 becomes an evaporator. And the second operation in which the second adsorption heat exchanger 23 serves as a condenser and the first adsorption heat exchanger 22 serves as an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated. Hereinafter, the flow of the refrigerant in the refrigerant circuit 10 during the first operation and the second operation is the same as the dehumidifying operation in the above-described all-ventilation mode. Only the air flow will be described.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is discharged to the outdoors as exhaust air EA through the exhaust port accompanying the outdoor air OA. In the second adsorption heat exchangers 23 and 33, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the adsorption heat generated at that time is absorbed by the refrigerant and the refrigerant evaporates. The outdoor air OA dehumidified by the second adsorption heat exchangers 23 and 33 is supplied indoors as supply air SA through the air supply port (adsorption heat exchangers 22, 23, 32, and 33 in FIG. 12). (See arrows on both sides of the).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet. Is done. The moisture desorbed from the second adsorption heat exchangers 23 and 33 is accompanied by the outdoor air OA and discharged to the outdoors as exhaust air EA through the exhaust port. In the first adsorption heat exchangers 22 and 32, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. And the outdoor air OA dehumidified by the 1st adsorption heat exchangers 22 and 32 is supplied indoors as supply air SA through an air supply port (Adsorption heat exchangers 22, 23, 32, and 33 of FIG. 13). (See arrows on both sides of the).

Here, the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 perform not only latent heat treatment but also sensible heat treatment.
As described above, in the air conditioning system 1, in the dehumidifying operation in the air supply mode of only the latent heat load processing system, the outdoor air is dehumidified and cooled by the sensible heat treatment ability obtained according to the switching time interval. The dehumidifying operation to supply to can be performed.

  The operation during the humidifying operation in the air supply mode will be described with reference to FIGS. 14 and 15. Here, FIG. 14 and FIG. 15 are schematic refrigerant circuit diagrams showing the operation during the humidifying operation in the air supply mode only in the latent heat load processing system of the air conditioning system 1. In addition, about the system control currently performed in the air conditioning system 1, since it is the same as that of the above-mentioned dehumidification operation of all ventilation modes, description is abbreviate | omitted.

  During the humidification operation, as shown in FIGS. 14 and 15, for example, in the latent heat system use unit 2, the first adsorption heat exchanger 22 becomes a condenser and the second adsorption heat exchanger 23 becomes an evaporator. And the second operation in which the second adsorption heat exchanger 23 serves as a condenser and the first adsorption heat exchanger 22 serves as an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated. Hereinafter, the flow of the refrigerant in the refrigerant circuit 10 during the first operation and the second operation is the same as the dehumidifying operation in the above-described all-ventilation mode. Only the air flow will be described.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is supplied indoors as supply air SA through the air supply port along with the outdoor air OA. In the second adsorption heat exchangers 23 and 33, the moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air is dehumidified, and the adsorption heat generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the outdoor air OA dehumidified by the second adsorption heat exchangers 23 and 33 is discharged outdoors as exhaust air EA through the exhaust port (of the adsorption heat exchangers 22, 23, 32, and 33 in FIG. 14). See arrows on both sides).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet. Is done. The moisture desorbed from the second adsorption heat exchangers 23 and 33 is supplied indoors as supply air SA through the air supply port along with the outdoor air OA. In the first adsorption heat exchangers 22 and 32, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the outdoor air OA dehumidified by the first adsorption heat exchangers 22 and 32 is discharged to the outdoors as exhaust air EA through the exhaust port (of the adsorption heat exchangers 22, 23, 32, and 33 in FIG. 15). See arrows on both sides).

Here, the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 perform not only latent heat treatment but also sensible heat treatment.
As described above, in the air conditioning system 1, in the humidification operation in the air supply mode of only the latent heat load processing system, the outdoor air is humidified and heated by the sensible heat treatment ability obtained according to the switching time interval. Humidification operation can be performed.

<Exhaust mode>
Next, the dehumidifying operation and the humidifying operation in the exhaust mode will be described. In the exhaust mode, when the air supply fan and the exhaust fan of the latent heat system utilization units 2 and 3 are operated, the indoor air RA is sucked into the unit through the internal air inlet and supplied indoors as the supply air SA through the air inlet. An operation is performed in which the indoor air RA is sucked into the unit through the inside air inlet and is discharged to the outside as exhaust air EA through the outlet.

  The operation during the dehumidifying operation in the exhaust mode will be described with reference to FIGS. 16 and 17. Here, FIGS. 16 and 17 are schematic refrigerant circuit diagrams showing the operation during the dehumidifying operation in the exhaust mode in only the latent heat load processing system of the air conditioning system 1. In addition, about the system control currently performed in the air conditioning system 1, since it is the same as that of the above-mentioned dehumidification operation of all ventilation modes, description is abbreviate | omitted.

  During the dehumidifying operation, as shown in FIGS. 16 and 17, for example, in the latent heat system use unit 2, the first adsorption heat exchanger 22 becomes a condenser and the second adsorption heat exchanger 23 becomes an evaporator. And the second operation in which the second adsorption heat exchanger 23 serves as a condenser and the first adsorption heat exchanger 22 serves as an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated. Hereinafter, the flow of the refrigerant in the refrigerant circuit 10 during the first operation and the second operation is the same as the dehumidifying operation in the above-described all-ventilation mode. Only the air flow will be described.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is discharged to the outdoors as exhaust air EA through the exhaust port accompanying the indoor air RA. In the second adsorption heat exchangers 23 and 33, the moisture in the indoor air RA is adsorbed by the adsorbent to dehumidify the indoor air RA, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. The indoor air RA dehumidified by the second adsorption heat exchangers 23 and 33 is supplied indoors as supply air SA through the air supply port (adsorption heat exchangers 22, 23, 32, and 33 in FIG. 16). (See arrows on both sides of the).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the second adsorption heat exchangers 23 and 33 is exhausted to the outdoors as exhaust air EA through the exhaust port accompanying the indoor air RA. In the first adsorption heat exchangers 22 and 32, the moisture in the indoor air RA is adsorbed by the adsorbent to dehumidify the indoor air RA, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. And the indoor air RA dehumidified by the 1st adsorption heat exchangers 22 and 32 is supplied indoors as supply air SA through an air supply port (Adsorption heat exchangers 22, 23, 32, and 33 of FIG. 17). (See arrows on both sides of the).

Here, the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 perform not only latent heat treatment but also sensible heat treatment.
As described above, in the air conditioning system 1, in the exhaust mode dehumidifying operation of only the latent heat load processing system, the indoor air is dehumidified and cooled by the sensible heat treatment capability obtained according to the switching time interval. The supplied dehumidifying operation can be performed.

  The operation during the humidifying operation in the exhaust mode will be described with reference to FIGS. Here, FIG. 18 and FIG. 19 are schematic refrigerant circuit diagrams showing the operation during the humidifying operation in the exhaust mode in only the latent heat load processing system of the air conditioning system 1. In addition, about the system control currently performed in the air conditioning system 1, since it is the same as that of the above-mentioned dehumidification operation of all ventilation modes, description is abbreviate | omitted.

  During the humidification operation, as shown in FIGS. 18 and 19, for example, in the latent heat system use unit 2, the first adsorption heat exchanger 22 becomes a condenser and the second adsorption heat exchanger 23 becomes an evaporator. And the second operation in which the second adsorption heat exchanger 23 serves as a condenser and the first adsorption heat exchanger 22 serves as an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated. Hereinafter, the flow of the refrigerant in the refrigerant circuit 10 during the first operation and the second operation is the same as the dehumidifying operation in the above-described all-ventilation mode. Only the air flow will be described.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is supplied indoors as the supply air SA through the air supply port along with the indoor air RA. In the second adsorption heat exchangers 23 and 33, the moisture in the indoor air RA is adsorbed by the adsorbent to dehumidify the indoor air RA, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the indoor air RA dehumidified by the second adsorption heat exchangers 23 and 33 is discharged to the outside as exhaust air EA through the exhaust port (of the adsorption heat exchangers 22, 23, 32, and 33 in FIG. 18). See arrows on both sides).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the second adsorption heat exchangers 23 and 33 is supplied indoors as the supply air SA through the air supply port along with the indoor air SA. In the first adsorption heat exchangers 22 and 32, the moisture in the indoor air RA is adsorbed by the adsorbent to dehumidify the indoor air RA, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. And the indoor air RA dehumidified by the 1st adsorption heat exchangers 22 and 32 is discharged | emitted outdoors as exhaust air EA through an exhaust port (of the adsorption heat exchangers 22, 23, 32, and 33 of FIG. 19). See arrows on both sides).

Here, the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 perform not only latent heat treatment but also sensible heat treatment.
As described above, in the air conditioning system 1, in the humidification operation in the exhaust mode of only the latent heat load treatment system, the indoor air is humidified and heated by the sensible heat treatment ability obtained according to the switching time interval. The humidification operation to supply can be performed.

  Next, the operation of the air conditioning system 1 when operating the entire air conditioning system 1 including the sensible heat system utilization units 4 and 5 will be described. The air conditioning system 1 processes an indoor latent heat load mainly by a latent heat load processing system (that is, the latent heat system utilization units 2 and 3), and mainly treats an indoor sensible heat load by a sensible heat load processing system (that is, utilization of a sensible heat system). It can be processed in units 4, 5). Below, various driving | operation operation | movement is demonstrated.

<Dehumidifying and cooling operation>
First, with regard to the operation in the cooling and dehumidifying operation in which the latent heat load processing system of the air conditioning system 1 is dehumidified in the full ventilation mode and the cooling operation is performed in the sensible heat load processing system of the air conditioning system 1, FIGS. This will be described with reference to FIGS. Here, FIG. 20 and FIG. 21 are schematic refrigerant circuit diagrams showing the operation during the dehumidifying and cooling operation in the total ventilation mode in the air conditioning system 1. FIG. 22 is a control flow diagram during normal operation in the air conditioning system 1. FIG. 23 is a control flow diagram during normal operation in the air conditioning system 1 (when changing the switching time intervals of the adsorption heat exchangers 22, 23, 32, and 33). In FIG. 22 and FIG. 23, the latent heat system utilization unit 2 and the sensible heat system utilization unit 4 pair and the latent heat system utilization unit 3 and the sensible heat system utilization unit 5 pair have the same control flow. Illustration of the control flow of the pair of the system utilization unit 3 and the sensible heat system utilization unit 5 is omitted.

First, the operation of the latent heat load processing system of the air conditioning system 1 will be described.
In the latent heat system use unit 2 of the latent heat load processing system, the first adsorption heat exchanger 22 becomes a condenser and the second adsorption heat exchanger 23 becomes the same as in the case of the single operation of the latent heat load processing system. The first operation to be an evaporator and the second operation to have the second adsorption heat exchanger 23 as a condenser and the first adsorption heat exchanger 22 as an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated.

In the following description, the operations of the two latent heat system use units 2 and 3 will be described together.
In the first operation, the regeneration operation for the first adsorption heat exchangers 22 and 32 and the adsorption operation for the second adsorption heat exchangers 23 and 33 are performed in parallel. During the first operation, as shown in FIG. 20, the latent heat system use-side four-way switching valves 21, 31 are in the first state (see the solid lines of the latent heat system use-side four-way switching valves 21, 31). Is set. In this state, the high-pressure gas refrigerant discharged from the compression mechanism 61 flows into the first adsorption heat exchangers 22 and 32 through the discharge gas communication pipe 8 and the latent heat system use-side four-way switching valves 21 and 31, and the first It condenses while passing through the adsorption heat exchangers 22 and 32. The condensed refrigerant is depressurized by the latent heat system use side expansion valves 24 and 34 and then evaporated while passing through the second adsorption heat exchangers 23 and 33, and the latent heat system use side four-way switching valve 21. , 31 is again sucked into the compression mechanism 61 through the suction gas communication pipe 9 (see the arrow attached to the refrigerant circuit 10 in FIG. 20). Here, the sensible heat system utilization side expansion valves 41 and 51 of the sensible heat system utilization units 4 and 5 are different from the operation of only the latent heat load processing system described above in order to perform the cooling operation, the air heat exchanger 42. , 52 is opened to allow the refrigerant to flow, and the opening degree is adjusted, so that a part of the high-pressure gas refrigerant compressed and discharged by the compression mechanism 61 flows through the latent heat system utilization units 2 and 3. Will be.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is discharged to the outdoors as exhaust air EA through the exhaust port accompanying the indoor air RA. In the second adsorption heat exchangers 23 and 33, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the adsorption heat generated at that time is absorbed by the refrigerant and the refrigerant evaporates. The outdoor air OA dehumidified by the second adsorption heat exchangers 23 and 33 is supplied indoors as supply air SA through the air supply port (adsorption heat exchangers 22, 23, 32, and 33 in FIG. 20). (See arrows on both sides of the).

  In the second operation, the adsorption operation for the first adsorption heat exchangers 22 and 32 and the regeneration operation for the second adsorption heat exchangers 23 and 33 are performed in parallel. During the second operation, as shown in FIG. 21, the latent heat system use-side four-way switching valves 21, 31 are in the second state (refer to the broken lines of the latent heat system use-side four-way switching valves 21, 31). Is set. In this state, the high-pressure gas refrigerant discharged from the compression mechanism 61 flows into the second adsorption heat exchangers 23 and 33 through the discharge gas communication pipe 8 and the latent heat system use side four-way switching valves 21 and 31, and the second It condenses while passing through the adsorption heat exchangers 23 and 33. The condensed refrigerant is depressurized by the latent heat system use side expansion valves 24 and 34, and then evaporated while passing through the first adsorption heat exchangers 22 and 32, and the latent heat system use side four-way switching valve 21. , 31 is again sucked into the compression mechanism 61 through the suction gas communication pipe 9 (see the arrow attached to the refrigerant circuit 10 in FIG. 21).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the second adsorption heat exchangers 23, 33 is discharged to the outdoors as exhaust air EA through the exhaust port accompanying the indoor air RA. In the first adsorption heat exchangers 22 and 32, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. And the outdoor air OA dehumidified by the 1st adsorption heat exchangers 22 and 32 is supplied indoors as supply air SA through an air supply port (Adsorption heat exchangers 22, 23, 32, and 33 of FIG. 21). (See arrows on both sides of the).

Here, the system control performed in the air conditioning system 1 will be described focusing on the latent heat load processing system.
First, when the target temperature and target relative humidity are set by the remote controllers 11 and 12, the latent heat system use side control units 28 and 38 of the latent heat system use units 2 and 3 together with the target temperature value and the target relative humidity value. The temperature value and the relative humidity value of the indoor air sucked into the unit detected by the RA suction temperature / humidity sensors 225, 235, and the unit detected by the OA suction temperature / humidity sensors 26, 36 The outdoor air temperature value and relative humidity value are input.

  Then, in step S11, the latent heat system use side control units 28 and 38 calculate the target value of enthalpy or the target value of absolute humidity from the target temperature value and target relative humidity value of indoor air, The current value of the enthalpy of the air sucked into the unit from the indoor or the current value of the absolute humidity is calculated from the temperature value and the relative humidity value detected by the humidity sensors 25 and 35, and the necessary latent heat capacity value which is the difference between the two values Δh is calculated. Then, the value of Δh is converted into a capability UP signal K1 for notifying the heat source side control unit 65 whether or not the processing capability of the latent heat system use units 2 and 3 needs to be increased. For example, when the absolute value of Δh is smaller than a predetermined value (that is, when the humidity value of indoor air is close to the target humidity value and there is no need to increase or decrease the processing capacity), the capability UP signal K1 is set to “ 0, and when the absolute value of Δh is larger than the predetermined value in the direction in which the processing capacity must be increased (that is, in the dehumidifying operation, the humidity value of indoor air is higher than the target humidity value and the processing capacity needs to be increased) If the capacity UP signal K1 is “A” and the absolute value of Δh is larger than the predetermined value in the direction in which the processing capacity must be reduced (that is, in the dehumidifying operation, the humidity value of the indoor air is If the humidity is lower than the target humidity value and the processing capacity needs to be lowered, the capacity UP signal K1 is set to “B”. Then, the capability UP signal K1 is transmitted from the latent heat system use side control units 28, 38 to the heat source side control unit 65, and is used for calculating the target condensation temperature value TcS and the target evaporation temperature value TeS in step S12. However, this point will be described later.

Next, operation | movement of the sensible heat load processing system of the air conditioning system 1 is demonstrated.
When the cooling operation of the sensible heat system utilization units 4 and 5 is performed, the three-way switching valve 62 of the heat source unit 6 is in a condensing operation state (a state in which the first port 62a and the third port 62c are connected). . The cooling / heating switching valves 71 and 81 of the connection units 14 and 15 are in a cooling operation state (a state where the first ports 71a and 81a and the second ports 71b and 81b are connected). Moreover, the opening degree of the sensible heat system utilization side expansion valves 41 and 51 of the sensible heat system utilization units 4 and 5 is adjusted so as to depressurize the refrigerant. The heat source side expansion valve 64 is open.

  In such a state of the refrigerant circuit 10, the high-pressure gas refrigerant discharged from the compression mechanism 61 passes through the three-way switching valve 62, flows into the heat source side heat exchanger 63, and is condensed to become liquid refrigerant. The liquid refrigerant is sent to the sensible heat system utilization units 4 and 5 through the heat source side expansion valve 64, the receiver 68 and the liquid communication pipe 7. Then, the liquid refrigerant sent to the sensible heat system use units 4 and 5 is decompressed by the sensible heat system use side expansion valves 41 and 51 and then taken indoors by the air heat exchangers 42 and 52. It evaporates by heat exchange with the air RA and becomes a low-pressure gas refrigerant. The gas refrigerant is again sucked into the compression mechanism 61 of the heat source unit 6 through the cooling / heating switching valves 71 and 81 of the connection units 14 and 15 and the suction gas communication pipe 9. On the other hand, the indoor air RA cooled by heat exchange with the refrigerant in the air heat exchangers 42 and 52 is supplied indoors as supply air SA. As will be described later, the sensible heat system use side expansion valves 41 and 51 have a superheat degree SH in the air heat exchangers 42 and 52, that is, the air heat exchangers 42 and 52 detected by the liquid side temperature sensors 43 and 53, respectively. The opening degree is such that the temperature difference between the liquid side refrigerant temperature value of 52 and the gas side refrigerant temperature value of the air heat exchangers 42 and 52 detected by the gas side temperature sensors 54 and 55 becomes the target superheat degree SHS. Control is being made.

Here, the system control currently performed in the air conditioning system 1 is demonstrated paying attention to a sensible heat load processing system.
First, when the target temperature is set by the remote controllers 11 and 12, the sensible heat system use side control units 48 and 58 of the sensible heat system use units 4 and 5 have the RA intake temperature sensor 45, The temperature value of the indoor air sucked into the unit detected by 55 is input.

  Then, in step S14, the sensible heat system utilization side control units 48 and 58 determine the temperature difference between the target temperature value of the indoor air and the temperature value detected by the RA suction temperature sensors 45 and 55 (hereinafter referred to as required sensible heat capacity). Value ΔT). Here, since the necessary sensible heat capacity value ΔT is the difference between the target temperature value of indoor air and the current temperature value of indoor air as described above, the sensible heat that must be processed in the air conditioning system 1. It corresponds to a load. Then, the value of the required sensible heat capacity value ΔT is converted into a capacity UP signal K2 for notifying the heat source side control unit 65 whether or not the processing capacity of the sensible heat system utilization units 4 and 5 needs to be increased. For example, when the absolute value of ΔT is smaller than a predetermined value (that is, when the temperature value of indoor air is close to the target temperature value and there is no need to increase or decrease the processing capacity), the capability UP signal K2 is set to “ 0, and the absolute value of ΔT is larger than the predetermined value in the direction in which the processing capacity must be increased (that is, in the cooling operation, the temperature value of the indoor air is higher than the target temperature value and the processing capacity needs to be increased). When the capacity UP signal K2 is “a” and the absolute value of ΔT is larger than the predetermined value in the direction in which the processing capacity must be lowered (that is, in the cooling operation, the temperature value of the indoor air is When the temperature is lower than the target temperature value and the processing capacity needs to be lowered), the capacity UP signal K2 is set to “b”.

  Next, in step S15, the sensible heat system use side control units 48 and 58 change the value of the target superheat degree SHS according to the value of the required sensible heat capacity value ΔT. For example, when it is necessary to reduce the processing capacity of the sensible heat system utilization units 4 and 5 (when the capacity UP signal K2 is “b”), the target superheat degree SHS is increased and the air heat exchangers 42 and 52 are increased. The opening degree of the sensible heat system use side expansion valves 41 and 51 is controlled so as to reduce the amount of heat exchanged between the refrigerant and the air.

  Next, in step S12, the heat source side control unit 65 transmits the capability UP signal K1 of the latent heat system use units 2 and 3 transmitted from the latent heat system use side control units 28 and 38 to the heat source side control unit 65, and the sensible heat system. The target condensation temperature value TcS and the target evaporation temperature value TeS are calculated using the capability UP signal K2 of the sensible heat system utilization units 4, 5 transmitted from the use side control units 48, 58 to the heat source side control unit 65. For example, the target condensation temperature value TcS is calculated by adding the capability UP signal K1 of the latent heat system utilization units 2 and 3 and the capability UP signal K2 of the sensible heat system utilization units 4 and 5 to the current target condensation temperature value. The The target evaporation temperature value TeS is calculated by subtracting the capability UP signal K1 of the latent heat system use units 2 and 3 and the capability UP signal K2 of the sensible heat system use units 4 and 5 from the current target evaporation temperature value. . Thereby, when the value of the capability UP signal K1 is “A” or when the value of the capability UP signal K2 is “a”, the target condensation temperature value TcS becomes high and the target evaporation temperature value TeS becomes low.

  Next, in step S13, a system condensing temperature value Tc and a system evaporating temperature value Te, which are values corresponding to actual measured values of the condensing temperature and evaporating temperature of the entire air conditioning system 1, are calculated. For example, the system condensing temperature value Tc and the system evaporation temperature value Te are the suction pressure value of the compression mechanism 61 detected by the suction pressure sensor 66 and the discharge pressure value of the compression mechanism 61 detected by the discharge pressure sensor 67. It is calculated by converting into the refrigerant saturation temperature at the pressure value. Then, the temperature difference ΔTc of the target condensation temperature value TcS with respect to the system condensation temperature value Tc and the temperature difference ΔTe of the target evaporation temperature value TeS with respect to the system evaporation temperature value Te are calculated, and by dividing these temperature differences, the compression mechanism 61 Determine whether the operating capacity needs to be increased or decreased and the range of increase or decrease.

  By using the operation capacity of the compression mechanism 61 determined in this way, the operation capacity of the compression mechanism 61 is controlled, so that system control is performed so as to approach the target relative humidity of indoor air. For example, when the value obtained by subtracting the temperature difference ΔTe from the temperature difference ΔTc is a positive value, the operating capacity of the compression mechanism 61 is increased. Conversely, when the value obtained by subtracting the temperature difference ΔTe from the temperature difference ΔTc is a negative value. Controls to reduce the operating capacity of the compression mechanism 61.

  Thus, in this air conditioning system 1, the latent heat load (equivalent to the required latent heat treatment capacity, Δh) that must be processed as the entire air conditioning system 1 and the sensible heat load that must be processed as the entire air conditioning system 1 (Necessary sensible heat treatment capacity, corresponding to ΔT) is a latent heat load treatment system (specifically, latent heat system use units 2 and 3) and a sensible heat load treatment system (specifically, sensible heat system use unit 4, 5). Here, the increase / decrease in the processing capacity of the latent heat load processing system and the increase / decrease in the processing capacity of the sensible heat load processing system are calculated by calculating the necessary latent heat treatment capacity value Δh and the required sensible heat treatment capacity value ΔT, Since the operation capacity of the compression mechanism 61 is controlled, the latent heat load processing in the latent heat load processing system having the adsorption heat exchangers 22, 23, 32, 33 and the sensible heat load processing having the air heat exchangers 42, 52 are performed. The sensible heat load processing in the system can be performed at the same time. Thereby, even when the heat sources of the latent heat load processing system and the sensible heat load processing system are made common as in the air conditioning system 1 of the present embodiment, the operation capacity of the compression mechanism that constitutes the heat source is favorably controlled. Can do.

  By the way, in the system control of the air conditioning system 1 described above, the required sensible heat treatment capability value ΔT is increased (that is, the capability UP signal K2 becomes “a”), and the required latent heat treatment capability value Δh is decreased (that is, In the case where the capacity UP signal K1 becomes “B”), basically, the operation capacity of the compression mechanism 61 is increased. Further, even when the necessary latent heat treatment capacity value Δh becomes large (that is, when the capacity UP signal K1 becomes “A”), basically, control for increasing the operation capacity of the compression mechanism 61 is performed.

  On the other hand, in the latent heat load processing by the latent heat load processing system, as described above, the sensible heat treatment is performed together with the latent heat treatment by the adsorption operation or the regeneration operation of the adsorption heat exchangers 22, 23, 32, 33. At this time, the ratio of the sensible heat treatment capacity to the latent heat treatment capacity changes as the switching time interval is changed, as shown in FIG. Therefore, in the air conditioning system 1, when the required latent heat treatment capacity value Δh is small and the necessary sensible heat treatment capacity value ΔT is large, the sensible heat treatment capacity ratio is increased by increasing the switching time interval, and It can cope with an increase in heat load. Here, since the operation for increasing the sensible heat treatment capacity in the latent heat load processing system of the air conditioning system 1 by increasing the switching time interval is not an operation for increasing the operating capacity of the compression mechanism 61, the entire air conditioning system 1 is wasted. This eliminates the possibility of efficient operation. When the required latent heat treatment capacity value Δh becomes large (that is, the capacity UP signal K1 is “A”), the sensible heat treatment capacity ratio is reduced by shortening the switching time interval to cope with an increase in the latent heat load. can do.

  In the air conditioning system 1 of the present embodiment, the above-described system control is performed according to the control flow shown in FIG. Hereinafter, system control of the air conditioning system 1 shown in FIG. 23 will be described. Note that steps S11 to S15 other than steps S16 to S19 in FIG. 23 are the same as steps S11 to S15 shown in FIG.

  In step S16, the latent heat system use side control units 28, 38 determine whether or not the switching time interval of the adsorption heat exchangers 22, 23, 32, 33 is in the sensible heat priority mode (ie, time D), and the capability UP signal. It is determined whether K1 is “A” (that is, the direction in which the latent heat treatment capability is increased). If both of these two conditions are satisfied, the switching time interval is changed to the latent heat priority mode (ie, time C) in step S18. Conversely, if any one of the two conditions is not satisfied, the process proceeds to step S17.

  In step S17, the latent heat system use side control units 28, 38 determine whether the switching time interval of the adsorption heat exchangers 22, 23, 32, 33 is in the latent heat priority mode (ie, time C), and the capability UP signal K1. Is “B” (that is, the direction in which the latent heat treatment capability is lowered), and the capability UP signal K2 transmitted from the sensible heat system use side control units 48 and 58 through the heat source side control unit 65 is “a” (ie, It is determined whether the sensible heat treatment ability is increased). If all three conditions are satisfied, the switching time interval is changed to the sensible heat priority mode (ie, time D) in step S19. Conversely, if any one of the two conditions is not satisfied, the process proceeds to step S12.

  By such system control, as described above, when the necessary latent heat treatment capacity value Δh is small and the necessary sensible heat treatment capacity value ΔT is large, the switching time interval is lengthened (specifically, normal operation) By changing from time C to time D (see FIG. 5), the sensible heat treatment capacity ratio can be increased to cope with an increase in sensible heat load. Moreover, in this system control, when the latent heat load becomes large as in step S16, it is possible to return to the latent heat priority mode. It can cope with an increase in heat load. Here, as an example of the dehumidifying and cooling operation, the case where the cooling operation of the sensible heat load processing system is performed while the latent heat load processing system of the air conditioning system 1 is performing the dehumidifying operation in the full ventilation mode has been described. The present invention is applicable even when the system is dehumidified in other modes such as a circulation mode and an air supply mode.

<Humidification heating operation>
Next, FIG. 22 and FIG. 23 illustrate operations in the humidifying and heating operation in which the heating operation is performed in the sensible heat load processing system of the air conditioning system 1 while performing the humidifying operation of the latent heat load processing system of the air conditioning system 1 in the total ventilation mode. This will be described with reference to FIGS. 24 and 25. FIG. Here, FIG. 24 and FIG. 25 are schematic refrigerant circuit diagrams showing the operation during humidification heating operation in the total ventilation mode in the air conditioning system 1.

First, the operation of the latent heat load processing system of the air conditioning system 1 will be described.
In the latent heat system use unit 2 of the latent heat load processing system, the first adsorption heat exchanger 22 becomes a condenser and the second adsorption heat exchanger 23 becomes the same as in the case of the single operation of the latent heat load processing system. The first operation to be an evaporator and the second operation to have the second adsorption heat exchanger 23 as a condenser and the first adsorption heat exchanger 22 as an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated.

In the following description, the operations of the two latent heat system use units 2 and 3 will be described together.
In the first operation, the regeneration operation for the first adsorption heat exchangers 22 and 32 and the adsorption operation for the second adsorption heat exchangers 23 and 33 are performed in parallel. During the first operation, as shown in FIG. 24, the latent heat system use-side four-way switching valves 21 and 31 are in the first state (see the solid line of the latent heat system use-side four-way switching valves 21 and 31 in FIG. 24). Is set. In this state, the high-pressure gas refrigerant discharged from the compression mechanism 61 flows into the first adsorption heat exchangers 22 and 32 through the discharge gas communication pipe 8 and the latent heat system use-side four-way switching valves 21 and 31, and the first It condenses while passing through the adsorption heat exchangers 22 and 32. The condensed refrigerant is depressurized by the latent heat system use side expansion valves 24 and 34 and then evaporated while passing through the second adsorption heat exchangers 23 and 33, and the latent heat system use side four-way switching valve 21. , 31 is again sucked into the compression mechanism 61 through the suction gas communication pipe 9 (see the arrow attached to the refrigerant circuit 10 in FIG. 24). Here, the sensible heat system utilization side expansion valves 41 and 51 of the sensible heat system utilization units 4 and 5 are different from the above-described operation of only the latent heat load processing system in order to perform the heating operation. , 52 is opened to allow the refrigerant to flow, and the opening degree is adjusted, so that a part of the high-pressure gas refrigerant compressed and discharged by the compression mechanism 61 flows through the latent heat system utilization units 2 and 3. Will be.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is supplied indoors as supply air SA through the air supply port along with the outdoor air OA. In the second adsorption heat exchangers 23 and 33, the moisture in the indoor air RA is adsorbed by the adsorbent to dehumidify the indoor air RA, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. Then, the indoor air RA dehumidified by the second adsorption heat exchangers 23 and 33 is discharged to the outside as exhaust air EA through the exhaust port (of the adsorption heat exchangers 22, 23, 32, and 33 in FIG. 24). See arrows on both sides).

  In the second operation, the adsorption operation for the first adsorption heat exchangers 22 and 32 and the regeneration operation for the second adsorption heat exchangers 23 and 33 are performed in parallel. During the second operation, as shown in FIG. 25, the latent heat system use-side four-way switching valves 21 and 31 are in the second state (see the broken lines of the latent heat system use-side four-way switching valves 21 and 31 in FIG. 25). Is set. In this state, the high-pressure gas refrigerant discharged from the compression mechanism 61 flows into the second adsorption heat exchangers 23 and 33 through the discharge gas communication pipe 8 and the latent heat system use side four-way switching valves 21 and 31, and the second It condenses while passing through the adsorption heat exchangers 23 and 33. The condensed refrigerant is depressurized by the latent heat system use side expansion valves 24 and 34, and then evaporated while passing through the first adsorption heat exchangers 22 and 32, and the latent heat system use side four-way switching valve 21. , 31 is again sucked into the compression mechanism 61 through the suction gas communication pipe 9 (see the arrow attached to the refrigerant circuit 10 in FIG. 25).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet. Is done. The moisture desorbed from the second adsorption heat exchangers 23 and 33 is supplied indoors as supply air SA through the air supply port along with the outdoor air OA. In the first adsorption heat exchangers 22 and 32, the moisture in the indoor air RA is adsorbed by the adsorbent to dehumidify the indoor air RA, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. And the indoor air RA dehumidified by the 1st adsorption heat exchangers 22 and 32 is discharged | emitted outdoors as exhaust air EA through an exhaust port (of the adsorption heat exchangers 22, 23, 32, and 33 of FIG. 25). (See arrows on both sides.)

Here, the system control performed in the air conditioning system 1 will be described focusing on the latent heat load processing system.
First, when the target temperature and target relative humidity are set by the remote controllers 11 and 12, the latent heat system use side control units 28 and 38 of the latent heat system use units 2 and 3 together with the target temperature value and the target relative humidity value. The temperature value and relative humidity value of the indoor air sucked into the unit detected by the RA suction temperature / humidity sensors 25, 35, and the air pressure sucked into the unit detected by the OA suction temperature / humidity sensors 26, 36. The outdoor air temperature value and relative humidity value are input.

  Then, in step S11, the latent heat system use side control units 28 and 38 calculate the target value of enthalpy or the target value of absolute humidity from the target temperature value and target relative humidity value of indoor air, The current value of the enthalpy of the air sucked into the unit from the indoor or the current value of the absolute humidity is calculated from the temperature value and the relative humidity value detected by the humidity sensors 25 and 35, and the necessary latent heat capacity value which is the difference between the two values Δh is calculated. Then, the value of Δh is converted into a capability UP signal K1 for notifying the heat source side control unit 65 whether or not the processing capability of the latent heat system use units 2 and 3 needs to be increased. For example, when the absolute value of Δh is smaller than a predetermined value (that is, when the humidity value of indoor air is close to the target humidity value and there is no need to increase or decrease the processing capacity), the capability UP signal K1 is set to “ 0, and when the absolute value of Δh is larger than the predetermined value in the direction in which the processing capacity must be increased (that is, in the humidification operation, the humidity value of indoor air is lower than the target humidity value and the processing capacity needs to be increased) When the capacity UP signal K1 is “A” and the absolute value of Δh is larger than the predetermined value in the direction in which the processing capacity must be lowered (that is, in the humidification operation, the humidity value of the indoor air is If it is higher than the target humidity value and the processing capacity needs to be lowered), the capacity UP signal K1 is set to “B”. Then, the capability UP signal K1 is transmitted from the latent heat system use side control units 28, 38 to the heat source side control unit 65, and is used for calculating the target condensation temperature value TcS and the target evaporation temperature value TeS in step S12. However, this point will be described later.

Next, operation | movement of the sensible heat load processing system of the air conditioning system 1 is demonstrated.
When the heating operation of the sensible heat system utilization units 4 and 5 is performed, the three-way switching valve 62 of the heat source unit 6 is in an evaporation operation state (a state in which the second port 62b and the third port 62c are connected). . The cooling / heating switching valves 71 and 81 of the connection units 14 and 15 are in a heating operation state (a state in which the first ports 71a and 81a and the third ports 71c and 81c are connected). Moreover, the opening degree of the sensible heat system utilization side expansion valves 41 and 51 of the sensible heat system utilization units 4 and 5 is adjusted so as to depressurize the refrigerant. The opening degree of the heat source side expansion valve 64 is adjusted so as to reduce the pressure.

  In such a state of the refrigerant circuit 10, the high-pressure gas refrigerant discharged from the compression mechanism 61 is discharged from the discharge side of the compression mechanism 61 and the three-way switching valve 62 to the discharge gas communication pipe 8 and the connection units 14, 15. And sent to the sensible heat system utilization units 4 and 5. The high-pressure gas refrigerant sent to the sensible heat system utilization units 4 and 5 is condensed in the air heat exchangers 42 and 52 by heat exchange with the indoor air RA sucked into the units, and becomes liquid refrigerant. It is sent to the heat source unit 6 through the sensible heat system use side expansion valves 41 and 51 and the liquid communication pipe 7. On the other hand, the indoor air RA heated by heat exchange with the refrigerant in the air heat exchangers 42 and 52 is supplied indoors as supply air SA. Then, the liquid refrigerant sent to the heat source unit 6 passes through the receiver 68 and is decompressed by the heat source side expansion valve 64, and then evaporated by the heat source side heat exchanger 63 to become a low pressure gas refrigerant. The air is again sucked into the compression mechanism 61 through 62. As will be described later, the sensible heat system use side expansion valves 41, 51 have a supercooling degree SC of the air heat exchangers 42, 52, that is, the air heat exchanger 42 detected by the liquid side temperature sensors 43, 53. , 52 so that the temperature difference between the refrigerant temperature value on the liquid side and the refrigerant temperature value on the gas side of the air heat exchangers 42, 52 detected by the gas side temperature sensors 44, 54 becomes the target supercooling degree SCS. The opening degree is controlled.

Here, the system control currently performed in the air conditioning system 1 is demonstrated paying attention to a sensible heat load processing system.
First, when the target temperature is set by the remote controllers 11 and 12, the sensible heat system use side control units 48 and 58 of the sensible heat system use units 4 and 5 have the RA intake temperature sensor 45, The temperature value of the indoor air sucked into the unit detected by 55 is input.

  Then, in step S14, the sensible heat system utilization side control units 48 and 58 determine the temperature difference between the target temperature value of the indoor air and the temperature value detected by the RA suction temperature sensors 45 and 55 (hereinafter referred to as required sensible heat capacity). Value ΔT). Here, since the necessary sensible heat capacity value ΔT is the difference between the target temperature value of indoor air and the current temperature value of indoor air as described above, the sensible heat that must be processed in the air conditioning system 1. It corresponds to a load. Then, the value of the required sensible heat capacity value ΔT is converted into a capacity UP signal K2 for notifying the heat source side control unit 65 whether or not the processing capacity of the sensible heat system utilization units 4 and 5 needs to be increased. For example, when the absolute value of ΔT is smaller than a predetermined value (that is, when the temperature value of indoor air is close to the target temperature value and there is no need to increase or decrease the processing capacity), the capability UP signal K2 is set to “ 0, and the absolute value of ΔT is larger than the predetermined value in the direction in which the processing capacity must be increased (that is, in the heating operation, the temperature value of the indoor air is lower than the target temperature value, and it is necessary to increase the processing capacity. When the capacity UP signal K2 is “a” and the absolute value of ΔT is larger than the predetermined value in the direction in which the processing capacity must be lowered (that is, in the heating operation, the temperature value of indoor air is When the temperature is higher than the target temperature value and the processing capacity needs to be lowered), the capacity UP signal K2 is set to “b”.

  Next, in step S15, the sensible heat system use side control units 48 and 58 change the value of the target supercooling degree SCS according to the value of the required sensible heat capacity value ΔT. For example, when it is necessary to reduce the processing capacity of the sensible heat system utilization units 4 and 5 (when the capacity UP signal K2 is “b”), the target supercooling degree SHS is increased and the air heat exchanger 42, The opening degree of the sensible heat system use side expansion valves 41 and 51 is controlled so as to reduce the amount of heat exchanged between the refrigerant and the air in 52.

  Next, in step S12, the heat source side control unit 65 transmits the capability UP signal K1 of the latent heat system use units 2 and 3 transmitted from the latent heat system use side control units 28 and 38 to the heat source side control unit 65, and the sensible heat system. The target condensation temperature value TcS and the target evaporation temperature value TeS are calculated using the capability UP signal K2 of the sensible heat system utilization units 4, 5 transmitted from the use side control units 48, 58 to the heat source side control unit 65. For example, the target condensation temperature value TcS is calculated by adding the capability UP signal K1 of the latent heat system utilization units 2 and 3 and the capability UP signal K2 of the sensible heat system utilization units 4 and 5 to the current target condensation temperature value. The The target evaporation temperature value TeS is calculated by subtracting the capability UP signal K1 of the latent heat system use units 2 and 3 and the capability UP signal K2 of the sensible heat system use units 4 and 5 from the current target evaporation temperature value. . Thereby, when the value of the capability UP signal K1 is “A” or when the value of the capability UP signal K2 is “a”, the target condensation temperature value TcS becomes high and the target evaporation temperature value TeS becomes low.

  Next, in step S13, a system condensing temperature value Tc and a system evaporating temperature value Te, which are values corresponding to actual measured values of the condensing temperature and evaporating temperature of the entire air conditioning system 1, are calculated. For example, the system condensing temperature value Tc and the system evaporation temperature value Te are the suction pressure value of the compression mechanism 61 detected by the suction pressure sensor 66 and the discharge pressure value of the compression mechanism 61 detected by the discharge pressure sensor 67. It is calculated by converting into the refrigerant saturation temperature at the pressure value. Then, the temperature difference ΔTc of the target condensation temperature value TcS with respect to the system condensation temperature value Tc and the temperature difference ΔTe of the target evaporation temperature value TeS with respect to the system evaporation temperature value Te are calculated, and by dividing these temperature differences, the compression mechanism 61 Determine whether the operating capacity needs to be increased or decreased and the range of increase or decrease.

  By using the operation capacity of the compression mechanism 61 determined in this way, the operation capacity of the compression mechanism 61 is controlled, so that system control is performed so as to approach the target relative humidity of indoor air. For example, when the value obtained by subtracting the temperature difference ΔTe from the temperature difference ΔTc is a positive value, the operating capacity of the compression mechanism 61 is increased. Conversely, when the value obtained by subtracting the temperature difference ΔTe from the temperature difference ΔTc is a negative value. Controls to reduce the operating capacity of the compression mechanism 61.

Thus, in this air conditioning system 1, the same system control as in the dehumidifying and cooling operation can be performed during the humidifying and heating operation.
In addition, in the humidification heating operation, as in the dehumidification heating operation, in the system control of the air conditioning system 1 described above, the required sensible heat treatment capacity value ΔT becomes large (that is, the capacity UP signal K2 is “a”), In addition, when the necessary latent heat treatment capacity value Δh is small (that is, when the capacity UP signal K1 is “B”), control is performed so as to increase the operating capacity of the compression mechanism 61. Even when the necessary latent heat treatment capacity value Δh becomes large (that is, when the capacity UP signal K1 is “A”), control is basically performed so as to increase the operating capacity of the compression mechanism 61. For this reason, in the air conditioning system 1 of the present embodiment, even during the humidifying and heating operation, the system involves changing the switching time intervals of the adsorption heat exchangers 22, 23, 32, and 33 in accordance with the control flow shown in FIG. Control can be performed. That is, as in the dehumidifying and cooling operation, when the necessary latent heat treatment capacity value Δh is small and the necessary sensible heat treatment capacity value ΔT is large, the switching time interval is increased (specifically, during normal operation). By changing from time C to time D (see FIG. 5), the sensible heat treatment capacity ratio can be increased to cope with an increase in sensible heat load. Moreover, in this system control, when the latent heat load becomes large as in step S16, it is possible to return to the latent heat priority mode, so that the sensible heat load is processed while processing the indoor latent heat load. It can cope with the increase of. Here, as an example of the humidification heating operation, the case where the heating operation of the sensible heat load processing system is performed while performing the humidification operation in the full ventilation mode of the latent heat load processing system of the air conditioning system 1 has been described. The present invention is applicable even when the system is dehumidified in other modes such as a circulation mode and an air supply mode.

<Simultaneous operation of dehumidification cooling and humidification heating>
Next, dehumidifying cooling and humidification in which the simultaneous operation of cooling and heating is performed in the sensible heat load treatment system of the air conditioning system 1 while the latent heat load treatment system of the air conditioning system 1 is simultaneously operated in dehumidification and humidification in the full ventilation mode. The operation in the simultaneous heating operation will be described with reference to FIGS. Here, FIG. 26 and FIG. 27 are schematic refrigerant circuit diagrams showing operations during simultaneous operation of dehumidification cooling and humidification heating in the total ventilation mode in the air conditioning system 1. Here, the pair of latent heat system utilization unit 2 and sensible heat system utilization unit 4 performs dehumidification cooling operation, and the pair of latent heat system utilization unit 3 and sensible heat system utilization unit 5 performs humidification heating operation. The case where the three-way switching valve 62 is in the condensing operation state as the entire unit 6 and the cooling load is large as the entire system will be described. In addition, about system control of the air conditioning system 1, since it is the same as that of the case of the above-mentioned dehumidification cooling operation and humidification heating operation, description is abbreviate | omitted.

First, the operation of the latent heat load processing system of the air conditioning system 1 will be described.
In the latent heat system utilization unit 2, the same operation as the dehumidifying operation in the full ventilation mode at the time of the dehumidifying and cooling operation described above is performed. On the other hand, in the latent heat system utilization unit 3, an operation similar to the humidification operation in the full ventilation mode during the humidification heating operation described above is performed.
Next, operation | movement of the sensible heat load processing system of the air conditioning system 1 is demonstrated. In the sensible heat system utilization unit 4 that is operated in a pair with the latent heat system utilization unit 2, an operation similar to the cooling operation during the above-described dehumidifying and cooling operation is performed. On the other hand, in the sensible heat system utilization unit 5 operated in a pair with the latent heat system utilization unit 3, an operation similar to the heating operation in the humidification heating operation described above is performed. Here, in the heat source unit 6, since the three-way switching valve 62 is in the condensing operation state, the refrigerant flow in the heat source side refrigerant circuit 10e is the same as in the cooling operation.

Thus, in the air conditioning system 1 of this embodiment, simultaneous operation of dehumidification cooling and humidification heating is also possible.
<System startup>
Next, the operation | movement at the time of starting of the air conditioning system 1 is demonstrated using FIG.5, FIG.20, FIG.21, FIG.28 and FIG. Here, FIG. 28 is a schematic refrigerant circuit diagram showing the operation of the air conditioning system 1 when the first system is started. FIG. 29 is a schematic refrigerant circuit diagram showing an operation at the time of starting the second system in the air conditioning system 1.

  There are three activation methods described below as operations at the time of activation of the air conditioning system 1. The first system activation method is a method of operating in a state where outdoor air does not pass through the adsorption heat exchangers 22, 23, 32, 33 of the latent heat load processing system of the air conditioning system 1. In the second system activation method, in the state where the switching of the adsorption operation and the regeneration operation of the adsorption heat exchangers 22, 23, 32, and 33 of the latent heat load treatment system of the air conditioning system 1 is stopped, the outdoor air is subjected to the latent heat load treatment. After passing through one of the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33 of the system, the air is discharged to the outside, and indoor air is discharged to the first adsorption heat exchangers 22, 32 and 2. In this operation method, the other of the adsorption heat exchangers 23 and 33 is passed through and then supplied indoors. The third system activation method is a method of operating with the switching time interval between the adsorption operation and the regeneration operation of the adsorption heat exchangers 22, 23, 32, and 33 longer than that in the normal operation.

First, the operation at the time of starting the first system will be described with reference to FIG. 28 on the assumption that the sensible heat load processing system of the air conditioning system 1 is in cooling operation.
When an operation command is issued from the remote controllers 11 and 12, the sensible heat load processing system (that is, the sensible heat system utilization units 4 and 5 and the heat source unit 6) of the air conditioning system 1 is activated and the cooling operation is performed. Here, since the operation during the cooling operation of the sensible heat load treatment system is the same as that during the dehumidifying and cooling operation described above, the description thereof is omitted.

On the other hand, in the latent heat load processing system of the air conditioning system 1, outdoor air is sucked into the unit by operation of an air supply fan, an exhaust fan, a damper, or the like, and the adsorption heat exchanger 22 of the latent heat system utilization units 2 and 3 is used. , 23, 32, and 33 are not passed and activated.
Then, in the adsorption heat exchangers 22, 23, 32, and 33 of the latent heat system use units 2 and 3, the refrigerant and the air are not in the heat exchange state, so the compression mechanism 61 of the heat source unit 6 is not activated and the latent heat In the load processing system, the latent heat treatment is not performed.

  Then, the operation at the time of starting the system is canceled after a predetermined condition is satisfied, and the operation is shifted to a normal dehumidifying and cooling operation. For example, after a predetermined time (for example, about 30 minutes) has elapsed from the system startup by a timer provided in the heat source side control unit 65, the operation at the time of system startup is canceled or input by the remote controllers 11 and 12 The temperature difference between the target temperature value of the indoor air and the temperature value of the indoor air sucked into the unit detected by the RA intake temperature sensors 45 and 55 has become a predetermined temperature difference (for example, 3 ° C.) or less. Later, this system startup operation is canceled.

  Thus, in the air conditioning system 1, at the time of system startup, the sensible heat treatment is mainly performed by supplying the air heat-exchanged indoors in the air heat exchangers 42 and 52 of the sensible heat system utilization units 4 and 5, In addition, since outdoor air is not allowed to pass by preventing outdoor air from passing through the adsorption heat exchangers 22, 23, 32, 33 of the latent heat system utilization units 2, 3, the latent heat load processing system is activated at the time of system startup. It is possible to prevent the introduction of a heat load from the outside air in a state where the air conditioning capability is not exhibited, and the target temperature of indoor air can be reached quickly. Accordingly, the latent heat load processing system that has the adsorption heat exchangers 22, 23, 32, and 33 mainly processes indoor latent heat loads, and the air heat exchangers 42 and 52 that mainly processes indoor sensible heat loads. In the air conditioning system 1 including the sensible heat load processing system, cooling can be performed quickly when the system is activated. Here, the case where the sensible heat load treatment system is air-cooled has been described, but the system activation method can be applied even when the air-warming operation is performed.

Next, the operation at the time of starting the second system will be described with reference to FIGS. 5 and 29 on the assumption that the sensible heat load treatment system of the air conditioning system 1 is in cooling operation.
When an operation command is issued from the remote controllers 11 and 12, the sensible heat load processing system (that is, the sensible heat system utilization units 4 and 5 and the heat source unit 6) of the air conditioning system 1 is activated and the cooling operation is performed. Here, the operation during the cooling operation of the sensible heat load treatment system is the same as described above, and thus the description thereof is omitted.

  On the other hand, in the latent heat load processing system of the air conditioning system 1, the switching operation of the latent heat system use side four-way switching valves 21 and 31 is not performed, and the operation is switched to the same air flow path as in the circulation mode by operation of a damper or the like. When the air supply fan and exhaust fan of the latent heat system utilization units 2 and 3 are operated in this state, the indoor air RA is sucked into the unit through the indoor air inlet and supplied indoors as the supply air SA through the air inlet. An operation is performed in which the air OA is sucked into the unit through the outside air inlet and the exhaust air EA is discharged outside through the exhaust port.

  When such an operation is performed, immediately after the system is started up, the desorbed moisture is given to the outdoor air OA sucked from the outside air inlet and discharged to the outside as exhaust air EA through the outlet, and indoor air The moisture in the RA is adsorbed by the adsorbent, the indoor air RA is dehumidified, and supplied to the indoor as the supply air SA through the air supply port. However, after a certain amount of time has elapsed since the system startup, as shown in FIG. 5, the adsorbent of the adsorption heat exchangers 22, 23, 32, and 33 adsorbs moisture to near the moisture adsorption capacity. As a result, the latent heat load processing system functions as a system for processing the sensible heat load. Thereby, the sensible heat processing capability as the air conditioning system 1 whole can be increased, and indoor sensible heat processing can be accelerated | stimulated.

  Then, the operation at the time of starting the system is canceled after a predetermined condition is satisfied, and the operation is shifted to a normal dehumidifying and cooling operation. For example, after a predetermined time (for example, about 30 minutes) has elapsed from the system startup by the timer provided in the heat source side control unit 265, the operation at the time of system startup is canceled or input by the remote controllers 11 and 12 The temperature difference between the target temperature value of the indoor air and the temperature value of the indoor air sucked into the unit detected by the RA intake temperature / humidity sensors 25 and 35 is less than a predetermined temperature difference (for example, 3 ° C.). After this, the system startup operation is canceled.

  Thus, in the air conditioning system 1, at the time of system startup, the sensible heat treatment is mainly performed by supplying the air heat-exchanged indoors in the air heat exchangers 42 and 52 of the sensible heat system utilization units 4 and 5, In addition, in a state where the switching of the adsorption operation and the regeneration operation of the adsorption heat exchangers 22, 23, 32, and 33 is stopped, the outdoor heat is passed through the adsorption heat exchangers 22, 23, 32, and 33 and then discharged to the outdoors. Thus, since the sensible heat treatment is performed, the indoor sensible heat treatment can be promoted to quickly reach the target temperature of the indoor air when the system is started. Accordingly, the latent heat load processing system that has the adsorption heat exchangers 22, 23, 32, and 33 mainly processes indoor latent heat loads, and the air heat exchangers 42 and 52 that mainly processes indoor sensible heat loads. In the air conditioning system 1 including the sensible heat load processing system, cooling can be performed quickly when the system is activated. Here, the case where the sensible heat load treatment system is air-cooled has been described, but the system activation method can be applied even when the air-warming operation is performed.

Next, regarding the operation at the time of starting the third system, the latent heat load processing system of the air conditioning system 1 is dehumidified in the total ventilation mode, and the sensible heat load processing system of the air conditioning system 1 is cooled. This will be described with reference to FIGS. 5, 20 and 21. FIG.
When an operation command is issued from the remote controllers 11 and 12, the sensible heat load processing system (that is, the sensible heat system utilization units 4, 5 and the heat source unit 6) is activated and the cooling operation is performed. Here, the operation during the cooling operation of the sensible heat load treatment system is the same as described above, and thus the description thereof is omitted.

  On the other hand, the latent heat load processing system of the air conditioning system 1 is similar to the above in that the dehumidifying operation is performed in the full ventilation mode, but the switching time interval between the adsorption operation and the regeneration operation is used in the normal operation. The switching time interval D giving priority to the sensible heat treatment is set longer than the switching time interval C giving priority to the latent heat treatment. For this reason, the switching operation of the latent heat system utilization side four-way switching valves 21 and 31 of the latent heat system utilization units 2 and 3 is performed at a slower cycle than during normal operation only when the system is activated. Then, immediately after the switching of the latent heat system use side four-way switching valves 21 and 31, the adsorption heat exchangers 22, 23, 32, and 33 mainly perform the latent heat treatment, but when the time D elapses, the sensible heat treatment is mainly performed. As a result, the latent heat load processing system mainly functions as a system for processing the sensible heat load. Thereby, the sensible heat processing capability as the air conditioning system 1 whole can be increased, and indoor sensible heat processing can be accelerated | stimulated.

  Then, the operation at the time of starting the system is canceled after a predetermined condition is satisfied, and the operation is shifted to a normal dehumidifying and cooling operation. For example, after a predetermined time (for example, about 30 minutes) has elapsed from the system startup by a timer provided in the heat source side control unit 65, the operation at the time of system startup is canceled or input by the remote controllers 11 and 12 The temperature difference between the target temperature value of the indoor air and the temperature value of the indoor air sucked into the unit detected by the RA intake temperature / humidity sensors 25 and 35 is less than a predetermined temperature difference (for example, 3 ° C.). After this, the system startup operation is canceled.

  As described above, in the air conditioning system 1, when the system is started, the switching time intervals in the adsorption heat exchangers 22, 23, 32, and 33 of the latent heat system use units 2 and 3 are set longer than those in the normal operation, and are mainly manifested. By performing the heat treatment, the target temperature of indoor air can be reached quickly. Accordingly, the latent heat load processing system that has the adsorption heat exchangers 22, 23, 32, and 33 mainly processes indoor latent heat loads, and the air heat exchangers 42 and 52 that mainly processes indoor sensible heat loads. In the air conditioning system 1 including the sensible heat load processing system, cooling can be performed quickly when the system is activated. Here, the case where the sensible heat load treatment system is air-cooled has been described, but the system activation method can be applied even when the air-warming operation is performed. Although the case where the latent heat load processing system is operated in the full ventilation mode has been described here, the system activation method can be applied in other modes such as a circulation mode and an air supply mode.

(3) Features of the air conditioning system The air conditioning system 1 of the present embodiment has the following features.
(A)
In the air conditioning system 1 of this embodiment, the latent heat system use side refrigerant circuit 10a, 10b having the adsorption heat exchangers 22, 23, 32, 33 and the sensible heat system use side refrigerant circuit 10c having the air heat exchangers 42, 52 are used. 10d is connected to the common heat source side refrigerant circuit 10e, so that a latent heat load processing system that mainly processes indoor latent heat loads and a sensible heat load processing system that mainly processes indoor sensible heat loads are configured. Yes. That is, in this air conditioning system 1, the latent heat load (that is, necessary latent heat treatment capability) that must be processed as the entire air conditioning system and the sensible heat load that is processed as the entire air conditioning system 1 (that is, necessary sensible heat). Heat treatment capacity) is processed using a latent heat load processing system and a sensible heat load processing system including the latent heat system use side refrigerant circuits 10a and 10b, the sensible heat system use side refrigerant circuits 10c and 10d, and the heat source side refrigerant circuit 10e. Yes. That is, all of the latent heat system use side refrigerant circuits 10a and 10b and the sensible heat system use side refrigerant circuits 10c and 10d are combined into one heat source. As a result, there are costs incurred when installing multiple air conditioners using adsorption heat exchangers or installing air conditioners using adsorption heat exchangers together with air conditioners using air heat exchangers. Increase of maintenance and maintenance points can be suppressed.

(B)
Further, in the air conditioning system 1 of the present embodiment, the latent heat system use side refrigerant circuits 10a and 10b are provided with the discharge gas communication pipe 8 and the intake gas communication pipe 9 on the discharge side and the suction side of the compression mechanism 61 of the heat source side refrigerant circuit 10e. Since the latent heat load processing system is connected to the system, the adsorption heat exchangers 22, 23, 32, 33 function as an evaporator or a condenser, so that dehumidification can be performed in an indoor air-conditioned space. While performing, it is possible to perform dehumidification or humidification according to the needs of each indoor air-conditioned space, such as performing humidification in other air-conditioned spaces.

(C)
Moreover, in the air conditioning system 1 of the present embodiment, the sensible heat system use side refrigerant circuits 10c and 10d are connected to the liquid side of the heat source side heat exchanger 63 of the heat source side refrigerant circuit 10e via the liquid communication pipe 7. The sensible heat load processing system is configured by being connected to the discharge side and the suction side of the compression mechanism 61 via the discharge gas communication pipe 8 and the suction gas communication pipe 9, and the discharge side and the suction side of the compression mechanism 61. Can be switched by the cooling / heating switching valves 71, 81 of the connection units 14, 15 as a switching mechanism, so that the cooling / heating switching valves 71, 81 are connected to each other via the discharge gas communication pipe 8. By switching, the air heat exchangers 42 and 52 function as a condenser for indoor heating, or the cooling / heating switching valves 71 and 81 are switched so as to be connected via the intake gas communication pipe 9. In Rukoto, it is possible to air heat exchangers 42 and 52 is caused to function as an evaporator performs the cooling of the indoor. In addition, each of the plurality of sensible heat system use side refrigerant circuits 10c and 10d can be cooled in an indoor air-conditioned space by causing the air heat exchangers 42 and 52 to function as an evaporator or a condenser. It is possible to construct an air conditioning system capable of simultaneous cooling and heating, in which cooling or heating is performed simultaneously according to the needs of each indoor air-conditioned space, such as heating in other air-conditioned spaces. is there.

(D)
In the air conditioning system 1 of the present embodiment, the increase / decrease in the processing capacity of the latent heat load processing system and the increase / decrease in the processing capacity of the sensible heat load processing system are mainly performed by controlling the operating capacity of the common compression mechanism 61. In the air conditioning system 1, the necessary latent heat treatment capacity value Δh and the necessary sensible heat treatment capacity value ΔT are calculated, and the operation capacity of the compression mechanism 61 is controlled based on these values. The latent heat load processing in the latent heat load processing system having 22, 23, 32, and 33 and the sensible heat load processing in the sensible heat load processing system having the air heat exchangers 42 and 52 can be performed at the same time. Thereby, even when the heat sources of the latent heat load processing system and the sensible heat load processing system are shared, it is possible to satisfactorily control the operation capacity of the compression mechanism constituting the heat source.

  The air conditioning system 1 calculates the target evaporation temperature value and the target condensation temperature value of the entire system based on the necessary latent heat treatment capacity value Δh and the required sensible heat treatment capacity value ΔT, and the suction pressure value of the compression mechanism 61. From the evaporation temperature value as a value corresponding to the evaporation temperature of the entire system and the discharge pressure value of the compression mechanism, and the condensation temperature value as a value corresponding to the condensation temperature of the entire system is calculated. The temperature difference between the evaporation temperature and the target condensation temperature is calculated, and the operation capacity of the compression mechanism constituting the heat source is controlled based on these temperature differences.

(E)
In the air conditioning system 1 of the present embodiment, for example, the required sensible heat treatment capability value ΔT is increased, and it is necessary to increase the sensible heat treatment capability in the sensible heat system use side refrigerant circuits 10c, 10d, and the necessary latent heat treatment capability value Δh. When the latent heat treatment capacity in the latent heat system use side refrigerant circuits 10a, 10b needs to be reduced, the switching time interval between the adsorption operation and the regeneration operation of the adsorption heat exchangers 22, 23, 32, 33 is increased. Thus, the sensible heat treatment capacity ratio of the adsorption heat exchangers 22, 23, 32, and 33 can be increased to increase the sensible heat treatment capacity in the latent heat load treatment system.

  Further, in this air conditioning system 1, when the necessary latent heat treatment capacity value Δh becomes large and the latent heat treatment capacity in the latent heat system use side refrigerant circuits 10a, 10b needs to be increased, the adsorption heat exchangers 22, 23, 32, By shortening the switching time interval between the adsorption operation and the regeneration operation of 33, the sensible heat treatment capacity ratio of the adsorption heat exchangers 22, 23, 32, 33 can be reduced and the latent heat treatment capacity in the latent heat load treatment system can be increased. It can be done.

  Thus, in the air conditioning system 1 of the present embodiment, the operating capacity of the compression mechanism is increased by changing the switching time interval between the adsorption operation and the regeneration operation of the adsorption heat exchangers 22, 23, 32, and 33. Since the sensible heat treatment capacity ratio of the adsorption heat exchangers 22, 23, 32, and 33 can be changed, there is no waste in the entire air conditioning system 1, and an efficient operation can be performed.

(F)
In the air conditioning system 1 of the present embodiment, at the time of system startup, the sensible heat treatment is mainly performed by supplying the air heat-exchanged indoors in the air heat exchangers 42 and 52 of the sensible heat system utilization units 4 and 5, In addition, since outdoor air is not allowed to pass by preventing outdoor air from passing through the adsorption heat exchangers 22, 23, 32, 33 of the latent heat system utilization units 2, 3, the latent heat load processing system is activated at the time of system startup. It is possible to prevent the introduction of a heat load from outside air in a state where the air conditioning capability is not exhibited, and the target temperature of indoor air can be quickly reached. Accordingly, the latent heat load processing system having the adsorption heat exchangers 22, 23, 32, 33 and mainly processing the indoor latent heat load, and the air heat exchangers 42 and 52 mainly processing the indoor sensible heat load. In the air conditioning system 1 including the sensible heat load processing system, cooling and heating can be performed quickly when the system is activated.

  Moreover, in the air conditioning system 1 of this embodiment, the sensible heat treatment is mainly performed by supplying the air heat-exchanged indoors in the air heat exchangers 42 and 52 of the sensible heat system utilization units 4 and 5 when the system is started. In the state where the adsorption heat exchangers 22, 23, 32, 33 are switched between the adsorption operation and the regeneration operation, after the outdoor air is passed through the adsorption heat exchangers 22, 23, 32, 33 Therefore, the sensible heat treatment can be performed so that the indoor sensible heat treatment can be promoted and the target temperature of the indoor air can be quickly reached when the system is activated. Accordingly, the latent heat load processing system having the adsorption heat exchangers 22, 23, 32, 33 and mainly processing the indoor latent heat load, and the air heat exchangers 42 and 52 mainly processing the indoor sensible heat load. In the air conditioning system 1 including the sensible heat load processing system, cooling and heating can be performed quickly when the system is activated.

  Moreover, in the air conditioning system 1 of this embodiment, at the time of system start-up, the switching time interval in the adsorption heat exchangers 22, 23, 32, 33 of the latent heat system use units 2, 3 is made longer than that during normal operation, By mainly performing sensible heat treatment, the target temperature of indoor air can be reached quickly. Accordingly, the latent heat load processing system having the adsorption heat exchangers 22, 23, 32, 33 and mainly processing the indoor latent heat load, and the air heat exchangers 42 and 52 mainly processing the indoor sensible heat load. In the air conditioning system 1 including the sensible heat load processing system, cooling and heating can be performed quickly when the system is activated.

In addition, the operation at the time of starting the system is canceled after a sufficient time has elapsed from the start of the system to the sensible heat treatment, or the difference between the indoor air target temperature and the indoor air temperature value is predetermined. By releasing after the temperature difference is less than or equal to, it is possible to promptly shift to a normal operation for processing the latent heat load and the sensible heat load.
(4) Modification 1
In the air conditioning system 1 of the above-described embodiment, the sensible heat system utilization units 4 and 5 and the connection units 14 and 15 constituting the sensible heat load processing system are separate units, but this modification shown in FIG. As described above, the cooling / heating switching valves 71 and 81 of the connection units 14 and 15 may be built in the sensible heat system utilization units 4 and 5. In this case, the connection unit controllers 72 and 82 provided in the connection units 14 and 15 are omitted, and the sensible heat system use side controllers 48 and 58 also have the functions of the connection unit controllers 72 and 82. .

(5) Modification 2
In the air conditioning system 1 of the above-described embodiment, the latent heat system use side refrigerant circuits 10a and 10b constituting the latent heat load processing system are built in the latent heat system use units 2 and 3, and the sensible heat load processing system constituting the sensible heat load processing system. The heat system use side refrigerant circuits 10c and 10d are built in the sensible heat system use units 4 and 5 and the connection units 14 and 15, and the latent heat system use units 2 and 3 and the sensible heat system use units 4 and 5 and the connection unit 14 are included. , 15 are installed separately, but like the air conditioning system 101 of this modification shown in FIG. 31, the latent heat system use side refrigerant circuits 110a, 110b and the sensible heat load processing that constitute the latent heat load processing system. The sensible heat system use-side refrigerant circuits 110c and 110d constituting the system may constitute the integrated use units 102 and 103.

  Thereby, like the air conditioning system 1 of the above-mentioned embodiment, it is equipped with the latent heat system utilization units 2 and 3 and the sensible heat system utilization side refrigerant circuit 10c, 10d provided with the latent heat system utilization side refrigerant circuit 10a, 10b indoors. Compared with the case where the sensible heat system utilization units 4 and 5 and the connection units 14 and 15 are installed separately, the unit size can be reduced and the labor for installing the units can be reduced. In this case, the RA suction temperature sensors 45 and 55 and the sensible heat system use side control units 48 and 58 provided in the sensible heat system use units 4 and 5 and the connection units 14 and 15 of the air conditioning system 1 of the above-described embodiment. The connection unit control units 72 and 82 are omitted, and the latent heat system use side control units 128 and 138 also have the functions of the sensible heat system use side control units 48 and 58 and the connection unit control units 72 and 82.

Further, in the air conditioning system 101 of the present modified example, similarly to the air conditioning system 1 described above, desorption or humidification is performed in the adsorption heat exchangers 122, 123, 132, 133, that is, the latent heat system use side refrigerant circuits 10a, 10b. In addition, only the operation of supplying indoors (that is, latent heat-treated) to the room can be performed.
Further, in the air conditioning system 101 of this modification, the latent heat system use-side refrigerant circuits 110a and 110b and the sensible heat system use-side refrigerant circuits 110c and 110d constituting the sensible heat load processing system are integrated use units 102 and 103. 32, the adsorption heat exchangers 122, 123, 132, 133, that is, the latent heat system use side refrigerant circuits 10a, 10b are dehumidified or humidified (that is, subjected to a latent heat treatment), as shown in FIG. Since the air can be further cooled or heated (ie, sensible heat treatment) (see arrows attached to both sides of the adsorption heat exchangers 122, 123, 132, 133 in FIG. 32), for example, adsorption heat exchange Some of the sensible heat load is processed together with the latent heat load by the units 122, 123, 132, and 133 to suit the indoor target air temperature. Even if the temperature changes to a high temperature, the air is not blown into the room as it is, and further, after sensible heat treatment by the air heat exchangers 142 and 152 to a temperature suitable for the indoor target air temperature, You can drive indoors.

In addition, about the structure of the refrigerant circuit 110 of the air conditioning system 101 of this modification, since it is the same as that of the structure of the refrigerant circuit 10 of the above-mentioned air conditioning system 1, the code | symbol which shows each part of the above-mentioned air conditioning system 1 is set to 100. It changes to the code | symbol of a number stand, and abbreviate | omits description of each part.
[Second Embodiment]
In the air conditioning system 1 of the first embodiment described above, the sensible heat system use side refrigerant circuits 10c and 10d are connected to the liquid communication pipe 7 connected to the liquid side of the heat source side heat exchanger 63 of the heat source side refrigerant circuit 10e. In addition, by switchingably connecting to the discharge gas communication pipe 8 and the intake gas communication pipe 9 via the cooling / heating switching valves 71 and 81, in each of the two sensible heat system use side refrigerant circuits 10c and 10d, By making the air heat exchangers 42 and 52 function as an evaporator or a condenser, each indoor location can be used such as cooling in an indoor air-conditioned space and heating in another air-conditioned space. The so-called air conditioning system capable of simultaneous cooling and heating, which performs cooling or heating at the same time, is configured. The air conditioning of the present embodiment shown in FIG. Like the system 201, the sensible heat system utilization side refrigerant circuits 210c and 210d are connected to the liquid side of the heat source side heat exchanger 263 of the heat source side refrigerant circuit 210e via the liquid connection pipe 207, and the heat source side refrigerant circuit By connecting to the suction side of the compression mechanism 261 of 210e via the suction gas communication pipe 209, the sensible heat system use side refrigerant circuits 210c and 210d may be configured to be used only for indoor cooling.

  In the air conditioning system 201 of the present embodiment, the three-way switching valve 62 and the connection units 14 and 15 of the heat source side refrigerant circuit 10e provided in the air conditioning system 1 of the first embodiment are omitted. However, this is different from the configuration of the refrigerant circuit 10 of the air-conditioning system 1 of the first embodiment, but the other configurations are the same as the configuration of the refrigerant circuit 10 of the air-conditioning system 1 of the first embodiment. The code | symbol which shows the part except the code | symbol of each part of the latent heat system utilization side refrigerant circuit 210a, 210b of the air conditioning system 201 of a form is changed into the code | symbol of the 200 series, and description of each part is abbreviate | omitted.

(2) Modification In the air conditioning system 201 of the second embodiment described above, the latent heat system use-side refrigerant circuits 210a and 210b constituting the latent heat load processing system are built in the latent heat system use units 2 and 3, and sensible heat The sensible heat system utilization side refrigerant circuits 210c and 210d constituting the load processing system are built in the sensible heat system utilization units 204 and 205, and the latent heat system utilization units 2 and 3 and the sensible heat system utilization units 204 and 205 are separately provided. However, as in the air conditioning system 301 of the present modification shown in FIG. 34, the latent heat system use side refrigerant circuits 310a and 310b that constitute the latent heat load treatment system and the sensible heat load treatment system that constitute the sensible heat load treatment system. The heat system use-side refrigerant circuits 310c and 310d may constitute an integrated use unit 302 or 303.

  Thereby, like the above-described air conditioning system 201 of the second embodiment, the latent heat system use units 2 and 3 and the sensible heat system use side refrigerant circuits 210c and 210d provided with the latent heat system use side refrigerant circuits 210a and 210b indoors. Compared with the case where the sensible heat system utilization units 204 and 205 provided with are installed separately, the unit size can be reduced and the labor for installing the units can be saved. In this case, the RA suction temperature sensors 245 and 255 and the sensible heat system use side control units 248 and 258 provided in the sensible heat system use units 204 and 205 of the air conditioning system 201 of the second embodiment described above are omitted. The latent heat system use side control units 328 and 338 also have the functions of the sensible heat system use side control units 248 and 258.

Further, in the air conditioning system 301 of the present modified example, similarly to the air conditioning system 201 described above, dehumidification or humidification is performed in the adsorption heat exchangers 322, 323, 332, 333, that is, the latent heat system use side refrigerant circuits 310a, 310b. In addition, only the operation of supplying indoors (that is, latent heat-treated) to the room can be performed.
Furthermore, in the air conditioning system 301 of the present modification, the sensible heat system use side refrigerant circuits 310c and 310d constituting the sensible heat load processing system of the latent heat system use side refrigerant circuits 310a and 310b are integrated into the integrated use units 302 and 303. Since it is built in, as shown in FIG. 35, it has been dehumidified or humidified (that is, subjected to latent heat treatment) in the adsorption heat exchangers 322, 323, 332, 333, that is, the latent heat system use side refrigerant circuits 310a, 310b. ) Since the air can be further cooled or heated (ie, sensible heat treatment) (see arrows attached to both sides of the adsorption heat exchangers 322, 323, 332, 333 in FIG. 35), for example, an adsorption heat exchanger 322, 323, 332, and 333 handle some of the sensible heat load along with the latent heat load, and are suitable for the indoor target air temperature. Even if the temperature has changed, the air is not blown out indoors as it is, and further, after sensible heat treatment by the air heat exchangers 342 and 352 to a temperature suitable for the indoor target air temperature, You can drive indoors.

In addition, about the structure of the refrigerant circuit 310 of the air conditioning system 301 of this modification, since it is the same as that of the structure of the refrigerant circuit 210 of the above-mentioned air conditioning system 201, the code | symbol which shows each part of the above-mentioned air conditioning system 201 is 300. It changes to the code | symbol of a number stand, and abbreviate | omits description of each part.
[Third Embodiment]
(1) Configuration of Air Conditioning System FIG. 36 is a schematic refrigerant circuit diagram of an air conditioning system 401 according to a third embodiment of the present invention. The air conditioning system 401 is an air conditioning system that processes a latent heat load and a sensible heat load in a building or the like by performing a vapor compression refrigeration cycle operation. The air conditioning system 401 is a so-called separate type multi-air conditioning system, and mainly includes a plurality of (in this embodiment, two) latent heat system utilization units 2 and 3 that are connected in parallel with each other. A plurality of (in this embodiment, two) sensible heat system utilization units 404 and 405, a heat source unit 406, latent heat system utilization units 2 and 3, and sensible heat system utilization units 404 and 405 and a heat source connected in parallel Connecting pipes 407, 408, and 409 for connecting the unit 406 are provided. In the present embodiment, the heat source unit 406 functions as a heat source common to the latent heat system use units 2 and 3 and the sensible heat system use units 404 and 405.

Since the latent heat system use units 2 and 3 have the same configuration as the latent heat system use units 2 and 3 of the first embodiment, description of each part is omitted here.
The sensible heat system utilization units 404 and 405 are different from the first embodiment in that the condensation sensors 446 and 456 and the RA suction temperature / humidity sensors 445 and 455 are provided. However, since the other configurations are the same as those of the sensible heat system utilization units 4 and 5 of the first embodiment, reference numerals indicating the respective parts of the sensible heat system utilization units 4 and 5 of the first embodiment are used. All the symbols are changed to the 400s, and the description of each part is omitted here.

The condensation sensors 446 and 456 are provided so as to function as a condensation detection mechanism that detects the presence or absence of condensation in the air heat exchangers 442 and 452. In the embodiment, the dew condensation sensors 446 and 456 are used. However, the present invention is not limited to this, and may function as a dew condensation detection mechanism. Therefore, a float switch may be provided instead of the dew condensation sensor.
The RA suction temperature / humidity sensors 445 and 455 are temperature / humidity sensors that detect the temperature and relative humidity of the indoor air RA sucked into the unit.

Since the heat source unit 406 has the same configuration as that of the heat source unit 6 of the first embodiment, all the reference numerals indicating the respective parts of the heat source unit 6 of the first embodiment are changed to the reference numerals of 400 series. Description is omitted.
Further, in the sensible heat system utilization units 404 and 405, the gas side of the air heat exchangers 442 and 452 communicates with the discharged gas via the connection units 414 and 415, similarly to the sensible heat system utilization units 4 and 5 of the first embodiment. The pipe 408 and the intake gas communication pipe 409 are connected so as to be switchable. The connection units 414 and 415 mainly connect the cooling / heating switching valves 471 and 481, the evaporation pressure control valves 473 and 483, the evaporation pressure sensors 474 and 484, and the connection units that control the operations of the components constituting the connection units 414 and 415. Control units 472 and 482 are provided. Here, the cooling / heating switching valves 471 and 481 and the connection unit control units 472 and 482 are the same as the cooling / heating switching valves 71 and 81 and the connection unit control units 72 and 82 of the first embodiment, and thus description thereof is omitted. The evaporation pressure control valves 473 and 483 control the evaporation pressure of the refrigerant in the air heat exchangers 442 and 452 when the air heat exchangers 442 and 452 of the sensible heat system utilization units 404 and 405 function as the refrigerant evaporator. It is an electric expansion valve provided to function as a pressure adjustment mechanism. The evaporation pressure sensors 474 and 484 are pressure sensors provided to function as a pressure detection mechanism that detects the pressure of the refrigerant in the air heat exchangers 442 and 452.

In addition, as will be described later, the sensible heat system utilization units 404 and 405 of the present embodiment perform a cooling operation so that no condensation occurs in the air heat exchangers 442 and 452 when performing a dehumidifying cooling operation, so-called sensible heat. It is controlled to perform cooling operation. For this reason, drain piping is not connected to the sensible heat system utilization units 404 and 405.
Moreover, as described above, the latent heat system utilization units 2 and 3 used in the latent heat load treatment system of the air conditioning system 401 can be subjected to latent heat treatment by the adsorption operation and the regeneration operation of the adsorption heat exchangers 22, 23, 32, and 33. Therefore, as with the sensible heat system utilization units 404 and 405, the drain pipe is not connected. That is, a drainless system is realized as the entire air conditioning system 401 of the present embodiment.

(2) Operation | movement of an air conditioning system Next, operation | movement of the air conditioning system 401 of this embodiment is demonstrated. The air conditioning system 401 can process an indoor latent heat load with a latent heat load processing system, and can process an indoor sensible heat load mainly with a sensible heat load processing system. Also in the air conditioning system 401 of this embodiment, the latent heat load processing system 401 can be operated independently, as in the air conditioning system 1 of the first embodiment. Since this operation is the same as the operation of the air conditioning system 1 of the first embodiment, a description thereof is omitted here.

Next, the operation of the air conditioning system 401 when the latent heat load processing system and the sensible heat load processing system are operated simultaneously will be described. The air conditioning system 401 can process an indoor latent heat load mainly by a latent heat load processing system, and can process an indoor sensible heat load mainly by a sensible heat load processing system. Below, various driving | operation operation | movement is demonstrated.
<Drainless dehumidifying and cooling operation>
FIG. 37, FIG. 38, FIG. 39 and FIG. 40 show the operation in the drainless cooling operation in which the sensible heat load processing system performs the sensible heat cooling operation while performing the dehumidifying operation in the full ventilation mode of the latent heat load processing system of the air conditioning system 401. Will be described. Here, FIG. 37 and FIG. 38 are schematic refrigerant circuit diagrams showing the operation during the drainless dehumidifying and cooling operation in the full ventilation mode in the air conditioning system 401. FIG. 39 is a control flowchart for the first drainless dehumidifying and cooling operation in the air conditioning system 401. FIG. 40 is a control flow diagram during the second drainless cooling operation in the air conditioning system 401. 39 and 40, the pair of latent heat system utilization unit 2 and sensible heat system utilization unit 404 of air conditioning system 401 and the pair of latent heat system utilization unit 3 and sensible heat system utilization unit 405 have the same control flow. Therefore, the control flow of the pair of the latent heat system use unit 3 and the sensible heat system use unit 405 is not shown.

  There are two operation methods described below as operations during the drainless dehumidifying and cooling operation of the air conditioning system 1. The first drainless dehumidifying and cooling operation method uses the evaporation pressure control valves 473 and 483 of the connection units 414 and 415 so that the evaporation pressure of the refrigerant in the air heat exchangers 442 and 452 becomes equal to or higher than the minimum evaporation temperature value Te3. It is the driving method to control to. Here, the minimum evaporating temperature value Te3 means that air is not condensed in the air heat exchangers 442 and 452, that is, at least in the air heat exchangers 442 and 452 so as to be at least the dew point temperature of indoor air. The evaporation temperature of the flowing refrigerant. Similarly to the first drainless dehumidifying and cooling operation method, the second drain dehumidifying and cooling operation method uses the evaporating pressure control valves 473 and 483 of the connection units 414 and 415 and the refrigerant in the air heat exchangers 442 and 452. The adsorption operation and regeneration operation of the adsorption heat exchangers 22, 32, 23, 33 of the latent heat system utilization units 2, 3 constituting the latent heat load processing system while controlling the evaporation pressure of the refrigerant to be equal to or higher than the minimum evaporation temperature value Te3. It is the driving | running method which performs control which changes the switching time interval of.

First, the operation | movement at the time of the 1st drainless dehumidification air_conditionaing | cooling operation is demonstrated using FIG.37, FIG38 and FIG.39.
First, the operation of the latent heat load processing system of the air conditioning system 401 will be described. Here, the operations necessary for realizing the sensible heat cooling operation of the sensible heat load processing system will be described later, and the basic operations of the latent heat load processing system will be described first.

  In the latent heat system use unit 2 of the latent heat load processing system, a first operation in which the first adsorption heat exchanger 22 serves as a condenser and the second adsorption heat exchanger 23 serves as an evaporator, and the second adsorption heat exchanger 23. And the second operation in which the first adsorption heat exchanger 22 becomes an evaporator are alternately repeated. Similarly, in the latent heat system utilization unit 3, the first operation in which the first adsorption heat exchanger 32 serves as a condenser and the second adsorption heat exchanger 33 serves as an evaporator, and the second adsorption heat exchanger 33 serves as a condenser. The second operation in which the first adsorption heat exchanger 32 becomes an evaporator is alternately repeated.

In the following description, the operations of the two latent heat system use units 2 and 3 will be described together.
In the first operation, the regeneration operation for the first adsorption heat exchangers 22 and 32 and the adsorption operation for the second adsorption heat exchangers 23 and 33 are performed in parallel. During the first operation, as shown in FIG. 37, the latent heat system use-side four-way switching valves 21 and 31 are in the first state (see the solid lines of the latent heat system use-side four-way switching valves 21 and 31 in FIG. 37). Is set. In this state, the high-pressure gas refrigerant discharged from the compression mechanism 461 flows into the first adsorption heat exchangers 22 and 32 through the discharge gas communication pipe 408 and the latent heat system use side four-way switching valves 21 and 31, and the first It condenses while passing through the adsorption heat exchangers 22 and 32. The condensed refrigerant is depressurized by the latent heat system use side expansion valves 24 and 34 and then evaporated while passing through the second adsorption heat exchangers 23 and 33, and the latent heat system use side four-way switching valve 21. , 31 through the intake gas communication pipe 409, the air is again drawn into the compression mechanism 461 (see the arrow attached to the latent heat system refrigerant circuit 410 in FIG. 37). Here, the sensible heat system utilization side expansion valves 441 and 451 of the sensible heat system utilization units 404 and 405 differ from the above-described operation of only the latent heat load processing system in order to perform the cooling operation, so that the air heat exchanger 442 is used. , 452 is opened to allow the refrigerant to flow, and the opening degree is adjusted, so that a part of the high-pressure gas refrigerant compressed and discharged by the compression mechanism 461 flows through the latent heat system utilization units 2 and 3. Will be.

  During the first operation, in the first adsorption heat exchangers 22 and 32, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the first adsorption heat exchangers 22 and 32 is discharged to the outdoors as exhaust air EA through the exhaust port accompanying the indoor air RA. In the second adsorption heat exchangers 23 and 33, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the adsorption heat generated at that time is absorbed by the refrigerant and the refrigerant evaporates. The outdoor air OA dehumidified by the second adsorption heat exchangers 23 and 33 is supplied indoors as supply air SA through the air supply port (adsorption heat exchangers 22, 23, 32, and 33 in FIG. 37). (See arrows on both sides of the).

  In the second operation, the adsorption operation for the first adsorption heat exchangers 22 and 32 and the regeneration operation for the second adsorption heat exchangers 23 and 33 are performed in parallel. During the second operation, as shown in FIG. 21, the latent heat system use-side four-way switching valves 21 and 31 are in the second state (see the broken lines of the latent heat system use-side four-way switching valves 21 and 31 in FIG. 38). Is set. In this state, the high-pressure gas refrigerant discharged from the compression mechanism 461 flows into the second adsorption heat exchangers 23 and 33 through the discharge gas communication pipe 408 and the latent heat system use-side four-way switching valves 21 and 31, and the second It condenses while passing through the adsorption heat exchangers 23 and 33. The condensed refrigerant is depressurized by the latent heat system use side expansion valves 24 and 34 and then evaporated while passing through the first adsorption heat exchangers 22 and 32, and the latent heat system use side four-way switching valve 21. , 31 is again sucked into the compression mechanism 461 through the suction gas communication pipe 409 (see the arrow attached to the latent heat system refrigerant circuit 410 in FIG. 38).

  During the second operation, in the second adsorption heat exchangers 23 and 33, moisture is desorbed from the adsorbent heated by the condensation of the refrigerant, and the desorbed moisture is given to the indoor air RA sucked from the inside air intake port. Is done. The moisture desorbed from the second adsorption heat exchangers 23, 33 is discharged to the outdoors as exhaust air EA through the exhaust port accompanying the indoor air RA. In the first adsorption heat exchangers 22 and 32, moisture in the outdoor air OA is adsorbed by the adsorbent and the outdoor air OA is dehumidified, and the heat of adsorption generated at that time is absorbed by the refrigerant and the refrigerant evaporates. The outdoor air OA dehumidified by the first adsorption heat exchangers 22 and 32 is supplied indoors as supply air SA through the air supply port (adsorption heat exchangers 22, 23, 32, and 33 in FIG. 38). (See arrows on both sides of the).

Here, the system control performed in the air conditioning system 401 will be described focusing on the latent heat load processing system.
First, when the target temperature and the target relative humidity are set by the remote controllers 411 and 412, the latent heat system use side control units 28 and 38 of the latent heat system use units 2 and 3 together with the target temperature value and the target relative humidity value. The temperature value and relative humidity value of the indoor air sucked into the unit detected by the RA suction temperature / humidity sensors 25, 35 and the air pressure detected by the OA suction temperature / humidity sensors 26, 36 are sucked into the unit. The outdoor air temperature value and relative humidity value are input.

  Then, in step S41, the latent heat system use side control units 28 and 38 calculate the target value of enthalpy or the target value of absolute humidity from the target temperature value and target relative humidity value of indoor air, The current value of the enthalpy of the air sucked into the unit from the indoors or the current value of the absolute humidity is calculated from the temperature value and the relative humidity value detected by the humidity sensors 25 and 35, and the necessary latent heat capacity value which is a difference between the two values is calculated. Δh is calculated. Then, the value of Δh is converted into a capability UP signal K1 for notifying the heat source side control unit 465 whether or not the processing capability of the latent heat system use units 2 and 3 needs to be increased. For example, when the absolute value of Δh is smaller than a predetermined value (that is, when the humidity value of indoor air is close to the target humidity value and there is no need to increase or decrease the processing capacity), the capability UP signal K1 is set to “ 0, and when the absolute value of Δh is larger than the predetermined value in the direction in which the processing capacity must be increased (that is, in the dehumidifying operation, the humidity value of indoor air is higher than the target humidity value and the processing capacity needs to be increased) If the capacity UP signal K1 is “A” and the absolute value of Δh is larger than the predetermined value in the direction in which the processing capacity must be reduced (that is, in the dehumidifying operation, the humidity value of the indoor air is If the humidity is lower than the target humidity value and the processing capacity needs to be lowered, the capacity UP signal K1 is set to “B”.

Next, operation | movement of the sensible heat load processing system of the air conditioning system 1 is demonstrated.
When performing cooling operation of the sensible heat system utilization units 404 and 405, the three-way switching valve 462 of the heat source unit 406 is in a condensing operation state (a state in which the first port 462a and the third port 462c are connected). . In addition, the cooling / heating switching valves 471 and 481 of the connection units 414 and 415 are in a cooling operation state (a state where the first ports 471a and 481a and the second ports 471b and 481b are connected). Moreover, the opening degree of the sensible heat system utilization side expansion valves 441 and 451 of the sensible heat system utilization units 404 and 405 is adjusted so as to depressurize the refrigerant. The heat source side expansion valve 464 is in an opened state.

  In such a state of the refrigerant circuit 410, the high-pressure gas refrigerant discharged from the compression mechanism 461 passes through the three-way switching valve 462, flows into the heat source side heat exchanger 463, and is condensed to become liquid refrigerant. This liquid refrigerant is sent to the sensible heat system utilization units 404 and 405 through the heat source side expansion valve 464, the receiver 468 and the liquid communication pipe 407. The liquid refrigerant sent to the sensible heat system utilization units 404 and 405 is depressurized by the sensible heat system utilization side expansion valves 441 and 451 and then taken indoors by the air heat exchangers 442 and 452. It evaporates by heat exchange with the air RA and becomes a low-pressure gas refrigerant. This gas refrigerant is again sucked into the compression mechanism 461 of the heat source unit 406 through the cooling / heating switching valves 471 and 481 of the connection units 414 and 415 and the suction gas communication pipe 409. On the other hand, the indoor air RA cooled by the heat exchange with the refrigerant in the air heat exchangers 442 and 452 is supplied indoors as the supply air SA. As will be described later, the sensible heat system use side expansion valves 441 and 451 are superheated in the air heat exchangers 442 and 452, that is, the air heat exchangers 442 and 453 detected by the liquid side temperature sensors 443 and 453, respectively. The opening degree is such that the temperature difference between the liquid side refrigerant temperature value of 452 and the gas side refrigerant temperature value of the air heat exchangers 442 and 452 detected by the gas side temperature sensors 454 and 455 becomes the target superheat degree SHS. Control is being made.

Here, the system control performed in the air conditioning system 401 will be described focusing on the sensible heat load processing system. Here, the control necessary for realizing the sensible heat cooling operation of the sensible heat load treatment system will be described later, and the basic control of the sensible heat load treatment system will be described.
First, when the target temperature is set by the remote controllers 411 and 412, the sensible heat system use side control units 448 and 458 of the sensible heat system use units 404 and 405 have the RA intake temperature together with these target temperature values. The temperature value of the indoor air sucked into the unit detected by the humidity sensors 445 and 455 is input.

  Then, in step S44, the sensible heat system utilization side control units 448 and 458 determine the temperature difference between the target temperature value of the indoor air and the temperature value detected by the RA intake temperature sensors 445 and 455 (hereinafter referred to as required sensible heat capacity). Value ΔT). Here, since the necessary sensible heat capacity value ΔT is the difference between the target temperature value of indoor air and the current temperature value of indoor air as described above, the sensible heat that must be processed in the air conditioning system 401. It corresponds to a load. Then, the value of the required sensible heat capacity value ΔT is converted into a capacity UP signal K2 for notifying the heat source side control unit 465 whether or not the processing capacity of the sensible heat system utilization units 404 and 405 needs to be increased. For example, when the absolute value of ΔT is smaller than a predetermined value (that is, when the temperature value of indoor air is close to the target temperature value and there is no need to increase or decrease the processing capacity), the capability UP signal K2 is set to “ 0, and the absolute value of ΔT is larger than the predetermined value in the direction in which the processing capacity must be increased (that is, in the cooling operation, the temperature value of the indoor air is higher than the target temperature value and the processing capacity needs to be increased). When the capacity UP signal K2 is “a” and the absolute value of ΔT is larger than the predetermined value in the direction in which the processing capacity must be lowered (that is, in the cooling operation, the temperature value of the indoor air is When the temperature is lower than the target temperature value and the processing capacity needs to be lowered), the capacity UP signal K2 is set to “b”.

  Next, in step S45, the sensible heat system use side control units 448 and 458 change the value of the target superheat degree SHS according to the value of the required sensible heat capacity value ΔT. For example, when it is necessary to reduce the processing capacity of the sensible heat system utilization units 404 and 405 (when the capacity UP signal K2 is “b”), the target superheat degree SHS is increased and the air heat exchangers 442 and 452 are increased. The opening degree of the sensible heat system use side expansion valves 441 and 451 is controlled so as to reduce the amount of heat exchanged between the refrigerant and the air.

  Next, in step S42, the heat source side control unit 465 transmits the capability UP signal K1 of the latent heat system use units 2 and 3 transmitted from the latent heat system use side control units 28 and 38 to the heat source side control unit 465, and the sensible heat system. The target condensation temperature value TcS and the target evaporation temperature value TeS are calculated using the capability UP signal K2 of the sensible heat system utilization units 404, 405 transmitted from the use side control units 448, 458 to the heat source side control unit 465. For example, the target condensation temperature value TcS is calculated by adding the capability UP signal K1 of the latent heat system utilization units 2 and 3 and the capability UP signal K2 of the sensible heat system utilization units 404 and 405 to the current target condensation temperature value. The The target evaporation temperature value TeS is calculated by subtracting the capability UP signal K1 of the latent heat system usage units 2 and 3 and the capability UP signal K2 of the sensible heat system usage units 404 and 405 from the current target evaporation temperature value. . Thereby, when the value of the capability UP signal K1 is “A” or when the value of the capability UP signal K2 is “a”, the target condensation temperature value TcS becomes high and the target evaporation temperature value TeS becomes low.

  Next, in step S43, a system condensing temperature value Tc and a system evaporating temperature value Te, which are values corresponding to actual measured values of the condensing temperature and evaporating temperature of the entire air conditioning system 1, are calculated. For example, the system condensing temperature value Tc and the system evaporating temperature value Te are the suction pressure value of the compression mechanism 461 detected by the suction pressure sensor 466 and the discharge pressure value of the compression mechanism 461 detected by the discharge pressure sensor 467. It is calculated by converting into the refrigerant saturation temperature at the pressure value. Then, the temperature difference ΔTc of the target condensation temperature value TcS with respect to the system condensation temperature value Tc and the temperature difference ΔTe of the target evaporation temperature value TeS with respect to the system evaporation temperature value Te are calculated, and by dividing these temperature differences, the compression mechanism 461 Determine whether the operating capacity needs to be increased or decreased and the range of increase or decrease.

  By using the operating capacity of the compression mechanism 461 determined in this way, the system capacity is controlled so as to approach the target relative humidity of indoor air by controlling the operating capacity of the compression mechanism 461. For example, when the value obtained by subtracting the temperature difference ΔTe from the temperature difference ΔTc is a positive value, the operating capacity of the compression mechanism 461 is increased. Conversely, when the value obtained by subtracting the temperature difference ΔTe from the temperature difference ΔTc is a negative value. Controls to reduce the operating capacity of the compression mechanism 461.

  Thus, in this air conditioning system 401, the latent heat load (which corresponds to the necessary latent heat treatment capacity, Δh) that must be processed as the entire air conditioning system 401 and the sensible heat load that must be processed as the entire air conditioning system 1 (Necessary sensible heat treatment capacity, corresponding to ΔT) is a latent heat load treatment system (specifically, latent heat system use units 2 and 3) and a sensible heat load treatment system (specifically, sensible heat system use unit 404, 405). Here, the increase / decrease in the processing capacity of the latent heat load processing system and the increase / decrease in the processing capacity of the sensible heat load processing system are calculated by calculating the necessary latent heat treatment capacity value Δh and the required sensible heat treatment capacity value ΔT, Since the operation capacity of the compression mechanism 461 is controlled, the latent heat load processing in the latent heat load processing system having the adsorption heat exchangers 22, 23, 32, 33 and the sensible heat load processing having the air heat exchangers 442, 452 are performed. The sensible heat load processing in the system can be performed at the same time. Thereby, even when the heat sources of the latent heat load processing system and the sensible heat load processing system are made common as in the air conditioning system 401 of the present embodiment, the operation capacity of the compression mechanism that constitutes the heat source is favorably controlled. Can do.

  By the way, in the air conditioning system 401, as described above, the latent heat treatment for mainly processing the indoor latent heat load is performed in the latent heat load processing system (that is, the latent heat system utilization units 2 and 3). In the system (that is, the sensible heat system utilization units 404 and 405), the sensible heat cooling operation is performed to process only the indoor sensible heat load. In the air conditioning system 401, the sensible heat cooling operation of the sensible heat load treatment system is realized by performing the following system control using the evaporation pressure control valves 473 and 483 of the connection units 414 and 415. ing.

  First, in step S46, the sensible heat system utilization side control units 448 and 458 determine the dew point temperature from the temperature value and relative humidity value of the indoor air sucked into the unit detected by the RA suction temperature / humidity sensors 445 and 455. And the minimum evaporation temperature value Te3 of the refrigerant flowing in the air heat exchangers 442 and 452 is calculated so that the air does not condense in the air heat exchangers 442 and 452, that is, at least the dew point temperature or more. .

  Next, in step S47, the lowest evaporation temperature value Te3 transmitted from the sensible heat system utilization side control units 448 and 458 to the connection unit control units 472 and 482 is set to the lowest evaporation pressure which is a saturation pressure corresponding to the temperature value Te3. Convert to the value P3. In step S48, the minimum evaporation pressure value P3 is compared with the refrigerant pressure value in the air heat exchangers 442 and 452 detected by the evaporation pressure sensors 474 and 484, and detected by the evaporation pressure sensors 474 and 484. The opening degree of the evaporating pressure adjusting valves 473 and 483 is adjusted so that the refrigerant pressure value in the air heat exchangers 442 and 452 is equal to or higher than the minimum evaporating pressure value P3.

  Thereby, even if the operating capacity of the compression mechanism 461 is changed according to the required sensible heat treatment capacity value, the pressure value of the refrigerant in the air heat exchangers 442 and 452 detected by the evaporation pressure sensors 474 and 484 is detected. However, since it is adjusted by the evaporation pressure control valves 473 and 483 so as to be equal to or higher than the minimum evaporation pressure value P3 corresponding to the dew point temperature of indoor air, the sensible heat cooling operation can be realized.

  During the drainless dehumidifying and cooling operation described above, the evaporation temperature of the air heat exchangers 442 and 452 of the sensible heat load treatment system of the air conditioning system 401 becomes equal to or lower than the dew point temperature (that is, the lowest evaporation temperature value Te3 or lower). When dew condensation is detected in the sensors 446 and 456, the connection unit control units 414 and 415 set the minimum evaporating pressure value P3 so that the pressure value is higher than the minimum evaporating pressure value P3 when dew condensation is detected. The sensible heat system use side control units 448 and 458 close the sensible heat system use side expansion valves 441 and 451, or the sensible heat system use side control units 448 and 458 condense on the heat source side control unit 465. When the heat source side control unit 465 stops the compression mechanism 461 by transmitting a signal informing that the air has been detected, dew condensation in the air heat exchangers 442 and 452 is ensured. It is possible to prevent.

Next, the operation | movement at the time of 2nd drainless dehumidification air_conditionaing | cooling operation is demonstrated using FIG.37, FIG38 and FIG.40.
In the first drainless dehumidifying and cooling operation method described above, indoor latent heat load processing is performed in the latent heat load processing system. In the sensible heat load processing system, indoor sensible heat is used by using the evaporation pressure control valves 473 and 483. A sensible cooling operation is performed to process only the load. That is, the latent heat treatment capacity (required latent heat treatment capacity, corresponding to Δh) that must be processed by the latent heat load processing system and the sensible heat load processing system, and the visible heat that must be processed by the latent heat load processing system and the sensible heat load processing system. The heat treatment capability (necessary sensible heat treatment capability, corresponding to ΔT) is processed using a latent heat load treatment system and a sensible heat load treatment system. Here, the increase or decrease in the processing capacity of the latent heat load processing system and the sensible heat load processing system is mainly performed by operating capacity control of the compression mechanism 461.

  And in the latent heat load process by the latent heat load processing system of the air conditioning system 1, as FIG. 5 shows, the 1st adsorption heat exchangers 22 and 32 and the 2nd adsorption heat exchanger 23 which comprise a latent heat load processing system. , 33 by the adsorption operation or the regeneration operation, not only the latent heat treatment but also the sensible heat treatment is performed. Here, if the processing capacity of the sensible heat treatment performed together with the latent heat treatment in the latent heat load processing system is the generated sensible heat processing capacity, the sensible heat load that must be processed by the sensible heat load processing system is determined from the required latent heat processing capacity. It is the amount minus the ability.

  For this reason, in the second drainless dehumidifying and cooling operation method, the following system control is performed in consideration of the processing of the sensible heat load in the latent heat load processing system of the air conditioning system 401. Note that the second drainless dehumidifying and cooling operation method is the same as the control flow in the first operation method except for steps S49 to S52 specific to this operation method (that is, steps S41 to S48). The description is omitted.

  In the latent heat system use side control units 28 and 38, in step S49, the switching time interval between the adsorption operation and the regeneration operation in the adsorption heat exchangers 22 and 23 and the adsorption heat exchangers 32 and 33 is set to the sensible heat priority mode (for example, FIG. 5), and when the capacity UP signal K2 is “b” (when the sensible heat treatment capacity in the sensible heat system utilization side units 404 and 405 is reduced), switching is performed in step S51. The time interval is changed to latent heat priority (for example, time C in FIG. 5). Conversely, in the case of other conditions, the process proceeds to step S50.

  In step S50, the switching time interval between the adsorption operation and the regeneration operation in the adsorption heat exchangers 22 and 23 and the adsorption heat exchangers 32 and 33 is the latent heat priority (for example, time C in FIG. 5), and the capacity is increased. When the signal K2 is “a” (when the necessary sensible heat treatment capability in the sensible heat system utilization side units 404 and 405 is increased), in step S52, the switching time interval is given priority to sensible heat (for example, FIG. 5). By changing to time D), the sensible heat treatment capability in the latent heat load treatment system can be increased.

  As a result, in the second operation method, when the required sensible heat treatment capacity value ΔT is increased and the sensible heat treatment capacity in the sensible heat load treatment system of the air conditioning system 1 needs to be increased, the latent heat system utilization units 2, 3 By increasing the switching time interval between the adsorption operation and the regeneration operation of the adsorption heat exchangers 22, 32, 23, 33, the latent heat treatment capacity processed in the adsorption heat exchangers 22, 32, 23, 33 is reduced. The sensible heat treatment capacity is increased to increase the sensible heat treatment capacity in the latent heat load treatment system, that is, the sensible heat treatment capacity ratio can be increased. The air heat exchangers 42 and 52 of the sensible heat load processing system are operated so that moisture in the air does not condense, and only the indoor sensible heat load is processed. However, it is possible to follow the fluctuation of the sensible heat treatment ability.

  As in the first operation method, during the drainless dehumidifying and cooling operation described above, the evaporation temperature of the air heat exchangers 442 and 452 of the sensible heat load treatment system of the air conditioning system 401 is lower than the dew point temperature (that is, the lowest evaporation). When the condensation sensors 446 and 456 detect condensation at a temperature value Te3 or lower), the connection unit controllers 472 and 482 set the pressure value higher than the minimum evaporation pressure value P3 when condensation is detected. The minimum evaporation pressure value P3 is corrected so that the sensible heat system use side control units 448 and 458 close the sensible heat system use side expansion valves 441 and 451, or the sensible heat system use side control unit 448, 458 transmits a signal notifying the heat source side control unit 465 that dew condensation has been detected, and the heat source side control unit 465 stops the compression mechanism 461, whereby the air heat exchanger 442, Condensation at 52 can be reliably prevented.

<Drainless system startup>
Next, the operation | movement at the time of starting of the air conditioning system 401 is demonstrated using FIG.41, FIG.42, FIG.43 and FIG. In the air conditioning system 401, the drainless system activation is performed to activate the system without causing condensation in the air heat exchangers 442 and 452 of the sensible heat system utilization units 404 and 405. Here, FIG. 41 is a schematic refrigerant circuit diagram illustrating the operation of the air conditioning system 401 when the first drainless system is activated. FIG. 42 is an air line diagram illustrating a state of indoor air when the drainless system of the air conditioning system 401 is activated. FIGS. 43 and 44 are schematic refrigerant circuit diagrams illustrating the operation of the air conditioning system 401 when the second drainless system is activated.

  There are two activation methods described below as operations at the time of activation of the air conditioning system 401. The first drainless system activation method is an operation method that prioritizes indoor latent heat load processing by the latent heat load processing system over indoor sensible heat load processing by the sensible heat load processing system of the air conditioning system 401. The second drainless system activation method is similar to the first drainless system activation method. The indoor latent heat load is processed by the latent heat load processing system rather than the indoor sensible heat load by the sensible heat load processing system. In the latent heat system use units 2 and 3 of the latent heat load processing system, the outdoor air is regenerated among the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33. An adsorption heat exchanger that discharges the outdoor air after passing through the adsorption heat exchanger and performs an adsorption operation among the first adsorption heat exchangers 22 and 32 and the second adsorption heat exchangers 23 and 33. It is the driving | running method supplied indoors after letting pass.

First, the operation at the time of starting the first drainless system will be described with reference to FIGS. 41 and 42.
When an operation command is issued from the remote controllers 411 and 412, the sensible heat load processing system of the air conditioning system 401 is stopped (that is, the sensible heat system use side expansion valves 441 and 451 of the sensible heat system use units 404 and 405 are closed). The latent heat load processing system is activated and the dehumidifying operation is performed. Here, the operation during the dehumidifying operation of the latent heat load processing system is the same as the operation during the drainless dehumidifying and cooling operation described above (however, the switching time interval is fixed at the time C in the latent heat priority mode), and thus the description thereof is omitted. .

  On the other hand, in the sensible heat system, for example, in the sensible heat system use side control units 448 and 458, the indoor air temperature value and relative humidity value (specifically, the RA intake temperature of the latent heat system use units 2 and 3). Calculate the dew point temperature or absolute humidity value of indoor air from the humidity sensor 25, 35 and the RA intake temperature of the sensible heat system utilization units 404, 405, the temperature value and the relative humidity value detected by the humidity sensors 445, 455) When the measured value of the dew point temperature or absolute humidity of indoor air exists in the hatched area of FIG. 25 (that is, the dew point temperature value or absolute humidity value of indoor air is higher than the target dew point temperature value or target absolute humidity value) If it is in the state), maintain the stopped state until the dew point temperature value or absolute humidity value of the indoor air falls below the target dew point temperature value or the target absolute humidity value, and air heat exchange immediately after startup Moisture in the air is to prevent the formation of condensation in the 442 and 452. Here, the dew point temperature or the absolute humidity value calculated from the target temperature value and the target humidity value input to the remote controllers 411 and 412, and the RA intake temperature / humidity sensor of the latent heat system use units 2 and 3 detected at the time of system startup. 25, 35, and the sensible heat system utilization units 404, 405, appropriate values that are intermediate between the dew point temperature value or the absolute humidity value calculated from the temperature value and the relative humidity value detected by the RA suction temperature / humidity sensors 445, 455. Set to dew point temperature value or absolute humidity value.

Then, after the target dew point temperature value or the target absolute humidity value is reached by the operation of the latent heat load processing system, the sensible heat load processing system is activated (specifically, the sensible heat system of the sensible heat system utilization units 404 and 405). By performing the drainless dehumidifying and cooling operation described above (with the use side expansion valves 441 and 451 in the control state), the temperature of the indoor air is cooled to the target temperature.
As described above, in the air conditioning system 1, the processing of the indoor latent heat load by the latent heat load processing system is prioritized over the processing of the indoor sensible heat load by the sensible heat load processing system. After sufficiently reducing the humidity of the indoor air by performing the latent heat treatment, the sensible heat treatment system can perform the sensible heat treatment. As a result, the latent heat load processing system including the latent heat system utilization units 2 and 3 having the adsorption heat exchangers 22, 23, 32, and 33 mainly processing the indoor latent heat load, and the air heat exchangers 442 and 452 are provided. The air heat exchangers 442 and 452 are configured to include a sensible heat load treatment system including sensible heat system utilization units 404 and 405 that operate so that moisture in the air does not condense and process only the indoor sensible heat load. In the air conditioning system 401, even when the system is activated under conditions where the dew point temperature of indoor air is high, the sensible heat load is processed promptly while preventing condensation in the air heat exchangers 442 and 452. be able to.

Next, the operation at the time of starting the second drainless system will be described with reference to FIGS. 43 and 44. FIG.
When an operation command is issued from the remote controllers 411 and 412, the latent heat load processing system is started and the dehumidifying operation is performed in a state where the sensible heat load processing system is stopped as in the case of starting the first drainless system. Here, about the operation | movement at the time of dehumidification operation | movement of a latent-heat load processing system, dehumidification operation is performed not by a full ventilation mode but by the circulation mode. The control of the latent heat system refrigerant circuit 410 of the latent heat load processing system is the same as the operation during the drainless dehumidifying and cooling operation (however, the switching time interval is fixed at the time C in the latent heat priority mode). Further, regarding the air flow of the latent heat system use units 2 and 3 of the latent heat load processing system, the indoor air RA is generated by the operation of the latent heat system use side four-way switching valves 21 and 31, the supply fan, the exhaust fan, the damper, and the like. An operation in which the air is sucked into the unit through the inside air inlet and supplied indoors as the supply air SA through the air inlet, and the outdoor air OA is sucked into the unit through the outside air inlet and discharged to the outside as the exhaust air EA through the exhaust port. Is done.

  As described above, in the air conditioning system 401, when the second drainless system is activated, the outdoor air is kept in a humid state by performing the dehumidifying operation (that is, the dehumidifying operation in the circulation mode) while circulating the indoor air. In some cases, such as when there is a possibility that indoor humidity may increase when outdoor air is supplied, it is possible to dehumidify while circulating indoor air, so the target dew point temperature value or target absolute humidity value can be quickly And the sensible heat load processing by the sensible heat load processing system can be performed.

(3) Features of the Air Conditioning System The air conditioning system 401 of the present embodiment has the following features in addition to the features of the air conditioning system 1 of the first embodiment.
(A)
The air conditioning system 401 of the present embodiment includes a latent heat system use-side refrigerant circuit 410a that can be discharged outdoors by adsorbing or desorbing moisture in the air in the adsorption heat exchangers 22, 23, 32, and 33. 410b including a latent heat load processing system for mainly processing an indoor latent heat load, and a sensible heat system capable of performing heat exchange between refrigerant and air so that moisture in the air is not condensed in the air heat exchangers 442 and 452. It includes a sensible heat load processing system that includes the use side refrigerant circuits 410c and 410d and processes only the indoor sensible heat load. For this reason, this air conditioning system 401 includes the latent heat system use units 2 and 3 having the latent heat system use side refrigerant circuits 410a and 410b and the sensible heat system use units 404 and 405 having the sensible heat system use side refrigerant circuits 410c and 410d. This is a drainless system that does not require drain piping. In the cooling operation, the sensible heat load treatment system has a large sensible heat treatment capacity value ΔT, and even when the sensible heat treatment capacity in the sensible heat load treatment system needs to be increased, the air heat exchanger 442, Since the evaporation temperature of 452 is restricted by the dew point temperature of the indoor air, the sensible heat treatment capacity cannot be increased.

  However, in the air conditioning system 401 of the present embodiment, when the necessary sensible heat treatment capacity value ΔT becomes large and it is necessary to increase the sensible heat treatment capacity in the sensible heat load treatment system, the adsorption heat exchange that constitutes the latent heat load treatment system. By increasing the switching time interval between the adsorption operation and the regeneration operation of the units 22, 23, 32, 33, the latent heat treatment capability processed in the adsorption heat exchangers 22, 23, 32, 33 is reduced and the sensible heat treatment capability is increased. In other words, the sensible heat treatment capacity ratio of the latent heat load treatment system can be increased to increase the sensible heat treatment capacity of the latent heat load treatment system.

  Accordingly, an air conditioning system including a latent heat load processing system that mainly processes an indoor latent heat load and a sensible heat load processing system that operates so that moisture in the air does not condense and processes only the indoor sensible heat load. 1, even when the required sensible heat treatment capacity is increased, the sensible heat load treatment system is operated so that moisture in the air does not condense, and only the indoor sensible heat load is treated to follow the fluctuation of the sensible heat treatment capacity. be able to.

(B)
In the air conditioning system 401 of this embodiment, based on the dew point temperature of indoor air, for example, the evaporation pressure is adjusted so that the evaporation temperature of the refrigerant in the air heat exchangers 442 and 452 does not become lower than the dew point temperature of indoor air. By controlling the valves 473 and 483, moisture in the air is not condensed on the surfaces of the air heat exchangers 442 and 452, and generation of drain water in the air heat exchangers 442 and 452 can be suppressed.

  Further, in the air conditioning system 401, the air heat exchange measured by the evaporation pressure sensors 474 and 484 instead of the dew point temperature is used as the control value of the refrigerant evaporation pressure in the air heat exchangers 442 and 452 by the evaporation pressure control valves 473 and 483. Since the evaporating pressure of the refrigerant in the containers 442 and 452 is used, control responsiveness can be improved as compared with the case where the evaporating pressure of the refrigerant is controlled using the dew point temperature.

(C)
In the air conditioning system 401 of the present embodiment, the condensation sensors 446 and 456 reliably detect condensation in the air heat exchangers 442 and 452, and when condensation is detected, the minimum evaporation pressure value calculated from the dew point temperature is detected. By changing P3, the evaporation pressure of the refrigerant in the air heat exchangers 442 and 452 can be changed, the compression mechanism 461 is stopped, the sensible heat system use units 404 and 405 are expanded on the sensible heat system use side. Since the valves 441 and 451 are closed, condensation in the air heat exchangers 442 and 452 can be reliably prevented.

(D)
In the air conditioning system 401 of the present embodiment, when the system is started, the indoor latent heat load processing by the latent heat load processing system is prioritized over the indoor sensible heat load processing by the sensible heat load processing system. By performing the latent heat treatment by the latent heat load treatment system, the sensible heat treatment can be performed by the sensible heat load treatment system after sufficiently reducing the humidity of the indoor air.

  More specifically, when the system starts up, the sensible heat load treatment is performed until the dew point temperature of the indoor air falls below the target dew point temperature value or until the absolute humidity of the indoor air falls below the target absolute humidity value. By stopping the indoor sensible heat load processing by the system and performing only the latent heat treatment by the latent heat load processing system, it is possible to shift to the sensible heat load processing by the sensible heat load processing system as quickly as possible.

  As a result, the latent heat load processing system having the adsorption heat exchangers 22, 23, 32, and 33 mainly for processing the indoor latent heat load, and the air heat exchangers 442 and 452 having the air heat exchangers 442 and 452 in the air In an air conditioning system 1 that is combined with a sensible heat load treatment system that operates so as to prevent moisture from condensing and processes only the indoor sensible heat load, the system is activated under conditions where the dew point temperature of the indoor air is high. Even when it is performed, the sensible heat load can be quickly processed while preventing condensation in the air heat exchangers 442 and 452.

(E)
Moreover, in the air conditioning system 401 of the present embodiment, when the system is started, outdoor air is passed outdoor after passing through the adsorption heat exchanger that performs the regeneration operation among the adsorption heat exchangers 22, 23, 32, and 33. It is possible to discharge the indoor air and to supply the indoor air again after passing through the adsorption heat exchanger performing the adsorption operation among the adsorption heat exchangers 22, 23, 32, and 33. Thus, when the system is activated, the dehumidifying operation is performed while circulating the indoor air, so that the sensible heat load processing system can be shifted to the sensible heat load processing system as quickly as possible.

(4) Modification 1
In the air conditioning system 401 of the third embodiment described above, the dew point of the indoor air is determined from the temperature and relative humidity of the indoor air detected by the RA suction temperature / humidity sensors 445 and 455 of the sensible heat system utilization units 404 and 405. The temperature is calculated and the minimum evaporating temperature value Te3 of the refrigerant in the air heat exchangers 442 and 452 is calculated and used for system control. As shown in FIG. 45, the sensible heat system utilization unit 404, Dew point sensors 447 and 457 may be provided at 405, and the dew point temperatures detected by the dew point sensors 447 and 457 may be used for system control.

(5) Modification 2
In the air conditioning system 401 of the third embodiment described above, the sensible heat system utilization units 404 and 405 and the connection units 414 and 415 constituting the sensible heat load processing system are separate units, but the book shown in FIG. As in the modification, the cooling / heating switching valves 471 and 481, the evaporation pressure control valves 473 and 483, and the evaporation pressure sensors 474 and 484 of the connection units 414 and 415 may be incorporated in the sensible heat system utilization units 404 and 405. In this case, the connection unit control units 472 and 482 provided in the connection units 414 and 415 are omitted, and the sensible heat system use side control units 448 and 458 also have the functions of the connection unit control units 472 and 482. .

(6) Modification 3
In the air conditioning system 401 of the above-described third embodiment, the latent heat system use-side refrigerant circuits 410a and 410b constituting the latent heat load processing system are built in the latent heat system use units 2 and 3 to configure the sensible heat load processing system. The sensible heat system utilization side refrigerant circuits 410c and 410d are built in the sensible heat system utilization units 404 and 405 and the connection units 414 and 415, and the latent heat system utilization units 2 and 3 and the sensible heat system utilization units 404 and 405 and the connection are connected. Although the units 414 and 415 are installed separately, like the air conditioning system 501 of the present modification shown in FIG. 47, the latent heat system use side refrigerant circuits 510a and 510b and the sensible heat constituting the latent heat load processing system. The sensible heat system use side refrigerant circuit 510c, 510d constituting the load processing system is integrated with the use unit 50. , It may constitute a 503.

  Thereby, like the above-mentioned air conditioning system 401 of the third embodiment, the latent heat system use units 2 and 3 and the sensible heat system use side refrigerant circuits 410c and 410d provided with the latent heat system use side refrigerant circuits 410a and 410b indoors. Compared to the case where the sensible heat system utilization units 404 and 405 and the connection units 414 and 415 provided with are separately installed, the unit size can be reduced and the labor for installing the units can be reduced. In this case, the RA suction temperature sensors 445 and 455 and the sensible heat system utilization side control unit 448 provided in the sensible heat system utilization units 404 and 405 and the connection units 414 and 415 of the air conditioning system 401 of the third embodiment described above. 458 and the connection unit control units 472 and 482 are omitted, and the latent heat system use side control units 528 and 538 also have the functions of the sensible heat system use side control units 448 and 458 and the connection unit control units 472 and 482. .

Further, in the air conditioning system 501 of the present modified example, similarly to the air conditioning system 401 described above, desorption or humidification is performed in the adsorption heat exchangers 522, 523, 532, and 533, that is, the latent heat system use side refrigerant circuits 510a and 510b. In addition, only the operation of supplying indoors (that is, latent heat-treated) to the room can be performed.
Further, in the air conditioning system 501 of this modification, the latent heat system use side refrigerant circuits 510a and 510b and the sensible heat system use side refrigerant circuits 510c and 510d constituting the sensible heat load processing system are integrated use units 502 and 503. 48, the adsorption heat exchangers 522, 523, 532, and 533, that is, the latent heat system use side refrigerant circuits 510a and 510b are dehumidified or humidified (that is, subjected to latent heat treatment). Since the air can be further cooled or heated (ie, sensible heat treatment) (see arrows attached to both sides of the adsorption heat exchangers 522, 523, 532, and 533 in FIG. 48), for example, adsorption heat exchange Some of the sensible heat load is processed together with the latent heat load by the units 522, 523, 532, and 533 to obtain the indoor target air temperature. Even if the temperature has changed, the air is not blown out into the room as it is, but is further subjected to a sensible heat treatment by the air heat exchangers 542 and 552 to a temperature suitable for the indoor target air temperature. Can be driven indoors.

In addition, about the structure of the refrigerant circuit 510 of the air conditioning system 501 of this modification, since it is the same as that of the refrigerant circuit 410 of the above-mentioned air conditioning system 401, the code | symbol which shows each part of the above-mentioned air conditioning system 401 is 500 It changes to the code | symbol of a number stand, and abbreviate | omits description of each part.
[Fourth Embodiment]
(1) Configuration of Air Conditioning System FIG. 49 is a schematic refrigerant circuit diagram of an air conditioning system 601 of a fourth embodiment according to the present invention. The air conditioning system 601 is an air conditioning system that processes an indoor latent heat load and a sensible heat load such as a building by performing a vapor compression refrigeration cycle operation. The air conditioning system 601 is a so-called separate type multi-air conditioning system, which mainly includes a plurality of (in this embodiment, two) latent heat system utilization units 2 and 3 that are connected in parallel to each other, A plurality of (in this embodiment, two) sensible heat system utilization units 604, 605, a heat source unit 606, a latent heat system utilization unit 2, 3 and a sensible heat system utilization unit 604, 605 and a heat source connected in parallel Communication pipes 607, 608, and 609 for connecting the unit 606 are provided. In the present embodiment, the heat source unit 606 functions as a heat source common to the latent heat system use units 2 and 3 and the sensible heat system use units 604 and 605.

Since the latent heat system use units 2 and 3 have the same configuration as the latent heat system use units 2 and 3 of the first embodiment, description of each part is omitted here.
The sensible heat system utilization units 604 and 605 are characterized in that the dew condensation sensors 646 and 656 are provided and the RA suction temperature / humidity sensors 645 and 655 are provided. Although different from 305, the other configurations are the same as those of the sensible heat system utilization units 304 and 305 of the second embodiment. All the symbols are changed to 600 numbers, and the description of each part is omitted here.

The condensation sensors 646 and 656 are provided so as to function as a condensation detection mechanism that detects the presence or absence of condensation in the air heat exchangers 642 and 652. In the embodiment, the dew condensation sensors 646 and 656 are used. However, the present invention is not limited to this, and it is only necessary to function as a dew condensation detection mechanism. Therefore, a float switch may be provided instead of the dew condensation sensor.
The RA suction temperature / humidity sensors 645 and 655 are temperature / humidity sensors that detect the temperature and relative humidity of the indoor air RA sucked into the unit.

Since the heat source unit 606 has the same configuration as that of the heat source unit 306 of the second embodiment, all the reference numerals indicating the respective parts of the heat source unit 306 of the second embodiment are changed to the reference numerals of 600 series. Description is omitted.
In the sensible heat system utilization units 604 and 605, the gas side of the air heat exchangers 642 and 652 is connected to the intake gas communication pipe 609 via the connection units 614 and 615. The connection units 614 and 615 mainly include evaporation pressure control valves 673 and 683, evaporation pressure sensors 674 and 684, and connection unit controllers 672 and 682 that control operations of the respective parts constituting the connection units 614 and 615. ing. The evaporation pressure control valves 673 and 683 control the evaporation pressure of the refrigerant in the air heat exchangers 642 and 652 when the air heat exchangers 642 and 652 of the sensible heat system utilization units 604 and 605 function as the refrigerant evaporator. It is an electric expansion valve provided to function as a pressure adjustment mechanism. The evaporation pressure sensors 674 and 684 are pressure sensors provided so as to function as a pressure detection mechanism for detecting the pressure of the refrigerant in the air heat exchangers 642 and 652.

  Further, the sensible heat system utilization units 604 and 605 of the present embodiment, like the sensible heat system utilization units 504 and 604 of the third embodiment, form condensation in the air heat exchangers 642 and 652 during the dehumidifying and cooling operation. Control is performed so as to perform a so-called sensible heat cooling operation in which the cooling operation is performed so as not to occur. For this reason, drain piping is not connected to the sensible heat system utilization units 604 and 605.

  Moreover, as described above, the latent heat system utilization units 2 and 3 used in the latent heat load processing system of the air conditioning system 601 can be subjected to latent heat treatment by the adsorption operation and the regeneration operation of the adsorption heat exchangers 22, 23, 32, and 33. Therefore, as with the sensible heat system utilization units 404 and 405, the drain pipe is not connected. That is, a drainless system is realized as the entire air conditioning system 401 of the present embodiment.

Note that the operation of the air conditioning system 601 of the present embodiment is the same as the operation of the air conditioning system 601 of the third embodiment, and thus the description thereof is omitted here, but in the air conditioning system 601 of the present embodiment. Has the same characteristics as the characteristics of the air conditioning system 401 of the third embodiment.
(4) Modification 1
In the air conditioning system 601 of the fourth embodiment described above, the dew point of the indoor air is determined from the indoor air temperature and relative humidity detected by the RA suction temperature / humidity sensors 645 and 655 of the sensible heat system utilization units 604 and 605. The temperature is calculated and the minimum evaporating temperature value Te3 of the refrigerant in the air heat exchangers 642 and 652 is calculated and used for system control. As shown in FIG. 50, the sensible heat system utilization unit 604, Dew point sensors 647 and 657 may be provided at 605, and the dew point temperatures detected by the dew point sensors 647 and 657 may be used for system control.

(5) Modification 2
In the air conditioning system 601 of the fourth embodiment described above, the sensible heat system utilization units 604 and 605 and the connection units 614 and 615 constituting the sensible heat load processing system are separate units, but the book shown in FIG. As in the modification, the evaporation pressure control valves 673 and 683 and the evaporation pressure sensors 674 and 684 of the connection units 614 and 615 may be built in the sensible heat system utilization units 604 and 605. In this case, the connection unit control units 672 and 682 provided in the connection units 614 and 615 are omitted, and the sensible heat system use side control units 648 and 658 also have the functions of the connection unit control units 672 and 682. .

(6) Modification 3
In the air conditioning system 601 of the fourth embodiment described above, the latent heat system use-side refrigerant circuits 610a and 610b constituting the latent heat load processing system are built in the latent heat system use units 2 and 3 to configure the sensible heat load processing system. The sensible heat system utilization side refrigerant circuits 610c and 610d are built in the sensible heat system utilization units 604 and 605 and the connection units 614 and 615, and the latent heat system utilization units 2 and 3 and the sensible heat system utilization units 604 and 605 are connected. Although the units 614 and 615 are installed separately, like the air conditioning system 701 of this modification shown in FIG. 52, the latent heat system use side refrigerant circuits 710a and 710b and the sensible heat constituting the latent heat load processing system are provided. The sensible heat system use-side refrigerant circuits 710c and 710d constituting the load processing system are integrated with the use unit 70. , It may constitute a 703.

  Thereby, like the above-mentioned air conditioning system 601 of the fourth embodiment, the latent heat system use units 2 and 3 and the sensible heat system use side refrigerant circuits 610c and 610d provided with the latent heat system use side refrigerant circuits 610a and 610b indoors. Compared with the case where the sensible heat system utilization units 604 and 605 and the connection units 614 and 615 provided separately are installed separately, the unit size can be reduced and the labor for installing the units can be reduced. In this case, the RA suction temperature sensors 645 and 655 and the sensible heat system utilization side control unit 648 provided in the sensible heat system utilization units 604 and 605 and the connection units 614 and 615 of the air conditioning system 601 of the fourth embodiment described above. 658 and the connection unit control units 672 and 682 are omitted, and the latent heat system use side control units 728 and 738 also have the functions of the sensible heat system use side control units 648 and 658 and the connection unit control units 672 and 682. .

Further, in the air conditioning system 701 of the present modified example, similarly to the air conditioning system 601, the adsorption heat exchangers 722, 723, 732, 733, that is, the latent heat system use side refrigerant circuits 710a, 710b are dehumidified or humidified. In addition, only the operation of supplying indoors (that is, latent heat-treated) to the room can be performed.
Further, in the air conditioning system 701 of the present modification, the latent heat system use side refrigerant circuits 710a and 710b and the sensible heat system use side refrigerant circuits 710c and 710d constituting the sensible heat load processing system are integrated with the use units 702 and 703. 53, the adsorption heat exchangers 722, 723, 732, 733, that is, the latent heat system use-side refrigerant circuits 710a, 710b have been dehumidified or humidified (that is, subjected to a latent heat treatment). Since the air can be further cooled or heated (ie, sensible heat treatment) (see arrows attached to both sides of the adsorption heat exchangers 722, 723, 732, and 733 in FIG. 53), for example, adsorption heat exchange 722, 723, 732, and 733 process some sensible heat load along with the latent heat load to the indoor target air temperature. Even if the temperature changes, the air is not blown into the room as it is, but after sensible heat treatment by the air heat exchangers 742 and 752 to a temperature suitable for the indoor target air temperature. Can be driven indoors.

Note that the configuration of the refrigerant circuit 710 of the air conditioning system 701 of the present modification is the same as the configuration of the refrigerant circuit 610 of the air conditioning system 601 described above, and reference numerals indicating the respective parts of the air conditioning system 601 are 700. It changes to the code | symbol of a number stand, and abbreviate | omits description of each part.
[ Reference example ]
FIG. 54 is a schematic refrigerant circuit diagram of an air conditioning system 801 as a reference example . The air conditioning system 801 is an air conditioning system that processes a latent heat load and a sensible heat load in a building or the like by performing a vapor compression refrigeration cycle operation. The air conditioning system 801 is a so-called separate type multi-air conditioning system, and mainly includes a latent heat load processing system 901 that mainly processes indoor latent heat loads, and a sensible heat load processing system 1001 that mainly processes indoor sensible heat loads. I have.

The latent heat load processing system 901 is a so-called separate type multi-air conditioning system, and mainly includes a plurality of (in this embodiment, two) latent heat system utilization units 902 and 903, a latent heat system heat source unit 906, and latent heat. Latent heat system connection pipes 907 and 908 for connecting the system use units 902 and 903 and the latent heat system heat source unit 906 are provided.
The latent heat system use units 902 and 903 mainly constitute a part of the latent heat system refrigerant circuit 910, and are similar to the latent heat system use side refrigerant circuits 10a and 10b of the first embodiment. 910b is provided. Regarding the configuration of the latent heat system use units 902 and 903, the reference numerals of the 920s and 930s are attached instead of the reference numerals of the 20s and 30s indicating the respective parts of the latent heat system use units 2 and 3 of the first embodiment. Description of each part is omitted.

  The latent heat system heat source unit 906 mainly constitutes a part of the latent heat system refrigerant circuit 910 and includes a latent heat system heat source side refrigerant circuit 910c. The latent heat system heat source side refrigerant circuit 910c mainly includes a latent heat system compression mechanism 961 and a latent heat system accumulator 962 connected to the suction side of the latent heat system compression mechanism 961, via the latent heat system connection pipes 907 and 908. The latent heat system utilization units 902 and 903 are connected in parallel.

  The sensible heat load treatment system 1001 is a so-called separate type multi-air conditioning system, and mainly includes a plurality of (in this embodiment, two) sensible heat system utilization units 1002 and 1003 and a sensible heat system heat source unit 1006. And sensible heat system use pipes 1007 and 1008 for connecting the sensible heat system utilization units 1002 and 1003 and the sensible heat system heat source unit 1006.

  The sensible heat system utilization units 1002, 1003 mainly constitute a part of the sensible heat system refrigerant circuit 1010, and the sensible heat system utilization side is the same as the sensible heat system utilization side refrigerant circuits 10c, 10d of the first embodiment. Refrigerant circuits 1010a and 1010b are provided. About the structure of the sensible heat system utilization unit 1002,1003, the code | symbol of the 1020th series and the 1030th series is attached instead of the code | symbol of the 40th series and the 50th series which show each part of the sensible heat system utilization unit 4,5 of 1st Embodiment. Thus, description of each part is omitted.

  The sensible heat system heat source unit 1006 mainly constitutes a part of the sensible heat system refrigerant circuit 1010 and includes a sensible heat system heat source side refrigerant circuit 1010c. The sensible heat system heat source side refrigerant circuit 1010c mainly includes a sensible heat system compression mechanism 1061 and a sensible heat system accumulator 1062 connected to the suction side of the sensible heat system compression mechanism 1061. Sensible heat system utilization units 1002 and 1003 are connected in parallel via 1007 and 1008.

Thus, in the air conditioning system 801 as a reference example, unlike the air conditioning systems of the first to fourth embodiments, each of the latent heat load processing system 901 and the sensible heat load processing system 1001 has a heat source (specifically, Since the latent heat system heat source unit 906 and the sensible heat system heat source unit 1006) are provided, the number of heat sources is increased as compared with the air conditioning systems of the first to fourth embodiments. Since one heat source of the latent heat load processing system 901 including 922, 923, 932, and 933 can be consolidated, the cost increase and the maintenance point that occur when installing a plurality of air conditioners using adsorption heat exchangers The increase can be suppressed.

  For example, in the air conditioning systems of the third and fourth embodiments described above, the sensible heat system utilization unit is provided with a dew condensation sensor, but the sensible heat cooling operation of the sensible heat load treatment system can be reliably performed. Is not necessarily provided.

  If the present invention is used, when installing a plurality of air conditioners using adsorption heat exchangers or installing air conditioners using adsorption heat exchangers together with air conditioners using air heat exchangers The increase in cost and the increase in maintenance points that occur during the process can be suppressed.

1 is a schematic refrigerant circuit diagram of an air conditioning system according to a first embodiment of the present invention. It is a schematic refrigerant circuit diagram showing the operation at the time of dehumidifying operation in the full ventilation mode when only the latent heat load processing system is operated. It is a schematic refrigerant circuit diagram showing the operation at the time of dehumidifying operation in the full ventilation mode when only the latent heat load processing system is operated. It is a control flow figure at the time of operating only a latent heat load processing system. It is the graph which displayed the latent heat processing capability and the sensible heat processing capability in an adsorption heat exchanger on the horizontal axis for the switching time interval of adsorption operation and regeneration operation. It is a schematic refrigerant circuit diagram showing the operation at the time of humidification operation in the full ventilation mode when only the latent heat load processing system is operated. It is a schematic refrigerant circuit diagram showing the operation at the time of humidification operation in the full ventilation mode when only the latent heat load processing system is operated. FIG. 5 is a schematic refrigerant circuit diagram showing an operation during a dehumidifying operation in a circulation mode when only the latent heat load processing system is operated. FIG. 5 is a schematic refrigerant circuit diagram showing an operation during a dehumidifying operation in a circulation mode when only the latent heat load processing system is operated. It is a schematic refrigerant circuit diagram showing the operation at the time of humidification operation in the circulation mode when only the latent heat load processing system is operated. It is a schematic refrigerant circuit diagram showing the operation at the time of humidification operation in the circulation mode when only the latent heat load processing system is operated. FIG. 6 is a schematic refrigerant circuit diagram illustrating an operation during a dehumidifying operation in an air supply mode when only the latent heat load processing system is operated. FIG. 6 is a schematic refrigerant circuit diagram illustrating an operation during a dehumidifying operation in an air supply mode when only the latent heat load processing system is operated. It is a schematic refrigerant circuit diagram showing the operation at the time of humidification operation in the air supply mode when only the latent heat load processing system is operated. It is a schematic refrigerant circuit diagram showing the operation at the time of humidification operation in the air supply mode when only the latent heat load processing system is operated. FIG. 6 is a schematic refrigerant circuit diagram illustrating an operation during a dehumidifying operation in an exhaust mode when only the latent heat load processing system is operated. FIG. 6 is a schematic refrigerant circuit diagram illustrating an operation during a dehumidifying operation in an exhaust mode when only the latent heat load processing system is operated. FIG. 3 is a schematic refrigerant circuit diagram showing an operation during a humidifying operation in an exhaust mode when only the latent heat load processing system is operated. FIG. 3 is a schematic refrigerant circuit diagram showing an operation during a humidifying operation in an exhaust mode when only the latent heat load processing system is operated. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of the dehumidification air_conditionaing | cooling operation of the whole ventilation mode in the air conditioning system of 1st Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of the dehumidification air_conditionaing | cooling operation of the whole ventilation mode in the air conditioning system of 1st Embodiment. It is a control flow figure at the time of normal operation in the air harmony system of a 1st embodiment. It is a control flow figure at the time of normal operation in the air harmony system of a 1st embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of humidification heating operation of the whole ventilation mode in the air conditioning system of 1st Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of humidification heating operation of the whole ventilation mode in the air conditioning system of 1st Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of simultaneous operation | movement of the dehumidification cooling of all ventilation mode and humidification heating in the air conditioning system of 1st Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of simultaneous operation | movement of the dehumidification cooling of all ventilation mode and humidification heating in the air conditioning system of 1st Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of system starting in the air conditioning system of 1st Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of system starting in the air conditioning system of 1st Embodiment. It is a schematic refrigerant circuit diagram of the air conditioning system concerning the modification 1 of 1st Embodiment. It is a schematic refrigerant circuit diagram of the air conditioning system concerning the modification 2 of 1st Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of the dehumidification air_conditionaing | cooling operation of all ventilation modes in the air conditioning system concerning the modification 2 of 1st Embodiment. It is a schematic refrigerant circuit figure of the air conditioning system of 2nd Embodiment concerning this invention. It is a schematic refrigerant circuit diagram of the air conditioning system concerning the modification of 2nd Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of the dehumidification air_conditionaing | cooling operation of all ventilation modes in the air conditioning system concerning the modification of 2nd Embodiment. It is a schematic refrigerant circuit figure of the air conditioning system of 3rd Embodiment concerning this invention. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of the drainless dehumidification cooling operation of the whole ventilation mode in the air conditioning system of 3rd Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of the drainless dehumidification cooling operation of the whole ventilation mode in the air conditioning system of 3rd Embodiment. It is a control flow figure at the time of the drainless dehumidification cooling operation in the air conditioning system of 3rd Embodiment. It is a control flow figure at the time of the drainless dehumidification cooling operation in the air conditioning system of 3rd Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of drain-less system starting in the air conditioning system of 3rd Embodiment. It is an air line figure which shows the state of indoor air at the time of drain-less system starting of the air conditioning system of 3rd Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of drain-less system starting in the air conditioning system of 3rd Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of drain-less system starting in the air conditioning system of 3rd Embodiment. It is a schematic refrigerant circuit diagram of the air conditioning system concerning the modification 1 of 3rd Embodiment. It is a schematic refrigerant circuit diagram of the air conditioning system concerning the modification 2 of 3rd Embodiment. It is a schematic refrigerant circuit figure of the air conditioning system concerning the modification 3 of 3rd Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of the dehumidification air_conditionaing | cooling operation of all ventilation modes in the air conditioning system concerning the modification 3 of 3rd Embodiment. It is a schematic refrigerant circuit figure of the air conditioning system of 4th Embodiment concerning this invention. It is a schematic refrigerant circuit diagram of the air conditioning system concerning the modification 1 of 4th Embodiment. It is a schematic refrigerant circuit diagram of the air conditioning system concerning the modification 2 of 4th Embodiment. It is a schematic refrigerant circuit figure of the air conditioning system concerning the modification 3 of 4th Embodiment. It is a schematic refrigerant circuit diagram which shows the operation | movement at the time of the dehumidification air_conditionaing | cooling operation of all ventilation modes in the air conditioning system concerning the modification 3 of 4th Embodiment. It is a schematic refrigerant circuit diagram of the air conditioning system as a reference example .

Explanation of symbols

1, 101, 201, 301, 401, 501, 601, 701, 801 Air conditioning system 22, 23, 32, 33, 122, 123, 132, 133, 322, 323, 332, 333, 522, 523, 532, 533, 722, 723, 732, 733, 922, 923, 932, 933 Adsorption heat exchanger 10a, 10b, 110a, 110b, 210a, 210b, 310a, 310b, 410a, 410b, 510a, 510b, 610a, 610b, 710a , 710b, 910a, 910b Latent heat system use side refrigerant circuit (first use side refrigerant circuit)
42, 52, 142, 152, 242, 252, 342, 352, 442, 452, 542, 552, 642, 652, 742, 752, 1022, 1032 Air heat exchanger 10c, 10d, 110c, 110d, 210c, 210d 310c, 310d, 410c, 410d, 510c, 510d, 610c, 610d, 710c, 710d, 1010a, 1010b Sensible heat system utilization side refrigerant circuit (second utilization side refrigerant circuit)

Claims (13)

An air conditioning system that processes indoor latent heat load and sensible heat load by performing a vapor compression refrigeration cycle operation,
Adsorption heat exchanger (22, 23, 32, 33) (122, 123, 132, 133) (322, 323, 332, 333) (522, 523, 532, 533) (722) , 723, 732, 733) (922, 923, 932, 933), and an adsorption operation in which the adsorption heat exchanger functions as a refrigerant evaporator to adsorb moisture in the air to the adsorbent; A plurality of first usage sides in which the adsorption heat exchanger can function as a refrigerant condenser to alternately perform a regeneration operation to desorb moisture from the adsorbent, and are connected in parallel to each other. Refrigerant circuits (10a, 10b) (110a, 110b) (210a, 210b) (310a, 310b) (410a, 410b) (510a, 510b) (610a, 610b) (710a, 7 And 0b),
Air heat exchangers (42, 52) (142, 152) (242, 252) (342, 352) (442, 452) (542, 552) (642, 652) (742, 752) (1022, 1032) A plurality of second use-side refrigerant circuits (10c, 10d) (110c, 110d) (210c, 210d) that are capable of performing heat exchange between the refrigerant and air and that are connected to each other in parallel. (310c, 310d) (410c, 410d) (510c, 510d) (610c, 610d) (710c, 710d) ,
Compression mechanism (61) (161) (261) (361) (461) (561) (661) (761) and heat source side heat exchanger (63) (163) (263) (363) (463) (563) (663) and (763), and only the compression mechanism of the compression mechanism and the heat source side heat exchanger is used in common for the first use side refrigerant circuit and the second use side refrigerant circuit. Heat source side refrigerant circuit (10e) (110e) (210e) (310e) (410e) (510e) (610e) (710e)
The first usage side refrigerant circuit includes discharge gas communication pipes (8) (108) (208) (308) (408) (508) (608) (708) connected to the discharge side of the compression mechanism, Inlet gas communication pipes (9) (109) (209) (309) (409) (509) (609) (709) connected to the suction side of the compression mechanism,
It is possible to supply indoors the air that has passed through the adsorption heat exchanger,
The air that has passed through the air heat exchanger can be supplied indoors.
Air conditioning system (1) (101) (201) (301) (401) (501) (601) (701) . An air conditioning system that processes indoor latent heat load and sensible heat load by performing a vapor compression refrigeration cycle operation,
Adsorption heat exchanger (22, 23, 32, 33) (122, 123, 132, 133) (322, 323, 332, 333) (522, 523, 532, 533) (722) , 723, 732, 733), the adsorption heat exchanger functioning as a refrigerant evaporator to adsorb moisture in the air to the adsorbent, and the heat of adsorption as a refrigerant condenser First use side refrigerant circuits (10a, 10b) (110a, 110b) (210a, 210b) (310a, capable of alternately performing a regeneration operation for desorbing moisture from the adsorbent by operating an exchanger 310b) (410a, 410b) ( 510a, 510b) (610a, 610b) and (710a, 710b),
Air heat exchangers (42, 52) (142, 152) (242, 252) (342, 352) (442, 452) (542, 552) (642, 652) (742, 752) A plurality of second usage-side refrigerant circuits (10c, 10d) (110c, 110d) (210c, 210d) (310c, 310d) that can perform heat exchange between the refrigerant and air and are connected in parallel to each other. (410c, 410d) (510c, 510d) (610c, 610d) (710c, 710d),
Compression mechanism (61) (161) (261) (361) (461) (561) (661) (761) and heat source side heat exchanger (63) (163) (263) (363) (463) (563) (663) and (763), and only the compression mechanism of the compression mechanism and the heat source side heat exchanger is used in common for the first use side refrigerant circuit and the second use side refrigerant circuit. Heat source side refrigerant circuit (10e) (110e) (210e) (310e) (410e) (510e) (610e) (710e)
The first usage side refrigerant circuit includes discharge gas communication pipes (8) (108) (208) (308) (408) (508) (608) (708) connected to the discharge side of the compression mechanism, Inlet gas communication pipes (9) (109) (209) (309) (409) (509) (609) (709) connected to the suction side of the compression mechanism,
It is possible to supply indoors the air that has passed through the adsorption heat exchanger,
The air that has passed through the air heat exchanger can be supplied indoors.
Air conditioning system (1) (101) (201) (301) (401) (501) (601) (701). The second usage side refrigerant circuit (10c, 10d) (110c, 110d) (410c, 410d) (510c, 510d) is a liquid side of the heat source side heat exchanger (63) (163) (463) (563). The liquid communication pipes (7), (107), (407), and (507) are connected to each other through the switching mechanisms (71 and 81) (171 and 181) (471 and 481) (571 and 581). the discharge gas connection pipe (8) (108) (408) (508) and the suction gas connection pipe (9) (109) (409) are connected switched to (509), in claim 1 or 2 The described air conditioning system (1) (101) (401) (501). The second usage side refrigerant circuit (210c, 210d) (310c, 310d) (610c, 610d) (710c, 710d) is a liquid side of the heat source side heat exchanger (263) (363) (663) (763). is connected to the liquid connecting pipe to be connected (207) (307) (607) (707) and the suction gas connection pipe (209) (309) (609) (709), the claim 1 or 2 Air conditioning system (201) (301) (601) (701). The first usage side refrigerant circuit (110a, 110b) (310a, 310b) (510a, 510b) (710a, 710b) and the second usage side refrigerant circuit (110c, 110d) (310c, 310d) (510c, 510d) The air according to any one of claims 1 to 4 , wherein (710c, 710d) constitutes an integrated use unit (102, 103) (302, 303) (502, 503) (702, 703). Harmonization systems (101) (301) (501) (701). The utilization units (102, 103) (302, 303) (502, 503) (702, 703) are connected to the adsorption heat exchangers (122, 123, 132, 133) (322, 323, 332, 333) (522). 523, 532, 533) (722, 723, 732, 733), the air conditioning system (101) (301) (301) according to claim 5 , wherein the air dehumidified or humidified can be supplied indoors. 501) (701). The utilization units (102, 103) (302, 303) (502, 503) (702, 703) are connected to the adsorption heat exchangers (122, 123, 132, 133) (322, 323, 332, 333) (522). 523, 532, 533) (722, 723, 732, 733) in the air heat exchanger (142, 152) (342, 352) (542, 552) (742, 752). The air conditioning system (101) (301) (501) (701) according to claim 5 , which is capable of heat exchange with a refrigerant. The air heat when the air heat exchanger (442, 452) (542, 552) (642, 652) (742, 752) is connected to the gas side and functions the air heat exchanger as a refrigerant evaporator. The air according to any one of claims 1 to 7 , comprising a pressure adjusting mechanism (473, 483) (573, 583) (673, 683) (773, 783) for controlling the evaporation pressure of the refrigerant in the exchanger. Harmonization system (401) (501) (601) (701). Based on the dew point temperature of the indoor air, the air heat exchangers (442, 452) (542, 552) are generated by the pressure adjusting mechanisms (473, 483) (573, 583) (673, 683) (773, 783). ) (642, 652) The air conditioning system (401) (501) (601) (701) according to claim 8 , wherein the evaporation pressure of the refrigerant when the (642, 652) (742, 752) functions as an evaporator is controlled. Pressure detecting mechanisms (474, 484) (574, 584) (674, 684) for detecting the refrigerant pressure in the air heat exchangers (442, 452) (542, 552) (642, 652) (742, 752) ( 774, 784),
The target evaporating pressure value (P3) is calculated from the dew point temperature of the indoor air, and is detected by the pressure detecting mechanism by the pressure adjusting mechanism (473, 483) (573, 583) (673, 683) (773, 783). Controlling the evaporation pressure of the refrigerant to be equal to or higher than the target evaporation pressure value,
The air conditioning system (401) (501) (601) (701) according to claim 9 . Condensation detection mechanisms (446, 456) (546, 556) (646, 656) for detecting the presence or absence of condensation in the air heat exchangers (442, 452) (542, 552) (642, 652) (742, 752) (746, 756)
Changing the target evaporation pressure value (P3) when dew condensation is detected by the dew condensation detection mechanism;
The air conditioning system (401) (501) (601) (701) according to claim 10 . Condensation detection mechanisms (446, 456) (546, 556) (646, 656) for detecting the presence or absence of condensation in the air heat exchangers (442, 452) (542, 552) (642, 652) (742, 752) (746, 756)
When condensation is detected by the condensation detection mechanism, the compression mechanism (461) (561) (661) (761) is stopped.
The air conditioning system (401) (501) (601) (701) according to claim 10 . Condensation detection mechanisms (446, 456) (546, 556) (646, 656) for detecting the presence or absence of condensation in the air heat exchangers (442, 452) (542, 552) (642, 652) (742, 752) (746, 756)
The second use side refrigerant circuit (410c, 410d) (510c, 510d) (610c, 610d) (710c, 710d) is a use side expansion valve (441, 451) connected to the liquid side of the air heat exchanger. (541, 551) (641, 651) (741, 751),
Closing the use side expansion valve when condensation is detected in the condensation detection mechanism;
The air conditioning system (401) (501) (601) (701) according to claim 10 .

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