JP2020016419A - Air conditioning system - Google Patents

Abstract

To provide an air conditioning system capable of suppressing time and labor when it is manufactured, and capable of suppressing power consumption.SOLUTION: In an air conditioning system, when a state in which a temperature difference as a value obtained by subtracting a preset temperature from a temperature of an air-conditioned space is a first temperature difference is defined as a first temperature difference state, and a state in which the temperature difference is a second temperature difference smaller than the first temperature difference is defined as a second temperature difference state, a temperature of a coolant flowing in a first heat exchanger of an indoor unit in the second temperature difference state becomes higher than that in the first temperature difference state, and when a state in which a humidity difference as a value obtained by subtracting preset humidity from absolute humidity of the air-conditioned space is a first humidity difference is defined as a first humidity difference state, and a state in which the humidity difference is smaller than the first humidity difference is defined as a second humidity difference state, a temperature of supplied air supplied from an outside air supply unit in the second humidity difference state becomes higher than that in the first humidity difference state.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an air conditioning system including an outside air supply device that supplies outside air to a space to be air-conditioned such as in a room.

  The air conditioner includes a direct expansion type air conditioner and a space expansion type air conditioner. The direct expansion type air conditioner and the inter-expansion type air conditioner differ in the air conditioning system of the air supplied to the air-conditioned space. In a direct expansion type air conditioner, a refrigerant is supplied to a heat exchanger that heats or cools air supplied to a space to be air-conditioned. In the direct expansion type air conditioner, the air supplied to the air-conditioned space is cooled or heated by the refrigerant supplied to the heat exchanger. On the other hand, in the inter-expansion type air conditioner, water is heated or cooled by the refrigerant in the heat source device. Then, in the inter-expansion type air conditioner, the water is supplied to a heat exchanger that heats or cools the air supplied to the air-conditioned space. In the inter-expansion air conditioner, the air supplied to the air-conditioned space is cooled or heated by the water supplied to the heat exchanger.

  Currently, direct expansion type air conditioners such as multi air conditioners for buildings are widely used in small and medium-sized buildings. However, from the viewpoint of suppressing the discharge of chlorofluorocarbon, an inter-expansion type air conditioner having a small total amount of refrigerant has been reviewed. Therefore, it is expected that an air conditioning system using both the direct expansion type air conditioner and the inter-expansion type air conditioner will be widely used in the future.

  Here, an air conditioner that heats or cools the air in the air-conditioned space sucked into the indoor unit and returns the heated or cooled air to the air-conditioned space is called an internal conditioner. An air conditioner that heats or cools the outside air sucked into the outside air supply device for ventilation and returns the heated or cooled outside air to the air-conditioned space is called an outside air conditioner. More and more buildings use a direct expansion type air conditioner for the internal control and a space expansion type air conditioner for the external control.

  2. Description of the Related Art Conventionally, a direct expansion type air conditioner, which is an internal control device, and an intermediate expansion type air conditioner, which is an external control device, are controlled independently of each other. For this reason, it can be said that there is room for reduction in the power consumption of the entire air conditioning system including the internal control device and the external control device.

  For this reason, a conventional air conditioning system equipped with a direct expansion type air conditioner, which is an internal control device, and an interexpansion type air conditioner, which is an external control device, also proposes an air conditioning system that reduces power consumption. (See Patent Document 1). Specifically, the air conditioning system described in Patent Literature 1 generates a plurality of optimal load distribution functions associated with each comfort index range. Further, the air conditioning system described in Patent Literature 1 selects any one of a plurality of optimum load distribution functions based on a comfort index set by a user. The air conditioning system described in Patent Literature 1 is based on the selected optimal load distribution function, so that the power consumption of the air conditioning system and the air conditioning load of the air conditioning system are reduced so that the power consumption of the entire air conditioning system is reduced. Determine the air conditioning load.

Japanese Patent No. 5951526

  In the air conditioning system described in Patent Literature 1, it is necessary to model each of the internal control device and the external control device, and to create an optimal load distribution function by a preliminary simulation. For this reason, the air conditioning system described in Patent Literature 1 has a problem that it takes time and effort to manufacture the air conditioning system.

  The present invention has been made to solve the above-described problems, and has as its object to obtain an air-conditioning system capable of suppressing troublesome manufacturing and reducing power consumption.

  An air conditioning system according to the present invention has a first heat exchanger and a first housing that houses the first heat exchanger, and is sucked into the first housing by a refrigerant flowing through the first heat exchanger. An indoor unit that cools air in the space to be air-conditioned, a second heat exchanger, and a second housing that houses the second heat exchanger, and the second housing is formed by water flowing through the second heat exchanger. An outside air supply device that cools outside air sucked into a body and supplies the cooled outside air to the air-conditioned space as supply air, a first temperature sensor that detects a temperature of the air-conditioned space, and the air-conditioned space A first humidity sensor that detects an absolute humidity of the air conditioner, and a control device that stores a set temperature and a set humidity of the air-conditioned space. A temperature difference that is a value obtained by subtracting the set temperature from the temperature of the air-conditioned space. Is the first temperature difference. State, the state in which the temperature difference is a second temperature difference smaller than the first temperature difference is a second temperature difference state, the first heat exchanger is in the second temperature difference state. The temperature of the flowing refrigerant is higher than the temperature of the refrigerant flowing through the first heat exchanger in the first temperature difference state, and is a value obtained by subtracting the set humidity from the absolute humidity of the air-conditioned space. When the state in which the humidity difference is the first humidity difference is a first humidity difference state, and the state in which the humidity difference is the second humidity difference smaller than the first humidity difference is the second humidity difference state The temperature of the supply air supplied from the outside air supply device in the second humidity difference state is higher than the temperature of the supply air supplied from the outside air supply device in the first humidity difference state. Configuration.

  The internal controller mainly handles sensible heat loads, and the external controller mainly handles latent heat loads. By changing the temperature of the refrigerant flowing through the first heat exchanger of the indoor unit of the internal control unit and the temperature of the air supplied from the outside air supply unit of the external control unit as in the present invention, the air conditioning load of the internal control unit is changed. Can be set to a load corresponding to the sensible heat load, and the air conditioning load of the external controller can be set to a load corresponding to the latent heat load. For this reason, the air conditioning system according to the present invention can reduce the power consumption of the entire air conditioning system. Further, the air conditioning system according to the present invention does not require a complicated modeling operation and a simulation operation in advance. For this reason, the air-conditioning system according to the present invention can also suppress troublesome manufacturing.

1 is a diagram illustrating a schematic configuration of an air-conditioning system according to Embodiment 1 of the present invention. FIG. 3 is a diagram illustrating a refrigerant circuit of the internal conditioner of the air-conditioning system according to Embodiment 1 of the present invention. FIG. 3 is a diagram illustrating a refrigerant circuit and a water circuit of the external conditioner of the air-conditioning system according to Embodiment 1 of the present invention. FIG. 2 is a diagram illustrating a schematic configuration of an outside air supply device of the outside air conditioner in the air-conditioning system according to Embodiment 1 of the present invention. FIG. 5 is a diagram for explaining a method of determining a target evaporation temperature of the refrigerant flowing through the first heat exchanger in the air-conditioning system according to Embodiment 1 of the present invention. FIG. 4 is a diagram for explaining a method of determining a target supply air temperature of supply air supplied from the outside air supply device into the room in the air-conditioning system according to Embodiment 1 of the present invention. FIG. 4 is an air line diagram for explaining a method for determining a target water temperature of water flowing through the second heat exchanger in the air-conditioning system according to Embodiment 1 of the present invention. FIG. 3 is an air line diagram for explaining a method of calculating a target water temperature of water flowing through a second heat exchanger in the air-conditioning system according to Embodiment 1 of the present invention. FIG. 4 is a diagram for explaining a control flow when the air-conditioning system according to Embodiment 1 of the present invention performs a cooling and dehumidifying operation. It is a figure which shows the schematic structure of the air conditioning system which concerns on Embodiment 2 of this invention. It is a figure showing a schematic structure of an outside air supply machine of an outside air conditioner in an air conditioning system concerning Embodiment 2 of the present invention. FIG. 13 is an air line diagram for explaining a method of determining an upper limit value of a target supply air temperature of supply air supplied from an outside air supply device into a room in the air conditioning system according to Embodiment 2 of the present invention.

  Hereinafter, in each embodiment, an example of an air conditioning system according to the present invention will be described. The specific configuration of the air-conditioning system according to the present invention is not limited to the configuration described in each of the following embodiments, and can be changed without departing from the spirit of the invention.

Embodiment 1 FIG.
FIG. 1 is a diagram showing a schematic configuration of the air-conditioning system according to Embodiment 1 of the present invention. FIG. 2 is a diagram illustrating a refrigerant circuit of the internal conditioner of the air-conditioning system according to Embodiment 1 of the present invention. FIG. 3 is a diagram illustrating a refrigerant circuit and a water circuit of the external conditioner of the air-conditioning system according to Embodiment 1 of the present invention. FIG. 4 is a diagram illustrating a schematic configuration of an outside air supply device of the outside air conditioner in the air-conditioning system according to Embodiment 1 of the present invention.

  As shown in FIG. 1, the air-conditioning system 100 according to Embodiment 1 includes an internal adjuster 1 and an external adjuster 2.

  The indoor unit 1 includes an outdoor unit 10 and an indoor unit 11. The outdoor unit 10 is arranged outdoors. The indoor unit 11 is provided in a room 101 whose inside is a space to be air-conditioned. The indoor unit 11 sucks and cools the air in the room 101 and blows out the cooled air into the room 101. The outdoor unit 10 and the indoor unit 11 are connected by a refrigerant pipe 18. Note that the numbers of the outdoor units 10 and the indoor units 11 shown in FIG. 1 are examples. For example, in FIG. 1, one indoor unit 11 is provided in one room 101, but one indoor unit 11 may be provided in one room 101. Further, for example, a plurality of rooms 101 may be cooled by one indoor unit 11. Further, in FIG. 1, the inner adjuster 1 includes a plurality of outdoor units 10, but the inner adjuster 1 may include only one outdoor unit 10. That is, all the indoor units 11 may be connected to one outdoor unit 10.

  The external conditioner 2 includes a chiller 30 which is an example of a heat source device, and an external air supply device 31 which is an air handling unit, for example. The chiller 30 is arranged outdoors. The outside air supply device 31 takes in outside air, cools the outside air, and supplies the cooled outside air into the room 101. The chiller 30 and the outside air supply device 31 are connected by a water pipe 46. Note that the numbers of the chillers 30 and the outside air supply devices 31 shown in FIG. 1 are examples. For example, in the first embodiment, the outside air is supplied from one outside air supply device 31 to a plurality of rooms 101 via a duct or the like. However, the present invention is not limited thereto, and the outside air conditioner 2 may include a plurality of outside air supply devices 31 such as providing the outside air supply device 31 for each room 101. Further, for example, the external conditioner 2 may include a plurality of chillers 30 such as connecting one chiller 30 to each of the plurality of outside air supply devices 31.

  As shown in FIG. 2, the internal conditioner 1 includes a refrigerant circuit 12. Each component of the refrigerant circuit 12 is housed in the outdoor unit 10 or the indoor unit 11. Specifically, the refrigerant circuit 12 includes, as constituent elements, a compressor 13, an outdoor heat exchanger 14, an expansion valve 15, and a first heat exchanger 16 that is an indoor heat exchanger. And these components are connected by the refrigerant piping, and the refrigerant circuit 12 is comprised. That is, the refrigerant pipe connecting the components of the refrigerant circuit 12 housed in the outdoor unit 10 and the components of the refrigerant circuit 12 housed in the indoor unit 11 is the refrigerant pipe 18 shown in FIG.

  The compressor 13 compresses a refrigerant. The outdoor heat exchanger 14 is a heat exchanger that functions as a condenser. The outdoor heat exchanger 14 is connected to a discharge port of the compressor 13. Further, the outdoor heat exchanger 14 is also connected to a first heat exchanger 16 via an expansion valve 15. The compressor 13 and the outdoor heat exchanger 14 are housed in the outdoor unit 10. The outdoor unit 10 also houses an outdoor unit fan 19. The outdoor unit fan 19 supplies the outdoor heat exchanger 14 with outside air, which is a heat exchange target of the refrigerant flowing through the outdoor heat exchanger 14.

  The expansion valve 15 expands the refrigerant to reduce the pressure. The first heat exchanger 16 is a heat exchanger that functions as an evaporator. The first heat exchanger 16 is connected to the outdoor heat exchanger 14 via the expansion valve 15 as described above. Further, the first heat exchanger 16 is connected to a suction port of the compressor 13. The expansion valve 15 and the first heat exchanger 16 are housed in the first housing 11a of the indoor unit 11. The first housing 11a of the indoor unit 11 also houses an indoor unit fan 20. That is, when the indoor unit fan 20 rotates in the first housing 11a, the air in the room 101 is sucked into the first housing 11a. Then, the air sucked into the first housing 11a is cooled by the refrigerant flowing through the first heat exchanger 16, and is blown into the room 101. The expansion valve 15 may be housed in the outdoor unit 10.

  Here, in the first embodiment, one refrigerant circuit 12 includes two indoor units 11. Therefore, the refrigerant circuit 12 is provided with two sets of the expansion valve 15 and the first heat exchanger 16. Each set of the expansion valve 15 and the first heat exchanger 16 is connected in parallel between the outdoor heat exchanger 14 and the suction port of the compressor 13.

  Further, as shown in FIG. 2, the refrigerant circuit 12 according to Embodiment 1 enables the indoor unit 11 to perform both the cooling operation and the heating operation, so that the four-way valve provided on the discharge side of the compressor 13 is provided. 17 is provided. The four-way valve 17 switches the connection destination of the discharge port of the compressor 13. Specifically, when the flow path of the four-way valve 17 is in a state where the discharge port of the compressor 13 is connected to the outdoor heat exchanger 14, the suction port of the compressor 13 is connected to the first heat exchanger 16. You. In this case, the outdoor heat exchanger 14 functions as a condenser, and the first heat exchanger 16 functions as an evaporator. Further, when the flow path of the four-way valve 17 is in a state where the discharge port of the compressor 13 is connected to the first heat exchanger 16, the suction port of the compressor 13 is connected to the outdoor heat exchanger 14. . In this case, the outdoor heat exchanger 14 functions as an evaporator, and the first heat exchanger 16 functions as a condenser. The four-way valve 17 is housed in the outdoor unit 10. When it is not necessary for the first heat exchanger 16 to function as a condenser, it is not necessary to provide the four-way valve 17.

  As shown in FIG. 3, the external conditioner 2 includes a refrigerant circuit 32 and a water circuit 40. Each component of the refrigerant circuit 32 is housed in the chiller 30. The components of the water circuit 40 are housed in the chiller 30 or the outside air supply device 31.

  The refrigerant circuit 32 includes, as constituent elements, a compressor 33, a refrigerant-air heat exchanger 34, an expansion valve 35, and a water-refrigerant heat exchanger 36. That is, the refrigerant channels of the compressor 33, the refrigerant-air heat exchanger 34, the expansion valve 35, and the water-refrigerant heat exchanger 36 are connected by the refrigerant pipe, and the refrigerant circuit 32 is configured. The compressor 33, the refrigerant-air heat exchanger 34, the expansion valve 35, and the water-refrigerant heat exchanger 36 are housed in the chiller 30, as described above. The chiller 30 also houses a chiller fan 38.

  The compressor 33 compresses the refrigerant. The refrigerant-air heat exchanger 34 is a heat exchanger that functions as a condenser. Specifically, the refrigerant flowing through the refrigerant-air heat exchanger 34 is cooled and condensed by the outside air supplied from the chiller fan 38. The refrigerant-air heat exchanger 34 is connected to a discharge port of the compressor 33. Further, the refrigerant-air heat exchanger 34 is also connected to a refrigerant flow path of the water-refrigerant heat exchanger 36 via an expansion valve 35. The expansion valve 35 expands the refrigerant to reduce the pressure.

  The water-refrigerant heat exchanger 36 is a heat exchanger that functions as an evaporator. Specifically, the refrigerant flowing in the refrigerant flow path of the water-refrigerant heat exchanger 36 is heated and evaporated when cooling the refrigerant flowing in the water flow path of the water-refrigerant heat exchanger 36. As described above, the refrigerant flow path of the water-refrigerant heat exchanger 36 is connected to the refrigerant-air heat exchanger 34 via the expansion valve 35. Further, the refrigerant flow path of the water-refrigerant heat exchanger 36 is connected to the suction port of the compressor 33. Here, as described later, water circulating in the water circuit 40 flows in the water flow path of the water-refrigerant heat exchanger 36. Therefore, when the water-refrigerant heat exchanger 36 functions as an evaporator, the outside air supplied into the room 101 is cooled by the water cooled by the water-refrigerant heat exchanger 36.

  The refrigerant circuit 32 according to the first embodiment includes a four-way valve 37 provided on the discharge side of the compressor 33. The four-way valve 37 switches the connection destination of the discharge port of the compressor 33. Specifically, when the flow path of the four-way valve 37 is in a state where the discharge port of the compressor 33 is connected to the refrigerant-air heat exchanger 34, the suction port of the compressor 33 is connected to the water-refrigerant heat exchanger 36. Connected to the refrigerant flow path. In this case, the refrigerant-air heat exchanger 34 functions as a condenser, and the water-refrigerant heat exchanger 36 functions as an evaporator. When the flow path of the four-way valve 37 is in a state where the discharge port of the compressor 33 is connected to the refrigerant flow path of the water-refrigerant heat exchanger 36, the suction port of the compressor 33 is connected to the refrigerant-air heat Connected to exchanger 34. In this case, the refrigerant-air heat exchanger 34 functions as an evaporator, and the water-refrigerant heat exchanger 36 functions as a condenser. In this case, the outside air supplied into the room 101 is heated by the water heated by the water-refrigerant heat exchanger 36. When it is not necessary to heat the outside air supplied into the room 101, it is not necessary to provide the four-way valve 37.

  The water circuit 40 includes a pump 41, a water-refrigerant heat exchanger 36, and a second heat exchanger 42 as constituent elements. The pump 41, the water flow path of the water-refrigerant heat exchanger 36, and the second heat exchanger 42 are connected by a water pipe to form a water circuit 40. As described above, the components of the water circuit 40 are housed in the chiller 30 or the outside air supply device 31. Therefore, the water pipe connecting the components of the water circuit 40 housed in the chiller 30 and the components of the water circuit 40 housed in the outside air supply device 31 is the water pipe 46 shown in FIG.

  The pump 41 discharges the sucked water and circulates the water in the water circuit 40. As described above, the water-refrigerant heat exchanger 36 exchanges heat between the refrigerant flowing through the refrigerant flow path and the water flowing through the water flow path. The second heat exchanger 42 cools or heats the outside air by the water flowing through the second heat exchanger 42.

  Further, the water circuit 40 according to the first embodiment includes a flow rate adjusting mechanism 43 that adjusts the flow rate of water flowing through the second heat exchanger 42. The flow control mechanism 43 includes a bypass pipe 44 and a three-way valve 45. The bypass pipe 44 is provided to bypass the second heat exchanger 42. The three-way valve 45 is provided at a connection point between the water pipe connecting the water-refrigerant heat exchanger 36 and the second heat exchanger 42 and the bypass pipe 44. That is, the first of the three openings of the three-way valve 45 is connected to the water-refrigerant heat exchanger 36. The second of the three openings of the three-way valve 45 is connected to the second heat exchanger 42. The third of the three openings of the three-way valve 45 is connected to the bypass pipe 44. As the flow rate of water flowing through the bypass pipe 44 by the three-way valve 45 increases, the flow rate of water flowing through the second heat exchanger 42 decreases.

  Among the components of the water circuit 40, the pump 41, the water-refrigerant heat exchanger 36, and the flow rate adjusting mechanism 43 are housed in the chiller 30. Among the components of the water circuit 40, the second heat exchanger 42 is housed in the second housing 50 of the outside air supply device 31. The flow rate adjusting mechanism 43 may be housed in the second housing 50 of the outside air supply device 31.

  As shown in FIG. 4, a first housing 51 and a first outlet 52 are formed in the second housing 50 of the outside air supply device 31. The first suction port 51 is a suction port for taking outside air into the second housing 50. The first suction port 51 communicates with the outside via, for example, a duct or the like. The first outlet 52 is an outlet for blowing outside air taken into the second housing 50 to the outside of the second housing 50. The first outlet 52 communicates with the inside of each room 101 via, for example, a duct or the like. In addition, the second housing 50 houses an air supply fan 55. Here, as described above, the second housing 50 houses the second heat exchanger 42 of the water circuit 40. Therefore, when the air supply fan 55 rotates, the outside air drawn into the second housing 50 from the first suction port 51 is cooled or heated by the water flowing through the second heat exchanger 42. Then, the cooled or heated outside air is supplied as supply air into each room 101 through the first outlet 52 and the duct.

  Note that the second housing 50 according to the first embodiment also has a second suction port 53 and a second outlet 54 formed therein. The second suction port 53 is a suction port for taking the air in the room 101 into the second housing 50. The second suction port 53 communicates with the inside of each room 101 via, for example, a duct or the like. The second outlet 54 is an outlet for blowing out the air in the room 101 taken into the second housing 50 to the outside of the second housing 50. The second outlet 54 communicates with the outside via, for example, a duct or the like. The second housing 50 houses an exhaust fan 56. When the exhaust fan 56 rotates, the air in the room 101 is sucked into the second housing 50 from the second suction port 53, and the air in the room 101 sucked into the second housing 50 is discharged to the second outlet. It is blown out from 54 outdoors. Further, the second housing 50 according to the first embodiment has a total heat exchange in which the outside air sucked from the first suction port 51 and the air in the room 101 sucked from the second suction port 53 exchange heat. A vessel 57 is also provided.

  In addition, as shown in FIG. 1, the air conditioning system 100 includes a plurality of sensors and a control device 60 that controls each component of the air conditioning system 100 based on detection values of these sensors.

  Specifically, the air conditioning system 100 includes a first temperature sensor 71, a second temperature sensor 72, a temperature sensor 73, a first humidity sensor 81, and a second humidity sensor 82.

  The first temperature sensor 71 is a sensor that detects the temperature in the room 101, that is, the temperature in the space to be air-conditioned. The first temperature sensor 71 may be at least one in the room 101. The installation position of the first temperature sensor 71 is arbitrary as long as the temperature in the room 101 can be detected. In the first embodiment, the first temperature sensor 71 is provided in each indoor unit 11. The second temperature sensor 72 is a sensor that detects the temperature of the outside air. The installation position of the second temperature sensor 72 is arbitrary as long as the temperature of the outside air can be detected. In the first embodiment, the second temperature sensor 72 is installed near the first suction port 51 in the second housing 50 of the outside air supply device 31. The temperature sensor 73 is a sensor that detects the temperature of supply air supplied from the outside air supply device 31 into the room 101. The installation position of the temperature sensor 73 is arbitrary as long as the temperature of the supply air supplied from the outside air supply device 31 into the room 101 can be detected. In the first embodiment, a temperature sensor 73 is installed near the first outlet 52 in the second housing 50 of the outside air supply device 31. In the first embodiment, the temperature indicates the dry bulb temperature unless otherwise specified.

  The first humidity sensor 81 is a sensor that detects the absolute humidity in the room 101, that is, the temperature of the absolute humidity in the space to be air-conditioned. The first humidity sensor 81 may be at least one in the room 101. The installation position of the first humidity sensor 81 is arbitrary as long as the absolute humidity in the room 101 can be detected. In the first embodiment, the first humidity sensor 81 is installed in each room 101 in the vicinity of a duct that connects the inside of each room 101 and the outside air supply device 31. The second humidity sensor 82 is a sensor that detects the absolute humidity of the outside air. The installation position of the second humidity sensor 82 is arbitrary as long as the absolute humidity of the outside air can be detected. In the first embodiment, the second humidity sensor 82 is installed near the first suction port 51 in the second housing 50 of the outside air supply device 31. In the first embodiment, the humidity refers to absolute humidity unless otherwise specified.

  The control device 60 is configured by dedicated hardware or a CPU (Central Processing Unit) that executes a program stored in a memory. Note that the CPU is also referred to as a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, or a processor.

  When the control device 60 is dedicated hardware, the control device 60 may be, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field-Programmable Gate Array), or a combination thereof. Applicable. Each of the function units realized by the control device 60 may be realized by individual hardware, or each function unit may be realized by one piece of hardware.

  When the control device 60 is a CPU, each function executed by the control device 60 is realized by software, firmware, or a combination of software and firmware. Software and firmware are described as programs and stored in memory. The CPU realizes each function of the control device 60 by reading and executing a program stored in the memory. Here, the memory is, for example, a nonvolatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, or an EEPROM.

  A part of the functions of the control device 60 may be realized by dedicated hardware, and a part may be realized by software or firmware.

  The control device 60 according to the first embodiment includes, as functional units, an input unit 61, a first arithmetic unit 62, a second arithmetic unit 63, a third arithmetic unit 64, a control unit 65, and a storage unit 66. .

  The input unit 61 is a functional unit to which detection values of the first temperature sensor 71, the second temperature sensor 72, the temperature sensor 73, the first humidity sensor 81, and the second humidity sensor 82 are input. The operation modes of the indoor unit 11 and the outside air supply unit 31 are also input to the input unit 61 from a remote controller (not shown) or the like. Further, the set temperature and the set humidity in the room 101 are also input to the input unit 61.

  The first calculation unit 62 is a function unit that calculates a target evaporation temperature of the refrigerant flowing through the first heat exchanger 16 when the first heat exchanger 16 of the indoor unit 11 functions as an evaporator. The target evaporation temperature is a control target value when controlling the temperature of the refrigerant flowing through the first heat exchanger 16. The second calculation unit 63 is a functional unit that calculates a target supply air temperature of the supply air supplied from the outside air supply device 31 into the room 101. The target supply air temperature is a control target value when controlling the temperature of the supply air supplied from the outside air supply device 31 into the room 101. The third calculation unit 64 is a function unit that calculates a target water temperature of the water flowing through the second heat exchanger 42 of the outside air supply device 31. The target water temperature is a control target value for controlling the temperature of the water flowing through the second heat exchanger 42.

  The control unit 65 is a functional unit that controls each component of the air-conditioning system 100 based on the information input to the input unit 61, the control target value calculated by each of the calculation units described above, and the like. The storage unit 66 stores information input to the input unit 61, information used when each of the arithmetic units calculates a control target value, a calculation result of each of the above arithmetic units, and information used by the control unit 65 for control. And the like.

  Next, the operation of the air-conditioning system 100 according to Embodiment 1 will be described. Hereinafter, an operation when the air conditioning system 100 performs the cooling and dehumidifying operation will be described.

  When the air conditioning system 100 performs the cooling and dehumidifying operation, the indoor unit 11 of the internal conditioner 1 sucks the air in the room 101 into the first housing 11a. Then, the indoor unit 11 of the internal conditioner 1 cools the air sucked into the first housing 11a by the refrigerant flowing through the first heat exchanger 16 so that the temperature in the room 101 becomes the set temperature, and is cooled. The supplied air is supplied into the room 101. When the air conditioning system 100 performs the cooling and dehumidifying operation, the outside air supply device 31 of the outside air conditioner 2 sucks outside air into the second housing 50. Then, the outside air supply device 31 of the outside air conditioner 2 is sucked into the second housing 50 by the water flowing through the second heat exchanger 42 to cool the outside air so that the absolute humidity in the room 101 becomes the set humidity. The dehumidified and cooled outside air is supplied into the room 101 as supply air.

  Here, the air-conditioning system 100 according to Embodiment 1 sets the target evaporation temperature of the refrigerant flowing through the first heat exchanger 16 so that the air conditioning load of the internal conditioner 1 becomes a load corresponding to the sensible heat load. It is determined as follows.

  First operation unit 62 of control device 60 of air-conditioning system 100 according to Embodiment 1 subtracts the set temperature in room 101 stored in storage unit 66 from the temperature detected by first temperature sensor 71, Calculate the temperature difference ΔT. In other words, the first calculation unit 62 calculates the temperature difference ΔT by subtracting the set temperature in the room 101 from the temperature in the room 101. Then, the first calculation unit 62 determines the target evaporation temperature Te_tgt of the refrigerant flowing through the first heat exchanger 16 according to the temperature difference ΔT.

  Specifically, when the temperature difference ΔT is large, the sensible heat load is large. Therefore, much energy is required to cool the air sucked into the first housing 11a of the indoor unit 11. On the other hand, when the temperature difference ΔT is small, the sensible heat load is small. Therefore, the energy for cooling the air sucked into the first housing 11a of the indoor unit 11 may be small. Therefore, the first calculation unit 62 decreases the target evaporation temperature Te_tgt when the temperature difference ΔT is large, and increases the target evaporation temperature Te_tgt when the temperature difference ΔT is small. That is, in the air-conditioning system 100 according to Embodiment 1, the state in which the temperature difference ΔT is the first temperature difference is referred to as a first temperature difference state, and the second temperature difference ΔT is smaller than the first temperature difference. When the state having the temperature difference is the second temperature difference state, the temperature of the refrigerant flowing through the first heat exchanger 16 in the second temperature difference state is the first heat exchange state in the first temperature difference state. It becomes higher than the temperature of the refrigerant flowing through the vessel 16.

  When a plurality of first temperature sensors 71 are installed in one room 101, the first calculation unit 62 calculates the temperature difference ΔT for the detected temperatures of all the first temperature sensors 71. Then, the first calculation unit 62 determines the target evaporation temperature Te_tgt of the refrigerant flowing through the first heat exchanger 16 using the largest value of the temperature difference ΔT. When a plurality of indoor units 11 are installed in one room 101 and a set temperature is set for each indoor unit 11, the first calculation unit 62 calculates a temperature for all the indoor units 11. The difference ΔT is calculated. Then, the first calculation unit 62 determines the target evaporation temperature Te_tgt of the refrigerant flowing through the first heat exchanger 16 using the largest value of the temperature difference ΔT. When a plurality of indoor units 11 are installed in one room 101 and a first temperature sensor 71 is provided for each indoor unit 11, the first calculation unit 62 calculates ΔT for each indoor unit 11. . Then, the first calculation unit 62 determines the target evaporation temperature Te_tgt of the refrigerant flowing through the first heat exchanger 16 using the largest value of the temperature difference ΔT. By determining the target evaporation temperature Te_tgt in this way, it is possible to prevent the internal conditioner 1 from becoming insufficient in capacity with respect to the sensible heat load.

  Specifically, in the first embodiment, the first calculation unit 62 determines the target evaporation temperature Te_tgt as follows.

  FIG. 5 is a diagram for explaining a method of determining the target evaporation temperature of the refrigerant flowing through the first heat exchanger in the air-conditioning system according to Embodiment 1 of the present invention. The horizontal axis in FIG. 5 is a temperature difference ΔT that is a value obtained by subtracting the set temperature in the room 101 from the temperature detected by the first temperature sensor 71. The vertical axis in FIG. 5 is the target evaporation temperature Te_tgt of the refrigerant flowing through the first heat exchanger 16.

  The storage unit 66 of the control device 60 stores an upper limit Te_max of the target evaporation temperature Te_tgt and a lower limit Te_min of the target evaporation temperature Te_tgt in advance. Then, when the temperature difference ΔT <0, the first calculation unit 62 determines the target evaporation temperature Te_tgt to the upper limit Te_max. When the temperature difference ΔT> ΔT1, the first calculation unit 62 determines the target evaporation temperature Te_tgt to be the lower limit Te_min. Further, when 0 ≦ temperature difference ΔT ≦ ΔT1, the first arithmetic unit 62 sets the target evaporation temperature between the upper limit Te_max and the lower limit Te_min such that the smaller the temperature difference ΔT, the larger the target evaporation temperature Te_tgt. Determine Te_tgt. ΔT1 is, for example, an allowable listing width of the temperature in the room 101 with respect to the set temperature. ΔT1 may be stored in the storage unit 66 in advance as a fixed value, or may be a value stored in the storage unit 66 by the user via the input unit 61.

  Further, the air conditioning system 100 according to Embodiment 1 sets the target of the supply air supplied from the outside air supply device 31 into the room 101 such that the air conditioning load of the outside air conditioner 2 becomes a load corresponding to the latent heat load. The supply air temperature is determined as follows.

  The second arithmetic unit 63 of the control device 60 of the air-conditioning system 100 according to Embodiment 1 subtracts the set humidity in the room 101 stored in the storage unit 66 from the detected humidity of the first humidity sensor 81, Calculate the humidity difference Δx. In other words, the second calculating unit 63 calculates the humidity difference Δx by subtracting the set humidity in the room 101 from the absolute humidity in the room 101. Then, the second calculation unit 63 determines the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101 according to the humidity difference Δx.

  Specifically, when the humidity difference Δx is large, the latent heat load is large. For this reason, it is necessary to cool the outside air drawn into the second housing 50 of the outside air supply device 31 to a lower temperature and remove more moisture from the outside air. On the other hand, when the humidity difference Δx is small, the latent heat load is small. For this reason, the amount by which the outside air is sucked into the second housing 50 of the outside air supply device 31 to cool the outside air and remove moisture may be small. Therefore, the second computing unit 63 decreases the target supply air temperature TSA_tgt when the humidity difference Δx is large, and increases the target supply air temperature TSA_tgt when the humidity difference Δx is small. That is, in the air-conditioning system 100 according to Embodiment 1, the state where the humidity difference Δx is the first humidity difference is referred to as the first humidity difference state, and the second humidity difference Δx is smaller than the first humidity difference. When the state of the humidity difference is the second humidity difference state, the temperature of the supply air supplied from the outside air supply device 31 into the room 101 in the second humidity difference state is equal to the temperature in the first humidity difference state. Then, the temperature becomes higher than the temperature of the supply air supplied from the outside air supply device 31 into the room 101.

  When a plurality of first humidity sensors 81 are installed in one room 101, the second calculation unit 63 calculates a humidity difference Δx with respect to the detected humidities of all the first humidity sensors 81. Then, the second calculation unit 63 determines the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101 using the humidity difference Δx having the largest value. Further, when the supply air is supplied into the plurality of rooms 101 by one outside air supply device 31, the second calculation unit 63 calculates the humidity difference Δx for all the rooms 101. Then, the second calculation unit 63 determines the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101 using the humidity difference Δx having the largest value.

  Specifically, in the first embodiment, the second calculation unit 63 determines the target supply air temperature TSA_tgt as follows.

  FIG. 6 is a diagram for explaining a method of determining a target supply air temperature of supply air supplied from the outside air supply device into the room in the air-conditioning system according to Embodiment 1 of the present invention. The horizontal axis in FIG. 6 is a humidity difference Δx, which is a value obtained by subtracting the set humidity in the room 101 from the detected humidity of the first humidity sensor 81. The vertical axis in FIG. 6 indicates the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101.

  The storage unit 66 of the control device 60 stores an upper limit TSA_max of the target supply air temperature TSA_tgt and a lower limit TSA_min of the target supply air temperature TSA_tgt in advance. Then, when the humidity difference Δx <0, the second calculation unit 63 determines the target supply air temperature TSA_tgt to be the upper limit value TSA_max. Further, when the humidity difference Δx> Δx1, the second calculating unit 63 determines the target supply air temperature TSA_tgt to be the lower limit value TSA_min. When 0 ≦ humidity difference Δx ≦ Δx1, the second calculating unit 63 sets the target supply air temperature TSA_tgt between the upper limit value TSA_max and the lower limit value TSA_min such that the smaller the humidity difference Δx, the larger the target supply air temperature TSA_tgt. Determine the air temperature TSA_tgt. Δx1 is, for example, an allowable listing width of the humidity in the room 101 with respect to the set humidity. Δx1 may be stored in the storage unit 66 in advance as a fixed value, or may be a value stored in the storage unit 66 by the user via the input unit 61.

  By determining the target evaporation temperature Te_tgt of the refrigerant flowing through the first heat exchanger 16 as described above, the air conditioning load of the internal conditioner 1 becomes a load corresponding to the sensible heat load. Further, by determining the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101 as described above, the air conditioning load of the outside air conditioner 2 becomes a load corresponding to the latent heat load. Therefore, the air-conditioning system 100 according to Embodiment 1 can reduce the power consumption of the entire air-conditioning system 100.

  Here, in a state where the target evaporation temperature Te_tgt of the refrigerant flowing through the first heat exchanger 16 is the lower limit Te_min, the state where the temperature difference ΔT exceeds the preset threshold ΔT_max continues for a preset time or more. Then In this case, the second calculation unit 63 sets the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101 to the lower limit value TSA_min. In other words, when the temperature difference ΔT exceeds the first threshold for the first specified time or more, in the air conditioning system 100 according to Embodiment 1, the temperature of the supply air supplied from the outside air supply device 31 into the room 101 Goes down. By increasing the sensible heat treatment capacity of the external conditioner 2 in this way, it is possible to prevent the air conditioning system 100 from becoming insufficient in capacity with respect to the sensible heat load.

  In a state where the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101 is the lower limit value TSA_min, the state where the humidity difference Δx exceeds the preset threshold value Δx_max is set in advance. It is assumed that it is continuous for more than the set time. In this case, the first calculation unit 62 sets the target evaporation temperature Te_tgt of the refrigerant flowing through the first heat exchanger 16 to the lower limit Te_min. In other words, when the humidity difference Δx exceeds the second threshold for the second specified time or more, the temperature of the refrigerant flowing through the first heat exchanger 16 decreases. By increasing the latent heat treatment capacity of the inner adjuster 1 in this way, it is possible to prevent the air conditioning system 100 from becoming insufficient in capacity against the latent heat load.

  In addition, when the supply air is supplied into the plurality of rooms 101 by one outside air supply device 31 and the indoor units 11 that perform cooling for each room 101 are different, the second arithmetic unit 63 is performed by different indoor units 11. The humidity difference Δx is referred to for each room 101. In a certain room 101, the state where the humidity difference Δx exceeds the threshold value Δx_max continues for a preset time or more. In this case, the first calculation unit 62 sets the target evaporation temperature Te_tgt of the indoor unit 11 responsible for cooling in the room 101 to the lower limit Te_min. When a plurality of first humidity sensors 81 are installed in one room 101, the second calculation unit 63 calculates the humidity difference Δx for the detected humidities of all the first humidity sensors 81. In this case, the largest value of the humidity difference Δx is used.

  Further, in the air-conditioning system 100 according to Embodiment 1, the temperature of the water flowing through the second heat exchanger 42 of the outside air supply device 31 is changed according to the outside air condition, and the power consumption is further reduced.

  Here, as a method of changing the temperature of the supply air supplied from the outside air supply device 31 into the room 101, a method of changing the temperature of the water flowing through the second heat exchanger 42 of the outside air supply device 31 and a method of changing the temperature of the outside air supply device A method of changing the flow rate of the water flowing through the second heat exchanger 42 of the number 31 may be considered. In the case of the method of changing the temperature of the water flowing through the second heat exchanger 42 of the outside air supply 31, the power consumption of the chiller 30 is reduced by increasing the temperature of the water flowing through the second heat exchanger 42 of the outside air supply 31. it can. Therefore, the power consumption of the air conditioning system 100 can be reduced. However, in order to make the temperature of the water flowing through the second heat exchanger 42 of the outside air supply 31 actually different, the water cooled by the water-refrigerant heat exchanger 36 of the chiller 30 is supplied to the second heat exchanger 42. You need to wait for it to arrive. For this reason, the method of changing the temperature of the water flowing through the second heat exchanger 42 of the outside air supply device 31 has a higher response than the method of changing the flow rate of the water flowing through the second heat exchanger 42 of the outside air supply device 31. It is difficult to make the temperature of the supply air supplied from the outside air supply device 31 into the room 101 finely follow the target water temperature.

  Therefore, in the air-conditioning system 100 according to Embodiment 1, the temperature of the water flowing through the second heat exchanger 42 of the outside air supply device 31 is changed according to the outside air condition, and then the temperature of the outside air supply device 31 is changed. (2) The flow rate of water flowing through the heat exchanger 42 is changed to change the temperature of supply air supplied from the outside air supply device 31 into the room 101. That is, in the air conditioning system 100 according to Embodiment 1, by changing the flow rate of the water flowing through the second heat exchanger 42 and the temperature of the water flowing through the second heat exchanger 42, the outside air supply device From 31, the temperature of the supply air supplied into the room 101 is changed. Thereby, the temperature of the supply air supplied from the outside air supply device 31 into the room 101 can be made to closely follow the target water temperature, and the power consumption of the air conditioning system 100 can be reduced.

FIG. 7 is an air line diagram for explaining a method of determining a target water temperature of the water flowing through the second heat exchanger in the air-conditioning system according to Embodiment 1 of the present invention. Note that the horizontal axis of FIG. 7 indicates the dry bulb temperature, and the vertical axis of FIG. 7 indicates the absolute humidity.
The third calculation unit 64 of the control device 60 divides the area according to the outside air temperature and the outside air absolute humidity, for example, as shown in FIG. To determine. Specifically, the third calculation unit 64 determines which area the outside air condition corresponds to based on the outside air temperature detected by the second temperature sensor 72 and the absolute humidity of the outside air detected by the second humidity sensor 82. to decide. Then, the third calculation unit 64 determines the target water temperature of the water flowing through the second heat exchanger 42 of the outside air supply device 31 based on the condition of the corresponding area.

  The target water temperature in each region becomes lower as the air-conditioning load increases in the region of the outside air condition. For example, the area A shown in FIG. 7 has a higher air conditioning load than the area B shown in FIG. For this reason, the target water temperature in the area A is lower than the target water temperature in the area B. Similarly, the area B shown in FIG. 7 has a higher air conditioning load than the area C shown in FIG. For this reason, the target water temperature in the area B is lower than the target water temperature in the area C. In other words, when the state in which the temperature of the outside air is the first temperature is the first temperature state, and the state in which the temperature of the outside air is the second temperature lower than the first temperature is the second temperature state, The temperature of the water flowing through the second heat exchanger 42 in the two-temperature state is higher than the temperature of the water flowing in the second heat exchanger 42 in the first temperature state. A state in which the absolute humidity of the outside air is the first absolute humidity is referred to as a first humidity state, and a state in which the absolute humidity of the outside air is the second absolute humidity lower than the first absolute humidity is referred to as a second humidity state. In this case, the temperature of the water flowing through the second heat exchanger 42 in the second humidity state becomes higher than the temperature of the water flowing in the second heat exchanger 42 in the first humidity state.

FIG. 8 is an air line diagram for explaining a method of calculating a target water temperature of the water flowing through the second heat exchanger in the air-conditioning system according to Embodiment 1 of the present invention. Note that the horizontal axis of FIG. 8 indicates the dry bulb temperature, and the vertical axis of FIG. 8 indicates the absolute humidity.
In each area, the air conditioning load is the highest at the point where the outside air temperature and the outside air humidity are the highest in that area. In each area, the temperature of the water flowing through the second heat exchanger 42 necessary for processing the air conditioning load in that area is the lowest in that area, where the outside air temperature and the outside air humidity are the highest. In each region, the temperature of the water flowing through the second heat exchanger 42 necessary for processing the air conditioning load is set as the target water temperature of the water flowing through the second heat exchanger 42. The point where the outside air temperature and the outside air humidity are highest in the region B is a point D shown in FIG. The point where the outside air temperature and the outside air humidity are highest in the region C is point E shown in FIG.

  A specific method of calculating the target water temperature of the water flowing through the second heat exchanger 42 will be described with reference to FIG. A point OA in FIG. 8 indicates the outside air environment at the time of calculating the target water temperature, for example. A point RA in FIG. 8 indicates a set temperature and a set humidity in the room 101. First, based on the outside air environment shown at the point OA, the set temperature and the set humidity in the room 101 shown at the point RA, and the heat exchange efficiency of the total heat exchanger 57, the air flowing into the second heat exchanger 42 is Calculate the environment. The environment of the air flowing into the second heat exchanger 42 is the point Coil_in in FIG. Here, the environment is a temperature and an absolute humidity.

  At point SA in FIG. 8, the target supply air temperature of the supply air supplied from the outside air supply device 31 into the room 101 and the supply air supply from the outside air supply device 31 into the room 101 become the target air temperature. It is a point indicating the absolute humidity in the case. The point Tw in FIG. 8 is a point indicating the temperature of the water flowing through the second heat exchanger 42 necessary for processing the air conditioning load and the absolute humidity of the saturated air at the temperature. Δx2 shown in FIG. 8 is a difference between the absolute humidity at the point Coil_in and the absolute humidity at the point SA. Δx3 shown in FIG. 8 is a difference between the absolute humidity at the point Coil_in and the absolute humidity at the point Tw. After calculating the point Coil_in as described above, the point Tw is calculated based on the environment of the point Coil_in, the environment indicated by the point SA, and the condition that the ratio between Δx2 and Δx3 is constant. Then, the temperature at the point Tw is set as the target water temperature of the water flowing through the second heat exchanger 42.

  Lastly, a control flow when the air conditioning system 100 performs the cooling and dehumidifying operation will be described.

FIG. 9 is a diagram for illustrating a control flow when the air-conditioning system according to Embodiment 1 of the present invention performs a cooling and dehumidifying operation.
When the cooling and dehumidifying operation of the air conditioning system 100 is started, in step S1, the first calculation unit 62 subtracts the set temperature in the room 101 from the temperature detected by the first temperature sensor 71, and calculates a temperature difference ΔT. . In step S1, the second calculating unit 63 calculates the humidity difference Δx by subtracting the set humidity in the room 101 from the detected humidity of the first humidity sensor 81.

  In step S2, the first calculation unit 62 determines the target evaporation temperature Te_tgt of the refrigerant flowing through the first heat exchanger 16 according to the temperature difference ΔT. In step S2, the second calculation unit 63 determines the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101 according to the humidity difference Δx.

  In step S3, the first calculation unit 62 determines whether or not the state where the temperature difference ΔT exceeds the threshold ΔT_max continues for a preset time. If the state where the temperature difference ΔT exceeds the threshold value ΔT_max is not continuous for a preset time, the process proceeds to step S5. On the other hand, when the state in which the temperature difference ΔT exceeds the threshold value ΔT_max continues for a preset time, in step S4, the second arithmetic unit 63 determines whether the supply air supplied from the outside air supply device 31 into the room 101 The target supply air temperature TSA_tgt is changed to the lower limit TSA_min.

  In step S5, the second calculation unit 63 determines whether or not the state in which the humidity difference Δx exceeds the preset threshold Δx_max continues for a preset time. If the state where the humidity difference Δx exceeds the preset threshold Δx_max is not continuous for a preset time, the process proceeds to step S7. On the other hand, if the state in which the humidity difference Δx exceeds the preset threshold Δx_max continues for a preset time, the first calculation unit 62 determines in step S6 that the target of the refrigerant flowing through the first heat exchanger 16 The evaporating temperature Te_tgt is changed to the lower limit Te_min.

  In step S7, the third calculation unit 64 determines a target water temperature Tw_tgt of the water flowing through the second heat exchanger 42.

  In step S8, the controller 65 sets the temperature of the refrigerant flowing through the first heat exchanger 16 to the target evaporation temperature Te_tgt, and sets the temperature of the supply air supplied from the outside air supply device 31 into the room 101 to the target supply air temperature TSA_tgt. The respective components of the air conditioning system 100 are controlled such that the temperature of the water flowing through the second heat exchanger 42 becomes the target water temperature Tw_tgt.

  In step S9, control device 60 determines whether or not a command to end the cooling and dehumidifying operation has been input. When the end command of the cooling and dehumidifying operation has not been input, steps S1 to S8 described above are repeated. On the other hand, when the cooling dehumidifying operation end command is input, the control flow of the cooling dehumidifying operation ends.

  As described above, the air conditioning system 100 according to Embodiment 1 detects the indoor unit 11, the outside air supply unit 31, the first temperature sensor 71 that detects the temperature in the room 101, and the absolute humidity in the room 101. The control device includes a first humidity sensor 81 and a control device 60 that stores a set temperature and a set humidity in the room 101. The indoor unit 11 has a first heat exchanger 16 and a first housing 11a that houses the first heat exchanger 16, and is sucked into the first housing 11a by the refrigerant flowing through the first heat exchanger 16. The air in the room 101 is cooled. The outside air supply device 31 has a second heat exchanger 42 and a second housing 50 that houses the second heat exchanger 42, and is sucked into the second housing 50 by water flowing through the second heat exchanger 42. The cooled outside air is cooled, and the cooled outside air is supplied into the room 101 as supply air. In the air-conditioning system 100 according to Embodiment 1, a state in which the temperature difference ΔT, which is a value obtained by subtracting the set temperature from the temperature in the room 101, is the first temperature difference is referred to as a first temperature difference state. When the state in which the temperature difference ΔT is the second temperature difference smaller than the first temperature difference is defined as the second temperature difference state, the temperature of the refrigerant flowing through the first heat exchanger 16 in the second temperature difference state Becomes higher than the temperature of the refrigerant flowing through the first heat exchanger 16 in the first temperature difference state. In the air-conditioning system 100 according to Embodiment 1, the state in which the humidity difference Δx obtained by subtracting the set humidity from the absolute humidity in the room 101 is the first humidity difference is referred to as the first humidity difference state. When the state where the humidity difference Δx is the second humidity difference smaller than the first humidity difference is the second humidity difference state, the supply air supplied from the outside air supply device 31 in the second humidity difference state Is higher than the temperature of the supply air supplied from the outside air supply device 31 in the first humidity difference state.

  The internal adjuster 1 mainly processes a sensible heat load, and the external adjuster 2 mainly processes a latent heat load. The temperature of the refrigerant flowing through the first heat exchanger 16 of the indoor unit 11 of the internal conditioner 1 and the temperature of the supply air supplied from the outside air supply device 31 of the external conditioner 2 are changed as in the first embodiment. Thereby, the air conditioning load of the internal control unit 1 can be set to a load corresponding to the sensible heat load, and the air conditioning load of the external control unit 2 can be set to a load corresponding to the latent heat load. Therefore, the air-conditioning system 100 according to Embodiment 1 can reduce the power consumption of the entire air-conditioning system 100. Further, the air conditioning system 100 according to Embodiment 1 does not require complicated modeling work and simulation work in advance. For this reason, the air-conditioning system 100 according to Embodiment 1 can also suppress troublesome manufacturing.

Embodiment 2 FIG.
By calculating the upper limit value TSA_max of the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101 as described below, the power consumption of the air conditioning system 100 can be further reduced. In the second embodiment, items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations as those in the first embodiment are described using the same reference numerals.

  FIG. 10 is a diagram illustrating a schematic configuration of an air conditioning system according to Embodiment 2 of the present invention. FIG. 11 is a diagram showing a schematic configuration of an outside air supply device of an outside air conditioner in the air conditioning system according to Embodiment 2 of the present invention.

  The air conditioning system 100 according to Embodiment 2 includes a temperature sensor 74 and a humidity sensor 83. The temperature sensor 74 is a sensor that detects the temperature of the air flowing into the second heat exchanger 42. The humidity sensor 83 is a sensor that detects the absolute humidity of the air flowing into the second heat exchanger 42. The temperature sensor 74 and the humidity sensor 83 are, for example, in the second housing 50 of the outside air supply device 31 on the downstream side of the air flow from the total heat exchanger 57 and upstream of the air flow on the second heat exchanger 42. It is installed in the position that becomes the side.

  Further, control device 60 of air-conditioning system 100 according to Embodiment 2 includes fourth operation unit 67 as a functional unit. The fourth calculation unit 67 is a functional unit that calculates the upper limit value TSA_max of the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101.

  Subsequently, a method of determining the upper limit value TSA_max of the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101 will be described.

  FIG. 12 is an air line diagram for explaining a method of determining an upper limit value of a target supply air temperature of supply air supplied from an outside air supply device into a room in the air conditioning system according to Embodiment 2 of the present invention. is there. The horizontal axis in FIG. 12 indicates the dry bulb temperature, and the vertical axis in FIG. 12 indicates the absolute humidity.

  In the second embodiment, the second heat exchanger 42 of the outside air supply device 31 can process a ventilation latent heat load, which is a load for dehumidifying outside air of a latent heat load to a set humidity. The upper limit value TSA_max is determined.

  Specifically, the upper limit value TSA_max is obtained as follows. The point Coil_in in FIG. 8 indicates the environment of the air flowing into the second heat exchanger 42. That is, the point Coil_in in FIG. 8 is the temperature of the air flowing into the second heat exchanger 42 detected by the temperature sensor 74 and the absolute humidity of the air flowing into the second heat exchanger 42 detected by the humidity sensor 83. Are shown. A point RA in FIG. 8 indicates a set temperature and a set humidity in the room 101. A point Tw in FIG. 8 indicates a target water temperature Tw_tgt of the water flowing through the second heat exchanger 42 and the absolute humidity of the saturated air at the target water temperature Tw_tgt.

  When determining the upper limit value TSA_max, first, the point Coil_in and the point Tw are connected by a straight line. Then, a point at which the humidity on the straight line is equal to the set humidity in the room 101 is obtained. The temperature at that point becomes the upper limit value TSA_max.

Therefore, the equation for calculating the upper limit TSA_max is as shown in the following equation (1).
TSA_max = TCoil_in− (TCoil_in−Tw_tgt) × (xCoil_in−xRA_set) ÷ (xCoil_in−xw) (1)
Note that TCoil_in is the temperature at the point Coil_in. That is, TCoil_in is the temperature of the air flowing into the second heat exchanger 42 detected by the temperature sensor 74. xCoil_in is the absolute humidity at the point Coil_in. That is, xCoil_in is the absolute humidity of the air flowing into the second heat exchanger 42 detected by the humidity sensor 83. xRA_set is the set humidity in the room 101. xw is the absolute humidity of the saturated air at the time of the target water temperature Tw_tgt.

  By determining the upper limit value TSA_max as in the second embodiment, when the latent heat load is small and the target supply air temperature TSA_tgt of the supply air supplied from the outside air supply device 31 into the room 101 becomes the upper limit value TSA_max. The second heat exchanger 42 of the outside air supply device 31 processes a latent heat load of ventilation, which is a load for dehumidifying outside air to a set humidity, among the latent heat loads. In other words, in the air conditioning system 100 according to Embodiment 2, the maximum value of the absolute humidity of the supply air supplied from the outside air supply device 31 is the same as the set humidity.

  As described above, in the air conditioning system 100 according to Embodiment 2, when the latent heat load is small, the second heat exchanger 42 of the outside air supply device 31 only needs to process only the ventilation latent heat load. The target supply air temperature TSA_tgt of the supply air supplied into the room 101 can be set high. Therefore, the power consumption of the air-conditioning system 100 can be further reduced by determining the upper limit value TSA_max as in the second embodiment.

  REFERENCE SIGNS LIST 1 internal controller, 2 outdoor controller, 10 outdoor unit, 11 indoor unit, 11 a first housing, 12 refrigerant circuit, 13 compressor, 14 outdoor heat exchanger, 15 expansion valve, 16 first heat exchanger, 17 Four-way valve, 18 refrigerant pipe, 19 outdoor unit fan, 20 indoor unit fan, 30 chiller, 31 outdoor air supply, 32 refrigerant circuit, 33 compressor, 34 refrigerant-air heat exchanger, 35 expansion valve, 36 water-refrigerant heat Exchanger, 37 four-way valve, 38 chiller fan, 40 water circuit, 41 pump, 42 second heat exchanger, 43 flow control mechanism, 44 bypass piping, 45 three-way valve, 46 water piping, 50 second housing, 51st 1 inlet, 52 first outlet, 53 second inlet, 54 second outlet, 55 air supply fan, 56 exhaust fan, 57 total heat exchanger, 60 control device, 61 input unit, 62 first Arithmetic unit, 63 second operation unit, 64 third operation unit, 65 control unit, 66 storage unit, 67 fourth operation unit, 71 first temperature sensor, 72 second temperature sensor, 73 temperature sensor, 74 temperature sensor, 81 first humidity Sensor, 82 second humidity sensor, 83 humidity sensor, 100 air conditioning system, 101 room.

Claims (6)

It has a first heat exchanger and a first housing accommodating the first heat exchanger, and cools air in a space to be air-conditioned sucked into the first housing by a refrigerant flowing through the first heat exchanger. Indoor unit,
A second heat exchanger and a second housing accommodating the second heat exchanger, wherein water flowing through the second heat exchanger cools outside air sucked into the second housing and is cooled. An outside air supply device that supplies the outside air to the air-conditioned space as supply air;
A first temperature sensor for detecting a temperature of the air-conditioned space;
A first humidity sensor that detects an absolute humidity of the air-conditioned space;
A control device that stores a set temperature and a set humidity of the air-conditioned space;
With
A state in which the temperature difference, which is a value obtained by subtracting the set temperature from the temperature of the space to be air-conditioned, is a first temperature difference is referred to as a first temperature difference state, and the second temperature difference is smaller than the first temperature difference. When the state that is the temperature difference is the second temperature difference state,
The temperature of the refrigerant flowing through the first heat exchanger in the second temperature difference state is higher than the temperature of the refrigerant flowing through the first heat exchanger in the first temperature difference state,
A state in which the humidity difference that is a value obtained by subtracting the set humidity from the absolute humidity of the air-conditioned space is a first humidity difference is referred to as a first humidity difference state, and the humidity difference is smaller than the first humidity difference. In the case where the state where the humidity difference is 2 is the second humidity difference state,
The temperature of the supply air supplied from the outside air supply device in the second humidity difference state is higher than the temperature of the supply air supplied from the outside air supply device in the first humidity difference state. The air conditioning system that is the configuration. A second temperature sensor that detects the temperature of the outside air;
A second humidity sensor for detecting the absolute humidity of the outside air;
With
When the state where the temperature of the outside air is the first temperature is the first temperature state, and the state where the temperature of the outside air is the second temperature lower than the first temperature is the second temperature state,
The temperature of the water flowing through the second heat exchanger in the second temperature state is higher than the temperature of the water flowing through the second heat exchanger in the first temperature state,
A state where the absolute humidity of the outside air is the first absolute humidity is a first humidity state, and a state where the absolute humidity of the outside air is the second absolute humidity lower than the first absolute humidity is a second humidity state. Then,
The temperature of the water flowing through the second heat exchanger in the second humidity state is higher than the temperature of the water flowing through the second heat exchanger in the first humidity state. Item 10. The air conditioning system according to Item 1. A flow rate adjusting mechanism for adjusting a flow rate of the water flowing through the second heat exchanger;
By changing the flow rate of the water flowing through the second heat exchanger and the temperature of the water flowing through the second heat exchanger, the temperature of the supply air supplied from the outside air supply device is changed. The air conditioning system according to claim 1, wherein the air conditioning system has a configuration.   The air conditioning system according to any one of claims 1 to 3, wherein a maximum value of an absolute humidity of the supply air supplied from the outside air supply device is the same as the set humidity.   The configuration according to any one of claims 1 to 4, wherein when the temperature difference exceeds a first threshold for a first specified time or more, the temperature of the supply air supplied from the outside air supply device is reduced. Air conditioning system.   The configuration according to any one of claims 1 to 5, wherein the temperature of the refrigerant flowing through the first heat exchanger is reduced when the humidity difference exceeds a second threshold for a second specified time or more. Air conditioning system.

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