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WO2024079807A1 - Air conditioning system - Google Patents

Air conditioning system Download PDF

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Publication number
WO2024079807A1
WO2024079807A1 PCT/JP2022/037947 JP2022037947W WO2024079807A1 WO 2024079807 A1 WO2024079807 A1 WO 2024079807A1 JP 2022037947 W JP2022037947 W JP 2022037947W WO 2024079807 A1 WO2024079807 A1 WO 2024079807A1
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WO
WIPO (PCT)
Prior art keywords
temperature
heat source
water
conditioning system
air temperature
Prior art date
Application number
PCT/JP2022/037947
Other languages
French (fr)
Japanese (ja)
Inventor
智 赤木
勝也 谷口
Original Assignee
三菱電機株式会社
三菱電機ビルソリューションズ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社, 三菱電機ビルソリューションズ株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2022/037947 priority Critical patent/WO2024079807A1/en
Publication of WO2024079807A1 publication Critical patent/WO2024079807A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/50—Air quality properties
    • F24F2110/62—Tobacco smoke

Definitions

  • This disclosure relates to an air conditioning system that circulates water from a heat source unit to an air conditioner.
  • Patent Document 1 describes an air conditioning system that circulates and supplies cold water from a central heat source unit to multiple air conditioners in parallel, with a pump for passing cold water through the parallel flow paths of each air conditioner, and each air conditioner is provided with a flow control valve that controls the flow rate of cold water passing through each air conditioner by the valve opening based on a signal from an air conditioning load detection means in the target air conditioning area, and the valve opening information of each flow control valve is input over time into an integrated control device that controls the entire system, and the valve opening information is used to determine the total air conditioning load factor of the entire group of air conditioners, and the temperature of the cold water from the central heat source unit is adjusted based on the total air conditioning load factor.
  • Patent Document 1 when adjusting the temperature of chilled water from a central heat source unit, the valve opening information of each flow control valve of each air conditioner is imported into the integrated control device.
  • the integrated control device is generally far away from each air conditioner, and many inexpensive air conditioners cannot output valve opening information of the flow control valve to the outside. Therefore, importing valve opening information of the flow control valve into the integrated control device would result in a complex system and would increase manufacturing costs.
  • This disclosure has been made to solve the problems described above, and aims to provide an air conditioning system that can be implemented with a simple configuration and at low cost.
  • the air conditioning system includes an indoor unit having a load-side heat exchanger and a flow control valve, a heat source unit having a compressor, a heat source-side heat exchanger, a water-refrigerant heat exchanger, and a heat source-side pump, a return air temperature sensor that detects the return air temperature of the indoor unit or a supply air temperature sensor that detects the supply air temperature of the indoor unit, an outlet water temperature sensor that detects the outlet water temperature of the water-refrigerant heat exchanger, and an integrated control device that controls the valve opening of the flow control valve so that the return air temperature or the supply air temperature becomes a set temperature, controls the frequency of the compressor so that the outlet water temperature becomes a target water temperature, and controls the target water temperature so that the return air temperature or the supply air temperature becomes a target value, the target value being an offset value relative to the set temperature.
  • the air conditioning system disclosed herein can be realized with a simple configuration and at low cost because there is no need to output valve opening information of the flow control valve to the outside and then import that information into the integrated control device.
  • FIG. 1 is a schematic configuration diagram of an air conditioning system according to an embodiment.
  • FIG. 11 is a schematic configuration diagram of a modified example of the air conditioning system according to the embodiment.
  • FIG. 2 is a block diagram of each controlled object when the indoor unit of the air conditioning system according to the embodiment is an FCU.
  • FIG. 2 is a block diagram of each controlled object when the indoor unit of the air conditioning system according to the embodiment is an AHU.
  • FIG. 11 is a block diagram of each controlled object in comparison with a conventional example when the indoor unit of the air conditioning system according to the embodiment is an FCU.
  • FIG. 11 is a block diagram of each controlled object in comparison with a conventional example when the indoor unit of the air conditioning system according to the embodiment is an AHU.
  • FIG. 11 is a diagram showing the effect during heating operation in comparison with a conventional example of the air conditioning system according to the embodiment.
  • FIG. 11 is a diagram showing the effect during cooling operation in comparison with a conventional example of the air conditioning system according to the embodiment.
  • Embodiment Fig. 1 is a schematic diagram of an air conditioning system according to an embodiment.
  • Fig. 2 is a schematic diagram of a modified example of the air conditioning system according to the embodiment.
  • the air conditioning system according to the embodiment is a single type in which a pump is provided only on the heat source side (11a, 11b, 11c).
  • the air conditioning system may be a multiple type in which a pump is provided on each of the heat source side (11a, 11b, 11c) and the load side (101) and they are provided in series.
  • the air conditioning system according to the first embodiment includes a plurality of heat source units 10a, 10b, and 10c that generate hot and cold water by heating or cooling as heat source units.
  • the air conditioning system according to the embodiment also includes a plurality of indoor units 40a and 40b as load units.
  • the heat source units 10a, 10b, and 10c are connected in parallel with each other, and the indoor units 40a and 40b are connected in parallel with each other.
  • Each indoor unit 40a and 40b is connected in series to each heat source unit 10a, 10b, and 10c.
  • the air conditioning system according to the embodiment includes three heat source units 10a, 10b, and 10c and two indoor units 40a and 40b, but is not limited thereto.
  • the number of heat source units may be one or two, or four or more.
  • the number of indoor units may be one, or three or more.
  • Each heat source unit 10a, 10b, 10c includes heat source side pumps 11a, 11b, 11c, compressors 12a, 12b, 12c, flow path switching valves 13a, 13b, 13c, heat source side heat exchangers 14a, 14b, 14c, throttling devices 15a, 15b, 15c, water-refrigerant heat exchangers 16a, 16b, 16c, and heat source side control devices 17a, 17b, 17c.
  • the refrigerant flow paths of the compressors 12a, 12b, 12c, flow path switching valves 13a, 13b, 13c, heat source side heat exchangers 14a, 14b, 14c, throttling devices 15a, 15b, 15c, and water-refrigerant heat exchangers 16a, 16b, 16c are connected by piping to form refrigerant circuits 20a, 20b, 20c in which the refrigerant circulates.
  • Each indoor unit 40a, 40b is equipped with a load-side heat exchanger 41a, 41b, a flow control valve 42a, 42b, and a load-side control device 43a, 43b.
  • the heat source-side pumps 11a, 11b, 11c, the water flow paths of the water-refrigerant heat exchangers 16a, 16b, 16c, the load-side heat exchangers 41a, 41b, and the flow control valves 42a, 42b are connected by piping to form water circuits 30a, 30b, 30c through which water circulates.
  • the air conditioning system according to the first embodiment also includes an integrated control device 1 that communicates with each of the heat source side control devices 17a, 17b, and 17c and each of the load side control devices 43a and 43b, and controls the entire system.
  • heat source unit 10 the three heat source units 10a, 10b, and 10c will be collectively referred to as heat source unit 10, and the same will apply to their components.
  • indoor unit 40 the two indoor units 40a and 40b will be collectively referred to as indoor unit 40, and the same will apply to their components.
  • the heat source side pump 11 is driven by an inverter with variable frequency and supplies the sucked cold/hot water to the water flow path of the water-refrigerant heat exchanger 16.
  • the compressor 12 sucks in a low-temperature, low-pressure refrigerant, compresses it, and discharges a high-temperature, high-pressure refrigerant.
  • the compressor 12 is an inverter compressor whose capacity, which is the amount of discharge per unit time, is controlled by changing the operating frequency.
  • the flow path switching valve 13 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the direction of the refrigerant flow.
  • the flow path switching valve 13 may be a combination of a two-way valve and a three-way valve instead of a four-way valve.
  • the heat source side heat exchanger 14 functions as an evaporator or a condenser, and exchanges heat between the air supplied by the fan and the refrigerant to evaporate and gasify the refrigerant or condense and liquefy the refrigerant.
  • the heat source side heat exchanger 14 functions as an evaporator during heating operation and as a condenser during cooling operation.
  • the throttling device 15 reduces the pressure of the refrigerant and expands it.
  • the throttling device 15 is, for example, an electronic expansion valve that can adjust the valve opening, and by adjusting the valve opening, it controls the refrigerant pressure flowing into the water-refrigerant heat exchanger 16 during cooling operation, and controls the refrigerant pressure flowing into the heat source side heat exchanger 14 during heating operation.
  • the water-refrigerant heat exchanger 16 exchanges heat between water and refrigerant, and heats or cools the circulating water to a target temperature using the heat of the refrigerant.
  • the heat source side control device 17 controls the operating frequency of the compressor 12, the rotation speed of the heat source side pump 11, the valve opening of the throttling device 15, and the flow path switching valve 13.
  • the heat source side control device 17 is composed of, for example, dedicated hardware, or a CPU (also called a central processing unit, processing device, arithmetic unit, microprocessor, or processor) that executes a program stored in a memory unit (not shown).
  • a CPU also called a central processing unit, processing device, arithmetic unit, microprocessor, or processor
  • the heat source side control device 17 is, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field-Programmable Gate Array), or a combination of these.
  • Each of the functional units realized by the heat source side control device 17 may be realized by individual hardware, or each functional unit may be realized by a single piece of hardware.
  • each function executed by the heat source side control device 17 is realized by software, firmware, or a combination of software and firmware.
  • the software and firmware are written as programs and stored in the memory unit.
  • the CPU realizes each function of the heat source side control device 17 by reading and executing the programs stored in the memory unit.
  • the storage unit stores various information, and includes, for example, a non-volatile semiconductor memory that allows data to be rewritten, such as a flash memory, an EPROM, and an EEPROM.
  • some of the functions of the heat source side control device 17 may be realized by dedicated hardware, and some by software or firmware.
  • the load side control device 43 and the integrated control device 1 have the same configuration as the heat source side control device 17 described above.
  • the load-side heat exchanger 41 exchanges heat between hot and cold water sent from the heat source unit 10 and air supplied by a fan to heat or cool the air.
  • the load-side heat exchanger 41 heats the air during heating operation and cools the air during cooling operation.
  • the heated or cooled air is then supplied to the space to be air-conditioned (indoors) to perform heating or cooling.
  • the flow rate control valve 42 is an electronic valve that can adjust the valve opening, and is a valve that adjusts the water flow rate passing through the installed piping.
  • the flow rate control valve 42 adjusts the water circulation amount of each water circuit 30a, 30b, 30c, thereby adjusting the hot and cold heat supply capacity to the space to be air-conditioned (indoors).
  • the load-side control device 43 controls the valve opening of the flow rate control valve 42.
  • the air conditioning system also includes a bypass circuit 50 provided in parallel with the indoor unit 40 to avoid a blocked state that would occur if all of the multiple flow rate control valves 42a, 42b were fully closed.
  • the bypass circuit 50 is provided with a bypass flow control valve 51 for adjusting the water flow rate of the bypass circuit 50.
  • a load-side pump 101 for adjusting the water flow rate on the load side is provided on the load side, and the water flow rate of the bypass circuit 50 is adjusted by coordinated control of the load-side pump 101 and the heat source-side pump 11, so the bypass flow control valve 51 can be omitted.
  • Outlet water temperature sensors 18a, 18b, 18c are provided on the outlet side of the water flow path of the water-refrigerant heat exchangers 16a, 16b, 16c to detect the outlet water temperature Tout of the water-refrigerant heat exchangers 16a, 16b, 16c.
  • Return air temperature sensors 44a, 44b are provided on the intake ports of the indoor units 40a, 40b to detect the return air temperature RA of the indoor units 40a, 40b.
  • Supply air temperature sensors 45a, 45b are provided on the exhaust ports of the indoor units 40a, 40b to detect the supply air temperature SA of the indoor units 40a, 40b.
  • the simplex air conditioning system shown in FIG. 1 is provided with a differential pressure gauge 61 for measuring the bypass differential pressure ⁇ P of the bypass circuit 50, i.e., the differential pressure of water between the upstream side and downstream side of the bypass circuit 50, and a load side flow meter 71 for measuring the total water flow rate on the load side.
  • the load side flow meter 71 is provided, for example, downstream of the junction of the cold and hot water flowing through each load side heat exchanger 41a, 41b on the load side of the water circuits 30a, 30b, 30c.
  • the heat source side flow meter 91 is provided, for example, downstream of the junction of the cold and hot water flowing through each load side heat exchanger 41a, 41b on the heat source side of the water circuits 30a, 30b, 30c.
  • a means for measuring the differential pressure between the upstream and downstream sides of each water-refrigerant heat exchanger 16a, 16b, 16c i.e., the water pressure difference between the upstream and downstream sides of each water-refrigerant heat exchanger 16a, 16b, 16c, may be provided so that the water flow rate of each heat source unit 10a, 10b, 10c can be obtained.
  • the water flow rate of each heat source unit 10a, 10b, 10c is obtained as being proportional to, for example, a proportionality coefficient of the differential pressure (for example, 0.5 power).
  • the proportionality coefficient of the differential pressure is determined by testing at the design stage, etc.
  • FIG. 3 is a block diagram of each control object when the indoor unit 40 of the air conditioning system according to the embodiment is an FCU.
  • FIG. 4 is a block diagram of each control object when the indoor unit 40 of the air conditioning system according to the embodiment is an AHU.
  • FIG. 5 is a block diagram of each control object compared with a conventional example when the indoor unit 40 of the air conditioning system according to the embodiment is an FCU.
  • FIG. 6 is a block diagram of each control object compared with a conventional example when the indoor unit 40 of the air conditioning system according to the embodiment is an AHU.
  • FIG. 7 is a diagram showing the effect during heating operation compared with the conventional example of the air conditioning system according to the embodiment.
  • FIG. 8 is a diagram showing the effect during cooling operation compared with the conventional example of the air conditioning system according to the embodiment.
  • Control target is indoor unit 40
  • the return air temperature RA ( ⁇ indoor temperature) to the indoor unit 40, which is an FCU
  • the valve opening of the flow rate control valve 42 is the manipulated variable.
  • the target value of the return air temperature RA, which is the controlled quantity, is the set temperature Tset. Note that this set temperature Tset is set by the user. That is, the valve opening of the flow rate control valve 42 is manipulated so that the return air temperature RA becomes the set temperature Tset.
  • the supply air temperature SA from the indoor unit 40 is the controlled quantity
  • the valve opening of the flow rate control valve 42 is the manipulated variable.
  • the target value of the supply air temperature SA which is the controlled quantity
  • Tset is set in advance. That is, the valve opening of the flow rate control valve 42 is manipulated so that the supply air temperature SA becomes the set temperature Tset.
  • a damper (not shown) is provided to adjust the amount of air supplied from the air outlet, and the opening degree is controlled based on the return air temperature RA.
  • the set temperature Tset which is the target value for the operation of the flow rate control valve 42, may be set to, for example, 16° C. in cooling operation so that the air is sufficiently cold, or to 45° C. in heating operation so that the user does not feel chilly.
  • Control target is heat source unit 10] 3 and 4
  • the outlet water temperature Tout of the water-refrigerant heat exchanger 16 is a controlled variable
  • the frequency of the compressor 12 is a manipulated variable.
  • the target value of the outlet water temperature Tout, which is the controlled variable is a target water temperature Twtg, which will be described later. That is, the frequency of the compressor 12 is manipulated so that the outlet water temperature Tout becomes the target water temperature Twtg.
  • the heat source side pump 11 and the bypass flow control valve 51 are operated in coordination so that the bypass differential pressure ⁇ P becomes the target differential pressure ⁇ Ptgt.
  • the coordinated operation of the heat source side pump 11 and the bypass flow control valve 51 is generally an exclusive operation that emphasizes energy saving, in which, for example, when the bypass differential pressure ⁇ P is less than the target differential pressure ⁇ Ptgt, the valve closing operation of the bypass flow control valve 51 takes precedence over increasing the speed of the heat source side pump 11, and when the bypass differential pressure ⁇ P is more than the target differential pressure ⁇ Ptgt, the deceleration of the heat source side pump 11 takes precedence over the valve opening operation of the bypass flow control valve 51.
  • the target differential pressure ⁇ Ptgt is obtained by tuning the actual air conditioning system. For example, when the flow control valve 42 is fully open, the differential pressure before and after the heat source unit 10, i.e., the differential pressure of water between the upstream and downstream sides of the heat source unit 10, is measured when the rated flow rate flows through the indoor unit 40, and this value is set as the target differential pressure ⁇ Ptgt.
  • the heat source pump 11 is operated in the same manner as in the simplex air conditioning system described above.
  • the load pump 101 is operated so that the differential pressure between its upstream and downstream sides, that is, the differential pressure of water between the upstream and downstream sides of the load pump 101, becomes the target differential pressure ⁇ Ptgt required to flow cold and hot water to the load side indoor unit 40.
  • the heat source pump 11 is operated so as to minimize the flow rate of the bypass circuit 50.
  • the heat source pump 11 is operated so that the measurement value of the heat source side flow meter 91 is slightly larger than the measurement value of the load side flow meter 71.
  • the operation of the valve opening of the flow control valve 42 and the frequency of the compressor 12 is basically the same as in the simplex air conditioning system described above.
  • the target water temperature Twtg is operated so that energy saving is improved within a range where the cooling and heating are not insufficient. That is, in the case of cooling operation, the target water temperature Twtg is operated so as to be higher, and in the case of heating operation, the target water temperature Twtg is operated so as to be lower.
  • the controlled amount of the operation of the target water temperature Twtg is the same as the controlled amount of the operation of the flow rate control valve 42. That is, as shown in FIG. 3, when the indoor unit 40 is an FCU, the return air temperature RA to the indoor unit 40, which is an FCU, is the controlled amount, and the target water temperature Twtg is the manipulated amount.
  • the target value of the return air temperature RA which is the controlled amount
  • the target value of the return air temperature RA is generally a value offset to the set temperature Tset set by the user, that is, the set temperature Tset ⁇ .
  • the supply air temperature SA from the indoor unit 40 which is an AHU
  • the target water temperature Twtg is the manipulated amount.
  • the target value of the supply air temperature SA which is a controlled variable, is generally an offset value relative to the set temperature Tset set by the user, that is, the set temperature Tset ⁇ .
  • the set temperature Tset ⁇ which is the target value for the operation of the target water temperature Twtg, is set to a value (Tset+ ⁇ ) offset to a higher temperature than the set temperature Tset during cooling operation, and to a value (Tset- ⁇ ) offset to a lower temperature than the set temperature Tset during heating operation, compared to the set temperature Tset, which is the target value for the operation of the flow rate control valve 42.
  • the target water temperature Twtg is a fixed value
  • the valve opening of the flow control valve 42 is operated so that the return air temperature RA or the supply air temperature SA becomes the set temperature Tset
  • the frequency of the compressor 12 is operated so that the outlet water temperature Tout becomes the target water temperature Twtg.
  • the target water temperature Twtg is a variable value
  • the valve opening of the flow control valve 42 and the target water temperature Twtg are operated so that the return air temperature RA or the supply air temperature SA becomes the set temperature Tset
  • the frequency of the compressor 12 is operated so that the outlet water temperature Tout becomes the target water temperature Twtg.
  • the valve opening of the flow control valve 42 and the target water temperature Twtg do not change once they have reached their target values.
  • the valve opening of the flow control valve 42 automatically changes in a direction toward energy conservation until the valve opening degree reaches full opening, or until the target water temperature Twtg reaches the settable limit value. Therefore, compared to conventional control methods, the control method according to the embodiment can improve energy conservation to a degree that does not result in insufficient cooling or heating.
  • the indoor unit 40 with the largest unachieved temperature width i.e., the largest difference between the set temperature Tset and the return air temperature RA or supply air temperature SA
  • the indoor unit 40 with the largest unachieved temperature width i.e., the largest difference between the set temperature Tset and the return air temperature RA or supply air temperature SA
  • the indoor unit 40 with the largest unachieved temperature width i.e., the largest difference between the set temperature Tset and the return air temperature RA or supply air temperature SA
  • the indoor unit 40 with the largest unachieved temperature width i.e., the largest difference between the set temperature Tset and the return air temperature RA or supply air temperature SA
  • the characteristic operation of the duplex air conditioning system according to the embodiment is the same as described above.
  • the target value is offset so that it does not overlap with the dead band.
  • the set temperature Tset and the set temperature Tset ⁇ are offset to a value that does not overlap with the dead band.
  • the target water temperature Twtg when the controlled quantity exceeds the target value, the target water temperature Twtg changes to the energy saving side, and when the controlled quantity falls short of the target value, the target water temperature Twtg changes to the side of increasing the cooling/heating capacity, but in order to quickly recover when the controlled quantity temporarily falls short of the target value and becomes incooled or insufficient to heat, the absolute value of the range by which the operation quantity is changed relative to the absolute value of the control deviation of the controlled quantity may be made larger than when the target value is exceeded.
  • the range of change in the target water temperature Twtg is made larger when the return air temperature RA or the supply air temperature SA does not reach the set temperature Tset than when it exceeds it.
  • not reaching the target value means that the controlled quantity has not reached the target value, i.e., the controlled quantity ⁇ the target value
  • overreaching the target value means that the controlled quantity exceeds the target value, i.e., the controlled quantity > the target value.
  • the air conditioning system includes an indoor unit 40 having a load-side heat exchanger 41 and a flow control valve 42, a heat source unit 10 having a compressor 12, a heat source-side heat exchanger 14, a water-refrigerant heat exchanger 16, and a heat source-side pump 11, a return air temperature sensor 44 that detects the return air temperature RA of the indoor unit 40 or a supply air temperature sensor 45 that detects the supply air temperature SA of the indoor unit 40, an outlet water temperature sensor 18 that detects the outlet water temperature Tout of the water-refrigerant heat exchanger 16, and a heat source-side control device 17 that controls the valve opening of the flow control valve 42 so that the return air temperature RA or the supply air temperature SA becomes the set temperature Tset, controls the frequency of the compressor 12 so that the outlet water temperature Tout becomes the target water temperature Twtg, and controls the target water temperature Twtg so that the return air temperature RA or the supply air temperature SA becomes the target value, and the target value is a value offset from the set temperature Tset.
  • the air conditioning system of the embodiment there is no need to output valve opening information of the flow control valve 42 to the outside and import that information into the integrated control device 1 that controls the entire system, so it can be realized with a simple configuration and low cost, and it is also possible to introduce this system into existing buildings.
  • the target water temperature Twtg is controlled so that the return air temperature RA or the supply air temperature SA is a value offset from the set temperature Tset, it is possible to improve energy conservation within a range that does not result in insufficient cooling or heating.
  • the integrated control device 1 increases the range of change in the target water temperature Twtg when the return air temperature RA or the supply air temperature SA does not reach the set temperature Tset compared to when it exceeds the set temperature Tset.
  • the air conditioning system according to the embodiment can quickly recover from the situation where the controlled variable temporarily does not reach the target value, resulting in insufficient cooling or heating.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

An air conditioning system provided with: an indoor unit having a load-side heat exchanger and a flow regulating valve; a heat source unit having an compressor, a heat source-side heat exchanger, a water-refrigerant heat exchanger, and a heat source-side pump; a return air temperature sensor for detecting a return air temperature of the indoor unit or a supply air temperature sensor for detecting a supply air temperature of the indoor unit; an outlet water temperature sensor for detecting an outlet water temperature of the water-refrigerant heat exchanger; and an integrated control device that controls the opening degree of the flow regulating valve so as to make the return or supply air temperature to be a set temperature, controls the frequency of the compressor so as to make the outlet water temperature to be a target water temperature, and controls the target water temperature so as to make the return or supply air temperature to be a target value, wherein the target value is a value offset with respect to the set temperature.

Description

空気調和システムAir Conditioning System
　本開示は、熱源機から空気調和機に水を循環供給する空気調和システムに関するものである。 This disclosure relates to an air conditioning system that circulates water from a heat source unit to an air conditioner.
　従来、各空気調和機を通る冷水の流量を弁開度により制御する流量調整弁を設ける方式の空気調和システムが提案されている（例えば、特許文献１参照）。 　Conventionally, air conditioning systems have been proposed that use flow control valves to control the flow rate of cold water passing through each air conditioner by changing the valve opening (see, for example, Patent Document 1).
　特許文献１は、中央熱源機から複数の空気調和機に並列的に冷水を循環供給する空気調和設備であって、前記各空気調和機の並列流路に冷水を通すポンプを設け、対象の空気調和領域における空調負荷検出手段の信号に基づき、各空気調和機を通る冷水の流量を弁開度により制御する流量調整弁を各空気調和機に設け、経時ごとに各流量調整弁の弁開度情報を、システム全体を制御する統合制御装置に取り込み、その弁開度情報を用いて空気調和機群全体の空調全負荷率を求めるとともに、その空調全負荷率に基づいて中央熱源機からの冷水温度を調整している。 Patent Document 1 describes an air conditioning system that circulates and supplies cold water from a central heat source unit to multiple air conditioners in parallel, with a pump for passing cold water through the parallel flow paths of each air conditioner, and each air conditioner is provided with a flow control valve that controls the flow rate of cold water passing through each air conditioner by the valve opening based on a signal from an air conditioning load detection means in the target air conditioning area, and the valve opening information of each flow control valve is input over time into an integrated control device that controls the entire system, and the valve opening information is used to determine the total air conditioning load factor of the entire group of air conditioners, and the temperature of the cold water from the central heat source unit is adjusted based on the total air conditioning load factor.
特開２００７－１４７０９４号公報JP 2007-147094 A
　特許文献１は、中央熱源機からの冷水温度を調整する際に、各空気調和機の各流量調整弁の弁開度情報を統合制御装置に取り込んでいるが、一般的に統合制御装置から各空気調和機までは距離が離れていることが多く、また、廉価な空気調和機では、流量調整弁の弁開度情報を外部に出力できないものが多い。そのため、流量調整弁の弁開度情報を統合制御装置に取り込むようにするにはシステムが複雑になり、また、製造コストが増大するという課題があった。 In Patent Document 1, when adjusting the temperature of chilled water from a central heat source unit, the valve opening information of each flow control valve of each air conditioner is imported into the integrated control device. However, the integrated control device is generally far away from each air conditioner, and many inexpensive air conditioners cannot output valve opening information of the flow control valve to the outside. Therefore, importing valve opening information of the flow control valve into the integrated control device would result in a complex system and would increase manufacturing costs.
　本開示は、以上のような課題を解決するためになされたもので、簡素な構成かつ低コストで実現可能な空気調和システムを提供することを目的としている。 This disclosure has been made to solve the problems described above, and aims to provide an air conditioning system that can be implemented with a simple configuration and at low cost.
　本開示に係る空気調和システムは、負荷側熱交換器および流量調整弁を有する室内機と、圧縮機、熱源側熱交換器、水冷媒熱交換器、および熱源側ポンプを有する熱源機と、前記室内機の還気温度を検知する還気温度センサまたは前記室内機の給気温度を検知する給気温度センサと、前記水冷媒熱交換器の出口水温を検知する出口水温センサと、前記還気温度または前記給気温度が設定温度となるように前記流量調整弁の弁開度を制御し、前記出口水温が目標水温となるように前記圧縮機の周波数を制御し、前記還気温度または前記給気温度が目標値となるように前記目標水温を制御する統合制御装置と、を備え、前記目標値は、前記設定温度に対してオフセットした値である。 The air conditioning system according to the present disclosure includes an indoor unit having a load-side heat exchanger and a flow control valve, a heat source unit having a compressor, a heat source-side heat exchanger, a water-refrigerant heat exchanger, and a heat source-side pump, a return air temperature sensor that detects the return air temperature of the indoor unit or a supply air temperature sensor that detects the supply air temperature of the indoor unit, an outlet water temperature sensor that detects the outlet water temperature of the water-refrigerant heat exchanger, and an integrated control device that controls the valve opening of the flow control valve so that the return air temperature or the supply air temperature becomes a set temperature, controls the frequency of the compressor so that the outlet water temperature becomes a target water temperature, and controls the target water temperature so that the return air temperature or the supply air temperature becomes a target value, the target value being an offset value relative to the set temperature.
　本開示に係る空気調和システムによれば、流量調整弁の弁開度情報を外部に出力して、その情報を統合制御装置に取り込む必要がないため、簡素な構成かつ低コストで実現可能となる。 The air conditioning system disclosed herein can be realized with a simple configuration and at low cost because there is no need to output valve opening information of the flow control valve to the outside and then import that information into the integrated control device.
実施の形態に係る空気調和システムの概略構成図である。1 is a schematic configuration diagram of an air conditioning system according to an embodiment. 実施の形態に係る空気調和システムの変形例の概略構成図である。FIG. 11 is a schematic configuration diagram of a modified example of the air conditioning system according to the embodiment. 実施の形態に係る空気調和システムの室内機がＦＣＵである場合の各制御対象のブロック線図である。FIG. 2 is a block diagram of each controlled object when the indoor unit of the air conditioning system according to the embodiment is an FCU. 実施の形態に係る空気調和システムの室内機がＡＨＵである場合の各制御対象のブロック線図である。FIG. 2 is a block diagram of each controlled object when the indoor unit of the air conditioning system according to the embodiment is an AHU. 実施の形態に係る空気調和システムの室内機がＦＣＵである場合の従来例と比較した各制御対象のブロック線図である。FIG. 11 is a block diagram of each controlled object in comparison with a conventional example when the indoor unit of the air conditioning system according to the embodiment is an FCU. 実施の形態に係る空気調和システムの室内機がＡＨＵである場合の従来例と比較した各制御対象のブロック線図である。FIG. 11 is a block diagram of each controlled object in comparison with a conventional example when the indoor unit of the air conditioning system according to the embodiment is an AHU. 実施の形態に係る空気調和システムの従来例と比較した暖房運転時の効果を示す図である。FIG. 11 is a diagram showing the effect during heating operation in comparison with a conventional example of the air conditioning system according to the embodiment. 実施の形態に係る空気調和システムの従来例と比較した冷房運転時の効果を示す図である。FIG. 11 is a diagram showing the effect during cooling operation in comparison with a conventional example of the air conditioning system according to the embodiment.
　以下、本開示の実施の形態を図面に基づいて説明する。なお、以下に説明する実施の形態によって本開示が限定されるものではない。また、以下の図面では各構成部材の大きさの関係が実際のものとは異なる場合がある。 Below, an embodiment of the present disclosure will be described with reference to the drawings. Note that the present disclosure is not limited to the embodiment described below. Also, the size relationships of the components in the drawings may differ from the actual ones.
　実施の形態．
　図１は、実施の形態に係る空気調和システムの概略構成図である。図２は、実施の形態に係る空気調和システムの変形例の概略構成図である。実施の形態に係る空気調和システムは、図１に示すように、ポンプが熱源側（１１ａ、１１ｂ、１１ｃ）のみに設けられた単式である。ただし、図２に示すように、ポンプが熱源側（１１ａ、１１ｂ、１１ｃ）および負荷側（１０１）にそれぞれ設けられ、それらが直列に設けられた複式でもよい。 Embodiment
Fig. 1 is a schematic diagram of an air conditioning system according to an embodiment. Fig. 2 is a schematic diagram of a modified example of the air conditioning system according to the embodiment. As shown in Fig. 1, the air conditioning system according to the embodiment is a single type in which a pump is provided only on the heat source side (11a, 11b, 11c). However, as shown in Fig. 2, the air conditioning system may be a multiple type in which a pump is provided on each of the heat source side (11a, 11b, 11c) and the load side (101) and they are provided in series.
　図１に示すように、実施の形態１に係る空気調和システムは、熱源側ユニットとして、加熱または冷却により冷温水を生成する複数の熱源機１０ａ、１０ｂ、１０ｃを備えている。また、実施の形態に係る空気調和システムは、負荷側ユニットとして、複数の室内機４０ａ、４０ｂを備えている。複数の熱源機１０ａ、１０ｂ、１０ｃは、互いに並列に接続されており、複数の室内機４０ａ、４０ｂは、互いに並列に接続されている。そして、各室内機４０ａ、４０ｂは、各熱源機１０ａ、１０ｂ、１０ｃに対して直列に接続されている。なお、実施の形態に係る空気調和システムは、３台の熱源機１０ａ、１０ｂ、１０ｃと２台の室内機４０ａ、４０ｂとを備えているが、それに限定されない。熱源機は１台または２台でもよいし、４台以上でもよい。また、室内機は１台でもよいし、３台以上でもよい。 As shown in FIG. 1, the air conditioning system according to the first embodiment includes a plurality of heat source units 10a, 10b, and 10c that generate hot and cold water by heating or cooling as heat source units. The air conditioning system according to the embodiment also includes a plurality of indoor units 40a and 40b as load units. The heat source units 10a, 10b, and 10c are connected in parallel with each other, and the indoor units 40a and 40b are connected in parallel with each other. Each indoor unit 40a and 40b is connected in series to each heat source unit 10a, 10b, and 10c. The air conditioning system according to the embodiment includes three heat source units 10a, 10b, and 10c and two indoor units 40a and 40b, but is not limited thereto. The number of heat source units may be one or two, or four or more. The number of indoor units may be one, or three or more.
　各熱源機１０ａ、１０ｂ、１０ｃは、熱源側ポンプ１１ａ、１１ｂ、１１ｃと、圧縮機１２ａ、１２ｂ、１２ｃと、流路切替弁１３ａ、１３ｂ、１３ｃと、熱源側熱交換器１４ａ、１４ｂ、１４ｃと、絞り装置１５ａ、１５ｂ、１５ｃと、水冷媒熱交換器１６ａ、１６ｂ、１６ｃと、熱源側制御装置１７ａ、１７ｂ、１７ｃとを備えている。そして、圧縮機１２ａ、１２ｂ、１２ｃ、流路切替弁１３ａ、１３ｂ、１３ｃ、熱源側熱交換器１４ａ、１４ｂ、１４ｃ、絞り装置１５ａ、１５ｂ、１５ｃ、および、水冷媒熱交換器１６ａ、１６ｂ、１６ｃの冷媒流路が配管で接続され、冷媒が循環する冷媒回路２０ａ、２０ｂ、２０ｃが構成されている。 Each heat source unit 10a, 10b, 10c includes heat source side pumps 11a, 11b, 11c, compressors 12a, 12b, 12c, flow path switching valves 13a, 13b, 13c, heat source side heat exchangers 14a, 14b, 14c, throttling devices 15a, 15b, 15c, water- refrigerant heat exchangers 16a, 16b, 16c, and heat source side control devices 17a, 17b, 17c. The refrigerant flow paths of the compressors 12a, 12b, 12c, flow path switching valves 13a, 13b, 13c, heat source side heat exchangers 14a, 14b, 14c, throttling devices 15a, 15b, 15c, and water- refrigerant heat exchangers 16a, 16b, 16c are connected by piping to form refrigerant circuits 20a, 20b, 20c in which the refrigerant circulates.
　また、各室内機４０ａ、４０ｂは、負荷側熱交換器４１ａ、４１ｂと、流量調整弁４２ａ、４２ｂと、負荷側制御装置４３ａ、４３ｂとを備えている。そして、熱源側ポンプ１１ａ、１１ｂ、１１ｃ、水冷媒熱交換器１６ａ、１６ｂ、１６ｃの水流路、負荷側熱交換器４１ａ、４１ｂ、および、流量調整弁４２ａ、４２ｂが配管で接続され、水が循環する水回路３０ａ、３０ｂ、３０ｃが構成されている。 Each indoor unit 40a, 40b is equipped with a load- side heat exchanger 41a, 41b, a flow control valve 42a, 42b, and a load- side control device 43a, 43b. The heat source- side pumps 11a, 11b, 11c, the water flow paths of the water- refrigerant heat exchangers 16a, 16b, 16c, the load- side heat exchangers 41a, 41b, and the flow control valves 42a, 42b are connected by piping to form water circuits 30a, 30b, 30c through which water circulates.
　また、実施の形態１に係る空気調和システムは、各熱源側制御装置１７ａ、１７ｂ、１７ｃおよび各負荷側制御装置４３ａ、４３ｂと通信を行い、システム全体を制御する統合制御装置１を備えている。 The air conditioning system according to the first embodiment also includes an integrated control device 1 that communicates with each of the heat source side control devices 17a, 17b, and 17c and each of the load side control devices 43a and 43b, and controls the entire system.
　なお、以下において、３台の熱源機１０ａ、１０ｂ、１０ｃの総称を熱源機１０とし、それらの構成要素についても同様とする。また、２台の室内機４０ａ、４０ｂの総称を室内機４０とし、それらの構成要素についても同様とする。 In the following, the three heat source units 10a, 10b, and 10c will be collectively referred to as heat source unit 10, and the same will apply to their components. Furthermore, the two indoor units 40a and 40b will be collectively referred to as indoor unit 40, and the same will apply to their components.
　熱源側ポンプ１１は、インバーターによって周波数可変に駆動され、吸入した冷温水を水冷媒熱交換器１６の水流路に供給する。圧縮機１２は、低温低圧の冷媒を吸入し、吸入した冷媒を圧縮し、高温高圧の冷媒を吐出する。圧縮機１２は、運転周波数を変化させることにより、単位時間あたりの送出量である容量が制御されるインバーター圧縮機である。流路切替弁１３は、例えば四方弁であり、冷媒の流れの方向を切り替えることで、冷房運転と暖房運転とを切り替えるものである。なお、流路切替弁１３として、四方弁に代えて二方弁および三方弁の組み合わせなどを用いてもよい。熱源側熱交換器１４は、蒸発器または凝縮器として機能し、ファンによって供給される空気と冷媒との間で熱交換を行い、冷媒を蒸発ガス化または凝縮液化するものである。熱源側熱交換器１４は、暖房運転時には蒸発器として機能し、冷房運転時には凝縮器として機能する。絞り装置１５は、冷媒を減圧して膨張させるものである。絞り装置１５は、例えば弁開度を調整することができる電子式膨張弁であり、弁開度を調整することによって、冷房運転時では水冷媒熱交換器１６に流入する冷媒圧力を制御し、暖房運転時では熱源側熱交換器１４に流入する冷媒圧力を制御する。水冷媒熱交換器１６は、水と冷媒との間で熱交換を行い、冷媒の熱で循環水を目的の温度に加熱または冷却するものである。熱源側制御装置１７は、圧縮機１２の運転周波数、熱源側ポンプ１１の回転数、絞り装置１５の弁開度、および、流路切替弁１３を制御するものである。 The heat source side pump 11 is driven by an inverter with variable frequency and supplies the sucked cold/hot water to the water flow path of the water-refrigerant heat exchanger 16. The compressor 12 sucks in a low-temperature, low-pressure refrigerant, compresses it, and discharges a high-temperature, high-pressure refrigerant. The compressor 12 is an inverter compressor whose capacity, which is the amount of discharge per unit time, is controlled by changing the operating frequency. The flow path switching valve 13 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the direction of the refrigerant flow. Note that the flow path switching valve 13 may be a combination of a two-way valve and a three-way valve instead of a four-way valve. The heat source side heat exchanger 14 functions as an evaporator or a condenser, and exchanges heat between the air supplied by the fan and the refrigerant to evaporate and gasify the refrigerant or condense and liquefy the refrigerant. The heat source side heat exchanger 14 functions as an evaporator during heating operation and as a condenser during cooling operation. The throttling device 15 reduces the pressure of the refrigerant and expands it. The throttling device 15 is, for example, an electronic expansion valve that can adjust the valve opening, and by adjusting the valve opening, it controls the refrigerant pressure flowing into the water-refrigerant heat exchanger 16 during cooling operation, and controls the refrigerant pressure flowing into the heat source side heat exchanger 14 during heating operation. The water-refrigerant heat exchanger 16 exchanges heat between water and refrigerant, and heats or cools the circulating water to a target temperature using the heat of the refrigerant. The heat source side control device 17 controls the operating frequency of the compressor 12, the rotation speed of the heat source side pump 11, the valve opening of the throttling device 15, and the flow path switching valve 13.
　熱源側制御装置１７は、例えば、専用のハードウェア、または記憶部（図示せず）に格納されるプログラムを実行するＣＰＵ（Central Processing Unit、中央処理装置、処理装置、演算装置、マイクロプロセッサ、プロセッサともいう）で構成される。熱源側制御装置１７が専用のハードウェアである場合、熱源側制御装置１７は、例えば、単一回路、複合回路、ＡＳＩＣ（Application Specific Integrated Circuit）、ＦＰＧＡ（Field-Programmable Gate Array）、またはこれらを組み合わせたものが該当する。熱源側制御装置１７が実現する各機能部のそれぞれを、個別のハードウェアで実現してもよいし、各機能部を一つのハードウェアで実現してもよい。熱源側制御装置１７がＣＰＵの場合、熱源側制御装置１７が実行する各機能は、ソフトウェア、ファームウェア、またはソフトウェアとファームウェアとの組み合わせにより実現される。ソフトウェアおよびファームウェアはプログラムとして記述され、記憶部に格納される。ＣＰＵは、記憶部に格納されたプログラムを読み出して実行することにより、熱源側制御装置１７の各機能を実現する。ここで、記憶部は、各種情報を記憶するものであり、例えば、フラッシュメモリ、ＥＰＲＯＭ、および、ＥＥＰＲＯＭなどの、データの書き換え可能な不揮発性の半導体メモリを備えている。なお、熱源側制御装置１７の機能の一部を専用のハードウェアで実現し、一部をソフトウェアまたはファームウェアで実現するようにしてもよい。なお、負荷側制御装置４３および統合制御装置１も上記の熱源側制御装置１７と同じ構成である。 The heat source side control device 17 is composed of, for example, dedicated hardware, or a CPU (also called a central processing unit, processing device, arithmetic unit, microprocessor, or processor) that executes a program stored in a memory unit (not shown). When the heat source side control device 17 is dedicated hardware, the heat source side control device 17 is, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field-Programmable Gate Array), or a combination of these. Each of the functional units realized by the heat source side control device 17 may be realized by individual hardware, or each functional unit may be realized by a single piece of hardware. When the heat source side control device 17 is a CPU, each function executed by the heat source side control device 17 is realized by software, firmware, or a combination of software and firmware. The software and firmware are written as programs and stored in the memory unit. The CPU realizes each function of the heat source side control device 17 by reading and executing the programs stored in the memory unit. Here, the storage unit stores various information, and includes, for example, a non-volatile semiconductor memory that allows data to be rewritten, such as a flash memory, an EPROM, and an EEPROM. Note that some of the functions of the heat source side control device 17 may be realized by dedicated hardware, and some by software or firmware. Note that the load side control device 43 and the integrated control device 1 have the same configuration as the heat source side control device 17 described above.
　負荷側熱交換器４１は、熱源機１０から送水される冷温水とファンによって供給される空気との間で熱交換を行い、空気を加熱または冷却するものである。負荷側熱交換器４１は、暖房運転時には空気を加熱し、冷房運転時には空気を冷却する。そして、加熱あるいは冷却された空気が空調対象空間（室内）へ供給され、暖房あるいは冷房が行われる。流量調整弁４２は、弁開度を調整することができる電子式の弁であり、設けられた配管を通過する水流量を調整する弁である。流量調整弁４２によって各水回路３０ａ、３０ｂ、３０ｃの水循環量を調節することで、空調対象空間（室内）への冷温熱供給能力が調節される。負荷側制御装置４３は、流量調整弁４２の弁開度を制御するものである。 The load-side heat exchanger 41 exchanges heat between hot and cold water sent from the heat source unit 10 and air supplied by a fan to heat or cool the air. The load-side heat exchanger 41 heats the air during heating operation and cools the air during cooling operation. The heated or cooled air is then supplied to the space to be air-conditioned (indoors) to perform heating or cooling. The flow rate control valve 42 is an electronic valve that can adjust the valve opening, and is a valve that adjusts the water flow rate passing through the installed piping. The flow rate control valve 42 adjusts the water circulation amount of each water circuit 30a, 30b, 30c, thereby adjusting the hot and cold heat supply capacity to the space to be air-conditioned (indoors). The load-side control device 43 controls the valve opening of the flow rate control valve 42.
　また、実施の形態に係る空気調和システムは、複数の流量調整弁４２ａ、４２ｂが全て全閉となった場合の閉塞状態を回避するため、室内機４０と並列して設けられたバイパス回路５０を備えている。 The air conditioning system according to the embodiment also includes a bypass circuit 50 provided in parallel with the indoor unit 40 to avoid a blocked state that would occur if all of the multiple flow rate control valves 42a, 42b were fully closed.
　また、図１に示す単式の空調システムでは、バイパス回路５０には、バイパス回路５０の水流量を調整するためのバイパス用流量調整弁５１が設けられている。一方、図２に示す複式の空調システムでは、負荷側の水流量を調節するための負荷側ポンプ１０１が負荷側に設けられており、負荷側ポンプ１０１と熱源側ポンプ１１との連携制御によりバイパス回路５０の水流量を調節するため、バイパス用流量調整弁５１は省略することができる。 In addition, in the simplex air conditioning system shown in FIG. 1, the bypass circuit 50 is provided with a bypass flow control valve 51 for adjusting the water flow rate of the bypass circuit 50. On the other hand, in the duplex air conditioning system shown in FIG. 2, a load-side pump 101 for adjusting the water flow rate on the load side is provided on the load side, and the water flow rate of the bypass circuit 50 is adjusted by coordinated control of the load-side pump 101 and the heat source-side pump 11, so the bypass flow control valve 51 can be omitted.
　水冷媒熱交換器１６ａ、１６ｂ、１６ｃの水流路の出口側には、水冷媒熱交換器１６ａ、１６ｂ、１６ｃの出口水温Ｔｏｕｔを検知する出口水温センサ１８ａ、１８ｂ、１８ｃが設けられている。室内機４０ａ、４０ｂの吸い込み口には、室内機４０ａ、４０ｂの還気温度ＲＡを検知する還気温度センサ４４ａ、４４ｂが設けられている。室内機４０ａ、４０ｂの吹き出し口には、室内機４０ａ、４０ｂの給気温度ＳＡを検知する給気温度センサ４５ａ、４５ｂが設けられている。 Outlet water temperature sensors 18a, 18b, 18c are provided on the outlet side of the water flow path of the water- refrigerant heat exchangers 16a, 16b, 16c to detect the outlet water temperature Tout of the water- refrigerant heat exchangers 16a, 16b, 16c. Return air temperature sensors 44a, 44b are provided on the intake ports of the indoor units 40a, 40b to detect the return air temperature RA of the indoor units 40a, 40b. Supply air temperature sensors 45a, 45b are provided on the exhaust ports of the indoor units 40a, 40b to detect the supply air temperature SA of the indoor units 40a, 40b.
　また、図１に示す単式の空調システムでは、バイパス回路５０の差圧すなわちバイパス回路５０の上流側と下流側との間の水の差圧であるバイパス差圧ΔＰを計測する差圧計６１、および、負荷側の合計水流量を計測する負荷側流量計７１を備えている。ここで、負荷側流量計７１は、例えば水回路３０ａ、３０ｂ、３０ｃの負荷側において各負荷側熱交換器４１ａ、４１ｂを流れる冷温水の合流点よりも下流側に設けられている。一方、図２に示す複式の空調システムでは、差圧計６１および負荷側流量計７１に加え、熱源側の合計水流量を計測する熱源側流量計９１を備えている。ここで、熱源側流量計９１は、例えば水回路３０ａ、３０ｂ、３０ｃの熱源側において各負荷側熱交換器４１ａ、４１ｂを流れる冷温水の合流点よりも下流側に設けられている。なお、熱源側流量計９１に代えて、各熱源機１０ａ、１０ｂ、１０ｃの水流量を求められるように、各水冷媒熱交換器１６ａ、１６ｂ、１６ｃの前後差圧すなわち各水冷媒熱交換器１６ａ、１６ｂ、１６ｃの上流側と下流側との間に水の差圧を計測する手段を設けてもよい。ここで、各熱源機１０ａ、１０ｂ、１０ｃの水流量は、例えば差圧の比例係数（例えば０．５乗）に比例するものとして求める。なお、差圧の比例係数は、設計段階の試験などにより決定する。 The simplex air conditioning system shown in FIG. 1 is provided with a differential pressure gauge 61 for measuring the bypass differential pressure ΔP of the bypass circuit 50, i.e., the differential pressure of water between the upstream side and downstream side of the bypass circuit 50, and a load side flow meter 71 for measuring the total water flow rate on the load side. Here, the load side flow meter 71 is provided, for example, downstream of the junction of the cold and hot water flowing through each load side heat exchanger 41a, 41b on the load side of the water circuits 30a, 30b, 30c. On the other hand, the duplex air conditioning system shown in FIG. 2 is provided with a heat source side flow meter 91 for measuring the total water flow rate on the heat source side in addition to the differential pressure gauge 61 and the load side flow meter 71. Here, the heat source side flow meter 91 is provided, for example, downstream of the junction of the cold and hot water flowing through each load side heat exchanger 41a, 41b on the heat source side of the water circuits 30a, 30b, 30c. Instead of the heat source side flow meter 91, a means for measuring the differential pressure between the upstream and downstream sides of each water- refrigerant heat exchanger 16a, 16b, 16c, i.e., the water pressure difference between the upstream and downstream sides of each water- refrigerant heat exchanger 16a, 16b, 16c, may be provided so that the water flow rate of each heat source unit 10a, 10b, 10c can be obtained. Here, the water flow rate of each heat source unit 10a, 10b, 10c is obtained as being proportional to, for example, a proportionality coefficient of the differential pressure (for example, 0.5 power). The proportionality coefficient of the differential pressure is determined by testing at the design stage, etc.
　図３は、実施の形態に係る空気調和システムの室内機４０がＦＣＵである場合の各制御対象のブロック線図である。図４は、実施の形態に係る空気調和システムの室内機４０がＡＨＵである場合の各制御対象のブロック線図である。図５は、実施の形態に係る空気調和システムの室内機４０がＦＣＵである場合の従来例と比較した各制御対象のブロック線図である。図６は、実施の形態に係る空気調和システムの室内機４０がＡＨＵである場合の従来例と比較した各制御対象のブロック線図である。図７は、実施の形態に係る空気調和システムの従来例と比較した暖房運転時の効果を示す図である。図８は、実施の形態に係る空気調和システムの従来例と比較した冷房運転時の効果を示す図である。 FIG. 3 is a block diagram of each control object when the indoor unit 40 of the air conditioning system according to the embodiment is an FCU. FIG. 4 is a block diagram of each control object when the indoor unit 40 of the air conditioning system according to the embodiment is an AHU. FIG. 5 is a block diagram of each control object compared with a conventional example when the indoor unit 40 of the air conditioning system according to the embodiment is an FCU. FIG. 6 is a block diagram of each control object compared with a conventional example when the indoor unit 40 of the air conditioning system according to the embodiment is an AHU. FIG. 7 is a diagram showing the effect during heating operation compared with the conventional example of the air conditioning system according to the embodiment. FIG. 8 is a diagram showing the effect during cooling operation compared with the conventional example of the air conditioning system according to the embodiment.
　次に、実施の形態に係る単式の空気調和システムの基本的な動作について説明する。 Next, we will explain the basic operation of the single-type air conditioning system according to the embodiment.
[制御対象が室内機４０]
　図３に示すように、室内機４０がＦＣＵ（ファンコイルユニット）の場合、ＦＣＵである室内機４０への還気温度ＲＡ（≒室内の温度）を被制御量として、流量調整弁４２の弁開度が操作量となる。また、被制御量である還気温度ＲＡの目標値は、設定温度Ｔｓｅｔである。なお、この設定温度Ｔｓｅｔは、ユーザによって設定される。つまり、還気温度ＲＡが設定温度Ｔｓｅｔとなるように、流量調整弁４２の弁開度が操作される。また、図４に示すように、室内機４０がＡＨＵ（エアハンドリングユニット）の場合、ＡＨＵである室内機４０からの給気温度ＳＡを被制御量として、流量調整弁４２の弁開度が操作量となる。また、被制御量である給気温度ＳＡの目標値は、設定温度Ｔｓｅｔである。なお、この設定温度Ｔｓｅｔは、あらかじめ設定される。つまり、給気温度ＳＡが設定温度Ｔｓｅｔとなるように、流量調整弁４２の弁開度が操作される。また、室内機４０がＡＨＵである場合には、吹き出し口から供給される風量を調整するためのダンパ（図示せず）が設けられており、還気温度ＲＡに基づいて、開度が操作される。なお、室内機４０がＡＨＵの場合、流量調整弁４２の操作の目標値である設定温度Ｔｓｅｔは、例えば、冷房運転であれば十分に冷えた風となるように１６℃に設定したり、暖房運転であればユーザが肌寒さを感じないように４５℃に設定したりするとよい。 [Control target is indoor unit 40]
As shown in FIG. 3, when the indoor unit 40 is an FCU (fan coil unit), the return air temperature RA (≒ indoor temperature) to the indoor unit 40, which is an FCU, is the controlled quantity, and the valve opening of the flow rate control valve 42 is the manipulated variable. The target value of the return air temperature RA, which is the controlled quantity, is the set temperature Tset. Note that this set temperature Tset is set by the user. That is, the valve opening of the flow rate control valve 42 is manipulated so that the return air temperature RA becomes the set temperature Tset. As shown in FIG. 4, when the indoor unit 40 is an AHU (air handling unit), the supply air temperature SA from the indoor unit 40, which is an AHU, is the controlled quantity, and the valve opening of the flow rate control valve 42 is the manipulated variable. The target value of the supply air temperature SA, which is the controlled quantity, is the set temperature Tset. Note that this set temperature Tset is set in advance. That is, the valve opening of the flow rate control valve 42 is manipulated so that the supply air temperature SA becomes the set temperature Tset. Furthermore, if the indoor unit 40 is an AHU, a damper (not shown) is provided to adjust the amount of air supplied from the air outlet, and the opening degree is controlled based on the return air temperature RA. If the indoor unit 40 is an AHU, the set temperature Tset, which is the target value for the operation of the flow rate control valve 42, may be set to, for example, 16° C. in cooling operation so that the air is sufficiently cold, or to 45° C. in heating operation so that the user does not feel chilly.
[制御対象が熱源機１０]
　図３および図４に示すように、水冷媒熱交換器１６の出口水温Ｔｏｕｔを被制御量として、圧縮機１２の周波数が操作量となる。また、被制御量である出口水温Ｔｏｕｔの目標値は、後述する目標水温Ｔｗｔｇである。つまり、出口水温Ｔｏｕｔが目標水温Ｔｗｔｇとなるように、圧縮機１２の周波数が操作される。 [Control target is heat source unit 10]
3 and 4, the outlet water temperature Tout of the water-refrigerant heat exchanger 16 is a controlled variable, and the frequency of the compressor 12 is a manipulated variable. The target value of the outlet water temperature Tout, which is the controlled variable, is a target water temperature Twtg, which will be described later. That is, the frequency of the compressor 12 is manipulated so that the outlet water temperature Tout becomes the target water temperature Twtg.
　また、実施の形態に係る単式の空気調和システムにおいて、熱源側ポンプ１１およびバイパス用流量調整弁５１は、バイパス差圧ΔＰが目標差圧ΔＰｔｇｔとなるように連携して操作される。熱源側ポンプ１１およびバイパス用流量調整弁５１の連携操作としては、例えば、バイパス差圧ΔＰが目標差圧ΔＰｔｇｔより不足している場合は熱源側ポンプ１１の増速よりバイパス用流量調整弁５１の弁閉動作が優先され、バイパス差圧ΔＰが目標差圧ΔＰｔｇｔより過剰の場合はバイパス用流量調整弁５１の弁開動作より熱源側ポンプ１１の減速が優先されるような、省エネ性を重視した排他的な操作が一般的である。ここで、目標差圧ΔＰｔｇｔは、実際の空気調和システムをチューニングすることにより求められ、例えば、流量調整弁４２の弁開度が全開時に、室内機４０に定格流量が流れる際の熱源機１０の前後差圧すなわち熱源機１０の上流側と下流側との間に水の差圧を測定し、その値を目標差圧ΔＰｔｇｔに設定する。 Furthermore, in the single air conditioning system according to the embodiment, the heat source side pump 11 and the bypass flow control valve 51 are operated in coordination so that the bypass differential pressure ΔP becomes the target differential pressure ΔPtgt. The coordinated operation of the heat source side pump 11 and the bypass flow control valve 51 is generally an exclusive operation that emphasizes energy saving, in which, for example, when the bypass differential pressure ΔP is less than the target differential pressure ΔPtgt, the valve closing operation of the bypass flow control valve 51 takes precedence over increasing the speed of the heat source side pump 11, and when the bypass differential pressure ΔP is more than the target differential pressure ΔPtgt, the deceleration of the heat source side pump 11 takes precedence over the valve opening operation of the bypass flow control valve 51. Here, the target differential pressure ΔPtgt is obtained by tuning the actual air conditioning system. For example, when the flow control valve 42 is fully open, the differential pressure before and after the heat source unit 10, i.e., the differential pressure of water between the upstream and downstream sides of the heat source unit 10, is measured when the rated flow rate flows through the indoor unit 40, and this value is set as the target differential pressure ΔPtgt.
　また、実施の形態に係る複式の空気調和システムにおいて、熱源側ポンプ１１は上述した単式の空気調和システムと同じように操作される。また、負荷側ポンプ１０１はその前後差圧すなわち負荷側ポンプ１０１の上流側と下流側との間の水の差圧を被制御量として、その差圧が負荷側の室内機４０に冷温水を流すのに必要な目標差圧ΔＰｔｇｔとなるように操作される。熱源側ポンプ１１は、バイパス回路５０の流量を最小化するように操作される。例えば、熱源側ポンプ１１は、負荷側流量計７１の計測値より熱源側流量計９１の計測値が僅かに大きくなるように操作される。なお、流量調整弁４２の弁開度および圧縮機１２の周波数の操作は、基本的に上述した単式の空気調和システムと変わらない。 In the duplex air conditioning system according to the embodiment, the heat source pump 11 is operated in the same manner as in the simplex air conditioning system described above. The load pump 101 is operated so that the differential pressure between its upstream and downstream sides, that is, the differential pressure of water between the upstream and downstream sides of the load pump 101, becomes the target differential pressure ΔPtgt required to flow cold and hot water to the load side indoor unit 40. The heat source pump 11 is operated so as to minimize the flow rate of the bypass circuit 50. For example, the heat source pump 11 is operated so that the measurement value of the heat source side flow meter 91 is slightly larger than the measurement value of the load side flow meter 71. The operation of the valve opening of the flow control valve 42 and the frequency of the compressor 12 is basically the same as in the simplex air conditioning system described above.
　次に、実施の形態に係る単式の空気調和システムの特徴的な動作について説明する。 Next, we will explain the characteristic operation of the single-type air conditioning system according to the embodiment.
[制御対象が空気調和システム]
　実施の形態では、目標水温Ｔｗｔｇが、不冷および不暖とならない範囲で省エネルギー性が向上するように操作される。つまり、冷房運転なら目標水温Ｔｗｔｇが高くなるように操作され、暖房運転なら目標水温Ｔｗｔｇが低くなるように操作される。具体的には、目標水温Ｔｗｔｇの操作の被制御量は、流量調整弁４２の操作の被制御量と同じものを採用する。つまり、図３に示すように、室内機４０がＦＣＵの場合、ＦＣＵである室内機４０への還気温度ＲＡを被制御量として、目標水温Ｔｗｔｇが操作量となる。また、被制御量である還気温度ＲＡの目標値は、一般的にユーザが設定する設定温度Ｔｓｅｔにオフセットした値、つまり設定温度Ｔｓｅｔ±αである。また、図４に示すように、室内機４０がＡＨＵの場合、ＡＨＵである室内機４０からの給気温度ＳＡを被制御量として、目標水温Ｔｗｔｇが操作量となる。また、被制御量である給気温度ＳＡの目標値は、一般的にユーザが設定する設定温度Ｔｓｅｔに対してオフセットした値、つまり設定温度Ｔｓｅｔ±αである。なお、目標水温Ｔｗｔｇの操作の目標値である設定温度Ｔｓｅｔ±αは、流量調整弁４２の操作の目標値である設定温度Ｔｓｅｔと比べて、冷房運転時は設定温度Ｔｓｅｔに対して高温側にオフセットした値（Ｔｓｅｔ＋α）、暖房運転時は設定温度Ｔｓｅｔに対して低温側にオフセットした値（Ｔｓｅｔ－α）に設定する。 [Control target is air conditioning system]
In the embodiment, the target water temperature Twtg is operated so that energy saving is improved within a range where the cooling and heating are not insufficient. That is, in the case of cooling operation, the target water temperature Twtg is operated so as to be higher, and in the case of heating operation, the target water temperature Twtg is operated so as to be lower. Specifically, the controlled amount of the operation of the target water temperature Twtg is the same as the controlled amount of the operation of the flow rate control valve 42. That is, as shown in FIG. 3, when the indoor unit 40 is an FCU, the return air temperature RA to the indoor unit 40, which is an FCU, is the controlled amount, and the target water temperature Twtg is the manipulated amount. In addition, the target value of the return air temperature RA, which is the controlled amount, is generally a value offset to the set temperature Tset set by the user, that is, the set temperature Tset±α. In addition, as shown in FIG. 4, when the indoor unit 40 is an AHU, the supply air temperature SA from the indoor unit 40, which is an AHU, is the controlled amount, and the target water temperature Twtg is the manipulated amount. Furthermore, the target value of the supply air temperature SA, which is a controlled variable, is generally an offset value relative to the set temperature Tset set by the user, that is, the set temperature Tset±α. The set temperature Tset±α, which is the target value for the operation of the target water temperature Twtg, is set to a value (Tset+α) offset to a higher temperature than the set temperature Tset during cooling operation, and to a value (Tset-α) offset to a lower temperature than the set temperature Tset during heating operation, compared to the set temperature Tset, which is the target value for the operation of the flow rate control valve 42.
　流量調整弁４２の開度信号を演算装置に取り込まない場合、図５～図８の各（ａ）に示すように従来の第一制御方法では、目標水温Ｔｗｔｇが固定値であり、還気温度ＲＡまたは給気温度ＳＡが設定温度Ｔｓｅｔとなるように流量調整弁４２の弁開度が操作され、出口水温Ｔｏｕｔが目標水温Ｔｗｔｇとなるように圧縮機１２の周波数が操作されていた。また、図５～図８の各（ｂ）に示すように従来の第二制御方法では、目標水温Ｔｗｔｇが可変値であり、還気温度ＲＡまたは給気温度ＳＡが設定温度Ｔｓｅｔとなるように流量調整弁４２の弁開度および目標水温Ｔｗｔｇが操作され、出口水温Ｔｏｕｔが目標水温Ｔｗｔｇとなるように圧縮機１２の周波数が操作されていた。しかし、これらの制御方法では、流量調整弁４２の弁開度および目標水温Ｔｗｔｇが目標値に到達していると変化しない。 When the opening signal of the flow control valve 42 is not input to the calculation device, as shown in each of (a) of Figures 5 to 8, in the conventional first control method, the target water temperature Twtg is a fixed value, the valve opening of the flow control valve 42 is operated so that the return air temperature RA or the supply air temperature SA becomes the set temperature Tset, and the frequency of the compressor 12 is operated so that the outlet water temperature Tout becomes the target water temperature Twtg. Also, as shown in each of (b) of Figures 5 to 8, in the conventional second control method, the target water temperature Twtg is a variable value, the valve opening of the flow control valve 42 and the target water temperature Twtg are operated so that the return air temperature RA or the supply air temperature SA becomes the set temperature Tset, and the frequency of the compressor 12 is operated so that the outlet water temperature Tout becomes the target water temperature Twtg. However, in these control methods, the valve opening of the flow control valve 42 and the target water temperature Twtg do not change once they have reached their target values.
　それに対して、図５～図８の各（ｃ）に示すように実施の形態に係る制御方法では、流量調整弁４２の弁開度が全開になるまで、または、目標水温Ｔｗｔｇが設定可能な限界値に至るまで、自動的に省エネルギーに向かう方向に変化する。そのため、実施の形態に係る制御方法では、従来の制御方法に比べて、不冷および不暖とならない範囲で省エネルギー性を向上させることができる。 In contrast, as shown in each of (c) of Figures 5 to 8, in the control method according to the embodiment, the valve opening of the flow control valve 42 automatically changes in a direction toward energy conservation until the valve opening degree reaches full opening, or until the target water temperature Twtg reaches the settable limit value. Therefore, compared to conventional control methods, the control method according to the embodiment can improve energy conservation to a degree that does not result in insufficient cooling or heating.
　なお、空気調和システムが室内機４０を複数備えており、それぞれの設定温度Ｔｓｅｔ、あるいは還気温度ＲＡまたは給気温度ＳＡが異なる場合は、例えば、その未達温度幅、つまり設定温度Ｔｓｅｔと還気温度ＲＡまたは給気温度ＳＡとの差が最も大きい室内機４０を代表として、その室内機４０の設定温度Ｔｓｅｔと還気温度ＲＡまたは給気温度ＳＡとを用いて、上記に示した制御を行えばよい。 In addition, if the air conditioning system has multiple indoor units 40 and each has a different set temperature Tset or a different return air temperature RA or supply air temperature SA, then, for example, the indoor unit 40 with the largest unachieved temperature width, i.e., the largest difference between the set temperature Tset and the return air temperature RA or supply air temperature SA, can be used as a representative and the above-described control can be performed using the set temperature Tset and return air temperature RA or supply air temperature SA of that indoor unit 40.
　なお、実施の形態に係る複式の空気調和システムの特徴的な動作について上記と同様である。 The characteristic operation of the duplex air conditioning system according to the embodiment is the same as described above.
　また、流量調整弁４２および目標水温Ｔｗｔｇの操作において、被制御量に不感帯が設けられている場合は、目標値が不感帯に重ならないようにオフセットする。つまり、設定温度Ｔｓｅｔおよび設定温度Ｔｓｅｔ±αに対してオフセットし、不感帯に重ならない値にする。 In addition, when operating the flow rate control valve 42 and the target water temperature Twtg, if a dead band is set for the controlled variable, the target value is offset so that it does not overlap with the dead band. In other words, the set temperature Tset and the set temperature Tset±α are offset to a value that does not overlap with the dead band.
　また、実施の形態では、目標水温Ｔｗｔｇの操作に関して、被制御量が目標値過達の時は目標水温Ｔｗｔｇが省エネ側に変化し、被制御量が目標値未達の時は目標水温Ｔｗｔｇが冷房／暖房能力が増加する側に変化するが、被制御量が一時的に目標値未達により不冷あるいは不暖の状態となった際に迅速にリカバリーできるように、被制御量の制御偏差の絶対値に対して操作量を変化させる幅の絶対値を、目標値過達時よりも大きくしてもよい。つまり、還気温度ＲＡまたは給気温度ＳＡが設定温度Ｔｓｅｔに対して過達時よりも未達時の方が、目標水温Ｔｗｔｇの変化幅を大きくする。ここで、目標値未達とは、被制御量が目標値に達していないこと、つまり被制御量＜目標値を意味し、目標値過達とは、被制御量が目標値を超えていること、つまり被制御量＞目標値を意味する。 Furthermore, in the embodiment, with regard to the operation of the target water temperature Twtg, when the controlled quantity exceeds the target value, the target water temperature Twtg changes to the energy saving side, and when the controlled quantity falls short of the target value, the target water temperature Twtg changes to the side of increasing the cooling/heating capacity, but in order to quickly recover when the controlled quantity temporarily falls short of the target value and becomes incooled or insufficient to heat, the absolute value of the range by which the operation quantity is changed relative to the absolute value of the control deviation of the controlled quantity may be made larger than when the target value is exceeded. In other words, the range of change in the target water temperature Twtg is made larger when the return air temperature RA or the supply air temperature SA does not reach the set temperature Tset than when it exceeds it. Here, "not reaching the target value" means that the controlled quantity has not reached the target value, i.e., the controlled quantity < the target value, and "overreaching the target value" means that the controlled quantity exceeds the target value, i.e., the controlled quantity > the target value.
　以上、実施の形態に係る空気調和システムは、負荷側熱交換器４１および流量調整弁４２を有する室内機４０と、圧縮機１２、熱源側熱交換器１４、水冷媒熱交換器１６、および熱源側ポンプ１１を有する熱源機１０と、室内機４０の還気温度ＲＡを検知する還気温度センサ４４または室内機４０の給気温度ＳＡを検知する給気温度センサ４５と、水冷媒熱交換器１６の出口水温Ｔｏｕｔを検知する出口水温センサ１８と、還気温度ＲＡまたは給気温度ＳＡが設定温度Ｔｓｅｔとなるように流量調整弁４２の弁開度を制御し、出口水温Ｔｏｕｔが目標水温Ｔｗｔｇとなるように圧縮機１２の周波数を制御し、還気温度ＲＡまたは給気温度ＳＡが目標値となるように目標水温Ｔｗｔｇを制御する熱源側制御装置１７と、を備え、目標値は、設定温度Ｔｓｅｔに対してオフセットした値である。 The air conditioning system according to the embodiment includes an indoor unit 40 having a load-side heat exchanger 41 and a flow control valve 42, a heat source unit 10 having a compressor 12, a heat source-side heat exchanger 14, a water-refrigerant heat exchanger 16, and a heat source-side pump 11, a return air temperature sensor 44 that detects the return air temperature RA of the indoor unit 40 or a supply air temperature sensor 45 that detects the supply air temperature SA of the indoor unit 40, an outlet water temperature sensor 18 that detects the outlet water temperature Tout of the water-refrigerant heat exchanger 16, and a heat source-side control device 17 that controls the valve opening of the flow control valve 42 so that the return air temperature RA or the supply air temperature SA becomes the set temperature Tset, controls the frequency of the compressor 12 so that the outlet water temperature Tout becomes the target water temperature Twtg, and controls the target water temperature Twtg so that the return air temperature RA or the supply air temperature SA becomes the target value, and the target value is a value offset from the set temperature Tset.
　実施の形態に係る空気調和システムによれば、流量調整弁４２の弁開度情報を外部に出力して、その情報をシステム全体を制御する統合制御装置１に取り込む必要がないため、簡素な構成かつ低コストで実現可能となり、また、既築向けに本システムを導入することが可能となる。また、還気温度ＲＡまたは給気温度ＳＡが設定温度Ｔｓｅｔにオフセットした値となるように目標水温Ｔｗｔｇを制御するため、不冷および不暖とならない範囲で省エネルギー性を向上させることができる。 According to the air conditioning system of the embodiment, there is no need to output valve opening information of the flow control valve 42 to the outside and import that information into the integrated control device 1 that controls the entire system, so it can be realized with a simple configuration and low cost, and it is also possible to introduce this system into existing buildings. In addition, since the target water temperature Twtg is controlled so that the return air temperature RA or the supply air temperature SA is a value offset from the set temperature Tset, it is possible to improve energy conservation within a range that does not result in insufficient cooling or heating.
　また、実施の形態に係る空気調和システムにおいて、統合制御装置１は、還気温度ＲＡまたは給気温度ＳＡが設定温度Ｔｓｅｔに対して過達時よりも未達時の方が、目標水温Ｔｗｔｇの変化幅を大きくする。 In addition, in the air conditioning system according to the embodiment, the integrated control device 1 increases the range of change in the target water temperature Twtg when the return air temperature RA or the supply air temperature SA does not reach the set temperature Tset compared to when it exceeds the set temperature Tset.
　実施の形態に係る空気調和システムによれば、被制御量が一時的に目標値未達により不冷あるいは不暖の状態となった際のリカバリーを迅速に行うことができる。 The air conditioning system according to the embodiment can quickly recover from the situation where the controlled variable temporarily does not reach the target value, resulting in insufficient cooling or heating.
　１　統合制御装置、１０　熱源機、１０ａ～１０ｃ　熱源機、１１　熱源側ポンプ、１１ａ～１１ｃ　熱源側ポンプ、１２　圧縮機、１２ａ～１２ｃ　圧縮機、１３　流路切替弁、１３ａ～１３ｃ　流路切替弁、１４　熱源側熱交換器、１４ａ～１４ｃ　熱源側熱交換器、１５　絞り装置、１５ａ～１５ｃ　絞り装置、１６　水冷媒熱交換器、１６ａ～１６ｃ　水冷媒熱交換器、１７　熱源側制御装置、１７ａ～１７ｃ　熱源側制御装置、１８　出口水温センサ、１８ａ～１８ｃ　出口水温センサ、２０ａ～２０ｃ　冷媒回路、３０ａ～３０ｃ　水回路、４０　室内機、４０ａ～４０ｂ　室内機、４１　負荷側熱交換器、４１ａ～４１ｂ　負荷側熱交換器、４２　流量調整弁、４２ａ～４２ｂ　流量調整弁、４３　負荷側制御装置、４３ａ～４３ｂ　負荷側制御装置、４４　還気温度センサ、４４ａ～４４ｂ　還気温度センサ、４５　給気温度センサ、４５ａ～４５ｂ　給気温度センサ、
５０　バイパス回路、５１　バイパス用流量調整弁、６１　差圧計、７１　負荷側流量計、９１　熱源側流量計、１０１　負荷側ポンプ。 1 Integrated control device, 10 Heat source device, 10a to 10c Heat source device, 11 Heat source side pump, 11a to 11c Heat source side pump, 12 Compressor, 12a to 12c Compressor, 13 Flow path switching valve, 13a to 13c Flow path switching valve, 14 Heat source side heat exchanger, 14a to 14c Heat source side heat exchanger, 15 Throttle device, 15a to 15c Throttle device, 16 Water refrigerant heat exchanger, 16a to 16c Water refrigerant heat exchanger, 17 Heat source side control device, 17a to 17c Heat source side control device, 18 Outlet water temperature sensor, 18a to 18c Outlet water temperature sensor, 20a to 20c Refrigerant circuit, 30a to 30c Water circuit, 40 Indoor unit, 40a to 40b Indoor unit, 41 Load side heat exchanger, 41a to 41b Load side heat exchanger, 42 Flow control valve, 42a to 42b flow control valve, 43 load side control device, 43a to 43b load side control device, 44 return air temperature sensor, 44a to 44b return air temperature sensor, 45 supply air temperature sensor, 45a to 45b supply air temperature sensor,
50 bypass circuit, 51 bypass flow control valve, 61 differential pressure gauge, 71 load side flow meter, 91 heat source side flow meter, 101 load side pump.

Claims (3)

  1. 　負荷側熱交換器および流量調整弁を有する室内機と、
    　圧縮機、熱源側熱交換器、水冷媒熱交換器、および熱源側ポンプを有する熱源機と、
    　前記室内機の還気温度を検知する還気温度センサまたは前記室内機の給気温度を検知する給気温度センサと、
    　前記水冷媒熱交換器の出口水温を検知する出口水温センサと、
    　前記還気温度または前記給気温度が設定温度となるように前記流量調整弁の弁開度を制御し、前記出口水温が目標水温となるように前記圧縮機の周波数を制御し、前記還気温度または前記給気温度が目標値となるように前記目標水温を制御する統合制御装置と、を備え、
    　前記目標値は、前記設定温度に対してオフセットした値である
    　空気調和システム。     an indoor unit having a load-side heat exchanger and a flow control valve;
    a heat source unit having a compressor, a heat source side heat exchanger, a water-refrigerant heat exchanger, and a heat source side pump;
    A return air temperature sensor that detects the return air temperature of the indoor unit or a supply air temperature sensor that detects the supply air temperature of the indoor unit;
    An outlet water temperature sensor that detects an outlet water temperature of the water-refrigerant heat exchanger;
    an integrated control device that controls a valve opening degree of the flow control valve so that the return air temperature or the supply air temperature becomes a set temperature, controls a frequency of the compressor so that the outlet water temperature becomes a target water temperature, and controls the target water temperature so that the return air temperature or the supply air temperature becomes a target value;
    The air conditioning system, wherein the target value is an offset value with respect to the set temperature.
  2. 　前記統合制御装置は、
    　前記還気温度または前記給気温度が前記設定温度に対して過達時よりも未達時の方が、前記目標水温の変化幅を大きくする
    　請求項１に記載の空気調和システム。     The integrated control device includes:
    The air conditioning system according to claim 1 , wherein the range of change in the target water temperature is made larger when the return air temperature or the supply air temperature does not reach the set temperature than when it exceeds the set temperature.
  3. 　冷房運転および暖房運転が可能な空気調和システムであって、
    　前記目標値は、冷房運転時には前記設定温度に対して高温側にオフセットした値であり、暖房運転時には前記設定温度に対して低温側にオフセットした値である
    　請求項１または２に記載の空気調和システム。     An air conditioning system capable of cooling and heating operations,
    The air conditioning system according to claim 1 or 2, wherein the target value is a value offset to a higher temperature side with respect to the set temperature during cooling operation, and is a value offset to a lower temperature side with respect to the set temperature during heating operation.
PCT/JP2022/037947 2022-10-12 2022-10-12 Air conditioning system WO2024079807A1 (en)

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008528922A (en) * 2005-02-02 2008-07-31 松下電工株式会社 Environmental equipment control system
WO2019116599A1 (en) * 2017-12-12 2019-06-20 日本ピーマック株式会社 Air-conditioning device and air-conditioning system

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008528922A (en) * 2005-02-02 2008-07-31 松下電工株式会社 Environmental equipment control system
WO2019116599A1 (en) * 2017-12-12 2019-06-20 日本ピーマック株式会社 Air-conditioning device and air-conditioning system

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