[go: up one dir, main page]

WO2019116599A1 - Dispositif de climatisation et système de climatisation - Google Patents

Dispositif de climatisation et système de climatisation Download PDF

Info

Publication number
WO2019116599A1
WO2019116599A1 PCT/JP2018/013249 JP2018013249W WO2019116599A1 WO 2019116599 A1 WO2019116599 A1 WO 2019116599A1 JP 2018013249 W JP2018013249 W JP 2018013249W WO 2019116599 A1 WO2019116599 A1 WO 2019116599A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
source water
heat source
temperature
air
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2018/013249
Other languages
English (en)
Japanese (ja)
Inventor
敏明 齋藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nippon Pmac Co Ltd
Original Assignee
Nippon Pmac Co Ltd
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 Nippon Pmac Co Ltd filed Critical Nippon Pmac Co Ltd
Publication of WO2019116599A1 publication Critical patent/WO2019116599A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/46—Improving electric energy efficiency or saving
    • 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
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/49—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring ensuring correct operation, e.g. by trial operation or configuration checks
    • 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
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • 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
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle

Definitions

  • the present invention relates to an air conditioner and an air conditioning system.
  • a water-to-air heat exchanger for indoor air conditioning is provided in parallel separately from a refrigerant-to-air heat exchanger for indoor air conditioning by heat pump and common to both these heat exchangers.
  • One switching fan is provided, and a switching damper is provided to select either or both of the heat exchangers for the air flow path of the fan, and the heat source water is the water-to-air heat exchanger and the heat pump.
  • a unit for air conditioning equipment has been proposed which is provided with piping equipment for supplying and circulating the water / refrigerant heat exchanger separately or both separately (for example, Patent Document 1).
  • an object of the present invention is to provide an air conditioning unit having a balance between comfort and energy saving.
  • the air conditioner is provided on the flow path of the heat source water, and a fan coil unit performing heat exchange between the heat source water and the air, and heat exchange is provided on the flow path between the heat source water and the heat transfer medium
  • the heat pump unit includes: a heat pump unit; a three-way valve provided on the flow path for branching heat source water to the fan coil side and the heat pump side; and a control device for controlling the three-way valve. Further, the control device controls the three-way valve so as to preferentially introduce the heat source water to the fan coil unit during partial load operation that operates at an output lower than the rated output of the air conditioner.
  • energy consumption can be improved by preferentially using a fan coil unit, where power consumption of the compressor tends to be large.
  • the fan coil unit includes a fan coil side heat exchanger that performs heat exchange between heat source water and air
  • the heat pump unit includes a compressor that compresses a heat medium, heat between heat medium and heat source water
  • First heat pump side hydrothermal medium heat exchanger for exchanging, first expansion valve for expanding a heat medium, heat pump side air heat medium heat exchanger for performing heat exchange between a heat medium and air, and Provided between the expansion valve and the heat pump side hydrothermal medium heat exchanger, and in the flow path of the heat source water before the first heat pump side
  • a second heat pump side hydrothermal medium heat exchanger that performs heat exchange may be provided.
  • the second heat pump side hydrothermal medium heat exchanger functions as a condenser particularly in a cooling operation performed with low-temperature heat source water in winter, or functions as an evaporator in a heating operation performed with high-temperature heat source water in summer. In any case, it is possible to reduce the load applied to the compressor provided in the heat pump unit and to improve energy saving.
  • a second expansion valve may be further provided between the second heat pump side hydrothermal medium heat exchanger and the heat pump side air thermal medium heat exchanger.
  • the three-way valve is a proportional valve, or further includes a proportional valve different from the three-way valve on the flow path of the heat source water
  • the control device controls the temperature of the heat source water at the heat source water inlet of the air conditioner and the air conditioner Based on the information indicating the relationship between the temperature difference of the heat source water at the heat source water outlet or the temperature difference of the heat source water at the heat source water outlet of the fan coil unit and the proportional valve opening degree, It may be controlled. In this manner, the flow rate can be adjusted by the temperature sensor without providing the flow rate sensor in the flow path of the heat source water.
  • the flow path of the heat source water is connected to a pump that changes the water supply amount of the heat source water
  • the control device is the temperature of the heat source water at the inlet of the heat source water of the air conditioner and the outlet of the heat source water of the air conditioner.
  • the water flow rate of the pump may be controlled based on information indicating the relationship between the temperature difference of the heat source water or the temperature difference of the heat source water at the heat source water outlet of the fan coil unit and the water flow rate of the pump. Even in this case, the flow rate can be adjusted by the temperature sensor without providing the flow rate sensor in the flow path of the heat source water.
  • the control device causes the heat pump unit to perform the heating operation when the cooling capacity becomes excessive to the predetermined set temperature.
  • the air conditioning system according to the invention may include a plurality of air conditioning devices and a temperature control device of heat source water.
  • operation modes such as a cooling operation, a heating operation, and a blowing operation can be changed for each of the above-described air conditioners.
  • heat recovery can be performed by the sending side of heat source water, and consumption energy can be reduced. Therefore, the system can reduce power consumption and realize ZEB (Zero Energy Building).
  • FIG. 1 is a diagram showing an example of an air conditioner according to the first embodiment.
  • the air conditioning apparatus 100 includes a fan coil unit 101, a heat pump unit 102, and a device common to these units in one casing.
  • the fan coil unit 101 is a device that performs heat exchange between heat source water and air supplied from a water heater or the like, and supplies air of a desired temperature by a blower fan.
  • the heat pump unit 102 includes a refrigeration cycle formed by a condenser, an expansion valve, an evaporator and a compressor, performs heat exchange between the cooling medium and the air, and an air of a desired temperature by a blower fan. Is a device that supplies Further, inside the air conditioning apparatus 100, the flow path 41 of the heat source water and the flow path 42 of the cooling / heating medium are provided.
  • the indoor humidity sensor 32, the apparatus outlet humidity sensor 37, and the two-way valve 13 are provided.
  • the blower fan 6 is commonly used for the fan coil unit 101 and the heat pump unit 102. That is, the blower fan 6 takes in, for example, the room air to be controlled in temperature, and discharges the air adjusted to a predetermined temperature by the heat exchangers of the fan coil unit 101 and the heat pump unit 102 into the room again.
  • the heat source water inlet temperature sensor 21, the indoor temperature sensor 22, the heat source water outlet temperature sensor 26, and the device outlet temperature sensor 27 are existing temperature sensors.
  • the heat source water inlet temperature sensor 21 is provided at the inlet of the flow path 41 of the heat source water inside the air conditioning apparatus 100, and measures the temperature of the heat source water introduced into the air conditioning apparatus 100.
  • the indoor temperature sensor 22 is provided in a room whose temperature is to be controlled, and measures the temperature in the room.
  • the heat source water outlet temperature sensor 26 is provided at the outlet of the flow path 41 of the heat source water inside the air conditioning apparatus 100, and measures the temperature of the heat source water flowing out of the air conditioning apparatus 100.
  • the device outlet temperature sensor 27 is provided at the outlet of the air conditioner 100, and measures the temperature of the air released by the air conditioner 100 into the room.
  • the indoor humidity sensor 32 and the apparatus blowing humidity sensor 37 are existing humidity sensors.
  • the indoor humidity sensor 32 is also provided in a room whose temperature is to be controlled, and measures the humidity in the room.
  • the air outlet humidity sensor 37 is provided at the outlet of the air conditioner 100, and measures the humidity of the air released into the room by the air conditioner 100.
  • the heat source water inlet temperature sensor 21, the indoor temperature sensor 22, the device outlet temperature sensor 27, the indoor humidity sensor 32, and the device outlet humidity sensor 37 output a signal corresponding to the measured temperature or humidity to the control device 7 described later.
  • the three-way valve 11 is a general valve, and in the present embodiment, a switching three-way valve. The three-way valve 11 causes the heat source water flowing into the air conditioner 100 to flow to the fan coil unit 101 side or the heat pump unit 102 side.
  • the two-way valve 13 is a general valve, and in this embodiment is a proportional two-way valve.
  • the two-way valve 13 is provided, for example, in the vicinity of the outlet of the flow passage 41 of the heat source water, and controls the flow rate of the heat source water flowing through the flow passage 41 of the heat source water by changing the opening degree.
  • the control device 7 includes a processing device such as a microcontroller and a processor, and is connected to a thermometer, a hygrometer, a valve, and the like included in the air conditioning device 100 by signal lines or wirelessly. Further, the control device 7 obtains a signal indicating temperature and humidity from a thermometer or a hygrometer, and controls opening and closing of a valve.
  • the fan coil unit 101 includes a fan coil side heat exchanger 1, a fan coil outlet temperature sensor 23, a fan coil outlet humidity sensor 33, and a heat source water fan coil outlet temperature sensor 24.
  • the fan coil side heat exchanger 1 is a heat exchanger which is provided on the flow path of the heat source water and performs heat exchange between the heat source water and the air.
  • the air is, for example, air in a room whose temperature is to be controlled.
  • the fan coil outlet temperature sensor 23 is an existing temperature sensor.
  • the fan coil outlet temperature sensor 23 is provided in the vicinity of the air outlet of the fan coil unit 101, and measures the temperature of air blown out through the fan coil side heat exchanger 1.
  • the fan coil blowing humidity sensor 33 is an existing humidity sensor.
  • the fan coil outlet humidity sensor 33 is also provided in the vicinity of the air outlet of the fan coil unit 101, and measures the humidity of air blown out through the fan coil side heat exchanger 1.
  • the heat source water fan coil outlet temperature sensor 24 is also an existing temperature sensor.
  • the heat source water fan coil outlet temperature sensor 24 is also provided near the outlet of the heat source water flow path of the fan coil unit 101, and measures the temperature of the air blown out through the fan coil side heat exchanger 1.
  • the fan coil outlet temperature sensor 23, the fan coil outlet humidity sensor 33, and the heat source water fan coil outlet temperature sensor 24 output a signal corresponding to the measured temperature or humidity to the control device 7 described later.
  • the heat pump unit 102 includes the heat pump side water heat medium heat exchanger 2, the expansion valve 3, the heat pump side air heat medium heat exchanger 4, the compressor 5, and the four-way valve 12 on the flow path of the cooling medium. , Form a refrigeration cycle. Further, the heat pump side air heat medium heat exchanger 4 includes a heat exchanger temperature sensor 28. The four-way valve 12 switches the flow path of the cooling medium between cooling and heating. The compressor 5 compresses a cooling medium, which is a low pressure gas, for example, into a high pressure and high temperature gas. The heat pump side water heat medium heat exchanger 2 is provided on the flow path of the heat source water and on the flow path of the cooling medium.
  • heat source water whose flow path is determined by the three-way valve 11 described later is introduced into the heat pump side water heat medium heat exchanger 2 via the fan coil unit 101 or not.
  • the cooling medium compressed by the compressor 5 is introduced to the heat pump side water heat exchanger 2 via the four-way valve 12 during cooling.
  • the heat pump side water heat medium heat exchanger 2 works as a condenser, and condenses, for example, a heat medium which is a high pressure gas into a high pressure liquid.
  • the cooling medium expanded by the expansion valve 3 is introduced.
  • the heat pump side water heat medium heat exchanger 2 works as an evaporator, and evaporates, for example, a heat medium which is a low pressure liquid into a low pressure gas.
  • the expansion valve 3 is, for example, an electronic expansion valve. Further, the expansion valve 3 decompresses the cooling medium, which is, for example, a high pressure liquid, to a low pressure liquid.
  • the heat pump side air heat medium heat exchanger 4 is provided on the flow path of the cooling medium and on the extension of the direction in which the blower fan 6 blows air. Further, the cooling medium which has been depressurized by the expansion valve 3 is introduced into the heat pump side air heat medium heat exchanger 4 at the time of cooling.
  • the heat pump side air heat transfer medium heat exchanger 4 functions as an evaporator, and evaporates, for example, a heat transfer medium which is a low pressure liquid into a low pressure gas. Further, at the time of heating, the cooling medium compressed by the compressor 5 is introduced through the four-way valve 12. At this time, the heat pump side water heat medium heat exchanger 2 works as a condenser, and condenses, for example, a heat medium which is a high pressure gas into a high pressure liquid.
  • FIG. 2 is a process flow diagram showing an example of the initialization process of the air conditioning apparatus 100.
  • the control device 7 of the air conditioning apparatus 100 performs, for example, the process shown in FIG. 2 after the air conditioning apparatus 100 is started.
  • the control device 7 acquires, for example, information preset by the user with respect to the air conditioner 100 (FIG. 2: S1).
  • the setting includes an operation mode indicating the type of operation such as a cooling operation and a heating operation, a temperature in the room during operation, a set temperature which is a target value of humidity, and a set humidity.
  • the set temperature is represented by Ts (° C.)
  • the set humidity is represented by Hs (%).
  • the control apparatus 7 acquires the output value of the sensor with which the air conditioning apparatus 100 is provided (S2).
  • a signal indicating a measured value is received from the indoor humidity sensor 32, the fan coil outlet humidity sensor 33, and the apparatus outlet humidity sensor 37, respectively.
  • the temperature of the heat source water at the inlet of the air conditioner 100 measured by the heat source water inlet temperature sensor 21 is Wa (° C.)
  • the indoor temperature measured by the indoor temperature sensor 22 is Ta (° C.)
  • the fan coil outlet temperature Tf (° C.) the outlet temperature of the fan coil unit 101 measured by the sensor 23
  • the temperature of the heat source water at the outlet of the air conditioner 100 measured by the sensor 26 is Wc (° C.)
  • the outlet temperature of the air conditioner 100 measured by the device outlet temperature sensor 27 is Tp (° C.)
  • the heat exchanger temperature sensor 28 The temperature of the heat pump side air heat medium heat exchanger 4 to be measured is Te (° C.), and the indoor humidity to be measured by the indoor humidity sensor 32 is Ha (%) Fan blowing humidity of the fan coil unit 101 in which the coil outlet humidity sensor 33 measures Hf (%), it is assumed that the balloon humidity
  • control device 7 calibrates the temperature of the heat source water after passing through the fan coil unit 101 measured by the heat source water fan coil outlet temperature sensor 24 (S3).
  • heat source water is allowed to flow through the flow path 41 and calibration is performed so that the temperature difference of the heat source water measured by the sensor becomes zero.
  • the blower fan 6 and the compressor 5 are stopped, the switching three-way valve 11 switches the flow path so that the heat source water flows to the fan coil side, and the proportional two-way valve 13 sets the opening degree to 100%.
  • the difference between the temperature Wa (° C.) of the heat source water at the inlet of the air conditioner 100 and the temperature Wb (° C.) of the heat source water at the outlet of the fan coil unit 101 at this time is calibrated to be zero.
  • the control device 7 calibrates the heat source water temperature after passing through the heat pump unit 102 measured by the heat source water outlet temperature sensor 26 (S4). Also in this step, in a state where the fan coil unit 101 and the heat pump unit 102 have stopped operation, heat source water is flowed through the flow path 41 and calibration is performed so that the temperature difference of the heat source water measured by the sensor becomes zero. Specifically, the blower fan 6 and the compressor 5 are stopped, the switching three-way valve 11 switches the flow path so as to flow the heat source water to the heat pump side, and the proportional two-way valve 13 sets the opening degree to 100%. The difference between the temperature Wa (° C.) of the heat source water at the inlet of the air conditioner 100 and the temperature Wc (° C.) of the heat source water at the outlet of the air conditioner 100 at this time is calibrated to be zero.
  • FIG. 3 is a processing flow diagram showing an example of processing during general operation.
  • the air conditioner 100 can perform the cooling operation and the heating operation by changing the operation of the fan coil unit 101 in accordance with the temperature of the heat source water and switching the four-way valve 12 of the heat pump unit 102.
  • the blower operation may be performed by operating only the blower fan 6. In the present embodiment, an example of performing a cooling operation will be described.
  • the control device 7 of the air conditioning apparatus 100 determines whether the dehumidifying and reheating operation is to be performed (FIG. 3: S11). In this step, for example, when cooling is performed in the rainy season, the sensible heat and latent heat are processed by the fan coil unit 101, and reheating is performed by the heat pump unit 102 so that the temperature blown out from the air conditioner 100 is not excessively lowered. Determine if reheating operation should be performed. For example, when the indoor temperature Ta is 24 ° C. or lower and the indoor humidity Ha is 60% or higher, the control device 7 determines that the dehumidifying and reheating operation is to be performed. The operation may be switched by setting the user to explicitly perform the "dehumidifying and reheating operation". In that case, it is determined in this step whether or not the operation setting is “dehumidifying and reheating operation”.
  • the air conditioning apparatus 100 performs the normal cooling operation (S12). On the other hand, when it is determined that the dehumidifying and reheating operation is to be performed (S11: YES), the air conditioning apparatus 100 performs the dehumidifying and reheating operation (S13).
  • FIG. 4 is a process flow diagram showing an example of a normal cooling operation.
  • the control device 7 of the air conditioning apparatus 100 determines whether the air conditioning load is large (FIG. 4: S21). In this step, the control device 7 determines that the air conditioning load is large when the difference between the indoor temperature Ta and the set temperature Ts is equal to or greater than the first threshold.
  • the first threshold is, for example, 3 ° C. That is, when the indoor temperature Ta is higher than the set temperature Ts by 3 ° C. or more, it is determined that the air conditioning load is large.
  • the air conditioning apparatus 100 When it is determined that the air conditioning load is large (S21: YES), the air conditioning apparatus 100 performs the maximum load operation using the fan coil unit 101 and the heat pump unit 102 (S22). In this step, the blower fan 6 and the compressor 5 are operated, the switching three-way valve 11 switches the flow path so that the heat source water flows to the fan coil side, and the opening degree of the proportional two-way valve 13 is 100%. As described above, when it is determined that the temperature difference between the room temperature and the set temperature is equal to or greater than the predetermined threshold and the air conditioning load is large, the operation at the rated output is performed. Thereafter, the process returns to S11 of FIG. 3 through the terminal A.
  • the control device 7 determines whether the air conditioning load is medium (S23). In this step, when the difference between the indoor temperature Ta and the set temperature Ts is less than the first threshold and greater than or equal to the second threshold, it is determined that the air conditioning load is medium.
  • the second threshold is a value smaller than the first threshold described above, and is, for example, 1 ° C. That is, when the difference between the indoor temperature Ta and the set temperature Ts is 1 ° C. or more and less than 3 ° C., it is determined that the air conditioning load is medium.
  • the air conditioner 100 When it is determined that the air conditioning load is medium (S23: YES), the air conditioner 100 performs a partial load operation using the fan coil unit 101 and the heat pump unit 102 (S24). In this step, the blower fan 6 and the compressor 5 are operated, the switching three-way valve 11 switches the flow path so that the heat source water flows to the fan coil side, and the opening degree of the proportional two-way valve 13 is 50%, for example.
  • the operating frequency of the compressor 5 is determined according to the size of the air conditioning load represented by the temperature difference between the room temperature and the set temperature.
  • the opening degree of the proportional two-way valve 13 may also be proportionally controlled according to the size of the air conditioning load.
  • the fan coil unit 101 is operated at the rated output, and the heat pump unit 102 is operated according to the air conditioning load. Operate with output. As described above, by controlling the fan coil unit 101 to operate with priority, the power consumption of the compressor 5 is reduced, and energy saving can be achieved as the entire apparatus. Thereafter, the process returns to S11 of FIG. 3 through the terminal A.
  • FIG. 5 is a second half of a process flowchart showing an example of a normal cooling operation.
  • the control device 7 determines whether the air conditioning load is small or the humidity is equal to or more than a predetermined value (FIG. 5: S25) .
  • the third threshold is a value smaller than the above-described second threshold, and is, for example, ⁇ 1 ° C.
  • the control device 7 determines whether the indoor humidity is higher than a predetermined threshold.
  • the predetermined threshold is, for example, a set humidity.
  • a portion by the fan coil unit 101 Load operation is performed (S26).
  • the blower fan 6 and the compressor 5 are stopped, the switching three-way valve 11 switches the flow path so that the heat source water flows to the fan coil side, and the opening degree of the proportional two-way valve 13 is 25%, for example.
  • the opening degree of the proportional two-way valve 13 may be proportionally controlled according to the size of the air conditioning load.
  • the dehumidifying operation by the heat pump unit 102 is performed (S27).
  • the compressor 5 of the heat pump unit 102 operates at, for example, a predetermined minimum output, and the operating frequency of the compressor 5 in stages according to the length of time elapsed from the start of the dehumidifying operation. Raise For example, the compressor 5 increases the operating frequency by 2 Hz every predetermined time in a period in which the indoor humidity is equal to or higher than the set humidity.
  • the processes of S26 and S27 are performed in parallel. Thereafter, the process returns to S11 of FIG. 3 via the terminal A.
  • the fan coil unit 101 is operated with a stepwise output or an output by proportional control according to the air conditioning load,
  • the heat pump unit 102 By operating the heat pump unit 102 only for dehumidification, energy saving can be achieved for the entire apparatus. That is, when the air conditioning load is small, basically the partial load operation is performed only by the fan coil unit 101, and when the dehumidification is necessary, the heat pump unit 102 is operated to perform the dehumidification operation.
  • the air conditioner 100 stops the operation of the fan coil unit 101 and the heat pump unit 102 (S28).
  • the difference between the room temperature Ta and the set temperature Ts is less than the third threshold, it is determined that there is no air conditioning load.
  • the difference between the room temperature Ta and the set temperature Ts is less than ⁇ 1 ° C.
  • the indoor humidity falls below the set humidity, for example, it can be determined that the target value has been reached.
  • the air conditioner 100 stops operation (thermo: OFF). Thereafter, the operation is stopped until the air conditioning load in the room becomes moderate or higher (S29: NO), and when the air conditioning load becomes medium or greater (S28: YES), the process proceeds to S11 of FIG. Return to
  • FIG. 6 is a diagram showing an example of a change in room temperature when the air conditioning apparatus 100 operates in the cooling operation.
  • the horizontal axis indicates the passage of time, and the vertical axis indicates room temperature.
  • the room temperature is shown as a relative value based on the set temperature Ts.
  • the indoor temperature Ta (° C.) is equal to or higher than Ts + 3 (° C.), and the air conditioning load is large.
  • the fan coil unit 101 and the heat pump unit 102 operate at the rated output in S22 of FIG. In the period from T1 to T2 in FIG.
  • the indoor temperature Ta (° C.) is from Ts + 1 (° C.) to Ts + 3 (° C.), and the air conditioning load is medium.
  • the fan coil unit 101 operates at the rated output and the heat pump unit 102 operates at the output according to the size of the air conditioning load in S24 of FIG. 4.
  • the indoor temperature Ta (° C.) is from Ts-1 (° C.) to Ts + 1 (° C.), and the air conditioning load is small.
  • the opening degree of the proportional two-way valve 13 is changed according to the air conditioning load to adjust the flow rate of the heat source water, and the fan coil unit 101 operates.
  • the heat pump unit 102 operates in S27 when the indoor humidity Ha is higher than a predetermined threshold.
  • the room temperature Ta (° C.) drops below Ts-1 (° C.) at T3 in FIG. 6, the fan coil unit 101 and the heat pump unit 102 stop operating at S28 in FIG. Thereafter, when the indoor temperature Ta (° C.) becomes equal to or higher than T + 1 (° C.) at T3 in FIG. 6, the air conditioning apparatus 100 resumes the operation.
  • the opening degree of the proportional two-way valve 13 is changed according to the air conditioning load to adjust the flow rate of the heat source water, and the fan coil unit 101 operates.
  • the heat pump unit 102 operates in S27 when the indoor humidity Ha is higher than a predetermined threshold.
  • the fan coil unit 101 is preferentially used according to the air conditioning load, it is possible to suppress an increase in the power consumption by the compressor 5 of the heat pump unit 102 in particular. .
  • FIG. 7 is a process flow diagram showing an example of an opening degree determination process for determining the opening degree of the proportional valve. For example, in S24 of FIG. 4 and S26 of FIG. 5, the opening degree of the proportional two-way valve 13 is determined by the opening degree determination process as shown in FIG. 7, and the flow rate of the heat source water is changed.
  • a so-called flow rate sensor is not provided in the flow path 41 of the heat source water, and the flow rate is estimated based on the temperature of the heat source water measured by the temperature sensor and changed to a desired flow rate.
  • heat source water at a predetermined temperature is introduced, the blower fan 6 and the compressor 5 are operated, and the opening degree of the proportional two-way valve 13 is set to 100%.
  • the difference between the temperature of the heat source water at the inlet of the air conditioner 100 and the temperature of the heat source water at the outlet with respect to the difference between the temperature and the temperature of the heat source water at the outlet when the degree of opening of the proportional two-way valve 13 is 50%.
  • the ratio is about 1.6 to 1.8 times.
  • the control device 7 Since such a ratio changes in accordance with the configuration of the air conditioner 100 (in other words, the type of product), the control device 7 is provided beforehand with the relationship between the opening degree of the proportional valve and the temperature of the heat source water at the inlet and outlet of the device. It shall be stored in a storage device such as a memory area. Specifically, in the case of 50% for the two-way valve 13, the temperature difference from the case of the rated flow rate (the opening is 100%) is stored with respect to the stepwise opening as in the case of 25%. .
  • a ratio using the difference between the inlet temperature measured by the heat source water inlet temperature sensor 21 and the outlet temperature of the entire apparatus measured by the heat source water outlet temperature sensor 26, and the inlet temperature measured by the heat source water inlet temperature sensor 21 The ratio using the difference with the outlet temperature of the fan coil unit 101 measured by the heat source water fan coil outlet temperature sensor 24 is stored.
  • the temperature difference at the inlet / outlet to be targeted when the flow rate of heat source water is to be 50% is known. It becomes possible to feedback control the opening degree of the proportional valve so that the target value becomes the target value. That is, the flow rate can be calculated based on the measurement value of the temperature sensor.
  • the control device 7 reads information indicating the relationship between the inlet / outlet temperature difference stored therein and the opening degree of the proportional valve (FIG. 7: S31). Further, the control device 7 specifies the temperature difference of the heat source water corresponding to the desired opening degree determined in accordance with the air conditioning load of the air in the target room (S32). In this step, the temperature difference of the target heat source water is determined. Further, in the present embodiment, a desired opening degree is called a distribution rate. In addition, although it demonstrated by two steps of S31 and S32 for convenience, it is good also as one process of reading the temperature difference of heat-source water memorize
  • the controller 7 determines the target value of the outlet temperature as follows, and performs feedback control of the opening degree of the proportional valve so that the outlet temperature approaches the target value.
  • Target value present inlet temperature + specified temperature difference ⁇ (1 / distribution rate)
  • the distribution rate is the desired degree of opening, for example 50%. Control can be made to gradually approach the target value by multiplying the temperature difference of the target value by the reciprocal of the desired opening degree. Further, the target value is appropriately updated when a predetermined time has elapsed or when the change in the temperature difference is stabilized.
  • the flow rate of the heat source water introduced into the fan coil unit 101 and the heat pump unit 102 is changed by the opening degree determination processing as described above. Also, independently of this, the operating frequency of the compressor of the heat pump unit 102 is changed according to the air conditioning load.
  • the air conditioning apparatus 100 can cause the indoor temperature and the indoor humidity to converge to the set temperature and the set humidity.
  • the temperature difference with the temperature of the heat source water at the outlet of the fan coil unit 101 measured by the water fan coil outlet temperature sensor 24 may be used. Even when such an inlet / outlet temperature difference is used, the opening degree of the proportional valve can be determined according to the process flow chart shown in FIG. 7 to control the flow rate of the heat source water.
  • FIG. 8 is a process flow chart showing an example of the dehumidifying and reheating operation shown in S13 of FIG.
  • the room air is dehumidified by the fan coil side heat exchanger 1 of the fan coil unit 101, and the heat pump unit 102 is set to the heating operation, and the air is blown out into the room by the heat pump side air heat medium heat exchanger 4.
  • the control device 7 determines whether the air conditioning load is large (FIG. 8: S41). Also in this step, the control device 7 determines that the air conditioning load is large when the difference between the room temperature Ta and the set temperature Ts is equal to or more than the first threshold. For example, when the indoor temperature Ta is higher by 3 ° C. or more than the set temperature Ts, it is determined that the air conditioning load is large.
  • the air conditioning apparatus 100 When it is determined that the air conditioning load is large (S41: YES), the air conditioning apparatus 100 performs the dehumidifying operation by the fan coil unit 101 and the reheating operation by the heat pump unit 102 (S42). In this step, the blower fan 6 and the compressor 5 are operated, the switching three-way valve 11 switches the flow path so that the heat source water flows to the fan coil side, and the opening degree of the proportional two-way valve 13 is 100%. Also, as described above, the four-way valve switches the refrigeration cycle to the heating operation side. As described above, when it is determined that the temperature difference between the room temperature and the set temperature is equal to or greater than the predetermined threshold and the air conditioning load is large, the operation at the rated output is performed.
  • the heat pump unit 102 performs a heating operation to raise the temperature of the air blown into the room.
  • the blown-out humidity of the air conditioning apparatus 100 measured by the apparatus blown-off humidity sensor 37 may be reheated so as to be higher than the dew point temperature by a predetermined temperature or more.
  • the dew point temperature may be calculated using the blowout temperature Tf (° C.) of the fan coil unit 101 and the blowout humidity Hf (%) of the fan coil unit 101, or the heat pump side air heat measured by the heat exchanger temperature sensor 28.
  • the evaporation temperature of the heat exchanger 4 may be used as an approximation. Thereafter, the process returns to S11 of FIG. 3 through the terminal A.
  • the control device 7 determines whether the air conditioning load is medium (S43). Also in this step, when the difference between the indoor temperature Ta and the set temperature Ts is less than the first threshold and greater than or equal to the second threshold, it is determined that the air conditioning load is medium. For example, when the difference between the indoor temperature Ta and the set temperature Ts is 1 ° C. or more and less than 3 ° C., it is determined that the air conditioning load is medium.
  • the air conditioning apparatus 100 performs the dehumidifying operation by the fan coil unit 101 and the reheating operation by the heat pump unit 102 (S44).
  • the blower fan 6 and the compressor 5 are operated, the switching three-way valve 11 switches the flow path so that the heat source water flows to the fan coil side, and the opening degree of the proportional two-way valve 13 is 50%, for example.
  • the heat pump unit 102 performs a heating operation, and the operating frequency of the compressor 5 warms the blowing temperature of the air conditioner 100 according to the set temperature.
  • the opening degree of the proportional two-way valve 13 may also be proportionally controlled according to the size of the air conditioning load.
  • the reheating operation may be performed so that the blow-out temperature of the air conditioning apparatus 100 measured by the apparatus blow-out temperature sensor 27 is higher than the dew point temperature by a predetermined temperature or more. Thereafter, the process returns to S11 of FIG. 3 through the terminal A.
  • FIG. 9 is a second half of the process flow diagram showing an example of the dehumidifying and reheating operation.
  • the control device 7 determines whether the air conditioning load is small (FIG. 9: S45).
  • the difference between the indoor temperature Ta and the set temperature Ts is less than the second threshold and greater than or equal to the third threshold, it is determined that the air conditioning load is small. For example, when the difference between the indoor temperature Ta and the set temperature Ts is ⁇ 1 ° C. or more and less than 1 ° C., it is determined that the air conditioning load is small.
  • the dehumidifying operation by the fan coil unit 101 and the reheating operation by the heat pump unit 102 are performed (S46).
  • the blower fan 6 and the compressor 5 are operated, the switching three-way valve 11 switches the flow path so that the heat source water flows to the fan coil side, and the opening degree of the proportional two-way valve 13 is 25%, for example.
  • the opening degree of the proportional two-way valve 13 may be proportionally controlled according to the size of the air conditioning load.
  • the reheating operation may be performed so that the blow-out temperature of the air conditioning apparatus 100 measured by the apparatus blow-out temperature sensor 27 is higher than the dew point temperature by a predetermined temperature or more. Thereafter, the process returns to S11 of FIG. 3 via the terminal A.
  • the air conditioner 100 stops the operation of the fan coil unit 101 and the heat pump unit 102 (S47).
  • S45 when the difference between the room temperature Ta and the set temperature Ts is less than the third threshold, it is determined that there is no air conditioning load. For example, when the difference between the room temperature Ta and the set temperature Ts is less than ⁇ 1 ° C., it can be determined that the room temperature has reached the target value, and the air conditioner 100 stops the operation (thermo: OFF). After that, the operation is stopped until the air conditioning load in the room becomes medium or more (S48: NO), and when the air conditioning load becomes medium or more (S48: YES), the process proceeds to S11 in FIG. Return to
  • FIG. 10 is a view showing an example of the air conditioning apparatus according to the second embodiment.
  • the components corresponding to those of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
  • the air conditioning apparatus 100 includes a proportional three-way valve 14 instead of the switching three-way valve 11 in the first embodiment. Moreover, the proportional two-way valve in the first embodiment is not provided. Then, the controller 7 adjusts the opening degree of the proportional three-way valve 14 to make the flow rate of the heat source water introduced into the air conditioner 100 constant, and the flow rate of the heat source water flowing to the fan coil unit 101 side The ratio to the flow rate of heat source water flowing directly to the side 102 is changed.
  • substantially the same processing as that shown in FIGS. 3 to 5 and 7 to 9 is performed.
  • S22 and S24 of FIG. 4 instead of changing the flow rate of the heat source water introduced into the air conditioner 100, the fan coil unit 101 side.
  • the opening degree of the proportional three-way valve 14 can be determined based on, for example, the temperature of the heat source water at the outlet of the fan coil unit 101 measured by the heat source water fan coil outlet temperature sensor 24.
  • the opening degree of the proportional three-way valve 14 may perform proportional control according to the air conditioning load, an example in which the opening degree is changed stepwise according to the air conditioning load will be described below.
  • control device 7 causes the proportional three-way valve 14 to set the opening degree on the fan coil unit 101 side to 100%. That is, the operation is performed with the output of the fan coil unit 101 being maximized.
  • the control device 7 causes the proportional three-way valve 14 to set the opening degree on the fan coil unit 101 side to, for example, 50%. That is, one half of the heat source water flows to the fan coil unit 101 side, and the other flows directly to the heat pump side water heat exchanger 2. Therefore, the fan coil unit 101 operates at half the rated output. Further, the remaining heat source water and the heat source water whose temperature has risen via the fan coil unit 101 join together and flow into the heat pump side hydrothermal medium heat exchanger 2.
  • the heat pump side hydrothermal medium heat exchange is more than the case where only the heat source water of 50% flow rate through the fan coil unit 101 flows into the heat pump side hydrothermal medium heat exchanger 2 as in the first embodiment.
  • the temperature of the heat source water flowing into the vessel 2 is lowered.
  • the temperature of the combined heat source water is 10.5 It becomes about ° C. Therefore, the condensation temperature of the heat pump side hydrothermal medium heat exchanger 2 at the time of cooling operation can be lowered, and the power consumption of the compressor 5 can be reduced.
  • the control device 7 causes the proportional three-way valve 14 to set the opening degree on the fan coil unit 101 side to, for example, 25%. That is, one fourth of the heat source water flows to the fan coil unit 101 side, and the remaining flows directly to the heat pump side water heat exchanger 2. Since the capacity of the fan coil unit 101 is determined by the flow rate of the heat source water, by controlling the flow rate, it is possible to cope with a smaller partial load, and the comfort is improved.
  • FIG. 11 is a view showing an example of the air conditioning apparatus according to the third embodiment.
  • the same reference numerals are given to components corresponding to the first embodiment or the second embodiment, and the description will be omitted.
  • the air conditioning apparatus 100 includes two heat exchangers in which the heat pump unit 102 performs heat exchange between the heat medium and the heat source water. Specifically, the second heat pump side water heat medium heat exchanger 8 is provided between the expansion valve 3 and the heat pump side air heat medium heat exchanger 4.
  • the air conditioning apparatus 100 is configured to be able to improve the operation efficiency of the compressor 5 when performing a cooling operation in winter and a heating operation in summer.
  • the cooling operation in winter and the heating operation in summer are referred to as "reverse mode operation".
  • the fan coil unit 101 is not used. That is, the switching three-way valve 11 shown in the first embodiment or the proportional three-way valve 14 shown in the second embodiment sets the opening degree of the heat pump unit 102 to 100%.
  • the power consumption of the compressor 5 is increased due to overload as compared with the case of cooling operation with heat source water of about 7 ° C.
  • the heat medium evaporates in the second heat pump side hydrothermal medium heat exchanger 8, and the temperature of the heat source water drops to about 43 ° C.
  • the heat medium condenses in the heat pump side air heat medium heat exchanger 4, and the temperature of the heat source water rises to about 48 ° C.
  • the load that is, power consumption
  • the power consumption of the compressor 5 is increased due to overload as compared with the case where the heating operation is performed by the heat source water at about 45 ° C.
  • the heat medium condenses in the second heat pump side hydrothermal medium heat exchanger 8, and the temperature of the heat source water rises to about 9 ° C.
  • the temperature of the heat medium on the heat pump side is lowered, and supercooling can be obtained as compared with the case of the heat pump side air heat medium heat exchanger alone. That is, the pressure is constant, and the temperature of the heat medium flowing into the expansion valve 3 is further reduced.
  • the heat medium evaporates in the heat pump side water heat exchanger 2 and the temperature of the heat source water drops to about 7 ° C.
  • the load of the compressor 5 can be reduced by the subcooling of the heat medium and the increase of the evaporation temperature in the heat pump side water heat exchanger 2.
  • the temperature of the heat source water is, for example, 5 ° C. or less, it is necessary to perform control for preventing freezing, the freezing is prevented by raising the temperature of the heat source water in the second heat pump side hydrothermal medium heat exchanger 8 Continuous operation can be performed without control of
  • the air conditioning apparatus 100 saves energy even during normal operation.
  • the same processing as shown in FIGS. 3 to 5 and 7 to 9 is performed.
  • the temperature of the heat source water having passed through the fan coil unit 101 has risen to about 12 ° C.
  • the heat medium evaporates in the second heat pump side hydrothermal medium heat exchanger 8, and the temperature of the heat source water drops to about 10 ° C.
  • the heat medium condenses in the heat pump side air heat medium heat exchanger 4, and the temperature of the heat source water rises to about 15 ° C.
  • the load on the compressor 5 can be reduced by reducing the condensation temperature in the heat pump side air heat medium heat exchanger 4.
  • the temperature of the heat source water having passed through the fan coil unit 101 is lowered to about 40 ° C.
  • the heat medium condenses in the second heat pump side hydrothermal medium heat exchanger 8, and the temperature of the heat source water rises to about 42 ° C.
  • subcooling of the heat medium is obtained.
  • the heat medium is evaporated by the heat pump side water heat exchanger 2, and the temperature of the heat source water is lowered to about 39.degree.
  • the load of the compressor 5 can be reduced by the subcooling of the heat medium and the increase of the evaporation temperature in the heat pump side air heat medium heat exchanger 4.
  • FIG. 12 is a view showing an example of the air conditioning apparatus according to the fourth embodiment.
  • components corresponding to those of the first to third embodiments are given the same reference numerals, and descriptions thereof will be omitted.
  • the air conditioning apparatus 100 includes a second expansion valve in addition to the configuration of the air conditioning apparatus 100 according to the third embodiment.
  • the second expansion valve 9 is provided between the second heat pump side hydrothermal medium heat exchanger 8 and the heat pump side air thermal medium heat exchanger 4.
  • the second expansion valve is also, for example, an electronic expansion valve.
  • the expansion valve 3 is opened and the second expansion valve 9 is operated in the case of the normal operation where the cooling operation is performed with heat source water of 7 ° C., for example. That is, the second expansion valve 9 is used instead of the expansion valve 3.
  • the second heat pump side water heat exchanger 8 also functions as a condenser to improve the condensing capacity. Therefore, according to the air conditioning apparatus 100 according to the present embodiment, the condensation temperature of the heat medium can be reduced, and the power consumption of the compressor 5 can be reduced.
  • the expansion valve 3 is opened and the second expansion valve 9 is operated.
  • the second heat pump side water heat exchanger 8 also functions as an evaporator to improve the evaporation capacity. Therefore, according to the air conditioning apparatus 100 according to the present embodiment, the evaporation temperature of the heat medium can be raised, and the power consumption of the compressor 5 can be reduced.
  • the second expansion valve 9 is opened and the expansion valve 3 is operated. That is, the operation is similar to that of the third embodiment.
  • FIG. 13 is a view showing an example of the air conditioning apparatus according to the fifth embodiment.
  • the components corresponding to those of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
  • the pump 200 is connected to the flow path 41 of the heat source water.
  • the pump 200 can change the water supply amount by changing, for example, the rotational speed of the rotary pump.
  • changing the water supply amount of the pump 200 also enables the heat source water flowing through the air conditioning apparatus 100 to be changed.
  • the flow rate can be changed.
  • information indicating the relationship between the inlet / outlet temperature difference of the heat source water and the water supply amount of the pump is stored in advance.
  • the control device 7 adjusts the water supply amount of the pump based on the information.
  • the pump 200 may be combined with the air conditioner 100 shown in FIG. 10, FIG. 11 and FIG.
  • FIG. 14 is a diagram illustrating an example of an air conditioning system including a plurality of air conditioning devices.
  • a plurality of air conditioners 100 are provided on each floor.
  • the air conditioning apparatus 100 is the apparatus described in the first to fifth embodiments.
  • the system also includes a pump 200, a refrigerator 300, an auxiliary heat source 400 such as a boiler, and a cooling tower 500.
  • the refrigerator 300 produces, for example, cold water of about 7 ° C. as heat source water.
  • the auxiliary heat source 400 produces, for example, hot water of about 45 ° C. as heat source water.
  • the cooling tower 500 is used for exhaust heat of the refrigerator.
  • the pump 200 also sends the heat source water to each of the plurality of air conditioners 100 through piping.
  • One pump 200 may be provided in a building, and heat source water may be supplied to all the air conditioners 100, or one pump 200 may be connected to each of the air conditioners 100. . Further, for example, one pump 200 may be connected to each group of some air conditioners 100, as in the case of a plurality of air conditioners 100 provided on the same floor. Moreover, clean air shall be taken in suitably via an outside air processing machine which is not illustrated.
  • the system according to the present embodiment can change the operation mode such as the cooling operation, the heating operation, and the blowing operation for each air conditioner 100.
  • the operation mode is different for each air conditioning apparatus 100, heat can be recovered on the delivery side of the heat source water, and energy consumption of the refrigerator 300 and the auxiliary heat source 400 can be reduced.
  • the air conditioner 100 preferentially uses the fan coil unit 101 and suppresses the use of the compressor 5 as much as possible, thereby reducing power consumption. Can.
  • the power consumption can also be reduced by decreasing the water supply amount of the pump 200. Therefore, the system can reduce power consumption and realize ZEB (Zero Energy Building).
  • FIG. 15 is a diagram showing an example of an air conditioning system including a plurality of air conditioning devices. Also in the example of FIG. 15, a plurality of air conditioners 100 are provided on each floor.
  • the air conditioning apparatus 100 is the apparatus described in the first to fifth embodiments.
  • the system also includes a pump 200, a heat storage tank 600, an outside air processor 700, and an air-cooled heat pump chiller 800.
  • the system is not limited to the air conditioner 100, and may include a radiation panel 900 that performs radiation air conditioning.
  • the heat storage tank 600 is a facility that holds a heat medium for heat storage.
  • the outside air processor 700 takes in open air (OA) and supplies indoor air with a supply air (SA: supply air).
  • SA supply air
  • the air-cooling heat pump chiller 800 is an air-cooling type cooling device using a heat pump, and cools the heat source water.
  • the pump 200 also sends the heat source water to each of the plurality of air conditioners 100 through piping.
  • One pump 200 may be provided in a building, and heat source water may be supplied to all the air conditioners 100, or one pump 200 may be connected to each of the air conditioners 100. . Further, for example, one pump 200 may be connected to each group of some air conditioners 100, as in the case of a plurality of air conditioners 100 provided on the same floor.
  • the system according to the present embodiment uses the heat storage tank 600 and the air-cooled heat pump chiller 800 to produce heat source water.
  • the air-cooled heat pump chiller 800 is operated at night to produce heat source water having a water temperature of 12 ° C., and the heat storage tank 600 stores heat.
  • heat is collected from the heat storage tank 600 until the temperature of the heat source water rises to 20 ° C., for example.
  • the air-cooled heat pump chiller 800 is operated. Reduce the temperature.
  • the air-cooled heat pump chiller 800 is operated at night to manufacture heat source water having a water temperature of 35 ° C. and store heat in the heat storage tank 600.
  • heat is collected from the heat storage tank 600 until the temperature of the heat source water falls to 25 ° C., for example, in winter daytime, and when the temperature of the heat source water reaches 25 ° C., the air-cooled heat pump chiller 800 is operated and the temperature of the heat source water Raise
  • the system according to the present embodiment can also change the operation mode such as the cooling operation, the heating operation, and the blowing operation for each air conditioner 100. Therefore, when an operation mode differs for every air conditioning apparatus 100, heat recovery can be performed by the sending side of heat source water, and consumption energy can be reduced.
  • the air conditioner 100 preferentially uses the fan coil unit 101 and suppresses the use of the compressor 5 as much as possible, thereby reducing power consumption. Can.
  • the power consumption can also be reduced by reducing the water supply amount of the pump 200.
  • the external air processor 700 is treated mainly by latent heat
  • the air conditioner 100 is treated mainly by sensible heat
  • the sensible heat is treated by the fan coil unit 101
  • the latent heat is treated by the heat pump unit 102, whereby the efficiency of the refrigerator is achieved.
  • the operating rate of the compressor of the refrigerator and the operating rate of the compressor of the heat pump unit 102 can be reduced at the same time. Therefore, the system can reduce power consumption and realize ZEB (Zero Energy Building).
  • the air conditioning system is provided with the refrigerator 300 and the auxiliary heat source 400, or the heat storage tank 600 and the heat source water temperature control device such as the air-cooled heat pump chiller 800 of the seventh embodiment. You may do so.
  • feedback control such as proportional integral differential (PID) control may be performed instead of the “proportional control” described above.
  • PID proportional integral differential
  • At least one of the humidity and the blowing humidity of the air conditioning apparatus 100 measured by the apparatus blowing humidity sensor 37 may be used, or a combination of two or more of them.
  • the dew point temperature calculated by the indoor temperature sensor 22 and the indoor humidity sensor 32, the dew point temperature calculated by the fan coil outlet temperature sensor 23 and the fan coil outlet humidity sensor 33, and the device outlet temperature sensor 27 and the device outlet humidity sensor 37 At least one of these dew point temperatures, or a combination of two or more of these may be used.
  • Air conditioner 101 fan coil unit 1: fan coil side heat exchanger 102: heat pump unit 2: heat pump side water heat medium heat exchanger 3: expansion valve 4: heat pump side air heat medium heat exchanger 5: compressor 6: Blower fan 7: Controller 8: Second heat pump side water heat exchanger 9: Second expansion valve 11: switching three-way valve 12: four-way valve 13: proportional two-way valve 14: proportional three-way valve 21: Heat source water inlet temperature sensor 22: indoor temperature sensor 23: fan coil outlet temperature sensor 24: heat source water fan coil outlet temperature sensor 26: heat source water outlet temperature sensor 27: device outlet temperature sensor 28: heat exchanger temperature sensor 32: indoor humidity Sensor 33: Fan coil outlet humidity sensor 37: Device outlet humidity sensor

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Signal Processing (AREA)
  • Physics & Mathematics (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention concerne une unité de climatisation, laquelle unité produit un équilibre entre le confort et les économies d'énergie. Selon la présente invention, un dispositif de climatisation comprend : un ventilo-convecteur qui est disposé dans une trajectoire d'écoulement d'eau de source de chaleur, et qui échange de la chaleur entre l'eau de source de chaleur et l'air; une unité de pompe à chaleur qui est disposée dans la trajectoire d'écoulement, et qui échange de la chaleur entre l'eau de source de chaleur et un milieu de transfert de chaleur ; une vanne à trois voies qui est disposée dans la trajectoire d'écoulement, et qui sépare l'eau de source de chaleur entre un côté de ventilo-convecteur et un côté de pompe à chaleur ; et un dispositif de commande pour commander la vanne à trois voies. Pendant une opération de charge partielle dans laquelle le dispositif de climatisation fonctionne avec une sortie inférieure à la sortie nominale du dispositif de climatisation, le dispositif de commande commande la vanne à trois voies de telle sorte que l'eau de source de chaleur est de préférence guidée vers le ventilo-convecteur.
PCT/JP2018/013249 2017-12-12 2018-03-29 Dispositif de climatisation et système de climatisation Ceased WO2019116599A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017237791A JP2019105397A (ja) 2017-12-12 2017-12-12 空気調和装置及び空気調和システム
JP2017-237791 2017-12-12

Publications (1)

Publication Number Publication Date
WO2019116599A1 true WO2019116599A1 (fr) 2019-06-20

Family

ID=66820129

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/013249 Ceased WO2019116599A1 (fr) 2017-12-12 2018-03-29 Dispositif de climatisation et système de climatisation

Country Status (2)

Country Link
JP (1) JP2019105397A (fr)
WO (1) WO2019116599A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112240608A (zh) * 2019-07-18 2021-01-19 木村工机株式会社 热交换器及空调机
US11441788B2 (en) * 2018-05-11 2022-09-13 Kyungdong Navien Co., Ltd. Method and system for determining hot water use by using temperature gap
WO2024079807A1 (fr) * 2022-10-12 2024-04-18 三菱電機株式会社 Système de climatisation

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7374633B2 (ja) * 2019-07-11 2023-11-07 日本ピーマック株式会社 空気調和機及び空気調和システム
JPWO2023181374A1 (fr) * 2022-03-25 2023-09-28

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4248059A (en) * 1977-10-29 1981-02-03 Kenneth Fowler Reversible-cycle closed-circuit refrigeration systems
JPH09196422A (ja) * 1996-01-22 1997-07-31 Nippon P-Mac Kk 空気調和ユニット
JP2005069552A (ja) * 2003-08-22 2005-03-17 Kimura Kohki Co Ltd 水熱源ヒートポンプユニット
WO2015114839A1 (fr) * 2014-02-03 2015-08-06 三菱電機株式会社 Dispositif de refroidissement et équipement de source de chaleur

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4248059A (en) * 1977-10-29 1981-02-03 Kenneth Fowler Reversible-cycle closed-circuit refrigeration systems
JPH09196422A (ja) * 1996-01-22 1997-07-31 Nippon P-Mac Kk 空気調和ユニット
JP2005069552A (ja) * 2003-08-22 2005-03-17 Kimura Kohki Co Ltd 水熱源ヒートポンプユニット
WO2015114839A1 (fr) * 2014-02-03 2015-08-06 三菱電機株式会社 Dispositif de refroidissement et équipement de source de chaleur

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11441788B2 (en) * 2018-05-11 2022-09-13 Kyungdong Navien Co., Ltd. Method and system for determining hot water use by using temperature gap
CN112240608A (zh) * 2019-07-18 2021-01-19 木村工机株式会社 热交换器及空调机
CN112240608B (zh) * 2019-07-18 2023-06-27 木村工机株式会社 热交换器及空调机
WO2024079807A1 (fr) * 2022-10-12 2024-04-18 三菱電機株式会社 Système de climatisation

Also Published As

Publication number Publication date
JP2019105397A (ja) 2019-06-27

Similar Documents

Publication Publication Date Title
KR101605901B1 (ko) 공기 조화기 및 그 제어방법
US10955160B2 (en) Air conditioner including a plurality of utilization units connected in parallel to a heat source unit
JP5802340B2 (ja) 空気調和装置
WO2019116599A1 (fr) Dispositif de climatisation et système de climatisation
JP5802339B2 (ja) 空気調和装置
JP6401015B2 (ja) 空気調和機
WO2016194098A1 (fr) Dispositif de climatisation et dispositif de commande de fonctionnement
CN103292527A (zh) 空调装置
KR20200083294A (ko) 항온항습기
JP4068927B2 (ja) 空気調和機
JP2001248937A (ja) ヒートポンプ給湯エアコン
JP2010236816A (ja) ヒートポンプ式空調機およびヒートポンプ式空調機の制御方法
JP3936345B2 (ja) 空気調和機
JP6625265B2 (ja) 空気調和機
JP2017089950A (ja) 空気調和システム
JP4743223B2 (ja) 空気調和装置
JP7374633B2 (ja) 空気調和機及び空気調和システム
WO2021214930A1 (fr) Système de climatisation et procédé de commande
JP2005098660A (ja) ヒートポンプ式空調装置
JP4187008B2 (ja) 空気調和装置
JP7462830B2 (ja) 空気調和装置
JP5768151B2 (ja) ヒートポンプ式空調機およびヒートポンプ式空調機の制御方法
CN113639443A (zh) 空调器及其控制方法
JP6203230B2 (ja) 空調装置、空調装置の制御方法
JP2002048382A (ja) 空気調和装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18888808

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18888808

Country of ref document: EP

Kind code of ref document: A1