WO2019167250A1 - Climatiseur - Google Patents

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Publication number
WO2019167250A1
WO2019167250A1 PCT/JP2018/008001 JP2018008001W WO2019167250A1 WO 2019167250 A1 WO2019167250 A1 WO 2019167250A1 JP 2018008001 W JP2018008001 W JP 2018008001W WO 2019167250 A1 WO2019167250 A1 WO 2019167250A1
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WO
WIPO (PCT)
Prior art keywords
heating
cooling
heat exchanger
heat medium
fcu
Prior art date
Application number
PCT/JP2018/008001
Other languages
English (en)
Japanese (ja)
Inventor
▲高▼田　茂生
拓哉 紺谷
Original Assignee
三菱電機株式会社
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 filed Critical 三菱電機株式会社
Priority to US16/965,810 priority Critical patent/US20210048216A1/en
Priority to JP2020503229A priority patent/JP6980089B2/ja
Priority to PCT/JP2018/008001 priority patent/WO2019167250A1/fr
Publication of WO2019167250A1 publication Critical patent/WO2019167250A1/fr

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    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F24F11/70—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
    • F24F11/84—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 using valves
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2221/00—Details or features not otherwise provided for
    • F24F2221/54—Heating and cooling, simultaneously or alternatively
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/003—Indoor unit with water as a heat sink or heat source

Definitions

  • the present invention relates to an air conditioner that performs heat exchange between a refrigerant circulating in a refrigerant circuit and a heat medium circulating in a heat medium circuit.
  • Patent Document 1 an air conditioning composite system that can simultaneously provide air conditioning and hot water supply has been proposed (see, for example, Patent Document 1).
  • the air conditioner and the water heater are usually connected in parallel, and the air conditioning temperature and the hot water temperature can be individually set.
  • Patent Document 1 when an air conditioner and a water heater are connected in parallel, much heat remains in the return water flowing out of the air conditioner and the water heater. Conventionally, the heat remaining in the return water cannot be effectively used by using the heat recovered by the air conditioner for a hot water heater. Therefore, the energy saving performance of the entire system is deteriorated.
  • the present invention has been made in view of the above-described problems in the conventional technology, and an object thereof is to provide an air conditioner that can improve the energy saving performance of the entire system.
  • the air conditioner of the present invention is an air conditioner including a cooling device, a heating device, and a heat medium circulation circuit through which a heat medium circulates, and the cooling device circulates a cooling refrigerant.
  • the heating device performs heat exchange between the heating refrigerant circuit in which the heating refrigerant circulates and the heating medium flowing through the heating medium and the heating refrigerant circuit, and the heating refrigerant circuit It has a heating side intermediate heat exchanger that functions as an evaporator, and the cooling device and the heating device are connected in series to the heat medium circulation circuit.
  • the cooling device and the heating device are connected in series and the heat medium is allowed to flow, so that the cooling device and the heating device use the exhaust heat recovered from each other, thereby improving energy saving. Can do.
  • FIG. 2 is a top cross-sectional view showing an example of the structure of the heat medium flow control valve in FIG. 1.
  • FIG. 5 is a top sectional view schematically showing a first state in the heat medium flow control valve of FIG. 4.
  • FIG. 5 is a top sectional view schematically showing a second state in the heat medium flow control valve of FIG. 4.
  • FIG. 5 is a top sectional view schematically showing a third state in the heat medium flow control valve of FIG. 4.
  • FIG. 6 is a top sectional view schematically showing a fifth state in the heat medium flow control valve of FIG. 4. It is a top surface sectional view showing roughly the 6th state in the heat carrier flow control valve of Drawing 4.
  • FIG. 6 is a schematic diagram illustrating an example of a configuration of an air conditioner according to Embodiment 3.
  • FIG. It is the schematic which shows the 1st example of the opening degree of a heat carrier flow control valve when the FCU capacity
  • FIG. 16 is a flowchart illustrating an example of a processing flow when heat recovery is not balanced in the cooling-side intermediate heat exchanger and the heating-side intermediate heat exchanger in the fifth embodiment.
  • FIG. 1 is a schematic diagram illustrating an example of a configuration of an air conditioner 100 according to the first embodiment.
  • the air conditioner 100 includes an outdoor unit 1, a plurality of indoor units 2a to 2c, and a relay device 3.
  • a refrigerant circuit is formed by connecting the outdoor unit 1 and the relay device 3 through the refrigerant pipe 10.
  • the plurality of indoor units 2a to 2c and the relay device 3 are connected by the heat medium pipe 20, whereby a heat medium circuit is formed.
  • the plurality of indoor units 2a to 2c are connected in series.
  • the outdoor unit 1 includes a compressor 11, a refrigerant flow switching device 12, a heat source side heat exchanger 13, and an accumulator 14.
  • the compressor 11 sucks low-temperature and low-pressure refrigerant, compresses the sucked refrigerant, and discharges high-temperature and high-pressure refrigerant.
  • the compressor 11 is composed of, for example, an inverter compressor whose capacity, which is a delivery amount per unit time, is controlled by changing an operation frequency.
  • the operating frequency of the compressor 11 is controlled by a control device 4 provided in the relay device 3 described later.
  • the refrigerant flow switching device 12 is, for example, a four-way valve, and switches between a cooling operation and a heating operation by switching the direction in which the refrigerant flows.
  • the refrigerant flow switching device 12 is switched so that the discharge side of the compressor 11 and the heat source side heat exchanger 13 are connected as shown by a solid line in FIG.
  • coolant flow path switching apparatus 12 switches so that the discharge side of the compressor 11 and the relay apparatus 3 side may be connected as shown with the broken line of FIG. 1 at the time of heating operation. Switching of the flow path in the refrigerant flow switching device 12 is controlled by the control device 4.
  • the heat source side heat exchanger 13 performs heat exchange between outdoor air supplied by a fan or the like (not shown) and the refrigerant.
  • the heat source side heat exchanger 13 functions as a condenser that radiates the heat of the refrigerant to the outdoor air and condenses the refrigerant during the cooling operation.
  • the heat source side heat exchanger 13 functions as an evaporator that evaporates the refrigerant during the heating operation and cools the outdoor air by the heat of vaporization at that time.
  • the accumulator 14 is provided on the low pressure side that is the suction side of the compressor 11.
  • the accumulator 14 separates the surplus refrigerant generated due to the difference in the operating state between the cooling operation and the heating operation or the surplus refrigerant generated due to the transient operation change into the gas refrigerant and the liquid refrigerant, and stores the liquid refrigerant.
  • FIG. 2 is a schematic diagram showing an example of the configuration of the indoor units 2a to 2c in FIG.
  • each of the plurality of indoor units 2 a to 2 c includes a fan coil unit (hereinafter referred to as “FCU (Fan Coil Unit)”) 21 and a heat medium flow control valve 22.
  • FCU Fan Coil Unit
  • the FCU 21 includes a use side heat exchanger 121 and a fan 122.
  • the use side heat exchanger 121 exchanges heat between indoor air and water supplied by the fan 122. As a result, cooling air or heating air, which is conditioned air supplied to the indoor space, is generated.
  • the fan 122 supplies air to the use side heat exchanger 121.
  • the rotation speed of the fan 122 is controlled by the control device 4. By controlling the number of rotations, the amount of air blown to the use side heat exchanger 121 is adjusted.
  • the heat medium flow control valve 22 is, for example, an electric three-way valve having an inlet 22a, a first outlet 22b, and a second outlet 22c, and is provided on the water inflow side of the FCU 21.
  • the heat medium flow control valve 22 is provided to branch inflowing water.
  • the first outlet 22 b is connected to the water inflow side of the FCU 21.
  • the second outlet 22 c is connected to the water outflow side of the FCU 21 through the indoor side bypass pipe 23. Thereby, the 2nd outflow port 22c of the heat carrier flow control valve 22 and the outflow side of the water of FCU21 are connected.
  • the indoor bypass pipe 23 is provided inside the indoor units 2a to 2c.
  • the present invention is not limited to this, and the indoor bypass pipe 23 is provided outside the indoor units 2a to 2c. Alternatively, it may be connected to the indoor units 2a to 2c via a connecting bracket or the like.
  • the indoor bypass pipe 23 is not necessarily provided for each of all the indoor units 2a to 2c. For example, the indoor bypass pipe 23 may not be provided in the FCU 21 that does not need to bypass water.
  • the heat medium flow control valve 22 may be a multi-way valve such as a four-way valve as long as it has at least the inlet 22a, the first outlet 22b, and the second outlet 22c.
  • a four-way valve is used as the heat medium flow control valve 22, and the outlets other than the first outlet 22b and the second outlet 22c are used for other purposes or sealed so as not to be used.
  • the four-way valve may be used as a pseudo three-way valve.
  • the heating medium flow rate adjustment valve 22 branches while adjusting the flow rate of the inflowing water, and the degree of opening is adjusted so that each branched water can be shut off.
  • a three-way valve with a flow adjustment function and a shut-off function is most suitable.
  • a three-way valve for adjusting the flow rate and a throttle device for blocking the flowing water may be combined.
  • a throttle device may be provided between the branch point and the junction of the pipes provided on the inflow / outlet side of the FCU 21 and the indoor side bypass pipe 23.
  • Each of the plurality of indoor units 2a to 2c includes an inlet temperature sensor 24, an outlet temperature sensor 25, and a suction temperature sensor 26.
  • the inlet temperature sensor 24 is provided on the water inflow side of the FCU 21 and detects the temperature of the water flowing into the FCU 21.
  • the outlet temperature sensor 25 is provided on the water outflow side of the FCU 21 and detects the temperature of the water flowing out of the FCU 21.
  • the suction temperature sensor 26 is provided on the air suction side of the FCU 21 and detects the suction air temperature of the air sucked into the FCU 21.
  • the relay device 3 in FIG. 1 includes an expansion valve 31, an intermediate heat exchanger 32, a pump 33, and a control device 4.
  • the expansion valve 31 expands the refrigerant.
  • the expansion valve 31 is configured by a valve capable of controlling the opening degree, such as an electronic expansion valve. The opening degree of the expansion valve 31 is controlled by the control device 4.
  • the intermediate heat exchanger 32 functions as a condenser or an evaporator, and between the refrigerant flowing through the refrigerant circuit connected to the refrigerant side flow path and the heat medium flowing through the heat medium circuit connected to the heat medium side flow path. Perform heat exchange at.
  • the intermediate heat exchanger 32 functions as an evaporator that evaporates the refrigerant during the cooling operation and cools the heat medium by heat of vaporization when the refrigerant evaporates. Further, the intermediate heat exchanger 32 functions as a condenser that radiates the heat of the refrigerant to the heat medium and condenses the refrigerant during the heating operation.
  • the pump 33 is driven by a motor (not shown) and circulates water as a heat medium flowing through the heat medium pipe 20.
  • the pump 33 is composed of, for example, a pump capable of capacity control, and the flow rate can be adjusted according to the magnitude of the load in the indoor units 2a to 2c.
  • the drive of the pump 33 is controlled by the control device 4. Specifically, the pump 33 is controlled by the control device 4 so that the flow rate of water increases as the load increases, and the flow rate of water decreases as the load decreases.
  • Control device 4 Based on various information received from each part such as the temperature before and after each use-side heat exchanger 121 and the pressure of the heat medium before and after the pump 33 in the air conditioner 100, the control device 4 is connected to the outdoor unit 1, the indoor units 2a to 2c, and the relay. The overall operation of the air conditioner 100 including the device 3 is controlled. Specifically, the control device 4 controls the operating frequency of the compressor 11, the driving of the pump 33, the opening degree of the heat medium flow control valve 22, the opening degree of the expansion valve 31, and the like. In particular, in the first embodiment, the control device 4 controls the driving of the pump 33 and the opening degree of the heat medium flow control valve 22 based on the capability of each FCU 21.
  • the control device 4 is configured with various functions by executing software on an arithmetic device such as a microcomputer, or configured with hardware such as a circuit device that realizes various functions.
  • the control device 4 is provided inside the relay device 3, but is not limited thereto, and may be provided in any of the outdoor unit 1 and the indoor units 2a to 2c, or separately. May be provided.
  • FIG. 3 is a functional block diagram showing an example of the configuration of the control device 4 of FIG.
  • the control device 4 includes an FCU capacity calculation unit 41, a valve opening degree determination unit 42, a valve control unit 43, a heat medium flow rate determination unit 44, a pump control unit 45, and a storage unit 46.
  • the FCU capability calculation unit 41 calculates the FCU capability (hereinafter simply referred to as “FCU capability”) that should be exhibited by each FCU 21.
  • the FCU capacity indicates the operation capacity [kW] of the FCU 21 necessary for air conditioning to the set temperature.
  • the FCU capacity includes various temperatures detected by the inlet temperature sensor 24, the outlet temperature sensor 25, and the suction temperature sensor 26, and the FCU setting capacity, the set inlet / outlet temperature difference, and the set water / air temperature difference stored in the storage unit 46. Calculated based on
  • the FCU setting capability indicates an FCU capability preset in each FCU 21.
  • the set inlet / outlet temperature difference indicates a set temperature difference between the outlet water temperature of the water flowing out from the FCU 21 and the inlet water temperature of the flowing in water.
  • the set water air temperature difference indicates a set temperature difference between the intake air temperature of the air sucked into the FCU 21 and the inlet water temperature of the water flowing into the FCU 21.
  • the valve opening degree determination unit 42 determines the opening degree of the corresponding heat medium flow control valve 22 based on the calculated FCU capacity in each FCU 21.
  • the valve control unit 43 generates a control signal for controlling the opening degree of each heat medium flow rate adjustment valve 22 based on the opening degree determined by the valve opening degree determination unit 42, and each heat medium flow rate adjustment valve 22 is supplied.
  • the heat medium flow rate determination unit 44 determines the flow rate of water flowing through each FCU 21 based on the calculated FCU capacity of each FCU 21. Specifically, the heat medium flow rate determination unit 44 determines the flow rate of water such that the larger the FCU capacity is, the larger the amount of water that flows to the corresponding FCU 21 is, and the smaller the FCU capacity is, the smaller the amount of water is.
  • the pump control unit 45 generates a control signal for controlling the driving of the pump 33 based on the flow rate of water determined by the heat medium flow rate determination unit 44 and supplies the control signal to the pump 33.
  • the storage unit 46 stores in advance the FCU setting capability, the set inlet / outlet temperature difference, and the set water / air temperature difference used by the FCU capability calculating unit 41.
  • FIG. 4 is a top sectional view showing an example of the structure of the heat medium flow control valve 22 of FIG.
  • the heat medium flow control valve 22 has a hollow cylindrical main body 22d, and an inlet 22a into which the heat medium flows is formed at the center of the upper surface or the bottom surface of the main body 22d.
  • a first outlet 22b and a second outlet 22c through which the heat medium flows out are formed on the side surface of the main body 22d of the heat medium flow control valve 22.
  • the first outlet 22 b is connected to the FCU 21, and the second outlet 22 c is connected to the indoor bypass pipe 23.
  • the side surface of the main body 22d is a first region of 0 ° to 120 °, and 120 ° to 240 It is divided into a second region of ° and a third region of 240 ° to 360 °.
  • the 1st outflow port 22b is formed in the 1st area
  • the 2nd outflow port 22c is formed in the 2nd area
  • a cylindrical opening adjustment valve 22e is provided in the internal space of the main body 22d.
  • the opening adjustment valve 22e is formed with an opening 22h in which a part of the arc of the cross section is opened, and the cross section is formed in a C shape.
  • the opening 22h at this time is formed in a range of 120 ° with the central axis as the center.
  • the inner periphery of the side surface in the third region different from the first region and the second region has the first region and the second region.
  • a side wall 22f having a thickness larger than that of the side surface is formed.
  • the side wall 22f is provided in contact with the outer periphery of the opening degree adjusting valve 22e.
  • a partition wall 22g is formed on the inner periphery of the side surface at the boundary between the first region and the second region so as to be in contact with the opening degree adjusting valve 22e.
  • the partition wall 22g distributes the amount of water flowing in from the inflow port 22a into the amount of water flowing out from the first outflow port 22b and the second outflow port 22c, respectively.
  • the opening adjustment valve 22e rotates around the central axis so as to follow the side wall 22f and the partition wall 22g.
  • the opening adjustment valve 22e rotates around the central axis so as to follow the side wall 22f and the partition wall 22g.
  • FIG. 5 to 10 are top sectional views schematically showing a state in which the opening degree adjusting valve 22e of the heat medium flow rate adjusting valve 22 in FIG. 4 is rotated.
  • the opening degree of the opening degree adjustment valve 22e when the inflow port 22a and the first outflow port 22b communicate with each other and the water flows is referred to as an FCU opening degree.
  • the opening degree of the opening degree adjustment valve 22e when the inflow port 22a and the second outflow port 22c communicate with each other and water flows is referred to as a bypass opening degree.
  • FIG. 5 is a top sectional view schematically showing a first state of the heat medium flow control valve 22 of FIG.
  • the opening 22h of the opening degree adjusting valve 22e coincides between one end of the side wall 22f and the partition wall 22g.
  • the opening degree of the heat medium flow control valve 22 is such that the FCU opening degree is 100% and the bypass opening degree is 0%. That is, the flow rate of water flowing out from the first outlet 22b is 100% of the flow rate of water flowing into the inlet 22a.
  • FIG. 6 is a top sectional view schematically showing a second state in the heat medium flow control valve 22 of FIG.
  • the opening adjustment valve 22e rotates clockwise from the first state, and the opening 22h of the opening adjustment valve 22e straddles the partition wall 22g.
  • the FCU opening degree is X% and the bypass opening degree is (100-X)%. That is, the flow rate of water flowing out from the first outlet 22b is X% of the flow rate of water flowing into the inlet 22a.
  • the flow rate of water flowing out from the second outlet 22c is (100 ⁇ X)% of the flow rate of water flowing into the inlet 22a.
  • FIG. 7 is a top sectional view schematically showing a third state in the heat medium flow control valve 22 of FIG.
  • the opening adjustment valve 22e rotates clockwise from the second state, and the opening 22h of the opening adjustment valve 22e coincides between the partition 22g and the other end of the side wall 22f. ing.
  • the opening degree of the heat medium flow control valve 22 is 0% for the FCU opening degree and X% for the bypass opening degree. That is, the flow rate of water flowing out from the second outlet 22c is 100% of the flow rate of water flowing into the inlet 22a.
  • FIG. 8 is a top sectional view schematically showing a fourth state in the heat medium flow control valve 22 of FIG.
  • the opening adjustment valve 22e rotates clockwise from the third state, and the opening 22h of the opening adjustment valve 22e straddles the other end of the side wall 22f.
  • the opening degree of the heat medium flow control valve 22 is 0% for the FCU opening degree and X% for the bypass opening degree. That is, the flow rate of water flowing out from the second outlet 22c is X% of the flow rate of water flowing into the inlet 22a.
  • FIG. 9 is a top sectional view schematically showing a fifth state in the heat medium flow control valve 22 of FIG.
  • the opening adjustment valve 22e rotates clockwise from the fourth state, and the opening 22h of the opening adjustment valve 22e is between one end and the other end of the side wall 22f.
  • the opening degree of the heat medium flow control valve 22 is 0% for the FCU opening degree and 0% for the bypass opening degree. That is, all water flowing into the inflow port 22a is blocked.
  • the opening degree of the heat medium flow control valve 22 is set as shown in FIG. Water flow is interrupted. Therefore, the burden on the pump 33 can be reduced.
  • FIG. 10 is a top sectional view schematically showing a sixth state in the heat medium flow control valve 22 of FIG.
  • the opening adjustment valve 22e rotates clockwise from the fifth state, and the opening 22h of the opening adjustment valve 22e straddles one end of the side wall 22f.
  • the opening degree of the heat medium flow control valve 22 is such that the FCU opening degree is X% and the bypass opening degree is 0%. That is, the flow rate of water flowing out from the first outlet 22b is X% of the flow rate of water flowing into the inlet 22a.
  • the flow rate of the heat medium flow control valve 22 is adjusted from both the first outlet 22b and the second outlet 22c by controlling the opening degree, so that the water flowing into the inlet 22a is adjusted. Water can flow out in a wet state.
  • FIG. 11 is a schematic diagram for explaining the flow of the heat medium.
  • the air conditioner 100 has three indoor units 2 connected in series.
  • a group of a plurality of indoor units 2 connected in series is referred to as a “system”. That is, the air conditioner 100 shown in FIG. 11 is configured such that a system # 1 including a plurality of indoor units 2a to 2c connected in series is connected in parallel to the relay device 3.
  • the water flowing out from the intermediate heat exchanger 32 flows out from the relay device 3 via the heat medium pipe 20.
  • the water that flows out from the relay device 3 flows into the foremost indoor unit 2a in the system # 1.
  • Water flowing into the indoor unit 2a of the system # 1 flows through the FCU 21a or the indoor bypass pipe 23 at a flow rate corresponding to the opening degree setting of the heat medium flow control valve 22.
  • the water that has flowed into the FCU 21a exchanges heat with the room air to absorb or dissipate heat to cool or heat the room air and flow out of the FCU 21a.
  • the water flowing out from the FCU 21a and the water flowing through the indoor bypass pipe 23 merge on the downstream side of the FCU 21a and flow into the subsequent indoor unit 2b.
  • the water flowing into the indoor unit 2b flows through the FCU 21b or the indoor bypass pipe 23 at a flow rate corresponding to the opening setting of the heat medium flow control valve 22.
  • the water flowing into the FCU 21b exchanges heat with the room air to absorb or dissipate heat to cool or heat the room air and flow out of the FCU 21b.
  • the water flowing out from the FCU 21b and the water flowing through the indoor bypass pipe 23 merge on the downstream side of the FCU 21b and flow into the subsequent indoor unit 2c.
  • the water flowing into the indoor unit 2c flows through the FCU 21c or the indoor bypass pipe 23 at a flow rate corresponding to the opening degree setting of the heat medium flow control valve 22.
  • the water flowing into the FCU 21c exchanges heat with the room air to absorb or dissipate heat to cool or heat the room air and flow out of the FCU 21c.
  • the water flowing out from the FCU 21c and the water flowing through the indoor bypass pipe 23 merge on the downstream side of the FCU 21c and flow out from the indoor unit 2c.
  • the water flowing out from the indoor unit 2c flows into the relay device 3 through the heat medium pipe 20.
  • the water that flows into the relay device 3 flows into the intermediate heat exchanger 32 via the pump 33. Thereafter, the above-described circulation is repeated.
  • the air conditioner 100 performs a flow rate adjustment process for adjusting the flow rate of water to each FCU 21 so that the required flow rate of water flows to each FCU 21 in the system # 1. Do.
  • the opening degree of the heat medium flow rate adjustment valve 22 corresponding to each FCU 21 is controlled in order to adjust the flow rate of water to each FCU 21.
  • the flow rate of water flowing through the FCU 21 can be calculated based on the differential pressure of water before and after passing through the heat medium flow control valve 22 and the Cv value representing the characteristics of the heat medium flow control valve 22.
  • the Cv value is a value determined by the type and port diameter of the heat medium flow control valve 22 and is a capacity coefficient of the valve.
  • the Cv value is a numerical value representing the flow rate of the fluid passing through the valve with a certain differential pressure. The larger the Cv value, the larger the water flow rate, and the smaller the Cv value, the smaller the water flow rate.
  • the FCU capacity calculation unit 41 calculates the FCU capacity that should be exhibited at each FCU 21 in the system # 1.
  • the FCU capacity of each FCU 21 is determined by using the FCU setting capacity preset in each FCU 21, the inlet water temperature and the outlet water temperature of water flowing into and out of the FCU 21, and the intake air temperature of the indoor air sucked by the fan 122. Calculated based on equation (1).
  • FCU capacity FCU setting capacity x (inlet / outlet temperature difference / set inlet / outlet temperature difference) ⁇ (Water / air temperature difference / set water / air temperature difference) ... (1)
  • the inlet / outlet temperature difference indicates the temperature difference between the current outlet water temperature of the water flowing out from the FCU 21 and the current inlet water temperature of the flowing in water.
  • the water / air temperature difference indicates a temperature difference between the current intake air temperature of the air sucked into the FCU 21 and the current inlet water temperature of the water flowing into the FCU 21.
  • the valve opening determining unit 42 determines the FCU 21 having the highest FCU capability as the representative FCU of the system among the calculated FCUs 21 in the system # 1. Then, the valve opening degree determination unit 42 determines the opening degree of the heat medium flow control valve 22 corresponding to the representative FCU so as to be fully opened to the FCU 21 side. Further, the valve opening degree determination unit 42 determines the opening degree of the heat medium flow control valve 22 corresponding to the FCU 21 other than the representative FCU based on the capacity ratio with the representative FCU.
  • FIG. 12 is a schematic diagram showing the opening degree of the heat medium flow control valve 22 corresponding to each FCU 21a to 21c of the system # 1 in FIG.
  • the FCU number is a number unique to each FCU 21 in the system # 1.
  • the FCU capability indicates the FCU capability of each FCU 21.
  • the heat medium flow adjustment valve opening indicates the opening of the heat medium flow adjustment valve 22 corresponding to each FCU 21, and indicates the opening on the FCU 21 side and the indoor bypass pipe 23 side.
  • the valve opening degree determination unit 42 determines the FCU 21c as the representative FCU of the system # 1. Then, the valve opening determining unit 42 sets the FCU opening of the heat medium flow control valve 22 corresponding to the FCU 21c to 100%, that is, fully opened to the FCU 21c side.
  • the bypass opening is determined to be 80%.
  • thermo-off indicates a case where the fan 122 of the FCU 21 is stopped. Specifically, for example, when the room temperature exceeds the set temperature during the heating operation, or when the room temperature falls below the set temperature during the cooling operation, the FCU 21 is thermo-off.
  • the control device 4 adjusts the opening degree of the heat medium flow control valve 22 according to the fluctuation of the thermo-OFF or the FCU capacity.
  • FIG. 13 is a schematic diagram showing the opening degree of the heat medium flow control valve 22 when the FCU 21b is thermo-OFF.
  • FIG. 14 is a schematic diagram showing the opening degree of the heat medium flow control valve 22 when the FCU capacity of the FCU 21c that is the representative FCU fluctuates.
  • the valve opening degree determination unit 42 determines the FCU opening degree of the heat medium flow control valve 22 corresponding to the FCU 21b as 0% and the bypass opening degree as 100%. In this case, since the FCU capacity of the FCU 21c, which is the representative FCU, has not changed, only the opening degree of the heat medium flow control valve 22 corresponding to the FCU 21b that is thermo-OFF is changed.
  • the FCU capacity of the FCU 21c that is the representative FCU changes, the capacity ratio of the FCU 21a and the FCU capacity of the 21b to the FCU capacity of the FCU 21c changes.
  • the FCU capacity of the FCU 21 c that is the representative FCU varies from 5 kW to 3 kW, and the FCU capacity of the FCUs 21 a and 21 b is 1/3 of the FCU capacity of the FCU 21 c.
  • the valve opening determining unit 42 determines the FCU opening of each heat medium flow control valve 22 corresponding to the FCUs 21a and 21b to 33% ( ⁇ 100% ⁇ 1/3), and the bypass opening 67%. To decide. As described above, when the FCU capacity of the FCU 21c that is the representative FCU fluctuates, the opening degree of the heat medium flow control valve 22 corresponding to the FCUs 21a and 21b other than the representative FCU is changed.
  • the FCU capability that should be exhibited at present is used as the FCU capability for controlling the opening degree of the heat medium flow control valve 22.
  • the present invention is not limited to this.
  • an FCU that is predetermined for each FCU 21 is used.
  • the setting ability may be used as it is. Thereby, it is not necessary to calculate the FCU capacity to be exhibited at each FCU 21, and the configuration related to the opening degree control of the heat medium flow control valve 22 can be simplified.
  • the representative FCU in the system is determined, and the heat medium corresponding to each FCU according to the capacity ratio between the FCU capacity of the representative FCU and the FCU capacity of the other FCU 21 is determined.
  • the opening degree of the flow regulating valve 22 is determined.
  • the representative FCU of each system is determined based on the FCU capacity of each FCU 21.
  • the present invention is not limited to this.
  • the representative FCU of each system may be determined in advance.
  • the indoor side bypass pipe 23 of the indoor unit 2 corresponding to the representative FCU can be omitted.
  • the heat medium flow rate adjustment valve 22 does not have to be provided with a plurality of outlets, and has a function of adjusting the flow rate of the inflowing water to flow out. It only has to have.
  • the plurality of indoor units 2 each having the indoor bypass pipe 23 are connected in series.
  • the heat of the heat medium is used by the plurality of indoor units 2, thereby reducing the remaining heat of the heat medium.
  • the heat medium is water
  • the phase change in the heat medium circuit is small, and the temperature change of the heat medium is small compared to the refrigerant. Therefore, a plurality of indoor units 2 can be connected in series.
  • the indoor units 2a to 2c include a heat medium flow rate adjustment valve 22 capable of adjusting the flow rate, a use-side heat exchanger 121 connected to the first outlet 22b of the heat medium flow rate adjustment valve 22, and a heat medium flow rate adjustment. And an indoor bypass pipe 23 connected to the second outlet 22 c of the valve 22. Moreover, in the air conditioner 100, the some indoor unit 2 is connected in series. Thereby, since the water of the required flow volume flows into FCU21, the heat which water has can be used efficiently.
  • the air conditioner 100 includes a control device 4 that controls the opening degree of the heat medium flow control valve 22 according to the capabilities of the FCU 21 of each of the plurality of indoor units 2a to 2c.
  • the control device 4 has a plurality of heat medium flow rates according to the capacity ratio between the FCU capacity of the representative FCU having the highest FCU capacity and the FCU capacity of other FCUs 21 among the FCU capacity of the FCUs 21 of the plurality of indoor units 2.
  • a valve opening determining unit 42 that adjusts the opening of the adjusting valve 22 is provided. Thereby, it is possible to supply a necessary amount of water to each FCU 21.
  • control device 4 further includes an FCU capacity calculation unit 41 that calculates the FCU capacity of each of the plurality of FCUs 21 based on the inlet temperature, the outlet temperature, and the intake air temperature of the FCU 21. As a result, the FCU capability that should be exhibited at each FCU 21 can be calculated.
  • Embodiment 2 an air conditioner according to Embodiment 2 of the present invention will be described.
  • system # 1 including indoor units 2a to 2c connected in series and system # 2 including a plurality of indoor units 2d to 2f connected in series are connected in parallel.
  • system # 1 including indoor units 2a to 2c connected in series and system # 2 including a plurality of indoor units 2d to 2f connected in series are connected in parallel.
  • FIG. 15 is a schematic diagram illustrating an example of the configuration of the air conditioner 200 according to Embodiment 2.
  • the air conditioner 200 includes an outdoor unit 1, a plurality of indoor units 2a to 2f, and a relay device 3.
  • a refrigerant circuit is formed by connecting the outdoor unit 1 and the relay device 3 through the refrigerant pipe 10.
  • the plurality of indoor units 2a to 2f and the relay device 3 are connected by the heat medium pipe 20, whereby a heat medium circuit is formed.
  • the indoor units 2a to 2c are connected in series to configure the system # 1
  • the indoor units 2d to 2f are connected in series to configure the system # 2.
  • the indoor units 2a to 2c of the system # 1 and the indoor units 2d to 2f of the system # 2 are connected in parallel.
  • the water flowing out from the intermediate heat exchanger 32 flows out from the relay device 3 via the heat medium pipe 20.
  • the water flowing out from the relay device 3 branches into two systems # 1 and # 2, and flows into the foremost indoor units 2a and 2d in each system # 1 and # 2.
  • strain # 1 since it is the same as that of Embodiment 1, description is abbreviate
  • Water flowing into the indoor unit 2d of the system # 2 flows through the FCU 21d or the indoor bypass pipe 23 at a flow rate corresponding to the opening setting of the heat medium flow control valve 22.
  • the water that flows into the FCU 21d exchanges heat with the indoor air, absorbs or dissipates heat, cools or heats the indoor air, and flows out of the FCU 21d.
  • the water flowing out from the FCU 21d and the water flowing through the indoor bypass pipe 23 merge on the downstream side of the FCU 21d, and flow into the indoor unit 2e at the subsequent stage.
  • the water flowing into the indoor unit 2e flows through the FCU 21e or the indoor bypass pipe 23 at a flow rate corresponding to the opening setting of the heat medium flow control valve 22.
  • the water that flows into the FCU 21e exchanges heat with the room air to absorb or dissipate heat to cool or heat the room air and flow out of the FCU 21e.
  • the water flowing out from the FCU 21e and the water flowing through the indoor bypass pipe 23 merge on the downstream side of the FCU 21e, and flow into the subsequent indoor unit 2f.
  • the water that flows into the indoor unit 2f flows through the FCU 21f or the indoor bypass pipe 23 at a flow rate that corresponds to the opening degree setting of the heat medium flow control valve 22.
  • the water that has flowed into the FCU 21f exchanges heat with the room air, absorbs or dissipates heat, cools or heats the room air, and flows out of the FCU 21f.
  • the water flowing out from the FCU 21f and the water flowing through the indoor bypass pipe 23 merge on the downstream side of the FCU 21f and flow out from the indoor unit 2f.
  • the water flowing out from the last indoor units 2c and 2f in each system # 1 and # 2 merges and then flows into the relay device 3 through the heat medium pipe 20.
  • the water that flows into the relay device 3 flows into the intermediate heat exchanger 32 via the pump 33. Thereafter, the above-described circulation is repeated.
  • the air conditioner 200 according to Embodiment 2 has a plurality of systems in which a plurality of indoor units 2 are connected in series, and the plurality of systems are connected in parallel. In this way, even when a plurality of systems composed of a plurality of indoor units 2 connected in series are provided, water in a necessary amount flows to the FCU 21 as in the first embodiment. Can efficiently utilize the heat of the.
  • Embodiment 3 an air conditioner according to Embodiment 3 of the present invention will be described.
  • system # 1 of indoor units 2a to 2c connected in series system # 2 of a plurality of indoor units 2d to 2f connected in series, and a plurality of indoor units connected in series
  • 2g to 2i of system # 3 are connected in parallel. Note that, in the following description, the same reference numerals are given to configurations common to Embodiments 1 and 2, and detailed description thereof is omitted.
  • FIG. 16 is a schematic diagram illustrating an example of a configuration of the air conditioner 300 according to the third embodiment.
  • the air conditioner 300 includes an outdoor unit 1, a plurality of indoor units 2a to 2i, and a relay device 3.
  • a refrigerant circuit is formed by connecting the outdoor unit 1 and the relay device 3 through the refrigerant pipe 10.
  • the plurality of indoor units 2a to 2i and the relay device 3 are connected by the heat medium pipe 20, whereby a heat medium circuit is formed.
  • the indoor units 2a to 2c are connected in series to form the system # 1
  • the indoor units 2d to 2f are connected in series to form the system # 2
  • the indoor units 2g to 2i are connected in series.
  • System # 3 is configured.
  • the indoor units 2a to 2c of the system # 1, the indoor units 2d to 2f of the system # 2, and the indoor units 2g to 2i of the system # 3 are connected in parallel.
  • an air conditioner 300 has a system # 1 in which indoor units 2a to 2c are connected in series, a system # 2 in which indoor units 2d to 2f are connected in series, and indoor units 2g to 2i are connected in series.
  • the system # 3 is connected in parallel to the relay device 3.
  • the water flowing out from the intermediate heat exchanger 32 flows out from the relay device 3 via the heat medium pipe 20.
  • the water flowing out from the relay device 3 branches into three systems # 1 to # 3 and flows into the foremost indoor units 2a, 2d and 2g in each system # 1 to # 3. Since the flow of water in the system # 1 and the system # 2 is the same as that in the second embodiment, the description thereof is omitted here.
  • Water flowing into the indoor unit 2g of the system # 3 flows through the FCU 21g or the indoor bypass pipe 23 at a flow rate according to the opening degree setting of the heat medium flow control valve 22.
  • the water that flows into the FCU 21g exchanges heat with the room air, absorbs heat or dissipates it, cools or heats the room air, and flows out of the FCU 21g.
  • the water flowing out from the FCU 21g and the water flowing through the indoor bypass pipe 23 merge on the downstream side of the FCU 21g and flow into the subsequent indoor unit 2h.
  • the water flowing into the indoor unit 2h flows through the FCU 21h or the indoor bypass pipe 23 at a flow rate corresponding to the opening degree setting of the heat medium flow control valve 22.
  • the water that flows into the FCU 21h exchanges heat with the room air to absorb or dissipate heat to cool or heat the room air and flow out of the FCU 21h.
  • the water flowing out of the FCU 21h and the water flowing through the indoor bypass pipe 23 merge on the downstream side of the FCU 21h and flow into the subsequent indoor unit 2i.
  • the water flowing into the indoor unit 2i flows through the FCU 21i or the indoor bypass pipe 23 at a flow rate corresponding to the opening setting of the heat medium flow control valve 22.
  • the water flowing into the FCU 21i exchanges heat with the room air to absorb or dissipate heat to cool or heat the room air and flow out of the FCU 21i.
  • the water flowing out from the FCU 21i and the water flowing through the indoor side bypass pipe 23 merge on the downstream side of the FCU 21i, and flow out from the indoor unit 2i.
  • the water that has flowed out of the last indoor units 2c, 2f, and 2i in each of the systems # 1 to # 3 merges, and then flows into the relay device 3 through the heat medium pipe 20.
  • the water that flows into the relay device 3 flows into the intermediate heat exchanger 32 via the pump 33. Thereafter, the above-described circulation is repeated.
  • FIGS. 17 to 20 are schematic diagrams illustrating the opening degree of the heat medium flow control valve 22 when the FCU capacity of the representative FCU differs for each of the systems # 1 to # 3.
  • the FCU 21 indicated by the bold line is the representative FCU in each of the systems # 1 to # 3.
  • FIG. 17 is a schematic diagram showing a first example of the opening degree of the heat medium flow control valve when the FCU capacity of the representative FCU is different for each of the systems # 1 to # 3.
  • the FCU opening degree of the heat medium flow control valve 22 corresponding to the representative FCU in all the systems # 1 to # 3 is set to 100% regardless of the size of the FCU capacity of the representative FCU. This is an example.
  • the representative FCUs of the systems # 1 to # 3 are the FCUs 21c, 21e, and 21g, respectively. Therefore, the heat medium flow control valves 22 corresponding to these FCUs 21c, 21e and 21g are set as shown in FIG. In this case, water flows uniformly in each of the systems # 1 to # 3, and the FCU opening degree of the heat medium flow control valve 22 corresponding to the representative FCU of each of the systems # 1 to # 3 is 100%. Therefore, the control of the heat medium flow control valve 22 corresponding to the representative FCU can be simplified.
  • the representative FCU of system # 2 has the highest FCU capacity, and water equivalent to system # 2 flows through system # 1 and system # 3. For this reason, the system # 1 and the system # 3 have excessive capacity, and the indoor space may be overcooled or overheated. Therefore, in this case, it is preferable to prevent over-cooling or over-warming by performing thermo-OFF in the system # 1 and the system # 3.
  • valve opening determination unit 42 thermo-OFFs the FCU 21a with the bypass opening of the heat medium flow control valve 22 corresponding to the FCU 21a in the system # 1 as 100%. Further, the valve opening determination unit 42 thermo-OFFs the FCU 21i with the bypass opening of the heat medium flow control valve 22 corresponding to the FCU 21i in the system # 3 as 100%.
  • FIG. 18 is a schematic diagram showing a second example of the opening degree of the heat medium flow control valve when the FCU capacity of the representative FCU is different for each of the systems # 1 to # 3.
  • a throttle device for adjusting the flow rate is provided.
  • each system # 1 to # 3 is supplied with an amount of water necessary for each system.
  • the FCU 21e which is the representative FCU of the system # 2
  • the control device 4 fully opens the aperture of the throttle device of the system # 2, and determines the apertures of the throttle devices of the systems # 1 and # 3 based on the FCU capacity of the representative FCU of the system # 2.
  • the FCU capacity of the FCU 21c that is the representative FCU of the system # 1 is 5 kW
  • the opening degree of the expansion device of the system # 1 is determined to be 71% ( ⁇ 5 kW / 7 kW ⁇ 100%).
  • the FCU capacity of the FCU 21g that is the representative FCU of the system # 3 is 4 kW
  • the opening degree of the expansion device of the system # 3 is determined to be 57% ( ⁇ 4 kW / 7 kW ⁇ 100%).
  • the heat-medium flow control valve 22 when there exists FCU21 which carries out thermo-OFF in a system
  • FIG. 19 is a schematic diagram showing a third example of the opening degree of the heat medium flow control valve when the FCU capacity of the representative FCU is different for each of the systems # 1 to # 3.
  • the third example shown in FIG. 19 is an example in which the FCU opening degree of the heat medium flow control valve 22 corresponding to the representative FCU in each of the systems # 1 to # 3 is varied according to the size of the FCU capacity of the representative FCU. .
  • the FCU opening degree of the heat medium flow control valve 22 corresponding to the representative FCU having the highest FCU capacity is determined to be 100%. . Then, the FCU opening degree of the heat medium flow control valve 22 corresponding to the other representative FCU is determined according to the capacity ratio.
  • the FCU capacity of FCU 21e which is the representative FCU of system # 2
  • the FCU capacity is 7 kW
  • the FCU capacity is the highest. Therefore, the control device 4 sets the FCU opening degree of the heat medium flow control valve 22 corresponding to the representative FCU of the system # 2 to 100%. Then, the control device 4 uses the FCU opening degree of the heat medium flow control valve 22 as a reference, and according to the ratio of the FCU capacity of the representative FCU, the heat medium flow control valve corresponding to the representative FCUs of the systems # 1 and # 3. 22 FCU opening is determined.
  • the FCU capacity of the FCU 21c that is the representative FCU of the system # 1 is 5 kW. Therefore, the FCU opening degree of the heat medium flow control valve 22 corresponding to the representative FCU of the system # 1 is 71% ( ⁇ 5 kW / 7 kW ⁇ 100%) due to the capacity ratio with the FCU capacity of the representative FCU in the system # 2. It is determined. Further, the FCU capacity of the FCU 21g which is the representative FCU of the system # 3 is 4 kW. Therefore, the FCU opening degree of the heat medium flow control valve 22 corresponding to the representative FCU of the system # 3 is 57% ( ⁇ 4 kW / 7 kW ⁇ 100%) due to the capacity ratio with the FCU capacity of the representative FCU in the system # 2. It is determined.
  • the indoor units 2 of each system # 1 to # 3 are installed by varying the opening degree of the heat medium flow control valve 22 according to the FCU capacity of the representative FCU for each system # 1 to # 3. It is possible to perform fine control such as controlling the air conditioning capacity for each air conditioning space. Moreover, since it is suppressed that the water of the flow volume more than necessary flows into FCU21, the utilization efficiency of heat can be improved more.
  • the FCU capacity necessary for each FCU 21 can be exhibited, but the same flow rate of water flows to each of the systems # 1 to # 3. Therefore, an excessive amount of water flows through the systems # 1 and # 3.
  • FIG. 20 is a schematic diagram showing a fourth example of the opening degree of the heat medium flow control valve when the FCU capacity of the representative FCU is different for each of the systems # 1 to # 3.
  • the fourth example shown in FIG. 20 is a heat medium flow rate corresponding to a representative FCU of a system other than the system including the representative FCU having the highest capability so as to suppress the flow of an excessive flow of water in the third example.
  • This is an example of adjusting the opening degree of the adjusting valve 22.
  • the valve opening degree determination unit 42 sets the FCU opening degree of the heat medium flow control valve 22 corresponding to the FCU 21e that is the representative FCU of the system # 2 to 100%. . Further, the valve opening determining unit 42 sets the opening degree of the heat medium flow control valve 22 corresponding to the representative FCUs 21c and 21g of the systems # 1 and # 3 other than the system # 2 as shown in FIG. To do. As shown in FIG. 10, the amount of water flowing to the FCU 21 subsequent to the corresponding FCU 21 is adjusted by setting the opening of the heat medium flow control valve 22.
  • the FCU opening degree of the heat medium flow rate adjustment valve 22 corresponding to the representative FCUs of the system # 1 and # 3 is represented by the FCU opening degree of the heat medium flow rate adjustment valve 22 corresponding to the representative FCU of the system # 2. It is set according to the ratio of the FCU capacity of the FCU. Moreover, the bypass opening degree of the heat medium flow control valve 22 at this time is set to 0%.
  • the heat medium flow control valve 22 corresponding to the FCU 21c that is the representative FCU of the system # 1 is set so that the FCU opening is 71% and the bypass opening is 0%. Further, the heat medium flow control valve 22 corresponding to the FCU 21g that is the representative FCU of the system # 3 is set so that the FCU opening degree is 57% and the bypass opening degree is 0%.
  • the opening degree of the heat medium flow rate adjustment valve 22 is set so that the bypass opening degree of the heat medium flow rate adjustment valve 22 corresponding to the representative FCU of the system other than the system including the representative FCU having the highest capacity becomes 0%.
  • the amount of water for each of the systems # 1 to # 3 can be adjusted.
  • the valve opening determination unit 42 fully opens the opening of the heat medium flow control valve 22 corresponding to the representative FCU of each system. Moreover, the valve opening degree determination part 42 determines the opening degree of the heat medium flow control valve 22 corresponding to another FCU based on the capacity ratio. Thereby, the opening degree control of the heat medium flow control valve 22 in each system can be simplified.
  • a throttle device is provided at the foremost stage of each system, and the control device 4 determines the opening degree of the throttle device of each system according to the capacity ratio of the representative FCU of each system. Thereby, the amount of water required for each system can be supplied.
  • valve opening determination unit 42 fully opens the opening of the heat medium flow control valve 22 connected to the representative FCU having the highest FCU capability among the representative FCUs of the respective systems. Further, the valve opening determining unit 42 determines the opening of the heat medium flow control valve 22 connected to another representative FCU based on the capacity ratio with the FCU capacity of the representative FCU having the highest capacity. The valve opening determination unit 42 then opens the opening of the heat medium flow control valve 22 corresponding to the other representative FCU so that the second outlet 22c communicates with the heat medium outflow side of the other representative FCU. To decide. Thereby, since the flow volume of the water with respect to each system
  • Embodiment 4 FIG. Next, an air conditioner according to Embodiment 4 of the present invention will be described.
  • the fourth embodiment is different from the first to third embodiments in that an indoor side control device is provided for each of the indoor units 2a to 2i. Note that, in the following description, the same reference numerals are given to configurations common to Embodiments 1 to 3, and detailed description thereof is omitted.
  • FIG. 21 is a schematic diagram illustrating an example of a configuration of the air conditioner 400 according to the fourth embodiment.
  • the air conditioner 400 includes an outdoor unit 1, a plurality of indoor units 2a to 2i, and a relay device 3.
  • a refrigerant circuit is formed by connecting the outdoor unit 1 and the relay device 3 through the refrigerant pipe 10.
  • the plurality of indoor units 2a to 2i and the relay device 3 are connected by the heat medium pipe 20, whereby a heat medium circuit is formed.
  • the indoor units 2a to 2c are connected in series to form the system # 1
  • the indoor units 2d to 2f are connected in series to form the system # 2
  • the indoor units 2g to 2i are connected in series.
  • System # 3 is configured.
  • the indoor units 2a to 2c of the system # 1, the indoor units 2d to 2f of the system # 2, and the indoor units 2g to 2i of the system # 3 are connected in parallel.
  • the indoor units 2a to 2i include an indoor control device 27 in addition to the configuration shown in FIG.
  • the indoor control device 27 controls the equipment of the indoor unit 2 provided with the device itself.
  • the indoor-side control device 27 performs control related to the indoor unit 2 that is its own device among various types of control performed by the control device 4 in the first to third embodiments. Specifically, the indoor side control device 27 controls the calculation of the FCU capacity of the FCU 21 and the opening degree of the heat medium flow control valve 22 based on the calculated FCU capacity.
  • the indoor side control device 27 communicates with the indoor side control device 27 provided in the other indoor unit 2 and the control device 4 provided in the relay device 3. For example, the indoor control device 27 exchanges sensor information such as the inlet temperature sensor 24, the outlet temperature sensor 25 and the suction temperature sensor 26, and information related to the opening control of the heat medium flow control valve 22.
  • the indoor side control device 27 for each of the indoor units 2a to 2i, interlock control can be performed among the outdoor unit 1, the indoor unit 2, and the relay device 3. Further, the replacement of the indoor unit 2 alone can be easily performed.
  • Embodiment 5 FIG. Next, an air conditioner according to Embodiment 5 of the present invention will be described.
  • the fifth embodiment is different from the first to fourth embodiments in that a cooling device and a heating device are provided in the air conditioner. Note that, in the following description, the same reference numerals are given to configurations common to Embodiments 1 to 4, and detailed description thereof is omitted.
  • FIG. 22 is a schematic diagram illustrating an example of a configuration of an air conditioner 500 according to Embodiment 5.
  • the air conditioner 500 includes an outdoor unit 1, a plurality of indoor units 2a to 2c, a relay device 3, a cooling device 5, and a heating device 6.
  • the indoor unit 2 is configured by only the system # 1 will be described as an example.
  • the present invention is not limited thereto, and the indoor unit 2 may be configured by a plurality of systems. Moreover, the indoor unit 2 may not be provided.
  • a refrigerant circuit is formed by connecting the outdoor unit 1 and the relay device 3 with the refrigerant pipe 10.
  • the plurality of indoor units 2a to 2c, the cooling device 5, the heating device 6, and the relay device 3 are connected by the heat medium pipe 20, thereby forming a heat medium circuit.
  • a plurality of indoor units 2a to 2c are connected in series to configure system # 1, and cooling device 5 and heating device 6 are connected in series to configure system # 4.
  • the indoor units 2a to 2c of the system # 1 and the cooling device 5 and the heating device 6 of the system # 4 are connected in parallel.
  • the cooling device 5 generates cold heat, and is provided in a room where heat is constantly generated, such as a refrigerator room, a freezer room, and a computer room, and is provided to cool the room.
  • the cooling device 5 includes a cooling side intermediate heat exchanger 51, a cooling side heat medium flow rate adjustment valve 52, a compressor 53, an expansion valve 54, and a use side heat exchanger 55.
  • the cooling-side intermediate heat exchanger 51 exchanges heat between the heat medium flowing through the heat medium circuit connected to the heat medium side flow path and the cooling refrigerant flowing through the cooling refrigerant circuit connected to the refrigerant side flow path. I do.
  • the cooling-side intermediate heat exchanger 51 functions as a condenser that radiates the heat of the cooling refrigerant to the heat medium and condenses the cooling refrigerant.
  • the cooling-side heat medium flow control valve 52 is an electric three-way valve having an inflow port 52a, a first outflow port 52b, and a second outflow port 52c, and is a water inflow side of the cooling side intermediate heat exchanger 51. Is provided.
  • the cooling-side heat medium flow control valve 52 is provided to branch in flowing water.
  • the first outlet 52 b is connected to the water inflow side of the cooling side intermediate heat exchanger 51.
  • the second outlet 52 c is connected to the water outflow side of the cooling side intermediate heat exchanger 51 via the cooling side bypass pipe 50.
  • the 2nd outflow port 52c of the cooling side heat-medium flow regulating valve 52 and the outflow side of the water of the cooling side intermediate heat exchanger 51 are connected.
  • the cooling side heat medium flow control valve 52 has the same structure as the heat medium flow control valve 22. That is, the cooling-side heat medium flow control valve 52 controls the opening degree of the cooling-side heat medium flow control valve 52 from the first outlet 52b and the second outlet 52c. Water can be discharged with the flow rate adjusted.
  • the cooling side bypass pipe 50 is provided inside the cooling device 5, but the present invention is not limited to this, and the cooling side bypass pipe 50 is provided outside the cooling device 5 and connected. It may be connected to the cooling device 5 via a metal fitting or the like. Thereby, since the piping length of the cooling side bypass piping 50 becomes short, the loss by the heat dissipation etc. when water flows through the inside of piping can be suppressed.
  • the compressor 53 sucks the low-temperature and low-pressure cooling refrigerant, compresses the sucked cooling refrigerant, and discharges the high-temperature and high-pressure cooling refrigerant.
  • the compressor 53 is composed of, for example, an inverter compressor.
  • the operation frequency of the compressor 53 is controlled by the control device 4.
  • the expansion valve 54 expands the cooling refrigerant.
  • the expansion valve 54 is configured by a valve capable of controlling the opening degree, such as an electronic expansion valve.
  • the opening degree of the expansion valve 54 is controlled by a control device of the cooling device 5 (not shown).
  • the use side heat exchanger 55 performs heat exchange between indoor air supplied by a fan (not shown) and the cooling refrigerant. Thereby, the air for cooling which is the conditioned air supplied to indoor space is produced
  • the cooling device 5 includes an inlet temperature sensor 56, an outlet temperature sensor 57, and a suction temperature sensor 58.
  • the inlet temperature sensor 56 is provided on the water inflow side in the cooling side intermediate heat exchanger 51 and detects the temperature of the water flowing into the cooling side intermediate heat exchanger 51.
  • the inlet temperature sensor 56 also serves as detection of the inlet temperature of water in the system # 4.
  • the outlet temperature sensor 57 is provided on the outflow side of the water in the cooling side intermediate heat exchanger 51 and detects the temperature of the water flowing out from the cooling side intermediate heat exchanger 51.
  • the suction temperature sensor 58 is provided on the air suction side of the cooling-side intermediate heat exchanger 51 and detects the suction air temperature of the air sucked into the cooling-side intermediate heat exchanger 51.
  • the heating device 6 generates heat and is provided in a room using radiant heating such as floor heating, a greenhouse for cultivation such as a tropical plant, and a room using hot water such as a hot water supply room. It is provided to generate and store hot water.
  • the heating device 6 includes a heating-side intermediate heat exchanger 61, a heating-side heat medium flow rate adjustment valve 62, a compressor 63, an expansion valve 64, a water heat exchanger 65, a hot water storage tank 71, and a water supply pump 72.
  • the heating-side intermediate heat exchanger 61 exchanges heat between the heat medium flowing through the heat medium circuit connected to the heat medium side flow path and the heating refrigerant flowing through the heating refrigerant circuit connected to the refrigerant side flow path. I do.
  • the heating-side intermediate heat exchanger 61 functions as an evaporator that evaporates the heating refrigerant and cools the heat medium by heat of vaporization when the heating refrigerant evaporates.
  • the heating-side heat medium flow control valve 62 is an electric three-way valve having an inlet 62a, a first outlet 62b, and a second outlet 62c, and is a water inflow side of the heating-side intermediate heat exchanger 61. Is provided.
  • the heating-side heat medium flow control valve 62 is provided to branch in flowing water.
  • the first outlet 62 b is connected to the water inflow side of the heating side intermediate heat exchanger 61.
  • the second outlet 62 c is connected to the water outflow side of the heating side intermediate heat exchanger 61 via the heating side bypass pipe 60. Thereby, the 2nd outflow port 62c of the heating side heat medium flow control valve 62 and the outflow side of the water of the heating side intermediate heat exchanger 61 are connected.
  • the heating side heat medium flow rate adjustment valve 62 has the same structure as the heat medium flow rate adjustment valve 22 and the cooling side heat medium flow rate adjustment valve 52. In other words, the heating-side heat medium flow control valve 62 controls the opening degree of the heating-side heat medium flow control valve 62 from the first outlet 62b and the second outlet 62c. Water can be discharged with the flow rate adjusted.
  • the heating-side bypass pipe 60 is provided inside the heating apparatus 6, but the present invention is not limited to this, and the heating-side bypass pipe 60 is provided outside the heating apparatus 6, and the connection fitting Etc., and may be connected to the heating device 6 via, for example.
  • the piping length of the heating side bypass piping 60 becomes short, the loss by the heat radiation etc. at the time of water flowing in the piping can be suppressed.
  • the compressor 63 sucks the low-temperature and low-pressure heating refrigerant, compresses the sucked heating refrigerant, and discharges the high-temperature and high-pressure heating refrigerant.
  • the compressor 63 is composed of, for example, an inverter compressor. The operating frequency of the compressor 63 is controlled by the control device 4.
  • the expansion valve 64 expands the heating refrigerant.
  • the expansion valve 64 is configured by a valve capable of controlling the opening degree, such as an electronic expansion valve.
  • the opening degree of the expansion valve 64 is controlled by a control device of the heating device 6 (not shown).
  • the water heat exchanger 65 performs heat exchange between a heating medium such as water stored in the hot water storage tank 71 and the heating refrigerant.
  • the hot water storage tank 71 stores water supplied from the outside.
  • the hot water storage tank 71 has a water inlet and an outlet at the lower part, and an inlet at the upper part.
  • the hot water storage tank 71 is supplied with water from the outside through a water supply port, and stores the supplied unheated unheated water. Unheated water stored in the hot water storage tank 71 flows out through the outlet and is supplied to the water heat exchanger 65.
  • the hot water storage tank 71 is supplied with heated water heated by the water heat exchanger 65 through the inflow port, and stores the supplied heated water.
  • the heated water stored in the hot water storage tank 71 is discharged to the outside and used as hot water such as a shower.
  • the water pump 72 is driven by a motor (not shown) and supplies water flowing out from the hot water storage tank 71 to the water heat exchanger 65.
  • the driving of the water pump 72 is controlled by a control device of the heating device 6 (not shown).
  • the heating device 6 includes an inlet temperature sensor 66, an outlet temperature sensor 67, and a heating medium temperature sensor 68.
  • the inlet temperature sensor 66 is provided on the inflow side of water in the heating-side intermediate heat exchanger 61 and detects the temperature of water flowing into the heating-side intermediate heat exchanger 61.
  • the outlet temperature sensor 67 is provided on the water outflow side of the heating side intermediate heat exchanger 61 and detects the temperature of the water flowing out of the heating side intermediate heat exchanger 61.
  • the outlet temperature sensor 67 also serves to detect the outlet temperature of water in the system # 4.
  • the heating medium temperature sensor 68 is provided around the heating side intermediate heat exchanger 61 and detects the temperature of the heating medium around the heating side intermediate heat exchanger 61.
  • the air conditioner 500 includes a system # 1 in which indoor units 2a to 2c are connected in series and a system # 4 in which a cooling device 5 and a heating device 6 are connected in series to the relay device 3. Connected in parallel.
  • the water flowing out from the intermediate heat exchanger 32 flows out from the relay device 3 via the heat medium pipe 20.
  • the water flowing out from the relay device 3 branches into two systems # 1 and # 4, and flows into the foremost indoor unit 2a of the system # 1 and the cooling device 5 of the system # 4.
  • strain # 1 since it is the same as that of Embodiment 1, description is abbreviate
  • Water flowing into the cooling device 5 of the system # 4 flows through the cooling-side intermediate heat exchanger 51 or the cooling-side bypass pipe 50 at a flow rate corresponding to the opening degree setting of the cooling-side heat medium flow rate adjustment valve 52.
  • the water flowing into the cooling side intermediate heat exchanger 51 exchanges heat with the cooling refrigerant to cool the cooling refrigerant, and flows out of the cooling side intermediate heat exchanger 51.
  • the water flowing out from the cooling side intermediate heat exchanger 51 and the water flowing through the cooling side bypass pipe 50 merge on the downstream side of the cooling side intermediate heat exchanger 51 and flow into the subsequent heating apparatus 6.
  • the water that has flowed into the heating device 6 flows through the heating side intermediate heat exchanger 61 or the heating side bypass pipe 60 at a flow rate corresponding to the opening degree setting of the heating side heat medium flow rate adjustment valve 62.
  • the water flowing into the heating side intermediate heat exchanger 61 exchanges heat with the heating refrigerant to heat the heating refrigerant, and flows out of the heating side intermediate heat exchanger 61.
  • the water flowing out from the heating side intermediate heat exchanger 61 and the water flowing through the heating side bypass pipe 60 merge on the downstream side of the heating side intermediate heat exchanger 61 and flow out from the heating device 6.
  • the cooling refrigerant flowing through the cooling refrigerant circuit is compressed and discharged by the compressor 53.
  • the cooling refrigerant discharged from the compressor 53 flows into the cooling side intermediate heat exchanger 51.
  • the cooling refrigerant flowing into the cooling-side intermediate heat exchanger 51 heats water by exchanging heat with the water flowing through the heat medium circuit and condensing while dissipating heat, and flows out of the cooling-side intermediate heat exchanger 51.
  • the cooling refrigerant that has flowed out of the cooling side intermediate heat exchanger 51 is decompressed and expanded by the expansion valve 54, and flows out of the expansion valve 54.
  • the cooling refrigerant flowing out of the expansion valve 54 flows into the use side heat exchanger 55.
  • the cooling refrigerant that has flowed into the use side heat exchanger 55 exchanges heat with room air, absorbs and evaporates, and flows out of the use side heat exchanger 55.
  • the cooling refrigerant flowing out from the use side heat exchanger 55 is sucked into the compressor 53. In the following, the cooling refrigerant repeats the circulation described above.
  • the heating refrigerant flowing through the heating refrigerant circuit is compressed by the compressor 63 and discharged.
  • the heating refrigerant discharged from the compressor 63 flows into the water heat exchanger 65.
  • the heating refrigerant that has flowed into the water heat exchanger 65 heats the unheated water by condensing it while exchanging heat with the unheated water that has flowed out of the hot water storage tank 71, and flows out of the water heat exchanger 65.
  • the heating refrigerant that has flowed out of the water heat exchanger 65 is decompressed and expanded by the expansion valve 64, and flows out of the expansion valve 64.
  • the heating refrigerant flowing out from the expansion valve 64 flows into the heating side intermediate heat exchanger 61.
  • the heating refrigerant flowing into the heating-side intermediate heat exchanger 61 exchanges heat with water flowing through the heat medium circuit, absorbs heat and evaporates, and flows out of the heating-side intermediate heat exchanger 61.
  • the heating refrigerant flowing out from the heating side intermediate heat exchanger 61 is sucked into the compressor 63. In the following, the heating refrigerant repeats the circulation described above.
  • unheated water flows out from the outlet provided in the lower part of the hot water storage tank 71.
  • Unheated water that has flowed out of the hot water storage tank 71 flows into the water heat exchanger 65.
  • Unheated water that has flowed into the water heat exchanger 65 is heated by exchanging heat with the refrigerant for heating, and flows out of the water heat exchanger 65.
  • Heated water that has flowed out of the water heat exchanger 65 flows into the hot water storage tank 71 from an inlet provided in the upper part of the hot water storage tank 71 and is stored in the hot water storage tank 71.
  • unheated water in hot water storage tank 71 repeats circulation mentioned above.
  • the control device 4 controls the cooling-side heat medium flow control valve 52 or the heating corresponding to the stopped device.
  • the opening degree of the side heat medium flow control valve 62 is controlled.
  • the cooling side intermediate heat exchanger 51 or the heating side intermediate heat exchanger 61 corresponding to the stopped apparatus is bypassed.
  • the control device 4 has at least one of the cooling side heat medium flow rate adjustment valve 52 and the heating side heat medium flow rate adjustment valve 62. The supply of water to system # 4 is shut off.
  • the flowing-in water is cooled by recovering the exhaust heat from the heating device 6, and heated-side intermediate heat exchange Out of the vessel 61. And the water which flowed out from the heating side intermediate heat exchanger 61 flows into the relay apparatus 3 as return water in the cooled state.
  • the exhaust heat from the cooling device 5 is used by the heating device 6.
  • the heat exchange efficiency of the heating device 6 is improved.
  • the return water to the relay device 3 is cooled by the exhaust heat from the heating device 6, the cooling of the water in the relay device 3 is assisted, and the energy saving performance of the entire system is improved.
  • cooling device 5 when the required operation capacity cannot be exhibited only by the heat exchange by the cooling side intermediate heat exchanger 51, the upstream side or the downstream side of the cooling side intermediate heat exchanger 51 on the cooling refrigerant circuit.
  • a cooling side auxiliary heat exchanger may be provided in series. Thereby, since the heat exchange amount which is insufficient only with the cooling side intermediate heat exchanger 51 is compensated by the cooling side auxiliary heat exchanger, the operation capability required by the cooling device 5 can be exhibited.
  • the cooling device 5 can exhibit the required operating capacity using only the cooling side intermediate heat exchanger 51. It is preferable that a cooling side auxiliary bypass pipe for bypassing the cooling side auxiliary heat exchanger is provided. This is because heat is not exchanged by the cooling side auxiliary heat exchanger, so that the amount of heat discharged to water by heat exchange in the cooling side intermediate heat exchanger 51 is increased, and the heating device 6 in the subsequent stage is increased. This is because it is possible to improve the exhaust heat utilization at the time.
  • the cooling side auxiliary heat exchanger is provided on the downstream side of the cooling side intermediate heat exchanger 51, the cooling side auxiliary bypass pipe is unnecessary. That is, when the shortage of heat exchange in the cooling side intermediate heat exchanger 51 is compensated by heat exchange by the cooling side auxiliary heat exchanger, a cooling side auxiliary heat exchanger may be used.
  • the heating device 6 when the necessary operation capability cannot be exhibited only by the heat exchange by the heating side intermediate heat exchanger 61, the upstream side or the downstream side of the heating side intermediate heat exchanger 61 on the heating refrigerant circuit.
  • a heating side auxiliary heat exchanger may be provided in series. Thereby, since the amount of heat exchange that is insufficient with only the heating-side intermediate heat exchanger 61 is compensated by the heating-side auxiliary heat exchanger, the operating capability required by the heating device 6 can be exhibited.
  • the heating device 6 can exhibit the required operating capability using only the heating side intermediate heat exchanger 61. It is preferable that a heating side auxiliary bypass pipe for bypassing the heating side auxiliary heat exchanger is provided. This is because heat is not exchanged by the heating side auxiliary heat exchanger, so that the amount of heat discharged to water by heat exchange in the heating side intermediate heat exchanger 61 is increased, and waste heat is utilized for the return water. It is because it can improve.
  • the heating side auxiliary heat exchanger is provided on the downstream side of the heating side intermediate heat exchanger 61, the heating side auxiliary bypass pipe is unnecessary. That is, when the shortage of heat exchange in the heating side intermediate heat exchanger 61 is compensated by heat exchange by the heating side auxiliary heat exchanger, a heating side auxiliary heat exchanger may be used.
  • the heat recovery is balanced is not limited to the case where the water inlet temperature and the outlet temperature in the system in which the cooling device 5 and the heating device 6 are connected in series match each other.
  • the balance is almost balanced.
  • the temperature change of water occurs in any of the heat medium circuits, for example, when water circulates in the heat medium pipe 20, when the temperature changes in the water by exchanging heat with the outside air, the temperature of the water Including the state where heat recovery is balanced in consideration of changes.
  • the operating state of the indoor unit 2 of the system # 1 and the system The load on the outdoor unit 1 side is adjusted according to the temperature state of the water flowing into and out of # 4.
  • FIG. 23 is a flowchart illustrating an example of a processing flow when heat recovery is not balanced in the cooling-side intermediate heat exchanger 51 and the heating-side intermediate heat exchanger 61 according to the fifth embodiment.
  • the control device 4 determines whether or not the indoor unit 2 of the system # 1 is in the heating operation.
  • step S1; Yes the control device 4 detects the inlet temperature of the water of the system # 4 detected by the inlet temperature sensor 56 and the outlet temperature sensor 67 in step S2. Compare the outlet temperature of the water in system # 4. As a result of the comparison, when the inlet temperature of the system # 4 is higher than the outlet temperature (step S2; Yes), the control device 4 increases the heat exchange amount in the intermediate heat exchanger 32 in step S3.
  • the respective units of the outdoor unit 1 such as the compressor 11 and the relay device 3 are controlled so as to increase the load of the compressor 11.
  • step S2 when the inlet temperature of the system # 4 is equal to or lower than the outlet temperature (step S2; No), since the return water flowing out from the system # 4 is in a state of being stored in heat, the control device 4 performs intermediate processing in step S4. In order to reduce the amount of heat exchange in the heat exchanger 32, each part of the outdoor unit 1 and the relay device 3 is controlled so as to reduce the load of the outdoor unit 1.
  • Step S1 when the indoor unit 2 is in the cooling operation (Step S1; No), the control device 4 compares the inlet temperature and the outlet temperature of the water of the system # 4 in Step S5. As a result of the comparison, when the inlet temperature of the system # 4 is equal to or lower than the outlet temperature (step S5; No), the control device 4 increases the heat exchange amount in the intermediate heat exchanger 32 in step S6. The respective units of the outdoor unit 1 and the relay device 3 are controlled so as to increase the load. On the other hand, when the inlet temperature of the system # 4 is higher than the outlet temperature (step S5; Yes), since the return water flowing out from the system # 4 is in a state of being stored, the control device 4 performs intermediate processing in step S7. In order to reduce the amount of heat exchange in the heat exchanger 32, each part of the outdoor unit 1 and the relay device 3 is controlled so as to reduce the load of the outdoor unit 1.
  • step S3 or step S6 when the load of the outdoor unit 1 is increased in step S3 or step S6, the control device 4 increases the amount of power increase on the outdoor unit 1 side that is increased by increasing the load in step S8, and the system # 4.
  • the amount of electric power reduction at the heat medium circuit side that is reduced by using heat, that is, the cooling device 5 and the heating device 6 is compared.
  • step S8; Yes when the power increase amount on the outdoor unit 1 side is larger than the power decrease amount on the heat medium circuit side (step S8; Yes), the control device 4 increases the outdoor temperature increased in step S3 or step S6 in step S9. Restore the load of machine 1.
  • step S10 the control device 4 adjusts the cooling-side heat medium flow adjustment valve 52 or the heating-side heat medium flow rate adjustment so as to bypass the cooling-side intermediate heat exchanger 51 or the heating-side intermediate heat exchanger 61 in the system # 4.
  • the opening degree of the valve 62 is controlled.
  • step S3 when the indoor unit 2 is in the heating operation and the load of the outdoor unit 1 is increased because the water inlet temperature of the system # 4 is higher than the outlet temperature (step S3), the control device 4 The opening degree of the side heat medium flow control valve 62 is controlled to bypass the heating side intermediate heat exchanger 61.
  • the control device 4 When the outdoor temperature is low during the heating operation, the heating-side intermediate heat exchanger 61 is bypassed in order to reduce the heat absorption while maintaining the exhaust heat.
  • step S6 when the indoor unit 2 is in the cooling operation and the load on the outdoor unit 1 is increased because the water inlet temperature of the system # 4 is equal to or lower than the outlet temperature (step S6), the control device 4 The opening degree of the flow rate adjustment valve 52 is controlled to bypass the cooling side intermediate heat exchanger 51.
  • step S8 when the amount of increase in power on the outdoor unit 1 side is equal to or less than the amount of power decrease on the heat medium circuit side (step S8; No), the controller 4 increases the outdoor unit 1 raised in step S3 or step S6 in step S11. Maintain the load.
  • the load of the outdoor unit 1 is adjusted according to the operating state of the indoor unit 2 and the temperature state of the water flowing into and out of the system # 4.
  • the driving capability of the cooling device 5 and the heating device 6 can be fully exerted, and the electric power required for the operation of the air conditioner 500 as a whole can be reduced.
  • steps S8 to S11 are not essential.
  • the outdoor unit load is controlled only by comparing the inlet temperature and the outlet temperature in system # 4. However, the temperature difference of other systems, the temperature change of water in the piping, etc. Considering this, the outdoor unit load may be controlled.
  • the cooling side intermediate heat exchanger 51 or the heating side intermediate heat exchanger 61 is bypassed in step S10.
  • the present invention is not limited to this, and may not be bypassed, for example.
  • the cooling side heat medium flow rate adjustment valve 52 or the heating side heat medium flow rate adjustment valve 62 is used to reduce the temperature difference between the inlet temperature and the outlet temperature of the water in the system # 4. May be adjusted. In this case, exhaust heat recovery can be performed while suppressing an increase in power on the outdoor unit 1 side.
  • the cooling-side intermediate heat exchanger 51 when the cooling-side intermediate heat exchanger 51 is bypassed, the cooling refrigerant in the cooling device 5 becomes insufficiently condensed. Therefore, as described above, the cooling-side auxiliary is connected in series to the cooling-side intermediate heat exchanger 51. It is necessary to provide a heat exchanger. Further, when the heating-side intermediate heat exchanger 61 is bypassed, the heating refrigerant in the heating device 6 becomes insufficiently evaporated, so that the heating-side auxiliary heat is serially connected to the heating-side intermediate heat exchanger 61 as described above. It is necessary to provide an exchanger.
  • the amount of power increase on the outdoor unit 1 side is compared with the amount of power decrease on the heat medium circuit side to determine whether or not the load of the changed outdoor unit 1 is returned.
  • the required flow rate of water is supplied to the FCUs 21a to 21c, the cooling device 5, and the heating device 6.
  • a flow rate adjustment process is performed so as to flow. That is, in the air conditioner 500, the heat medium flow rate adjustment valve 22, the cooling side heat medium flow rate adjustment valve 52, and the heating side corresponding to the FCUs 21a to 21c, the cooling side intermediate heat exchanger 51, and the heating side intermediate heat exchanger 61, respectively.
  • the opening degree of the heat medium flow control valve 62 is controlled.
  • the flow rates of water to the FCUs 21a to 21c, the cooling-side intermediate heat exchanger 51, and the heating-side intermediate heat exchanger 61 are changed to the FCUs 21a to 21c, the cooling-side intermediate heat exchanger 51, and the heating-side intermediate heat exchanger 61, respectively. It is adjusted according to the ability required for each.
  • the order of the cooling device 5 and the heating device 6 in the system # 4 may be reversed.
  • the heating device 6 is provided on the upstream side of the water in the system # 4.
  • the cooling device 5 may be provided on the downstream side.
  • the number of the cooling devices 5 and the heating devices 6 connected in series to the system # 4 is not limited to this example, and may be plural.
  • the cooling side bypass pipe 50 of the cooling device 5 and the heating side bypass pipe 60 of the heating device 6 can be omitted.
  • the cooling side intermediate heat since water flows through the cooling side intermediate heat exchanger 51 without exchanging heat by flowing water through the cooling side intermediate heat exchanger 51 with the cooling device 5 stopped, the cooling side intermediate heat The same effect as when the exchanger 51 is bypassed can be obtained.
  • the heating side intermediate heat exchanger 61 without exchanging heat by flowing water through the heating side intermediate heat exchanger 61 with the heating device 6 stopped the heating side intermediate heat exchange The same effect as the case where the device 61 is bypassed can be obtained.
  • cooling-side intermediate heat exchanger 51 and the heating-side intermediate heat exchanger 61 when water passes through the cooling-side intermediate heat exchanger 51 and the heating-side intermediate heat exchanger 61, the cooling-side intermediate heat exchanger 51 and the heating-side intermediate heat exchanger 61 cause some heat loss and pressure loss. Occurs. Therefore, it is preferable that the cooling side bypass pipe 50 and the heating side bypass pipe 60 are provided.
  • the cooling-side heat medium flow rate adjustment valve 52 does not need to be provided with a plurality of outlets, and adjusts the flow rate of inflowing water. What is necessary is just to have the function to let it flow out.
  • the heating-side heat medium flow rate adjustment valve 62 does not need to be provided with a plurality of outlets, and adjusts the flow rate of inflowing water. What is necessary is just to have the function to let it flow out.
  • the cooling device 5 and the heating device 6 connected in series are connected in parallel to the system # 1 as the system # 4.
  • the present invention is not limited to this, for example, the cooling device 5 Only system # 4 may be used.
  • the load of the outdoor unit 1 and the flow of water in the system # 4 are controlled according to the operating state of the system # 1.
  • the control device 4 performs control to reduce the load on the outdoor unit 1. Thereby, electric power can be reduced as the air conditioner 500 whole.
  • the indoor unit 2 of the system # 1 performs the cooling operation
  • the temperature of the water flowing out from the cooling device 5 of the system # 4 becomes higher than the temperature of the flowing water.
  • the return water is in a high temperature state. Therefore, it is necessary to increase the load on the outdoor unit 1 side.
  • the control for increasing the load is performed, the power of the air conditioner 500 as a whole increases. Therefore, in this case, the inflow of water to the cooling device 5 is blocked. Thereby, the load of the pump 33 is lowered and energy saving can be improved.
  • the cooling side auxiliary heat exchanger is provided in series with the cooling side intermediate heat exchanger 51, and the cooling refrigerant is condensed by the cooling side auxiliary heat exchanger.
  • step S1 when the indoor unit 2 is in the heating operation (step S1; Yes), the control device 4 detects the temperature of water detected by the inlet temperature sensor 56 of the cooling device 5 and the discharge provided in the compressor. The temperature of the refrigerant detected by the temperature sensor is compared.
  • the control device 4 controls to bypass the water to the cooling side bypass pipe 50, and the cooling device 5 You may make it operate
  • the cooling device 5 when the cooling device 5 does not have the cooling side auxiliary condenser, the cooling device 5 cannot condense the refrigerant, so that the control device 4 stops the outdoor unit 1 when the temperature of water is higher than the temperature of the refrigerant. It may be. Thereby, in the heating operation, when the temperature of water becomes higher than the temperature of the refrigerant, it is possible to prevent the cooling side intermediate heat exchanger 51 from being able to discharge heat from the refrigerant to the water.
  • only the heating device 6 may be connected in parallel to the system # 1 as the system # 4. Also in this case, the load of the outdoor unit 1 and the flow of water in the system # 4 are controlled according to the operating state of the system # 1.
  • the indoor unit 2 of the system # 1 When the indoor unit 2 of the system # 1 performs the heating operation, the temperature of the water flowing out from the heating device 6 of the system # 4 is lower than the temperature of the flowing water, so that the return water to the relay device 3 Becomes a low temperature state. Therefore, it is necessary to increase the load on the outdoor unit 1 side. However, if the control for increasing the load is performed, the power of the air conditioner 500 as a whole increases. Therefore, in this case, the inflow of water to the heating device 6 is blocked. Thereby, the load of the pump 33 is lowered and energy saving can be improved.
  • the indoor unit 2 of the system # 1 performs the cooling operation
  • the temperature of the water flowing out from the heating device 6 of the system # 4 becomes lower than the temperature of the flowing water.
  • the return water is in a low temperature state. Therefore, on the outdoor unit 1 side, the load may be reduced. Therefore, the control device 4 performs control to reduce the load on the outdoor unit 1. Thereby, electric power can be reduced as the air conditioner 500 whole.
  • the heating side auxiliary heat exchanger is provided in series with the heating side intermediate heat exchanger 61 in the heating device 6, and the heating side auxiliary heat exchanger evaporates the heating refrigerant.
  • control according to the presence or absence of the heating side auxiliary heat exchanger may be performed during the cooling operation described above. That is, when the indoor unit 2 is in the cooling operation (step S1; No), the control device 4 detects the water temperature detected by the inlet temperature sensor 66 of the heating device 6 and the suction temperature sensor provided in the compressor. The refrigerant temperature is compared.
  • the control device 4 performs control so as to bypass the water to the heating side bypass pipe 60, so that the heating device 6 is substantially Alternatively, it may be operated only by the heating side auxiliary condenser.
  • the control device 4 stops the outdoor unit 1. It may be. Thereby, in the cooling operation, when the temperature of water becomes lower than the temperature of the refrigerant, it is possible to prevent the cooling side intermediate heat exchanger 51 from being able to exhaust heat from the refrigerant to the water.
  • the cooling device 5 and the heating device 6 may be connected to the system # 1 in parallel as different systems. Also in this case, the load of the outdoor unit 1 and the flow of water in each system are controlled according to the operating state of the system # 1.
  • the control device 4 controls the load of the outdoor unit 1 to be reduced and to block or bypass the inflow of water to the system of the heating device 6.
  • the control device 4 performs control so as to reduce the load of the outdoor unit 1 and to block or bypass the inflow of water to the system of the cooling device 5.
  • the load of the outdoor unit 1 and the flow of water in each system are controlled in accordance with the operating state of the indoor unit 2 in the system # 1, so that the power of the air conditioner 500 as a whole can be reduced.
  • the load on the pump 33 is reduced, and energy saving can be improved.
  • the cooling device 5 condenses the cooling refrigerant by the cooling side auxiliary heat exchanger, and the heating device 6 evaporates the heating refrigerant by the heating auxiliary heat exchanger.
  • the cooling device 5 and the heating device 6 are connected in series. Therefore, since the exhaust heat from the cooling device 5 is used by the heating device 6, the heat exchange efficiency of the heating device 6 can be improved. Further, since the return water is cooled by the exhaust heat from the heating device 6, the energy saving performance of the entire system can be improved.
  • the cooling device 5 further includes a cooling side bypass pipe 50 that bypasses the cooling side intermediate heat exchanger 51. Accordingly, when the cooling-side intermediate heat exchanger 51 does not perform heat exchange between water and the cooling refrigerant, water passes through the cooling-side intermediate heat exchanger 51 because water passes through the cooling-side bypass pipe 50. Compared with the case where it does, the loss and pressure loss by heat dissipation can be suppressed.
  • the cooling side bypass pipe 50 is formed via the outside of the cooling device 5. Therefore, since the piping length of the cooling side bypass piping 50 becomes short, the loss by the heat dissipation etc. when water flows through the inside of piping can be suppressed.
  • the heating device 6 further includes a heating side bypass pipe 60 that bypasses the heating side intermediate heat exchanger 61.
  • a heating side bypass pipe 60 that bypasses the heating side intermediate heat exchanger 61.
  • the heating side bypass pipe 60 is formed via the outside of the heating device 6. Therefore, since the piping length of the heating side bypass piping 60 becomes short, the loss by the heat radiation etc. at the time of water flowing in the piping can be suppressed.
  • the cooling device 5 further includes a cooling side auxiliary heat exchanger connected in series on the upstream side or the downstream side of the cooling side intermediate heat exchanger 51 on the cooling refrigerant circuit.
  • the cooling device 5 further includes a cooling side auxiliary bypass pipe that bypasses the cooling side auxiliary heat exchanger provided on the upstream side of the cooling side intermediate heat exchanger 51. Thereby, when only the cooling side intermediate heat exchanger 51 can be used, the cooling side auxiliary heat exchanger can be bypassed when the cooling device 5 can exhibit the required operating capacity.
  • the heating device 6 further includes a heating side auxiliary heat exchanger connected in series on the upstream side or downstream side of the heating side intermediate heat exchanger 61 on the heating refrigerant circuit.
  • the heating device 6 further includes a heating side auxiliary bypass pipe that bypasses the heating side auxiliary heat exchanger provided on the upstream side of the heating side intermediate heat exchanger 61. Thereby, the heating side auxiliary heat exchanger can be bypassed when only the heating side intermediate heat exchanger 61 is used and the heating device 6 can exhibit the required driving capability.
  • the air conditioner 500 can be used outdoors depending on the operating state of the indoor unit 2 of the system # 1 and the temperature state of the water flowing into and out of the system # 4 to which the cooling device 5 and the heating device 6 are connected.
  • a control device 4 for adjusting the load of the machine 1 is further provided.
  • the control apparatus 4 is the case where the indoor unit 2 is heating operation, and the inlet temperature of the water which flows in into system
  • control device 4 is configured so that the indoor unit 2 is in the heating operation and the outlet temperature of the system # 4 is equal to or higher than the inlet temperature, or the indoor unit 2 is in the cooling operation and the inlet temperature of the system # 4 is higher than the outlet temperature.
  • the load on the outdoor unit 1 is reduced.
  • the driving capability of the cooling device 5 and the heating device 6 can be fully exerted, and the electric power required for the operation of the air conditioner 500 as a whole can be reduced.
  • Embodiment 6 FIG. Next, an air conditioner according to Embodiment 6 of the present invention will be described.
  • the opening degree of the heat medium flow control valve 22 is controlled so as to suppress the shortage of the rising ability when the indoor units 2a to 2i start operation from the stopped state. Note that, in the following description, the same reference numerals are given to configurations common to the first embodiment, and detailed description is omitted.
  • the valve opening determining unit 42 is configured so that the water circulating in the heat medium circuit flows through the indoor bypass pipe 23 when all the indoor units 2a to 2i are stopped.
  • the opening degree of the heat medium flow control valve 22 in the indoor units 2a to 2i is determined.
  • the valve opening determination unit 42 sets the openings of all the heat medium flow control valves 22 so that the bypass opening becomes 100%, and the water outflow side of the second outlet 22c and the FCU 21. To communicate with.
  • the valve opening degree determination unit 42 determines the water in the second outlet 22c and the FCU 21.
  • the opening degrees of all the heat medium flow control valves 22 are determined so as to communicate with the outflow side.
  • heat is stored in water, which is a heat medium, so that it is possible to suppress a shortage of capacity when the indoor units 2a to 2i start operation from a stopped state.
  • the first to sixth embodiments of the present invention have been described above.
  • the present invention is not limited to the above-described first to sixth embodiments of the present invention, and various modifications can be made without departing from the scope of the present invention.
  • Various modifications and applications are possible.
  • the outdoor unit 1 and the relay device 3 have been described as being configured separately, the present invention is not limited to this, and the outdoor unit 1 and the relay device 3 may be integrated. It is also possible to combine the inventions of Embodiments 1 to 6.
  • the opening degree of the heat medium flow control valve 22 has been described as being determined based on the FCU capability obtained based on various temperature information, this is not limited to this example.
  • the opening degree of the heat medium flow control valve 22 may be determined based on information on the thermo-ON and the thermo-OFF of the indoor unit 2.
  • a radiation panel may be used as the load side unit. Since the radiant panel exchanges heat only when the heat medium flows through the pipe, the heat medium flows through the bypass pipe so that the heat medium does not flow through the pipe of the radiant panel when the thermostat is OFF.
  • the pump 33 has been described as being provided in the relay device 3, the present invention is not limited thereto, and the pump 33 may be configured separately from the relay device 3 as a pump unit, for example.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

La présente invention concerne un dispositif de refroidissement comprenant un échangeur de chaleur intermédiaire côté refroidissement qui échange de la chaleur entre un fluide caloporteur et un fluide frigorigène pour le refroidissement qui circule à travers un circuit de fluide frigorigène pour le refroidissement, et un dispositif de chauffage comprenant un échangeur de chaleur intermédiaire côté chauffage qui échange de la chaleur entre le fluide caloporteur et un fluide frigorigène pour le chauffage qui circule à travers un circuit de fluide frigorigène pour le chauffage, qui sont raccordés en série dans un circuit de circulation de fluide caloporteur à travers lequel circule le fluide caloporteur.
PCT/JP2018/008001 2018-03-02 2018-03-02 Climatiseur WO2019167250A1 (fr)

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JP2020503229A JP6980089B2 (ja) 2018-03-02 2018-03-02 空気調和機
PCT/JP2018/008001 WO2019167250A1 (fr) 2018-03-02 2018-03-02 Climatiseur

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JP7034250B2 (ja) * 2018-03-02 2022-03-11 三菱電機株式会社 空気調和機
CN113573543B (zh) * 2021-06-10 2023-09-29 华为数字能源技术有限公司 分布式复合制冷系统和数据中心
KR102494941B1 (ko) * 2022-06-17 2023-02-06 고려대학교 산학협력단 열교환기의 빙결방지를 위한 히트펌프 시스템

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JPH04113139A (ja) * 1990-09-04 1992-04-14 Ebara Corp 地域冷暖房システム
WO2013038577A1 (fr) * 2011-09-13 2013-03-21 三菱電機株式会社 Dispositif de pompe à chaleur et procédé de commande de dispositif de pompe à chaleur
WO2016088262A1 (fr) * 2014-12-05 2016-06-09 三菱電機株式会社 Appareil à cycle de réfrigération

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JP2001099514A (ja) * 1999-09-30 2001-04-13 Sanyo Electric Co Ltd 蓄熱式空調冷凍装置
US9322562B2 (en) * 2009-04-01 2016-04-26 Mitsubishi Electric Corporation Air-conditioning apparatus
US8616017B2 (en) * 2009-05-08 2013-12-31 Mitsubishi Electric Corporation Air conditioning apparatus
ES2814352T3 (es) * 2012-11-29 2021-03-26 Mitsubishi Electric Corp Dispositivo de acondicionamiento de aire
KR20200014296A (ko) * 2017-05-26 2020-02-10 엘리언스 포 서스터너블 에너지, 엘엘씨 다중-회로, 상-변화 복합체 열 교환기를 포함한 시스템

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JPH04113139A (ja) * 1990-09-04 1992-04-14 Ebara Corp 地域冷暖房システム
WO2013038577A1 (fr) * 2011-09-13 2013-03-21 三菱電機株式会社 Dispositif de pompe à chaleur et procédé de commande de dispositif de pompe à chaleur
WO2016088262A1 (fr) * 2014-12-05 2016-06-09 三菱電機株式会社 Appareil à cycle de réfrigération

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