JP5737173B2 - Air conditioning system that adjusts temperature and humidity - Google Patents

Description

  The present invention relates to an air conditioning system for adjusting temperature and humidity.

  Conventionally, there exists an air conditioning system that can adjust not only the temperature of the target space but also the humidity. For example, Patent Document 1 (Japanese Patent Application Laid-Open No. 2010-242959) discloses an air conditioning system installed in a semiconductor manufacturing factory or the like. In this air conditioning system, in the air conditioning unit, the indoor air can be cooled with cold water supplied from the chiller unit to cool or dehumidify the air, and the air is heated by the electric heater and the air is humidified by the watering device. You can also. And temperature adjustment and humidity adjustment are performed by cooling dehumidification operation, reheat dehumidification operation, heating humidification operation, and the like.

  In the air conditioning system disclosed in Patent Document 1 (Japanese Patent Application Laid-Open No. 2010-242959), the sensible heat load and the latent heat load in the indoor space are estimated. For example, in the sensible heat estimation operation in the PID temperature controller, the correction value Δu obtained by the PID operation with the difference between the measured temperature and the set temperature as a deviation is used.

  However, when only using the method of determining the correction value Δu based on a change of about several seconds in the PID controller and estimating the current load thereby, the correction value Δu indicates the change immediately before the estimation. In some cases, the load increase / decrease cannot always be estimated correctly. That is, in the air conditioning system described in Patent Document 1 (Japanese Patent Laid-Open No. 2010-242959), the load estimation accuracy may be insufficient.

  An object of the present invention is to perform an appropriate air conditioning control by accurately estimating an air conditioning load such as a current cooling load in an air conditioning system that adjusts temperature and humidity.

  An air conditioning system according to a first aspect of the present invention is an air conditioning system that adjusts the temperature and humidity of a target space, and a blower fan that blows air into the target space, a cooler that cools the air, and dehumidification that dehumidifies the air A heater, a heater that heats the air, a humidifier that humidifies the air, a temperature sensor that detects the temperature of the target space, a humidity sensor that detects the humidity of the target space, and a control unit. The control unit has a storage unit that stores the target temperature and target humidity of the target space. The control unit determines the required cooling output value and the required heating output value based on the deviation between the current temperature detected by the temperature sensor and the target temperature. The control unit determines the dehumidification request output value and the humidification request output value based on the deviation between the current humidity detected by the humidity sensor and the target humidity. The control unit controls the cooler based on the cooling request output value, controls the dehumidifier based on the dehumidification request output value, controls the heater based on the heating request output value, and controls the humidifier based on the humidification request output value. Furthermore, the control unit periodically estimates the cooling load, the dehumidifying load, the heating load, and the humidifying load of the target space. When the control unit determines that the cooling request output value, the dehumidification request output value, the heating request output value, and the humidification request output value need to be changed based on the estimated cooling load, dehumidification load, heating load, and humidification load. In addition, the cooling request output value, the dehumidification request output value, the heating request output value, and the humidification request output value are rewritten. In the estimation by the control unit, the cooling load is a value obtained by normalizing the difference between the current cooling request output value and the cooling request output value at the previous estimation (the value after rewriting when there is rewriting) to 0 to 1. It is calculated by multiplying the rated capacity of the cooler and adding the previously estimated cooling load. In the estimation by the control unit, the dehumidification load is a value obtained by normalizing the difference between the current dehumidification request output value and the dehumidification request output value at the previous estimation (the value after rewriting when rewritten) to 0 to 1. It is calculated by multiplying the rated capacity of the dehumidifier and adding the previously estimated dehumidifying load. In the estimation by the control unit, the heating load is a value obtained by normalizing the difference between the current heating request output value and the heating request output value at the time of the previous estimation (the value after rewriting when rewritten) to 0 to 1. It is calculated by multiplying the rated capacity of the heater and adding the previously estimated heating load. In the estimation by the control unit, the humidification load is a value obtained by normalizing the difference between the present humidification request output value and the humidification request output value at the previous estimation (the value after rewriting when rewritten) to 0 to 1. It is calculated by multiplying the rated capacity of the humidifier and adding the humidification load estimated last time.

  An air conditioning system according to a second aspect of the present invention is an air conditioning system that adjusts a physical quantity that is the temperature and / or humidity of a target space, and includes an air conditioner, a sensor that detects the physical quantity of the target space, and a control unit. I have. The air conditioner processes an air conditioning load that is a sensible heat load and / or a latent heat load of the target space. The control unit includes a storage unit that stores a target value that is a target temperature and / or target humidity of the target space. And a control part determines an output value based on the deviation of the present physical quantity and target value which were detected with the sensor, and controls an air conditioner with the output value. The control unit periodically estimates the air conditioning load, and rewrites the output value when it is determined that the output value needs to be changed based on the estimated air conditioning load. In the estimation by the control unit, the air conditioning load is set to a value obtained by normalizing the difference between the current output value and the output value at the previous estimation (the value after rewriting when the rewriting is performed) to 0 to 1. It is calculated by multiplying the rated capacity and adding the previously estimated air conditioning load.

  In the air conditioning system according to the first aspect of the present invention and the air conditioning system according to the second aspect, air conditioning processing such as cooling, dehumidification, heating, and humidification of air blown into the target space is performed, and the temperature and humidity of the target space are adjusted. Is done. In this adjustment, basically, the output value is determined based on the deviation of the current temperature and the current humidity with respect to the target temperature and the target humidity to control the air conditioner such as a cooler. The load is periodically estimated, and the output value is rewritten when it is determined that the output value needs to be changed. Thus, as compared with the case where only basic adjustment based on the output value determined based on the deviation is performed, appropriate air conditioning control corresponding to the load is performed. In periodic load estimation, the difference between the current output value and the output value at the previous estimation is used, and the difference normalized to 0 to 1 is multiplied by the rated capacity of the device. The current load is estimated by adding the estimated load of. As a result, the demerit of the estimation method (determination method) in which only a minute time change is considered in determining the output value based on the deviation between the target temperature and the current temperature, etc. As a result, the load is relieved by rewriting the output value, and as a result, the load estimation accuracy is improved and appropriate air conditioning control is performed.

  The air conditioning system which concerns on the 3rd viewpoint of this invention is an air conditioning system which concerns on a 1st viewpoint, Comprising: When the capability of a cooler changes with the air volume of a ventilation fan, a control part changes a cooling load, and the present cooling request | requirement. Multiply the difference between the output value and the required cooling output value at the previous estimation (the value after rewriting when it was rewritten) from 0 to 1 by the rated capacity of the cooler, and Multiply by a correction coefficient based on the ratio of the current air volume and the rated air volume, and calculate by adding the cooling load estimated last time. In addition, when the capacity of the dehumidifier changes depending on the air volume of the blower fan, the control unit sets the dehumidification load to the current dehumidification request output value and the dehumidification request output value at the previous estimation (if rewritten, Value) normalized by 0 to 1, multiplied by the rated capacity of the dehumidifier, and then multiplied by a correction factor based on the ratio of the current air flow rate of the blower fan to the rated air flow. Calculate by adding a dehumidifying load. In addition, when the capacity of the heater changes depending on the air volume of the blower fan, the control unit sets the heating load to the current heating request output value and the previous heating request output value at the time of the previous estimation ( Value) normalized by 0 to 1, multiplied by the rated capacity of the heater, and then multiplied by a correction factor based on the ratio of the current air flow rate of the blower fan to the rated air flow rate. The calculation is performed by adding a heating load. In addition, when the capacity of the humidifier changes depending on the air volume of the blower fan, the control unit sets the humidification load to the current cooling request output value and the humidification request output value at the previous estimation (if rewritten, Multiplied by the rated capacity of the humidifier and the correction coefficient based on the ratio of the current air flow rate of the blower fan to the rated air flow rate. It is calculated by adding a humidification load.

  When a device that exchanges heat between the heat medium and air is used as a cooler or a dehumidifier, the capacity may vary depending on the air volume of the blower fan. Even in such a case, in order to ensure the accuracy of load estimation, each load is estimated here using a correction coefficient based on the ratio between the current air flow rate of the blower fan and the rated air flow rate. Thereby, more appropriate air conditioning control can be performed.

  The air conditioning system which concerns on the 4th viewpoint of this invention is an air conditioning system which concerns on either of a 1st viewpoint-the 3rd viewpoint, Comprising: A cooler and a dehumidifier are the cooling heat exchange which had the cooling function and the dehumidification function of air together It is a vessel. In this cooling heat exchanger, a heat medium for cooling the air blown into the target space flows. The cooling heat exchanger exchanges heat between the heat medium and air.

  Here, a cooling heat exchanger for lowering the temperature of air is also used as a dehumidifier, and air is cooled and dehumidified by one heat exchanger. For this reason, the manufacturing cost and running cost of the air conditioning system can be suppressed, and the air conditioning system can be downsized.

  According to the air conditioning system according to the first aspect of the present invention and the air conditioning system according to the second aspect, only a minute time change is considered in determining the output value based on the deviation between the target temperature and the current temperature. Disadvantages of the estimation method (determination method) are alleviated by periodic load estimation and rewriting of output values as necessary, so that estimation accuracy is improved and appropriate air conditioning control is performed.

  According to the air conditioning system according to the third aspect of the present invention, each load can be estimated using a correction coefficient based on the ratio between the current air flow rate and the rated air flow rate of the blower fan, and more appropriate air conditioning control is possible. It becomes.

  According to the air conditioning system of the fourth aspect of the present invention, the manufacturing cost and running cost of the air conditioning system can be suppressed.

1 is a schematic configuration diagram of an air conditioning system according to an embodiment of the present invention. The block diagram of the controller of an air conditioning system. The figure which shows the input and output of each PID. The figure which shows the correction based on the comparison result of the increment value of the output value of each PID. The figure which shows the correction based on the comparison result of the increment value of the output value of each PID. The wet air diagram which shows air cooling and dehumidification at the time of air_conditioning | cooling dehumidification driving | operation. The humid air line figure which shows air cooling and dehumidification at the time of air_conditioning | cooling humidification driving | operation. The humid air line figure which shows air cooling and dehumidification at the time of a dehumidification heating driving | operation. The humid air diagram which shows air cooling and dehumidification at the time of heating humidification driving | operation. (A) The figure which shows the time change of each conventional output value in the transfer from a 1st condition (dehumidification heating operation) to a 2nd condition (cooling humidification operation). (B) The figure which shows the time change of the conventional temperature and humidity in the transfer from a 1st condition (dehumidification heating operation) to a 2nd condition (cooling humidification operation). (C) The figure which shows the time change of each output value in the transfer from a 1st condition (dehumidification heating operation) to a 2nd condition (cooling humidification operation). (D) The figure which shows the time change of the temperature in the transition from a 1st condition (dehumidification heating operation) to a 2nd condition (cooling humidification operation). (A) The figure which shows the time change of each conventional output value in the transfer from a 2nd condition (cooling humidification operation) to a 1st condition (dehumidification heating operation). (B) The figure which shows the time change of the conventional temperature and humidity in the transition from a 2nd condition (cooling humidification operation) to a 1st condition (dehumidification heating operation). (C) The figure which shows the time change of each output value in the transfer from a 2nd condition (cooling humidification operation) to a 1st condition (dehumidification heating operation). (D) The figure which shows the time change of the temperature in the transition from a 2nd condition (cooling humidification operation) to a 1st condition (dehumidification heating operation). The figure which shows the cooling request output value of a periodic cooling load estimation process and cooling PID. The wet air diagram which shows the relationship between the magnitude of an air volume, and the amount of reheating.

(1) Overall configuration of the air conditioning system The air conditioning system 10 according to an embodiment of the present invention processes the sensible heat load and latent heat load of the indoor space RM by a necessary amount, and adjusts the humidity and temperature of the indoor space RM. The system is configured to be capable of being installed in a clean room such as a semiconductor manufacturing factory. As shown in FIG. 1, the air conditioning system 10 takes in indoor air RA from the indoor space RM, and sends the air after adjusting the humidity and temperature to the indoor space RA as supply air SA. The air conditioning system 10 mainly includes a chiller unit 50 and an air conditioning unit 20, and includes a refrigerant circuit 51, a heat dissipation circuit 60, and a heat medium circuit 40.

(2) Detailed Configuration of Air Conditioning System (2-1) Refrigerant Circuit The refrigerant circuit 51 is included in the chiller unit 50 and is a closed circuit that circulates refrigerant and performs a vapor compression refrigeration cycle. The refrigerant circuit 51 is connected with a compressor 52, a radiator 54, an expansion valve 56, an evaporator 58, and the like.

  The compressor 52 can adjust the operating capacity. Electric power is supplied to the motor of the compressor 52 via an inverter. When the output frequency of the inverter is changed, the rotational speed (rotational speed) of the motor is changed, and the operating capacity of the compressor 52 is changed.

  The radiator 54 includes a first heat transfer tube connected to the refrigerant circuit 51 and a second heat transfer tube connected to the heat dissipation circuit 60, and the refrigerant flowing through the first heat transfer tube on the refrigerant circuit 51 side. And a heat medium flowing through the second heat transfer tube on the side of the heat radiation circuit 60 are exchanged.

  The evaporator 58 includes a first heat transfer tube connected to the refrigerant circuit 51 and a second heat transfer tube connected to the heat medium circuit 40, and flows through the first heat transfer tube on the refrigerant circuit 51 side. Heat exchange is performed between the refrigerant and the heat medium flowing through the second heat transfer tube on the heat medium circuit 40 side.

(2-2) Heat Dissipation Circuit The heat dissipation circuit 60 is filled with water as a heat medium. The heat radiator 54, the water pump 62, and the cooling tower 70 are connected to the heat radiation circuit 60. The water pump 62 can adjust the discharge flow rate and circulates water in the heat dissipation circuit 60. In the cooling tower 70, water circulating in the heat dissipation circuit 60 is cooled. In FIG. 1, the arrow attached to the water pump 62 means the direction in which water flows in the heat dissipation circuit 60.

(2-3) Heat medium circuit The heat medium circuit 40 constitutes a closed circuit filled with water as a heat medium. The evaporator 58, the circulation pump 42, and the air cooling heat exchanger 22 described above are connected to the heat medium circuit 40. The circulation pump 42 can adjust the capacity and can adjust the discharge flow rate, and circulates water in the heat medium circuit 40. In the evaporator 58, the heat medium circulating in the heat medium circuit 40 is cooled. In FIG. 1, the arrow attached to the circulation pump 42 means the direction of water flow in the heat medium circuit 40.

  FIG. 1 shows only one air conditioning unit 20 and its air cooling heat exchanger 22, but the heat medium circuit 40 includes air cooling heat exchangers 22 and evaporators of a plurality of air conditioning units. 58, the overall flow rate is determined by the discharge flow rate of the circulation pump 42, and the flow rate of the heat medium flowing to each air cooling heat exchanger 22 is determined by the opening degree of the flow rate adjustment valve 44.

(2-4) Configuration of Air Conditioning Unit The air conditioning unit 20 has a substantially rectangular parallelepiped casing 21. An air passage through which air flows is formed inside the casing 21. One end of the suction duct 32 is connected to the inflow end of the air passage. The other end of the suction duct 32 is connected to the indoor space RM. One end of the air supply duct 31 is connected to the outflow end of the air passage. The other end of the air supply duct 31 is connected to the indoor space RM.

  In the air passage in the casing 21, an air cooling heat exchanger 22, an electric heater 24, a watering humidifier 26, and a blower fan 28 are arranged in order from the upstream side to the downstream side. The electric heater 24 heats the air that has passed through the air cooling heat exchanger 22. The electric heater 24 is a device for raising the temperature of air, can change the output stepwise, and can adjust the amount of heating of air. The watering type humidifier 26 humidifies the air flowing in the casing 21 by spraying water in a tank (not shown) installed outside the casing 21 from the nozzle into the air. The watering type humidifier 26 is a device for increasing the humidity of the air and can adjust the amount of humidification to the air. The blower fan 28 is a blower that can change the rotation speed stepwise by inverter control and can adjust the amount of blown air. The blower fan 28 generates a flow of air that is blown out to the indoor space RM via the air cooling heat exchanger 22, the electric heater 24, and the watering humidifier 26.

  The air cooling heat exchanger 22 is a device that cools air to lower the temperature of the air or dehumidify the air to lower the humidity. That is, the air cooling heat exchanger 22 has both an air cooling function and a dehumidifying function, and can cool the air to a dew point temperature or lower. The air cooling heat exchanger 22 is a fin-and-tube heat exchanger having a plurality of heat transfer fins and a heat transfer tube penetrating the heat transfer fins. As described above, cold water that is a heat medium circulating in the heat medium circuit 40 flows through the heat transfer tubes of the air cooling heat exchanger 22, and the cold heat of the cold water is supplied to the air through the heat transfer tubes and the heat transfer fins. This cools the air.

(2-5) Configuration of Air Conditioning System Controller The air conditioning system 10 further includes an air conditioning system controller 80 as control means. The controller 80 will be described in detail later.

(3) Basic operation of the air conditioning system Next, the operation of the air conditioning system 10 will be described. The air conditioning system 10 includes a cooling and dehumidifying operation for cooling and dehumidifying air (see FIG. 6), a cooling and humidifying operation for cooling and humidifying air (see FIG. 7), and a dehumidifying and heating operation for dehumidifying and heating air (see FIG. 6). 8) and heating / humidifying operation for heating and humidifying air (see FIG. 9), for example, the temperature and humidity of the indoor space RM are set to 23 ° C. which is a set temperature (target temperature). Air conditioning is performed so that the humidity (target humidity) is 50%.

  In the cooling and dehumidifying operation shown in FIG. 6, the compressor 52, the water pump 62, the circulation pump 42, and the blower fan 28 are operated. In the cooling and dehumidifying operation, basically, the electric heater 24 is stopped and the watering of the watering humidifier 26 is also stopped. In the cooling and dehumidifying operation, a refrigeration cycle is performed in the refrigerant circuit 51. Specifically, the refrigerant compressed by the compressor 52 dissipates heat into the water flowing through the heat dissipation circuit 60 and condenses in the radiator 54. The refrigerant cooled by the radiator 54 is depressurized by the expansion valve 56 and then evaporates by absorbing heat from the water flowing through the heat medium circuit 40 in the evaporator 58. The refrigerant evaporated in the evaporator 58 is sucked into the compressor 52 and compressed. The water flowing through the heat dissipation circuit 60 heated by the radiator 54 radiates heat to the outdoor air in the cooling tower 70. In the heat medium circuit 40, the water cooled by the evaporator 58 of the refrigerant circuit 51 cools the air flowing through the air passage in the casing 21 in the air cooling heat exchanger 22. The water that has passed through the air cooling heat exchanger 22 returns to the evaporator 58 of the refrigerant circuit 51 and is cooled again. In the heat medium circuit 40, cold heat obtained from the refrigerant by the water in the evaporator 58 is conveyed to the air cooling heat exchanger 22 and supplied to the air. In the air conditioning unit 20, the indoor air RA taken in from the indoor space RM by the suction duct 32 flows through the air passage in the casing 21. The air is cooled and dehumidified by the water in the heat medium circuit 40 in the air cooling heat exchanger 22. The air cooled / dehumidified by the air cooling heat exchanger 22 is supplied to the indoor space RM as the supply air SA via the air supply duct 31. The sensible heat load and the latent heat load of the indoor air are just processed by the cooling / dehumidification by the air-cooling heat exchanger 22 and the air-cooling dehumidifying operation is performed when the air is not reheated or humidified. It will be.

  The cooling / humidifying operation shown in FIG. 7 is an operation in which humidification by watering of the watering humidifier 26 is performed in addition to the cooling / dehumidifying operation. Until the air is cooled by the water of the heat medium circuit 40 in the air cooling heat exchanger 22 and dehumidified, it is the same as the above-described cooling and dehumidifying operation, and water sprayed by the watering humidifier 26 is applied to the cooled / dehumidified air. Is done. The cooling / humidifying operation is an operation performed when the set temperature is achieved by cooling / dehumidifying by the air cooling heat exchanger 22 but the humidity of the indoor space RM is lower than the set humidity due to the dehumidifying effect accompanying cooling. is there.

  The dehumidifying and heating operation shown in FIG. 8 is an operation also called a reheat dehumidifying operation, and the set humidity is achieved by dehumidification / cooling by the air cooling heat exchanger 22, but the temperature of the indoor space RM is reduced by the cooling effect accompanying dehumidification. This operation is performed when the temperature falls below the set temperature. In this dehumidifying heating operation, when the amount of cold supplied to the air for dehumidification in the air cooling heat exchanger 22 is large and the air is cooled more than necessary, the electric heater 24 is activated to reheat the air. .

  In the heating / humidifying operation shown in FIG. 9, the electric heater 24, the watering humidifier 26 and the blower fan 28 are operated. On the other hand, the compressor 52, the water pump 62, and the circulation pump 42 are stopped. In the heating and humidifying operation, in the air conditioning unit 20, the air taken from the indoor space RM is first heated by the electric heater 24, then humidified by the watering humidifier 26, and supplied to the indoor space RM as supply air SA. The

(4) Detailed Control by Controller of Air Conditioning System The basic operation of the air conditioning system described above is controlled by the controller 80 shown in FIG. Specifically, the controller 80 provided in the air-conditioning system 10 as a control means includes a compressor 52, an expansion valve 56, a water pump 62, a circulation pump 42, a flow rate adjustment valve 44, an electric heater 24, a watering humidifier 26, and a blower. The fan 28, etc. are controlled. The controller 80 controls not only the devices of the air conditioning unit 20 and the heat medium circuit 40 but also the devices of the refrigerant circuit 51 and the heat dissipation circuit 60 of the chiller unit 50. Here, the devices of the air conditioning unit 20 and the heat medium circuit 40 are controlled. The explanation will focus on control. In the control of the equipment of the refrigerant circuit 51 and the heat dissipation circuit 60, the output and opening degree of the compressor 52, the expansion valve 56, and the water pump 62 are adjusted, and the temperature of the cold water flowing out from the evaporator 58 in the heat medium circuit 40 is the target. Here, the explanation is made on the assumption that the temperature of the cold water is controlled to a constant target value.

  As shown in FIG. 2, the controller 80 receives inputs from an indoor temperature sensor 95 that measures the temperature of the air in the indoor space RM, an indoor humidity sensor 96 that measures the humidity of the air in the indoor space RM, and other various sensors. The electric heater 24 of the air conditioning unit 20, the watering type humidifier 26, the blower fan 28, the circulation pump 42 of the heat medium circuit 40, and the flow rate adjustment valve 44 are controlled. The controller 80 also has a memory 81 as a storage unit. This memory 81 stores the set temperature and set humidity of the indoor space RM input by the user.

  The controller 80 controls each device by the CPU executing a program written in the memory 81 or the like, and the controller 80 has various functions when the CPU executes the program. Here, the functions of these controllers 80 are referred to as a cold heat amount adjustment unit 82, a heating amount adjustment unit 84, a humidification amount adjustment unit 86, and an air blowing amount adjustment unit 88, as shown in FIG. In FIG. 2, the controller 80 is represented as including two PID adjusters. Among these, the one that receives the set temperature and the measured value of the room temperature by the room temperature sensor 95 and outputs the required cooling output value TcMV or the required heating output value ThMV is called the temperature PID controller 101. A device that receives the measured value of indoor humidity by 96 and outputs the dehumidification request output value HcMV or the humidification request output value HhMV is called a humidity PID controller 102. The temperature PID adjuster 101 includes a heating PID 101a that outputs a required heating output value ThMV, and a cooling PID 101b that outputs a required cooling output value TcMV. The humidity PID controller 102 includes a dehumidification PID 102a that outputs a dehumidification request output value HcMV, and a humidification PID 102b that outputs a humidification request output value HhMV. Then, the cold energy adjustment unit 82 sends the larger value of the cooling request output value TcMV and the dehumidification request output value HcMV to the circulation pump 42 and the flow rate adjustment valve 44 as the cold output instruction value. The heating amount adjusting unit 84 sends the heating request output value ThMV to the electric heater 24 as a heating output instruction value. The humidification amount adjustment unit 86 sends the humidification request output value HhMV to the watering humidifier 26 as a humidification output instruction value. Further, the blower amount adjusting unit 88 sends the blower output instruction value to the blower fan 28.

(4-1) Determination of Cooling Request Output Value and Heating Request Output Value by Temperature PID Controller The temperature PID controller 101 is a PID controller having a control input (PV), a setting input (SV), and a control output (MV). It is a device that performs calculations based on standard PID control basic equations. The current temperature PVt, which is a measured value of the room temperature by the room temperature sensor 95, is input as the control input (PV), the set temperature SVt stored in the memory 81 is input as the set input (SV), and the control output (MV). The cooling request output value TcMV and the heating request output value ThMV are output.

As shown in FIG. 3, the temperature PID adjuster 101 is based on a deviation between the current temperature PVt measured by the indoor temperature sensor 95 and the set temperature SVt, and performs proportional operation (P operation), integration operation (I operation), and differentiation. The cooling required output value TcMV and the heating required output value ThMV are calculated using the PID control logic combined with the operation (D operation). The following equations 1 and 2 are used for the PID control logic. Expression 2 is an arithmetic expression for the PID operation.
(Formula 1):
u (n) = u (u−1) + Δu (n)
(Formula 2):
Δu (n) = Kp × [e (n) −e (n−1)] + (T / Tl) × e (n) + (TD / T) × [e (n) −2 × e (n− 1) + e (n-2)]
u (n) is the output value calculated by the current sensible heat load calculation, u (n-1) is the output value calculated by the previous sensible heat load calculation, and Δu (n) is the correction value. Represents each. Kp represents a proportional gain, Tl represents an integration time, TD represents a differentiation time, and T represents a time step. e (n) is the difference between the measured value of the indoor temperature sensor 95 in the current sensible heat load calculation and the set temperature, and e (n-1) is the measured value of the indoor temperature sensor 95 in the previous sensible heat load calculation. The difference from the set temperature, e (n−2), represents the difference between the measured value of the room temperature sensor 95 and the set temperature in the previous sensible heat load calculation.

(4-2) Determination of Dehumidification Request Output Value and Humidification Request Output Value by Humidity PID Controller The humidity PID controller 102 is also a PID controller similar to the temperature PID controller 101, and has room humidity as a control input (PV). The current humidity PVh, which is the measured value of the room humidity by the sensor 96, is input, the set humidity SVh stored in the memory 81 is input as the setting input (SV), the dehumidification request output value HcMV and the humidification are output as the control output (MV). The requested output value HhMV is output.

  As shown in FIG. 3, the humidity PID controller 102 uses a PID control logic similar to the temperature PID controller 101 based on the deviation between the current humidity PVh measured by the indoor humidity sensor 96 and the set humidity SVh. The dehumidification request output value HcMV and the humidification request output value HhMV are calculated. Since the calculation method is the same as that of the temperature PID controller 101, description thereof is omitted.

(4-3) Correction of cooling request output value and dehumidification request output value by cooling energy adjustment unit The cooling energy adjustment unit 82 adjusts the cooling energy supplied from the heat medium to the air in the air cooling heat exchanger 22. The controller 80 is a functional unit of the controller 80, and sends the cooling output instruction value to the circulation pump 42 and the flow rate adjustment valve 44 to adjust the flow rate of the heat medium flowing through the air cooling heat exchanger 22. Here, since it is assumed that the temperature of the cold water flowing out from the evaporator 58 is controlled to a constant target value in the heat medium circuit 40, the cooling is performed according to the flow rate of the heat medium (cold water) flowing through the air cooling heat exchanger 22. The amount of cold heat supplied from the heat medium to the air in the heat exchanger 22 changes.

  As described above, the larger one of the cooling request output value TcMV and the dehumidification request output value HcMV is sent from the cooling heat amount adjustment unit 82 to the circulation pump 42 and the flow rate adjustment valve 44 as the cooling heat output instruction value. The cooling heat amount adjustment unit 82 corrects the cooling request output value TcMV and the dehumidification request output value HcMV.

(4-3-1) Correction by Heating Request Output Value and Humidity Request Output Value The cooling request output value TcMV and the heating request output value ThMV are values related to conflicting requests, and therefore one of them is not zero. For example, correction by the cold energy adjustment unit 82 is performed so that the other becomes zero (see FIGS. 3 to 5).

  In addition, since the dehumidification request output value HcMV and the humidification request output value HhMV are values related to conflicting requests, the correction by the heat quantity adjustment unit 82 is performed so that if one is not zero, the other is zero. Is done.

(4-3-2) Correction Based on Comparison Results of Increment Values As described above, the cooling request output value TcMV and the heating request output value ThMV do not enter values in the other unless one of them is zero. When shifting from the dehumidifying and heating operation to the cooling and humidifying operation due to the load fluctuation of the RM, it is assumed that the humidification operation is delayed and the humidity of the indoor space RM is significantly lower than the set humidity (FIG. 10A). (See (b)). On the other hand, when the operation is switched from the cooling / humidifying operation to the dehumidifying / heating operation, it is assumed that the heating operation is delayed and the temperature of the indoor space RM is significantly lower than the set temperature (FIG. 11 (a), ( b)). If it becomes like this, it will be necessary to move the watering type humidifier 26 which humidifies, and the electric heater 24 which heats, and will consume useless energy.

  In order to avoid such a situation, here, when the increment value ΔTcMV of the cooling request output value TcMV is larger than zero and the increment value ΔHcMV of the dehumidification request output value HcMV is equal to or less than zero, the dehumidification request output value HcMV is set. Set to zero (see FIG. 4). Further, when the increment value ΔTcMV of the cooling request output value TcMV is equal to or less than zero and the increment value ΔHcMV of the dehumidification request output value HcMV is greater than zero, the cooling request output value TcMV is set to zero (see FIG. 5).

  In addition, regarding the cooling request output value TcMV and the dehumidification request output value HcMV, both of which are control parameters of the air cooling heat exchanger 22, by monitoring the increment value ΔTcMV and the increment value ΔHcMV, which of cooling / dehumidification is dominant Can be determined. Based on such new knowledge of the present inventor, here, when the increment value ΔTcMV of the cooling request output value TcMV is larger than zero and the increment value ΔHcMV of the dehumidification request output value HcMV is less than or equal to zero, the dehumidification request output value In addition to the correction of setting HcMV to zero, the cooling heat amount adjusting unit 82 is corrected to set the larger one of the cooling request output value TcMV and the dehumidification request output value HcMV to the new cooling request output value TcMV. Yes. In addition to the modification that the cooling request output value TcMV is zero when the increment value ΔTcMV of the cooling request output value TcMV is equal to or less than zero and the increment value ΔHcMV of the dehumidification request output value HcMV is greater than zero, the cooling request output The cooling amount adjustment unit 82 is made to correct the larger output value of the value TcMV and the dehumidification request output value HcMV to a new dehumidification request output value. Here, the larger output value of the cooling request output value TcMV and the dehumidification request output value HcMV is the larger one of the current cooling request output value TcMV and the dehumidification request output value HcMV, or the previous time. If the required cooling output value TcMV or the dehumidification required output value HcMV is large, it is the value.

(4-3-3) Correction Based on Periodic Cooling Load Estimation Processing and Dehumidification Load Estimation Processing As described above, the cooling energy adjustment unit 82 is the cooling request output value output from the cooling PID 101b of the temperature PID controller 101. The dehumidification request output value HcMV output from the dehumidification PID 102a of the TcMV and humidity PID controller 102 is corrected. In addition to this, the cooling energy adjustment unit 82 is different from the PID operation (calculation) performed at intervals of several seconds (refer to the time interval Tp in FIG. 12) (intervals of several minutes or more in FIG. 12). The output value is also corrected based on the cooling load estimation process and the dehumidification load estimation process that are periodically performed at the time interval Tb). The cooling load estimation process and the dehumidification load estimation process, and the correction of the output value based thereon will be described with reference to FIG.

Ｑｓｌｏａｄ（ｉ−１）は、前回の推定処理における最適制御値、Ｑｓｃは、空気冷却熱交換器２２の定格能力、をそれぞれ表している。定格能力Ｑｓｃについては、値を大きくしすぎると負荷増減量が大きくなりハンチングの要因になり、小さすぎると逆に応答性がわるくなるので、運転温湿度条件での顕熱能力値、潜熱能力値を用いる。もし空気冷却熱交換器２２やチラーユニット５０が過剰設計されている場合でも、その過剰に設計された設計値に基づいた顕熱能力値、潜熱能力値を用いる。 The heat quantity adjustment unit 82 periodically estimates the cooling load and the dehumidifying load of the indoor space RM, and determines that it is necessary to change the cooling request output value TcMV and the dehumidification request output value HcMV based on the estimated loads. Sometimes, the cooling request output value TcMV and the dehumidification request output value HcMV are rewritten. FIG. 12 shows an overview of the processing for estimating the cooling load of the indoor space RM and the correction (rewriting) of the required cooling output value TcMV based on the estimation processing. The cooling load estimation process is periodically performed at a time interval Tb of several minutes. In this estimation process, first, the cooling request output value TcMV calculated by the PID operation is received from the cooling PID 101b, and the optimum control value Qsload is calculated. This calculation is performed using the following calculation formula.
(Formula 3):

Qsload (i-1) represents the optimum control value in the previous estimation process, and Qsc represents the rated capacity of the air cooling heat exchanger 22, respectively. As for the rated capacity Qsc, if the value is too large, the load increase / decrease amount becomes large, which causes hunting, and if it is too small, the responsiveness will be adversely affected. Is used. Even if the air cooling heat exchanger 22 and the chiller unit 50 are excessively designed, the sensible heat capacity value and the latent heat capacity value based on the excessively designed values are used.

  TcMVpv (i) is the cooling request output value TcMV received this time, and TcMVmv (i-1) is the optimum control value (the previous cooling request output value TcMV after rewriting) transmitted to the cooling PID 101b in the previous estimation process. Represents each. However, when the optimal control value is not transmitted to the cooling PID 101b in the previous estimation process, TcMVmv (i-1) becomes the cooling request output value TcMVpv (i-1) received in the previous estimation process.

  Further, (Gac / Ga) raised to the 0.5th power (square root) is a correction coefficient according to the air volume of the blower fan 28. Gac represents the rated air volume of the blower fan 28, and Ga represents the current air volume.

  If the difference between the optimum control value Qsload obtained as described above and the requested cooling output value TcMV received from the cooling PID 101b this time is large, it is transmitted to the cooling PID 101b and the requested cooling output value TcMV is rewritten. If the difference between the optimum control value Qsload and the cooling request output value TcMV is small, the optimum control value Qsload is not transmitted to the cooling PID 101b, and the cooling request output value TcMV is not corrected (rewritten).

  At the start of control, the inverter frequency of the motor of the circulation pump 42, the opening degree of the flow rate adjusting valve 44, the amount of water flowing into the air cooling heat exchanger 22 and the water supply head are calculated from the piping model of the heat medium circuit 40. The capacity is calculated from the inlet conditions (inlet air amount, air temperature / humidity) of the air conditioning unit 20 and the input values of heating and humidification, and is set as the current cooling load. For the previous Qsload (i-1) other than at the start of the control, for example, considering the time delay of the control operation (water supply pressure), the same calculation is performed from the previous opening of the flow rate adjustment valve 44 and the current water supply pressure. Sometimes you want. For example, the control value at the load of 5 kW was transmitted to the circulation pump 42 last time, but the water supply pressure did not increase and the capacity of 4 kW was only available, but the temperature of the indoor space RM was too low and the opening of the flow rate adjustment valve 44 If the current capacity becomes 4 kW or more even if the load increase / decrease is subtracted from the previous 5 kW, it becomes a disturbance factor, so replace the previous load with the capacity at the current water supply pressure. It may be calculated again.

Ｑｌｌｏａｄ（ｉ−１）は、前回の推定処理における最適制御値、Ｑｌｃは、空気冷却熱交換器２２の定格能力、をそれぞれ表している。 Next, the estimation process of the dehumidifying load of the indoor space RM and the correction of the dehumidification request output value HcMV are the same as the above-described estimation process of the cooling load of the indoor space RM and the correction of the cooling request output value TcMV. Only the calculation formula of the control value Qlload is shown below.
(Formula 4):

Qlload (i-1) represents the optimum control value in the previous estimation process, and Qlc represents the rated capacity of the air cooling heat exchanger 22, respectively.

  HcMVpv (i) is the dehumidification request output value HcMV received this time, and HcMVmv (i-1) is the optimum control value (previous dehumidification request output value HcMV after rewriting) transmitted to the dehumidification PID 102a in the previous estimation process. Represents each. However, when the optimal control value is not transmitted to the dehumidifying PID 102a in the previous estimation process, HcMVmv (i-1) becomes the dehumidification request output value HcMVpv (i-1) received in the previous estimation process.

(4-4) Determination of cooling output instruction value by cooling amount adjustment unit As described above, the cooling amount adjustment unit 82 uses the larger value of the cooling request output value TcMV and the dehumidification request output value HcMV as the cooling output instruction value. To the circulation pump 42 and the flow rate adjusting valve 44. In accordance with this, the discharge flow rate of the circulation pump 42 and the opening degree of the flow rate adjustment valve 44 are adjusted, and the flow rate of the heat medium (cold water) flowing through the air cooling heat exchanger 22 is adjusted.

(4-5) Correction of Heating Request Output Value by Heating Amount Adjusting Unit The heating amount adjusting unit 84 is a functional unit of the controller 80 provided for adjusting the heating amount supplied from the electric heater 24 to the air. The heating output instruction value is sent to the electric heater 24.

  The heating amount adjustment unit 84 sends the heating output instruction value based on the heating request output value ThMV output from the heating PID 101a to the electric heater 24, but before that, the heating request output value ThMV is corrected.

(4-5-1) Correction by cooling request output value Since the cooling request output value TcMV and the heating request output value ThMV are values related to conflicting demands, if one is a non-zero value, the other is zero. Thus, the heating request output value ThMV is corrected (corrected to zero) by the heating amount adjusting unit 84 (see FIGS. 3 to 5).

(4-5-2) Correction Based on Periodic Heating Load Estimation Processing The heating amount adjustment unit 84 periodically estimates the heating load of the indoor space RM, and based on the estimated load, calculates the heating request output value ThMV. When it is determined that a change is necessary, the heating request output value ThMV is rewritten.

Ｅｌｏａｄ（ｉ−１）は、前回の推定処理における最適制御値、Ｅｃは、電気ヒータ２４の定格能力、をそれぞれ表している。 Although the estimation process of the heating load of the indoor space RM and the correction of the required heating output value ThMV are the same as the estimation process of the cooling load of the indoor space RM and the correction of the required cooling output value TcMV, the optimum control value Eload Only the calculation formula is shown below.
(Formula 5):

Eload (i-1) represents the optimum control value in the previous estimation process, and Ec represents the rated capacity of the electric heater 24, respectively.

  ThMVpv (i) is the heating request output value ThMV received this time, and ThMVmv (i-1) is the optimum control value (last heating request output value ThMV after rewriting) transmitted to the heating PID 101a in the previous estimation process. Represents each. However, when the optimal control value is not transmitted to the heating PID 101a in the previous estimation process, ThMVmv (i-1) becomes the heating request output value ThMVpv (i-1) received in the previous estimation process.

  Since the heating capacity of the electric heater 24 is hardly affected by the air volume of the blower fan 28, the correction coefficient of (Gac / Ga) of 0.5th power used in the cooling load estimation process is not used.

(4-6) Determination of Heating Output Instruction Value by Heating Amount Adjustment Unit The heating amount adjustment unit 84 sends the heating request output value ThMV output from the heating PID 101a to the electric heater 24 as a heating output instruction value. Based on this, the output of the electric heater 24 is automatically adjusted, and the amount of heating supplied from the electric heater 24 to the air is adjusted.

(4-7) Correction of Humidification Request Output Value by Humidification Amount Adjustment Unit The humidification amount adjustment unit 86 is a functional unit of the controller 80 provided for adjusting the humidification amount supplied to the air from the watering humidifier 26. Yes, the humidification output instruction value is sent to the watering humidifier 26.

  The humidification amount adjustment unit 86 sends a humidification output instruction value based on the humidification request output value HhMV output from the humidification PID 102b to the watering humidifier 26, but before that, the humidification request output value HhMV is corrected.

(4-7-1) Correction by Dehumidification Request Output Value Since the dehumidification request output value HcMV and the humidification request output value HhMV are values related to conflicting demands, if one is a non-zero value, the other is zero. The humidification request output value HhMV is corrected (corrected to zero) by the humidification amount adjustment unit 86 (see FIGS. 3 to 5).

(4-7-2) Correction based on periodic humidification load estimation processing The humidification amount adjustment unit 86 periodically estimates the humidification load of the indoor space RM, and based on the estimated load, the humidification request output value HhMV When it is determined that a change is necessary, the humidification request output value HhMV is rewritten.

Ｋｌｏａｄ（ｉ−１）は、前回の推定処理における最適制御値、Ｋｃは、散水式加湿器２６の定格能力、をそれぞれ表している。 Although the estimation process of humidification of the indoor space RM and the correction of the humidification request output value HhMV are the same as the estimation process of the cooling load of the indoor space RM and the correction of the cooling request output value TcMV, the optimal control value Kload Only the calculation formula is shown below.
(Formula 6):

Kload (i-1) represents the optimum control value in the previous estimation process, and Kc represents the rated capacity of the watering humidifier 26, respectively.

  HhMVpv (i) is the humidification request output value HhMV received this time, and HhMVmv (i-1) is the optimal control value (the previous humidification request output value HhMV after rewriting) transmitted to the humidification PID 102b in the previous estimation process. Represents each. However, when the optimal control value is not transmitted to the humidification PID 102b in the previous estimation process, HhMVmv (i-1) becomes the humidification request output value HhMVpv (i-1) received in the previous estimation process.

  In addition, since the humidification capability of the watering type humidifier 26 is hardly influenced by the air volume of the blower fan 28, the correction coefficient of 0.5 (Gac / Ga) used in the cooling load estimation process is not used. .

(4-8) Determination of Humidification Output Instruction Value by Humidification Amount Adjustment Unit The humidification amount adjustment unit 86 sends the humidification request output value HhMV output from the humidification PID 102b to the watering humidifier 26 as a humidification output instruction value. Based on this, the watering amount of the watering humidifier 26 is automatically adjusted, and the amount of humidification supplied to the air from the watering humidifier 26 is adjusted.

(4-9) Determination of Blowing Output Instruction Value by Blowing Amount Adjustment Unit The blowing amount adjustment unit 88 is a functional unit of the controller 80 provided to adjust the blowing amount by the blower fan 28, and the blowing output instruction value is determined. The amount of air blown to the indoor space RM through the air cooling heat exchanger 22, the electric heater 24, and the watering type humidifier 26 is adjusted by changing the rotational speed of the blower fan 28 to the blower fan 28. . The fan step of the blower fan 28 that has received the blowout output instruction value is adjusted according to the instruction value.

  The air flow rate adjustment unit 88 includes a first combination and a first combination of the cooling amount, heating amount, humidification amount, and air blowing amount that can handle the sensible heat load and latent heat load of the required amount of the indoor space RM. The second combination is selected when there is a second combination having a smaller air flow rate than the combination. On the premise of the blast volume of the blower fan 28 determined in this manner, the cooling amount adjustment unit 82, the heating amount adjustment unit 84, and the humidification amount adjustment unit 86 have the cooling request output value TcMV, the dehumidification request output value HcMV, The required output value ThMV and the humidification required output value HhMV are obtained, and the cooling output instruction value, the heating output instruction value, and the humidification output instruction value are determined.

  Specifically, the air flow rate adjusting unit 88 selects the combination that minimizes the air flow rate from the combinations of the cooling heat amount, heating amount, humidification amount, and air flow rate that can handle the required amount of sensible heat load and latent heat load. The amount of cooling, heating and humidification are determined on the premise of the amount of air blown.

  This is, for example, a method for determining the amount of air blown, which the present inventor has noticed and invented that the following situation has conventionally occurred. In the clean room air conditioning, the target set temperature and set humidity are 23 ° C./50%, and the air is 27 ° C./60%. The amount of water contained in the air is reduced by cooling to / 95% and reheated to 23 ° C / 50% with an electric heater (the amount of water at 27 ° C and 60% relative humidity) Less water at 12 ° C. and 95% relative humidity). In this situation, the ratio of the energy consumed by the electric heater to the energy consumption of the entire air conditioning system is 20% to 40%, and the electric heater is less energy efficient than the heat pump. The overall energy consumption is large.

  In this situation, the inventor of the present application uses the sensible heat load and the sensible heat ratio of the latent heat load to be processed by the air cooling heat exchanger 22 from the sensible heat ratio (SHF) which is the ratio of the sensible heat load to the latent heat load. It has been found that whether or not is greatly deviated depends on the air volume. When the cooling capacity is the same, the sensible heat ratio increases as the air volume increases, and the sensible heat ratio decreases as the air volume decreases. And this inventor has created the model formula or data of the amount of sensible heat processing (cooling processing amount) and the amount of latent heat processing (dehumidification processing amount) of the cooling heat exchanger by the air volume (air flow) and the amount of cooling in advance, For each fan step of the blower fan 28, the amount of cooling, heating and humidification required for load processing are obtained, and the amount of blown air is kept within the range of the capabilities of the air cooling heat exchanger 22, the electric heater 24 and the watering humidifier 26. It is inventing to calculate a combination of the amount of cooling, heating and humidification that can be minimized.

  As described above, the air flow rate adjustment unit 88 and the controller 80 determine the air flow output instruction value from the smallest air flow rate that can be processed by the required amount of sensible heat load and latent heat load, and the above-described cooling output is based on the air flow rate. An instruction value, a heating output instruction value, and a humidification output instruction value are determined.

  In order to shorten the calculation time, instead of calculating every fan step, only the upper and lower steps of the current value of the fan step are calculated, and the refrigerant amount, heating amount, and humidification that can minimize the air flow rate over several times A combination of amounts may be calculated and each indicated value may be determined.

  Moreover, since there is only one combination of the refrigerant amount and the heating amount in the fan step of one blower fan for the same sensible heat load and latent heat load, it is not a change in only the blowout output instruction value, but the blowout output instruction value is changed. When it is changed, the cooling output instruction value and the heating output instruction value are always changed.

(5) Features of air conditioning system (5-1)
In this air conditioning system 10, the air cooling heat exchanger 22 is responsible for two operations of air cooling and dehumidification, and the controller 80 outputs the larger output value of the cooling request output value TcMV and the dehumidification request output value HcMV. Accordingly, the amount of cold supplied from the heat medium to the air is controlled in the air cooling heat exchanger 22. On the other hand, since cooling and heating are operations that are opposite to each other, and dehumidification and humidification are also operations that are opposite, heating by the electric heater 24 corresponding to the heating request output value ThMV is not performed unless the cooling request output value TcMV is zero. If the dehumidification request output value HcMV is not zero, the watering humidifier 26 according to the humidification request output value HhMV is not humidified.

  In such an air conditioning system 10, if the cooling request output value TcMV and the dehumidification request output value HcMV are forcibly based on the increment value ΔTcMV of the cooling request output value TcMV and the increment value ΔHcMV of the dehumidification request output value HcMV as described above. If the control to zero is not performed, the load fluctuation of the indoor space RM occurs and the second situation (cooling / humidification operation) where cooling and humidification are required from the first situation (dehumidification heating operation) where heating and dehumidification are required When it is necessary to shift to (), the heating and humidification operations are actually delayed, and unnecessary energy consumption occurs (see FIGS. 10A and 10B). This is because if the humidification is performed after the dehumidification request output value HcMV becomes zero from the first situation to the second situation, the cooling request output value TcMV that has become larger than the dehumidification request output value HcMV until then. In the air cooling heat exchanger 22, the amount of cooling heat adjusted based on the air temperature is supplied from the heat medium to the air, and a dehumidifying operation exceeding the dehumidifying request amount may be performed. This is because the humidity of the indoor space RM is already much lower than the target humidity. Further, as shown in FIG. 11 (a), when a load change that needs to shift from the second situation to the first situation occurs, heating is performed after the cooling request output value TcMV becomes zero. Until then, the amount of cooling heat adjusted based on the dehumidification request output value HcMV that is larger than the cooling request output value TcMV is supplied from the heat medium to the air in the air cooling heat exchanger 22, and the cooling request amount This is because the above cooling operation may be performed, and in that case, the temperature of the indoor space RM is already much lower than the target temperature when heating is started (see FIG. 11B). .

  In order to avoid such unnecessary energy consumption, in the air conditioning system 10, when the increment value ΔTcMV of the cooling request output value TcMV is larger than zero and the increment value ΔHcMV of the dehumidification request output value HcMV is equal to or less than zero. When the dehumidification request output value HcMV is set to zero (see FIG. 4), the cooling request output is output when the increment value ΔTcMV of the cooling request output value TcMV is less than zero and the increment value ΔHcMV of the dehumidification request output value HcMV is greater than zero. The value TcMV is set to zero (see FIG. 5). That is, in the air conditioning system 10, the cooling request output value TcMV and the dehumidification request output value HcMV that determine the control of the amount of cooling for the air cooling heat exchanger 22 that performs two operations of air cooling and dehumidification are either cooling or dehumidifying. The controller 80 determines whether the output becomes dominant, and performs control to set the output value that is not dominant to zero. Specifically, the increment value ΔTcMV of the cooling request output value TcMV and the increment value ΔHcMV of the dehumidification request output value HcMV are monitored, and when one is greater than zero and the other is less than zero, the increment value is less than zero. The output value is forcibly rewritten to zero. Thereby, the followability to the load fluctuation of sensible heat and latent heat is improved, and it is suppressed that the start of heating and humidification is delayed and unnecessary energy consumption occurs (FIGS. 10C and 10D). (See FIGS. 11 (c) and 11 (d)).

(5-2)
Further, in the air conditioning system 10, when the increment value ΔTcMV of the cooling request output value TcMV is larger than zero and the increment value ΔHcMV of the dehumidification request output value HcMV is less than or equal to zero, the cooling becomes more dominant than the dehumidification. The dehumidification request output value HcMV is forcibly rewritten to zero, and the larger one of the cooling request output value TcMV and the dehumidification request output value HcMV is written as a new cooling request output value TcMV. (See FIG. 4). As described above, when cooling becomes dominant among cooling and dehumidification, and the increment value of the dehumidification request output value HcMV becomes zero or less, the cooling operation that becomes dominant is given priority. Since the cooling request output value TcMV and the dehumidification request output value HcMV are rewritten, the delay of the humidification operation is suppressed, and the cooling request output value TcMV is appropriately corrected to follow the load fluctuations of sensible heat and latent heat. Is improved (see FIGS. 10C and 10D).

  On the other hand, when the increment value ΔTcMV of the cooling request output value TcMV is less than or equal to zero and the increment value ΔHcMV of the dehumidification request output value HcMV is greater than zero, it is determined that the dehumidification is more dominant than the cooling. The required output value TcMV is forcibly rewritten to zero, and the larger output value of the cooling request output value TcMV and the dehumidification request output value HcMV is written as a new dehumidification request output value HcMV (see FIG. 5). . Thus, when the dehumidification of cooling and dehumidification becomes dominant and the increment value ΔTcMV of the cooling request output value TcMV becomes equal to or less than zero, the dehumidifying operation that becomes dominant is given priority. Since the cooling request output value TcMV and the dehumidification request output value HcMV are rewritten at the same time, the delay of the heating operation is suppressed, and the dehumidification request output value is appropriately corrected to follow the load fluctuation of sensible heat and latent heat. (See FIGS. 11C and 11D).

(5-3)
In this air conditioning system 10, basically, output values (heating request output value ThMV, cooling request output value TcMV, dehumidification request output value HcMV, humidification request) based on the deviation of the current temperature and current humidity with respect to the set temperature and set humidity. The output value HhMV) is determined by the temperature PID controller 101 and the humidity PID controller 102, and each device (circulation pump 42, flow rate adjustment valve 44, electric heater 24, watering type humidifier 26) is controlled. . However, the air conditioning system 10 periodically estimates the cooling load, the dehumidifying load, the heating load, and the humidifying load of the indoor space RM in order to further increase the estimation accuracy of the latent heat load and the sensible heat load and perform appropriate control. For example, in the cooling load estimation process, if the difference between the estimated optimum control value Qsload and the cooling request output value TcMV received from the cooling PID 101b is large, the cooling request output value TcMV of the cooling PID 101b is corrected (rewritten). Is called. In this way, in each load estimation process, the output values (heating request output value ThMV, cooling request output value TcMV, dehumidification request output value HcMV, humidification request output value HhMV) are corrected. Compared with the case where control is performed using only the humidity PID controller 102, appropriate air conditioning control corresponding to the load is performed.

  Since the periodic load estimation process is performed at intervals of several minutes of one minute or more, it is taken into consideration that the PID operation performed at intervals of several seconds in the temperature PID controller 101 and the humidity PID controller 102 cannot be considered. Since the estimation is performed, the merit that the estimation accuracy of the latent heat load and the sensible heat load becomes high is obtained. That is, the disadvantage of the estimation method that only the minute time change is considered in the determination of the output value based on the deviation in the temperature PID controller 101 and the humidity PID controller 102 is mitigated by the periodic load estimation process. As a result, load estimation accuracy is improved and appropriate air conditioning control is performed.

  In the air conditioning system 10, the optimum control value Qsload for the cooling load and the optimum control value Qlload for the dehumidifying load are calculated using a correction coefficient according to the air volume of the blower fan 28 that is (Gac / Ga) to the 0.5th power (square root). It is carried out. In an apparatus that exchanges heat between the heat medium and air, such as the air-cooled heat exchanger 22, the capacity changes depending on the air volume of the air passing through, but here, a correction coefficient based on the air volume is used. A more appropriate optimum control value is obtained, and appropriate air conditioning control can be performed.

(5-4)
In the air conditioning system 10, the air cooling heat exchanger 22 is responsible for cooling and dehumidifying the air blown into the indoor space RM, and the electric heater 24 is responsible for heating. When cold heat is supplied from the cold water, which is a heat medium, to the air in the air cooling heat exchanger 22, the temperature of the air is lowered, and moisture contained in the air is condensed to reduce the humidity of the air. Therefore, accompanying the dehumidification of the air in order to process the latent heat load of the indoor space RM by a necessary amount, the sensible heat load of the indoor space RM is processed more than necessary, and the temperature of the air is too low. Although a phenomenon may occur, at that time, the air is reheated by the electric heater 24, and the sensible heat load and the latent heat load of the indoor space RM are processed by a necessary amount (see FIG. 8). Here, considering that the required amount of latent heat load in the indoor space RM is processed, when the amount of air blown by the blower fan 28 is large, the amount of cold heat from the heat medium to air per unit time in the air cooling heat exchanger 22. However, if the amount of blown air is small, a large amount of cold heat per unit time is required. Therefore, until now, in order to give a margin to the control, control for securing a certain amount of air flow has been often employed.

  However, the inventor of the present application shows that the ratio of the sensible heat load processing amount to the total amount of the sensible heat load and latent heat load processed by the air cooling heat exchanger 22 when the blast amount is larger than when the blast amount is small ( When the latent heat load is processed, the amount of sensible heat load that is processed at the same time increases. Therefore, the inventor of the present application pays attention to the blast amount, and the first combination and the first combination among the combinations of the cold amount, the heating amount, and the blast amount that can handle the required amount of sensible heat load and latent heat load. It has been devised to select the second combination and adjust the amount of cooling, heating and blowing when there is a second combination having a smaller blowing rate than the combination. As a result, even when the air cooling heat exchanger 22 processes the sensible heat load of air beyond the required amount, the excess processing amount can be kept small. The amount of heating can be suppressed, and energy saving of the air conditioning system 10 can be achieved.

  For example, referring to FIG. 13, when the air volume is 1, the dehumidification amount (cooling amount) 1, and the heating amount 1 are the first combination, the reheat amount by the electric heater 24 becomes the first reheat amount. On the other hand, when the air volume 2 is smaller than the air volume 1, the dehumidification amount (cooling amount) 2 and the heating amount 2 are combined, the reheat amount by the electric heater 24 becomes the second reheat amount. In the case of the second combination of the air volume 2 with a small air volume, it is necessary to increase the amount of cold water flowing to the air cooling heat exchanger 22 by the amount of the air volume, but when the amount of reheat by the electric heater 24 is the first combination The second reheat amount is smaller than the first reheat amount. In the second combination, since the amount of cold water increases, the power consumption of the chiller unit 50 slightly increases, but the power consumption of the electric heater 24 decreases, and the power consumption is suppressed as a whole. This is because the efficiency of the chiller unit 50 that performs the vapor compression refrigeration cycle is higher than the efficiency of the electric heater 24. That is, even if the electric heater 24 having relatively low energy efficiency is employed, the air conditioning system 10 that restricts the air blowing amount of the blower fan 28 as much as possible can suppress the heating amount of reheating by the electric heater 24, and the entire air conditioning system 10. Energy saving can be achieved.

(6) Modification (6-1) Modification 1A
In the air conditioning system 10 according to the above-described embodiment, circulation is performed according to the cooling output instruction value of the cooling heat amount adjustment unit 82 on the assumption that the temperature of the cooling water flowing out from the evaporator 58 is controlled to be constant in the heat medium circuit 40. The discharge flow rate of the pump 42 and the opening degree of the flow rate adjustment valve 44 are adjusted, the flow rate of the heat medium (cold water) flowing through the air cooling heat exchanger 22 is adjusted, and the heat medium in the air cooling heat exchanger 22 is changed from air to air. It explains that the amount of supplied cold heat is adjusted.

  However, the parameter of the temperature of the cold water flowing out from the evaporator 58 in the heat medium circuit 40 is further used to adjust the amount of cold heat supplied from the heat medium to the air in the air cooling heat exchanger 22 according to the temperature of the cold water and the flow rate of the cold water. Can also be done. In this case, when adjusting the temperature of the chilled water, the output and opening of the compressor 52, the expansion valve 56, and the water pump 62 of the chiller unit 50 are adjusted. The amount of reheat of the electric heater 24 can be suppressed by lowering the temperature and further reducing the air volume.

(6-2) Modification 1B
In the air conditioning system 10 according to the above-described embodiment, the PID control logic is used in the temperature PID controller 101 and the humidity PID controller 102. In addition to this PID control logic, a derivative such as PI control or I-PD is used. It is also possible to use another known control logic such as PID control.

(6-3) Modification 1C
In the air conditioning system 10 according to the above embodiment, the indoor air RA taken from the indoor space RM flows through the air passage in the casing 21 of the air conditioning unit 20 and is supplied to the indoor space RM as the supply air SA after air conditioning. However, as indicated by a broken line in FIG. 1, the outdoor air OA taken from the outside is taken into the casing 21 through the outside air intake duct 33, and the air is conditioned and supplied to the indoor space RM. It can also be configured as follows. The present invention can also be applied to an air conditioning system that takes both indoor air RA and outdoor air OA into the air conditioning unit 20 and supplies the air to the indoor space RM.

(6-4) Modification 1D
In the air conditioning system 10 according to the above embodiment, in view of the fact that the heating capacity of the electric heater 24 and the humidification capacity of the watering type humidifier 26 are hardly affected by the air volume of the blower fan 28, the optimum in the periodic load estimation processing. In the calculation of the control value, the correction coefficient based on the air volume of the blower fan 28 is not used. However, when a hot water coil (air heating heat exchanger) is used as a heater or a steam coil is used as a humidifier, the cooling load It is desirable to use a correction coefficient based on the air volume of the blower fan 28 as in the calculation of the optimum control value Qsload and the optimum control value Qlload of the dehumidifying load.

DESCRIPTION OF SYMBOLS 10 Air conditioning system 22 Air cooling heat exchanger 24 Electric heater 26 Watering type humidifier 28 Blower fan 42 Circulation pump 44 Flow control valve 50 Chiller unit (cooling device)
80 controller (control unit)
81 Memory (storage unit)
82 Cooling amount adjustment unit 84 Heating amount adjustment unit 86 Humidification amount adjustment unit 88 Air flow rate adjustment unit 95 Indoor temperature sensor 96 Indoor humidity sensor 101 Temperature PID controller 102 Humidity PID controller HcMV Dehumidification request output value HhMV Humidification request output value TcMV Cooling Required output value ThMV Heating request output value ΔHcMV Dehumidification request output value increment value ΔTcMV Cooling request output value increment value Qsload Cooling load optimum control value (cooling load)
Qlload Optimal control value for dehumidification load (dehumidification load)
Eload Optimal control value of heating load (heating load)
Kload Humidification load optimum control value (humidification load)

JP 2010-242995 A

Claims (3)

An air conditioning system (10) for adjusting the temperature and humidity of a target space (RM),
A blower fan (28) for blowing air into the target space;
A cooler (22) for cooling the air;
A dehumidifier (22) for dehumidifying the air;
A heater (24) for heating the air;
A humidifier (26) for humidifying the air;
A temperature sensor (95) for detecting the temperature of the target space;
A humidity sensor (96) for detecting the humidity of the target space;
A storage unit (81) for storing the target temperature and target humidity of the target space, and a cooling request output value (TcMV) and a heating request based on a deviation between the current temperature detected by the temperature sensor and the target temperature An output value (ThMV) is determined, a dehumidification request output value (HcMV) and a humidification request output value (HhMV) are determined based on a deviation between the current humidity detected by the humidity sensor and the target humidity, and the cooling request Control the cooler by an output value, control the dehumidifier by the dehumidification request output value, control the heater by the heating request output value, and control the humidifier by the humidification request output value Part (80),
With
The controller is
Periodically estimating the cooling load (Qsload), dehumidification load (Qlload), heating load (Eload) and humidification load (Kload) of the target space, and estimating the estimated cooling load, dehumidification load, heating load and humidification When it is determined that the cooling request output value, the dehumidification request output value, the heating request output value, and the humidification request output value need to be changed based on a load, the cooling request output value, the dehumidification request output value, Rewrite the heating request output value and the humidification request output value,
The cooling load is set to a value obtained by normalizing the difference between the current cooling request output value and the cooling request output value at the previous estimation (the value after rewriting when rewritten) to 0 to 1. Multiply by the rated capacity of the vessel, and calculate by adding the cooling load estimated last time,
The dehumidification load is set to a value obtained by normalizing the difference between the current dehumidification request output value and the dehumidification request output value at the time of the previous estimation (the value after rewriting when rewritten) to 0 to 1. Multiply by the rated capacity of the vessel, and calculate by adding the dehumidification load estimated last time,
The heating load is set to a value obtained by normalizing a difference between the current heating request output value and the heating request output value at the previous estimation (a value after rewriting when the rewriting is performed) to 0 to 1. Multiply by the rated capacity of the vessel, and calculate by adding the heating load estimated last time,
The humidification load is set to a value obtained by normalizing a difference between the current humidification request output value and the humidification request output value at the previous estimation (a value after rewriting when rewritten) to 0 to 1. Multiply by the rated capacity of the vessel and calculate by adding the humidification load estimated last time,
Air conditioning system. The controller is
When the capacity of the cooler varies depending on the air volume of the blower fan, the cooling load is set to the current cooling request output value and the cooling request output value at the time of the previous estimation (the value after rewriting when there is a rewriting). ) Multiplied by the rated capacity of the cooler, and the correction factor based on the ratio between the current air flow rate and the rated air flow rate of the blower fan. Calculating by adding the cooling load,
When the capacity of the dehumidifier varies depending on the air volume of the blower fan, the dehumidification load is determined by changing the current dehumidification request output value and the dehumidification request output value at the time of the previous estimation (the value after rewriting when there is a rewrite). ) Multiplied by the rated capacity of the dehumidifier multiplied by the normalized value of 0 to 1, and further multiplied by a correction coefficient based on the ratio of the current air flow rate to the rated air flow of the blower fan, and the previous estimation Calculated by applying the dehumidification load
When the capacity of the heater varies depending on the air volume of the blower fan, the heating load is determined based on the current heating request output value and the previous heating request output value at the time of the previous estimation (the value after rewriting when there is a rewriting). ) Multiplied by the rated capacity of the heater multiplied by the normalized value of 0 to 1, and further multiplied by a correction coefficient based on the ratio of the current air flow rate to the rated air flow rate of the blower fan, the previous estimation Calculating by applying the heating load
When the performance of the humidifier varies depending on the air volume of the blower fan, the humidification load is determined by changing the current cooling request output value and the humidification request output value at the previous estimation (the value after rewriting when there is a rewrite). ) Multiplied by the rated capacity of the humidifier, normalized by the difference between 0 and 1, and then multiplied by a correction factor based on the ratio of the current air flow rate to the rated air flow rate of the blower fan. Calculating by adding the humidified load,
The air conditioning system according to claim 1. The cooling device and the dehumidifier have a cooling function and a dehumidifying function for the air, in which a heat medium for cooling the air blown into the target space flows and heat exchange is performed between the heat medium and the air. It is a cooling heat exchanger (22) that has both.
The air conditioning system according to claim 1 or 2 .

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