WO2016157481A1 - Air-conditioning device - Google Patents

Air-conditioning device Download PDF

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Publication number
WO2016157481A1
WO2016157481A1 PCT/JP2015/060391 JP2015060391W WO2016157481A1 WO 2016157481 A1 WO2016157481 A1 WO 2016157481A1 JP 2015060391 W JP2015060391 W JP 2015060391W WO 2016157481 A1 WO2016157481 A1 WO 2016157481A1
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WO
WIPO (PCT)
Prior art keywords
heat
air
heat medium
refrigerant
heat exchanger
Prior art date
Application number
PCT/JP2015/060391
Other languages
French (fr)
Japanese (ja)
Inventor
永登 齋藤
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 GB1711510.6A priority Critical patent/GB2549231B/en
Priority to PCT/JP2015/060391 priority patent/WO2016157481A1/en
Publication of WO2016157481A1 publication Critical patent/WO2016157481A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • F24F3/065—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units with a plurality of evaporators or condensers
    • 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
    • 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
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02732—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two three-way 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/13—Pump speed control
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet

Definitions

  • the present invention relates to an air conditioner that extracts air from a heat medium circulation circuit during construction applied to, for example, a building multi-air conditioner.
  • a pipe between the heat source side refrigerant circulating in a refrigeration cycle circuit (hereinafter referred to as a primary side circuit) configured by connecting a pipe between the outdoor unit and the relay unit, and between the relay unit and the indoor unit.
  • a primary side circuit configured by connecting a pipe between the outdoor unit and the relay unit, and between the relay unit and the indoor unit.
  • an air conditioner that exchanges heat with an indoor-side refrigerant that circulates in a heat medium circulation circuit (hereinafter referred to as a secondary circuit).
  • an indoor refrigerant that circulates in a secondary circuit configured by connecting a pipe to an indoor unit uses water or a solution obtained by mixing brine with water.
  • air is likely to enter the circuit. Failure can occur due to air entering the water or brine solution of the secondary circuit. Therefore, it is necessary to perform an operation for removing air in the secondary circuit (hereinafter referred to as an air removal operation) before operating the air conditioner (see, for example, Patent Document 2).
  • the present invention is intended to solve the above-described problems, and quantitatively determines the completion of the air removal operation, and aims to avoid air remaining in the heat medium circulation circuit and prolonged construction time. To do.
  • An air conditioner includes a compressor that compresses a heat source side refrigerant, a heat source side heat exchanger that exchanges heat with the heat source side refrigerant, a throttling device that adjusts the pressure of the heat source side refrigerant, and the heat source side refrigerant and heat medium
  • a refrigerant circulation circuit configured by pipe-connecting a heat source side refrigerant side of a heat exchanger related to heat medium that performs heat exchange with the heat medium, a heat medium side of the heat exchanger related to heat medium, a pump for circulating the heat medium, and
  • a heat medium circulation circuit configured by pipe connection of a use side heat exchanger that exchanges heat between the heat medium and the air in the air-conditioning target space, and the heat medium circulation circuit releases internal air Air that has an air removal valve, opens the air removal valve when the heat medium circulation circuit is installed, drives the pump to circulate the heat medium, and removes air from the heat medium circulation circuit The removal operation is executed and the air removal operation is completed.
  • the completion of the air removal operation is determined based on the number of revolutions of the pump, and the determination to complete the air removal operation is quantitatively performed. It is possible to avoid residuals and prolonged construction time.
  • FIG. 1 is a schematic diagram illustrating an installation example of an air-conditioning apparatus 100 according to Embodiment 1 of the present invention. Based on FIG. 1, the structure of the air conditioning apparatus 100 is demonstrated.
  • the air conditioner 100 performs a cooling operation or a heating operation using a primary side circuit 20 that circulates a heat source side refrigerant and a secondary side circuit 30 that circulates a heat medium such as water or antifreeze.
  • a heat medium such as water or antifreeze.
  • the size relationship of each component may be different from the actual one.
  • the subscripts may be omitted.
  • the level of temperature, pressure, etc. is not particularly determined in relation to absolute values, but is relatively determined in terms of the state and operation of the system, apparatus, and the like.
  • an air conditioner 100 includes, for example, one heat source device 1 that is a heat source device, a plurality of indoor units 3, and between the heat source device 1 and the indoor unit 3. And an intervening relay unit 2.
  • the relay unit 2 performs heat exchange between the heat source side refrigerant and the heat medium.
  • the heat source device 1 and the relay unit 2 are connected by a refrigerant pipe 4 that conducts the heat source side refrigerant.
  • the relay unit 2 and the indoor unit 3 are connected by a pipe 5 that conducts the heat medium. By having the refrigerant pipe 4 and the pipe 5, cold heat or hot heat generated by the heat source device 1 is delivered to the indoor unit 3.
  • the number of connected heat source devices 1, indoor units 3, and relay units 2 is not limited to the illustrated number.
  • the heat source device 1 is normally disposed in an outdoor space 6 that is a space outside a building 9 such as a building, and supplies cold or hot heat to the indoor unit 3 via the relay unit 2.
  • the indoor unit 3 is disposed in a living space 7 such as a living room or a server room in a building 9 that can carry cooling air or heating air, and the cooling air or heating air is supplied to the living space 7 that is an air-conditioning target area. Supply.
  • the relay unit 2 is disposed separately from the heat source device 1 and the indoor unit 3 in a non-residential space 8 that is a position different from the outdoor space 6 and the residential space 7, and connects the heat source device 1 and the indoor unit 3. Then, the cold or warm heat supplied from the heat source device 1 is transmitted to the indoor unit 3.
  • Examples of the heat source side refrigerant of the primary side circuit 20 include single refrigerants such as R-22, R-134a, and R32, pseudo-azeotropic refrigerant mixtures such as R-410A and R-404A, and non-common refrigerants such as R-407C.
  • the heat medium of the secondary side circuit 30 for example, water, an antifreeze solution, a mixed solution of water and antifreeze solution, a mixed solution of water and an additive having a high anticorrosion effect, or the like can be used.
  • the outdoor space 6 assumes a place existing outside the building 9, for example, a rooftop as shown in FIG.
  • the non-residential space 8 is a space inside the building 9 but different from the residential space 7, for example, a place where there is no person at all times, such as on the corridor, a common zone with a ceiling in the common zone, an elevator, etc.
  • a room, a computer room, a warehouse, etc. are assumed.
  • the living space 7 is assumed to be an interior of the building 9 where there are always people or where there are many or a small number of people temporarily, such as offices, classrooms, conference rooms, canteens, server rooms, etc. ing.
  • the heat source device 1 and the relay unit 2 are connected using two refrigerant pipes 4.
  • the relay unit 2 and each indoor unit 3 are connected by two pipes 5 respectively.
  • the construction of the air conditioner 100 is facilitated by connecting the heat source device 1 to the relay unit 2 through the two refrigerant pipes 4 and connecting the indoor unit 3 to the relay unit 2 through the two pipes 5.
  • FIG. 2 is a schematic circuit diagram showing the configuration of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the heat source device 1 and the relay unit 2 are connected by the refrigerant pipe 4 via the heat exchangers 25 a and 25 b provided in the relay unit 2. Further, the relay unit 2 and the indoor unit 3 are connected by a pipe 5.
  • Heat source device (outdoor unit) 1 In the heat source device 1, a compressor 10, a first refrigerant flow switching device 11 such as a four-way valve, a heat source side heat exchanger 12, and an accumulator 19 are connected and connected in series through a refrigerant pipe 4. Yes. Further, the heat source device 1 is provided with refrigerant connection pipes 4a and 4b and check valves 13a, 13b, 13c and 13d. By providing the refrigerant connection pipes 4a and 4b and the check valves 13a, 13b, 13c, and 13d, the flow of the heat source side refrigerant flowing into the relay unit 2 is made to be a constant direction regardless of the operation requested by the indoor unit 3. be able to.
  • the compressor 10 sucks the heat-source-side refrigerant, compresses the heat-source-side refrigerant, transfers the heat-source-side refrigerant to a primary side circuit 20 in a high temperature / high pressure state, and includes, for example, an inverter compressor capable of capacity control. Good.
  • the first refrigerant flow switching device 11 switches the flow of the heat source side refrigerant during the heating operation and the flow of the heat source side refrigerant during the cooling operation.
  • the heat source side heat exchanger 12 functions as an evaporator during heating operation, functions as a condenser (or radiator) during cooling operation, and includes a fluid of air supplied from a blower such as a fan (not shown), a heat source side refrigerant, and the like.
  • the heat source side refrigerant is evaporated and condensed or liquefied.
  • the accumulator 19 is provided on the suction side of the compressor 10 and stores excess refrigerant due to a difference between the heating operation and the cooling operation, or excess refrigerant with respect to a transient change in operation.
  • the check valve 13c is provided in the refrigerant pipe 4 between the relay unit 2 and the first refrigerant flow switching device 11, and the heat source side refrigerant is only in a predetermined direction (direction from the relay unit 2 to the heat source device 1). Allow flow.
  • the check valve 13a is provided in the refrigerant pipe 4 between the heat source side heat exchanger 12 and the relay unit 2, and allows the flow of the heat source side refrigerant only in a predetermined direction (direction from the heat source device 1 to the relay unit 2). Allow.
  • the check valve 13d is provided in the refrigerant connection pipe 4a and causes the heat source side refrigerant discharged from the compressor 10 to flow through the relay unit 2 during the heating operation.
  • the check valve 13 b is provided in the refrigerant connection pipe 4 b and distributes the heat source side refrigerant returned from the relay unit 2 during the heating operation to the suction side of the compressor 10.
  • the refrigerant connection pipe 4 a includes a refrigerant pipe 4 between the first refrigerant flow switching device 11 and the check valve 13 c, and a refrigerant pipe 4 between the check valve 13 a and the relay unit 2. And connect.
  • the refrigerant connection pipe 4b includes a refrigerant pipe 4 between the check valve 13c and the relay unit 2, a refrigerant pipe 4 between the heat source side heat exchanger 12 and the check valve 13a, Connect.
  • FIG. 2 the case where the refrigerant connection pipes 4a and 4b and the check valves 13a, 13b, 13c and 13d are provided is shown as an example. However, the present invention is not limited to this, and it is not always necessary to provide them. Absent.
  • Each indoor unit 3 is equipped with a use side heat exchanger 35.
  • the use side heat exchanger 35 is connected to the heat medium flow switching flow rate adjusting device 40 of the relay unit 2 by the pipe 5.
  • the use side heat exchanger 35 exchanges heat between air supplied from a blower such as a fan (not shown) and a heat medium, and generates heating air or cooling air to be supplied to the living space 7. To do.
  • FIG. 2 shows an example in which four indoor units 3 are connected to the relay unit 2, and are illustrated as an indoor unit 3a, an indoor unit 3b, an indoor unit 3c, and an indoor unit 3d from the upper side of the drawing.
  • the use side heat exchanger 35 is also used from the upper side of the page with the use side heat exchanger 35a, the use side heat exchanger 35b, the use side heat exchanger 35c, and the use side heat. It is illustrated as an exchanger 35d.
  • the number of connected indoor units 3 is not limited to the four shown in FIG.
  • the relay unit 2 includes two heat exchangers for heat medium 25, two expansion devices 26, two switch devices (switch devices 27, switch devices 29), and two second refrigerant flow switching devices 28.
  • a pump 31 that is two heat medium transfer devices, four heat medium flow switching flow rate adjustment devices 40, and two air removal valves 41 and 42 are mounted.
  • the two heat exchangers for heat medium 25 serve as condensers (heat radiators) for cooling when supplying heat to the indoor unit 3 that is performing the heating operation.
  • heat exchangers for heat medium 25a, 25b serve as condensers (heat radiators) for cooling when supplying heat to the indoor unit 3 that is performing the heating operation.
  • it When supplying cold heat to the indoor unit 3 in operation, it functions as an evaporator, performs heat exchange between the heat source side refrigerant and the heat medium, and is generated by the heat source device 1 and stored in the heat source side refrigerant. Transfers cold or warm heat to the heat medium.
  • the heat exchanger related to heat medium 25a is provided between the expansion device 26a and the second refrigerant flow switching device 28a in the primary circuit 20, and serves to cool the heat medium in the cooling / heating mixed operation mode.
  • the heat exchanger related to heat medium 25b is provided between the expansion device 26b and the second refrigerant flow switching device 28b in the primary circuit 20, and serves to heat
  • the two expansion devices 26 have functions as pressure reducing valves and expansion valves, and expand the heat source side refrigerant by reducing the pressure.
  • the expansion device 26a is provided on the upstream side of the heat exchanger related to heat medium 25a in the flow of the heat source side refrigerant during the cooling operation.
  • the expansion device 26b is provided on the upstream side of the heat exchanger related to heat medium 25b in the flow of the heat source side refrigerant during the cooling operation.
  • the two throttling devices 26 may be configured by a device whose opening degree can be variably controlled, for example, an electronic expansion valve.
  • the two opening / closing devices are configured by electromagnetic valves or the like that can be opened / closed by energization, and open / close the refrigerant pipe 4. That is, the opening and closing of the two opening / closing devices 27 and 29 is controlled according to the operation mode, and the flow path of the heat source side refrigerant is switched.
  • the opening / closing device 27 is provided in the refrigerant pipe 4 on the inlet side of the heat source side refrigerant.
  • the opening / closing device 29 is provided in a pipe connecting the refrigerant pipe 4 on the inlet side of the heat source side refrigerant and the refrigerant pipe 4 on the outlet side.
  • the opening / closing devices 27 and 29 may be any devices that can switch the refrigerant flow path. For example, an electronic expansion valve or the like that can variably control the opening degree may be used.
  • the two second refrigerant flow switching devices 28 are constituted by, for example, a four-way valve or the like, and the heat exchanger related to heat medium 25 is a condenser or an evaporator depending on the operation mode.
  • the flow of the heat source side refrigerant is switched so as to act as
  • the second refrigerant flow switching device 28a is provided on the downstream side of the heat exchanger related to heat medium 25a in the flow of the heat source side refrigerant during the cooling operation.
  • the second refrigerant flow switching device 28b is provided on the downstream side of the heat exchanger related to heat medium 25b in the flow of the heat source side refrigerant in the cooling operation mode.
  • the two pumps 31 (pumps 31 a and 31 b) circulate the heat medium that conducts the pipe 5 to the secondary circuit 30.
  • the pump 31 a is provided in the pipe 5 between the heat exchanger related to heat medium 25 a and the heat medium flow switching flow control device 40.
  • the pump 31 b is provided in the pipe 5 between the heat exchanger related to heat medium 25 b and the heat medium flow switching flow control device 40.
  • the two pumps 31 may be configured by, for example, capacity-controllable pumps, and the flow rate thereof may be adjusted according to the load in the indoor unit 3.
  • the two air removal valves 41 and 42 are used to evacuate the secondary circuit 30 during construction.
  • the number of connected air removal valves is not limited to two as shown in FIG.
  • the four heat medium flow path switching flow rate adjusting devices 40 are composed of one drive device and a valve body, and the heat medium flow path is used as a heat exchanger between heat mediums. It switches between 25a and the heat exchanger between heat media 25b, and adjusts the flow rate of the heat medium to each branch.
  • the number of heat medium flow switching flow rate adjusting devices 40 according to the number of indoor units 3 installed (here, four) is provided, and each of them can be connected to each other. . Further, in the heat medium flow switching flow rate adjusting device 40, one of them is connected to the heat exchanger related to heat medium 25a and the other is connected to the heat exchanger related to heat medium 25b.
  • the heating medium channel switching flow rate adjustment device 40a In correspondence with the indoor unit 3, from the upper side of the page, the heating medium channel switching flow rate adjustment device 40a, the heating medium channel switching flow rate adjustment device 40b, the heating medium channel switching flow rate adjustment device 40c, and the heating medium channel switching flow rate adjustment are adjusted. Illustrated as device 40d.
  • the switching of the heat medium flow path includes not only complete switching from one to the other but also partial switching from one to the other.
  • the heat medium flow switching flow rate adjusting device 40 can also adjust the flow rate, and controls the flow rate of the heat medium flowing through the pipe 5 by adjusting the opening area.
  • One of the heat medium flow switching flow rate adjusting devices 40 is connected to the use side heat exchanger 35 and the other is connected to the heat exchanger related to heat medium 25. That is, the heat medium flow switching flow rate adjusting device 40 adjusts the amount of the heat medium flowing into the indoor unit 3 according to the temperature of the heat medium flowing into the indoor unit 3 and the temperature of the heat medium flowing out, according to the indoor load. An optimal amount of heat medium can be provided to the indoor unit 3.
  • the heat medium flow path switching flow rate adjustment device 40 When the indoor unit 3 does not require a load such as stop or thermo OFF, or when it is desired to shut off the heat medium flow path due to maintenance or the like, the heat medium flow path switching flow rate adjustment device 40 is fully closed. As a result, the supply of the heat medium to the indoor unit 3 can be stopped.
  • the relay unit 2 is provided with a temperature sensor 55 (temperature sensors 55a and 55b) for detecting the temperature of the heat medium on the outlet side of the heat exchanger related to heat medium 25.
  • Information (temperature information) detected by the temperature sensor 55 is sent to a control device 50 that performs overall control of the operation of the air-conditioning apparatus 100, and the driving frequency of the compressor 10, the rotational speed of the blower (not shown), the first refrigerant flow It is used for control such as switching of the path switching device 11, driving frequency of the pump 31, switching of the second refrigerant flow switching device 28, switching of the flow path of the heat medium, adjustment of the heat medium flow rate of the indoor unit 3.
  • a control device 50 that performs overall control of the operation of the air-conditioning apparatus 100, and the driving frequency of the compressor 10, the rotational speed of the blower (not shown), the first refrigerant flow It is used for control such as switching of the path switching device 11, driving frequency of the pump 31, switching of the second refrigerant flow switching device 28, switching of the flow path
  • control device 50 is mounted in the relay unit 2
  • the present invention is not limited to this, and the control device 50 is mounted to be communicable with the heat source device 1 or the indoor unit 3 or each unit. You may do it.
  • the control device 50 is constituted by a microcomputer or the like, and based on detection information from various detection means and instructions from a remote controller, the driving frequency of the compressor 10, the rotational speed of the blower (including ON / OFF), the first refrigerant flow path. Switching of the switching device 11, driving of the pump 31, opening of the expansion device 26, opening and closing of the switching devices 27 and 29, switching of the second refrigerant flow switching device 28, switching and driving of the heat medium flow switching flow rate adjusting device 40 Etc., each actuator (pump 31, throttle device 26) is controlled.
  • the control device 50 constantly acquires the rotation speed N of the pumps 31a and 31b in the air removal operation mode described later, and starts a timer when the rotation speed Nb when air is sucked is detected. Then, the generation interval between the rotation speeds Nb up to the next rotation speed Nb is detected.
  • the pipe 5 that conducts the heat medium is composed of one that is connected to the heat exchanger related to heat medium 25a and one that is connected to the heat exchanger related to heat medium 25b.
  • the pipe 5 is branched (here, four branches each) according to the number of indoor units 3 connected to the relay unit 2.
  • the pipe 5 is connected by a heat medium flow switching flow rate adjusting device 40. By controlling the heat medium flow switching flow rate adjusting device 40, the heat medium from the heat exchanger related to heat medium 25a flows into the use side heat exchanger 35, or the heat medium from the heat exchanger related to heat medium 25b is used as the heat medium. Whether to flow into the use side heat exchanger 35 is determined.
  • the compressor 10 In the air conditioner 100, the compressor 10, the first refrigerant flow switching device 11, the heat source side heat exchanger 12, the switching device 27, the switching device 29, the second refrigerant flow switching device 28, and heat exchange between heat media.
  • the refrigerant flow path of the container 25, the expansion device 26, and the accumulator 19 are connected by the refrigerant pipe 4 to constitute the primary side circuit 20.
  • the secondary medium circuit 30 is configured by connecting the heat medium flow path of the heat exchanger 25 between the heat medium 25, the pump 31, the heat medium flow path switching flow rate adjusting device 40, and the use side heat exchanger 35 with the pipe 5. ing.
  • a plurality of use side heat exchangers 35 are connected in parallel to each of the heat exchangers 25 between heat mediums, and the secondary side circuit 30 has a plurality of systems.
  • the heat source device 1 and the relay unit 2 are connected via the heat exchangers 25a and 25b provided in the relay unit 2, and the relay unit 2 and the indoor unit 3 are connected. Are connected via heat exchangers 25a and 25b. That is, in the air conditioner 100, the heat source side refrigerant circulating in the primary circuit 20 and the heat medium circulating in the secondary circuit 30 exchange heat in the intermediate heat exchangers 25a and 25b. By using such a configuration, the air conditioner 100 can realize an optimal cooling operation or heating operation according to the indoor load.
  • FIG. 3 is a refrigerant circuit diagram illustrating a refrigerant flow in the mixed operation mode of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the heating main The operation mode will be described.
  • tube represented by the thick line has shown the piping through which the heat source side refrigerant
  • the flow direction is shown by the solid line arrow.
  • the first refrigerant flow switching device 11 relays the heat source side refrigerant discharged from the compressor 10 without passing through the heat source side heat exchanger 12. Switch to flow into unit 2.
  • the pumps 31a and 31b are driven, the heat medium flow switching flow rate adjusting devices 40a to 40d are opened, the heat exchanger 25a between the heat medium and the use side heat exchanger 35 generating the cooling load, The heat medium is circulated between the heat exchanger 25b between the heat medium and the use side heat exchanger 35 where the heat load is generated.
  • the second refrigerant flow switching device 28a is switched to the cooling side, the second refrigerant flow switching device 28b is switched to the heating side, the expansion device 26a is fully opened, the opening / closing device 27 is closed, and the opening / closing device 29 is closed. ing.
  • the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, conducts the refrigerant connection pipe 4 a, passes through the check valve 13 d, and flows out of the heat source device 1.
  • the high-temperature and high-pressure gas refrigerant that has flowed out of the heat source device 1 flows into the relay unit 2 through the refrigerant pipe 4.
  • the high-temperature and high-pressure gas refrigerant that has flowed into the relay unit 2 flows through the second refrigerant flow switching device 28b into the heat exchanger related to heat medium 25b that acts as a condenser.
  • the gas refrigerant that has flowed into the heat exchanger related to heat medium 25b is condensed and liquefied while dissipating heat to the heat medium circulating in the secondary circuit 30, and becomes liquid refrigerant.
  • the liquid refrigerant flowing out of the heat exchanger related to heat medium 25b is expanded by the expansion device 26b and becomes a low-pressure two-phase refrigerant.
  • This low-pressure two-phase refrigerant flows into the heat exchanger related to heat medium 25a acting as an evaporator via the expansion device 26a.
  • the low-pressure two-phase refrigerant flowing into the heat exchanger related to heat medium 25a evaporates by absorbing heat from the heat medium circulating in the secondary circuit 30 and cools the heat medium.
  • the low-pressure two-phase refrigerant flows out of the heat exchanger related to heat medium 25a, flows out of the relay unit 2 through the second refrigerant flow switching device 28a, and flows into the heat source device 1 again through the refrigerant pipe 4.
  • the low-temperature and low-pressure two-phase refrigerant that has flowed into the heat source device 1 flows into the heat source side heat exchanger 12 that acts as an evaporator through the check valve 13b.
  • coolant which flowed into the heat source side heat exchanger 12 absorbs heat from external air in the heat source side heat exchanger 12, and turns into a low temperature and low pressure gas refrigerant.
  • the low-temperature and low-pressure gas refrigerant flowing out from the heat source side heat exchanger 12 is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
  • the opening degree of the expansion device 26b is controlled so that the subcooling (supercooling degree) of the outlet refrigerant of the heat exchanger related to heat medium 25b becomes a target value. Note that the expansion device 26b may be fully opened, and the subcool may be controlled by the expansion device 26a.
  • the heat of the heat source side refrigerant is transmitted to the heat medium in the heat exchanger related to heat medium 25b, and the heated heat medium is caused to flow in the pipe 5 by the pump 31b.
  • the heated heat medium that has been pressurized and discharged by the pump 31b flows into the use-side heat exchanger 35 where the thermal load is generated via the heat medium flow switching flow rate adjusting device 40.
  • the cold heat of the heat source side refrigerant is transmitted to the heat medium in the intermediate heat exchanger 25a, and the cooled heat medium is caused to flow in the pipe 5 by the pump 31a.
  • the cooled heat medium that has been pressurized and flowed out by the pump 31a flows into the use-side heat exchanger 35 where the cold load is generated via the heat medium flow switching flow rate adjusting device 40.
  • the heat medium flow switching flow rate adjustment device 40 is switched to the direction in which the heat exchanger related to heat medium 25b and the pump 31b are connected.
  • the indoor unit 3 is switched to the direction in which the heat exchanger related to heat medium 25a and the pump 31a are connected. That is, the heat medium flow switching device 40 can switch the heat medium supplied to the indoor unit 3 for heating or cooling.
  • the cooling operation of the living space 7 by the heat medium absorbing heat from the indoor air or the heating operation of the living space 7 by the heat medium radiating heat to the indoor air is performed.
  • the flow rate of the heat medium is controlled to a flow rate necessary to cover the air conditioning load required indoors by the action of the heat medium flow switching flow rate adjusting device 40 and flows into the use side heat exchanger 35.
  • the heat medium that has been used for the cooling operation and has passed through the use-side heat exchanger 35 and whose temperature has risen slightly passes through the heat medium flow switching flow rate adjusting device 40 and flows into the heat exchanger related to heat medium 25a, and is again pumped. It is sucked into 31a.
  • the heat medium that has been used for the heating operation and has passed through the use-side heat exchanger 35 and has slightly decreased in temperature passes through the heat medium flow switching flow adjustment device 40 and flows into the heat exchanger related to heat medium 25b, and is again pumped. It is sucked into 31b.
  • the heat medium flow switching flow rate adjustment device 40 is switched to the direction in which the heat exchanger related to heat medium 25b and the pump 31b are connected.
  • the indoor unit 3 is switched to the direction in which the heat exchanger related to heat medium 25a and the pump 31a are connected.
  • the warm heat medium and the cold heat medium are introduced into the use-side heat exchanger 35 having a heat load and a heat load, respectively, without being mixed by the action of the heat medium flow switching flow control device 40.
  • the heat medium used in the heating operation mode is caused to flow into the heat exchanger related to heat medium 25b, which gives heat from the refrigerant for heating use, and the heat medium used in the cooling operation mode is used for cooling use.
  • the heat is introduced into the heat exchanger related to heat medium 25a that receives the heat, and each heat exchanges again with the refrigerant, and then is transferred to the pumps 31a and 31b.
  • the air conditioning load required in the living space 7 is the difference between the temperature detected by the temperature sensor 55b on the heating side and the temperature of the heat medium flowing out from the use side heat exchanger 35 on the cooling side. This can be covered by controlling the difference between the temperature of the heat medium flowing out from the use side heat exchanger 35 and the temperature detected by the temperature sensor 55a as a target value.
  • FIG. 4 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 according to Embodiment 1 of the present invention is in the heating only operation mode.
  • the heating only operation mode will be described by taking as an example a case where a heating load is generated in all of the use side heat exchangers 35a to 35d.
  • the flow direction is indicated by a solid arrow.
  • the heat source side refrigerant discharged from the compressor 10 does not pass through the heat source side heat exchanger 12 in the first refrigerant flow switching device 11. It switches so that it may flow into relay unit 2.
  • the pumps 31a and 31b are driven, the heat medium flow switching flow rate adjusting devices 40a to 40d are opened, and the heat exchangers 25a and 25b between the heat medium and the use side heat exchangers 35a to 35d are connected. The heat medium circulates between them.
  • the second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b are switched to the heating side, the opening / closing device 27 is closed, and the opening / closing device 29 is open.
  • the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, conducts the refrigerant connection pipe 4 a, passes through the check valve 13 d, and flows out of the heat source device 1.
  • the high-temperature and high-pressure gas refrigerant that has flowed out of the heat source device 1 flows into the relay unit 2 through the refrigerant pipe 4.
  • the high-temperature and high-pressure gas refrigerant that has flowed into the relay unit 2 is branched, passes through the second refrigerant flow switching devices 28a and 28b, and flows into the heat exchangers 25a and 25b, respectively.
  • the high-temperature and high-pressure gas refrigerant that has flowed into the intermediate heat exchangers 25a and 25b is condensed and liquefied while dissipating heat to the heat medium passing through the secondary circuit 30, and becomes a high-pressure liquid refrigerant.
  • the liquid refrigerant flowing out from the heat exchangers 25a and 25b is expanded by the expansion devices 26a and 26b, and becomes a low-temperature and low-pressure two-phase refrigerant.
  • These two-phase refrigerants merge, flow out of the relay unit 2 through the opening / closing device 29, and flow into the heat source device 1 again through the refrigerant pipe 4.
  • the refrigerant flowing into the heat source device 1 is conducted through the refrigerant connection pipe 4b, passes through the check valve 13b, and flows into the heat source side heat exchanger 12 that functions as an evaporator.
  • the heat-source-side refrigerant that has flowed into the heat-source-side heat exchanger 12 absorbs heat from the air in the outdoor space 6 (hereinafter referred to as “outside air”) by the heat-source-side heat exchanger 12, and becomes a low-temperature / low-pressure gas refrigerant.
  • the low-temperature and low-pressure gas refrigerant flowing out from the heat source side heat exchanger 12 is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
  • the expansion device 26 has a value obtained by converting the pressure of the heat-source-side refrigerant flowing between the heat exchanger related to heat medium 25 and the expansion device 26 into a saturation temperature, and the temperature on the outlet side of the heat exchanger related to heat medium 25.
  • the degree of opening is controlled so that the subcool (degree of supercooling) obtained as a difference from the above becomes constant.
  • the heat of the heat source side refrigerant is transmitted to the heat medium in both the heat exchangers 25a and 25b, and the heated heat medium is caused to flow in the pipe 5 by the pumps 31a and 31b.
  • the heat medium pressurized and discharged by the pumps 31a and 31b flows into the use side heat exchangers 35a to 35d via the heat medium flow switching flow rate adjusting device 40.
  • the living space 7 is heated by the heat medium radiating heat to the indoor air by the use side heat exchangers 35a to 35d.
  • the heat medium flows out of the use side heat exchangers 35a to 35d and flows into the heat medium flow switching flow rate adjusting device 40 again.
  • the heat medium flow switching device 40 controls the flow rate of the heat medium to a flow rate necessary to cover the air conditioning load required in the room, so that the use side heat exchangers 35a to 35d are used. Flow into.
  • the heat medium that has flowed out of the heat medium flow switching flow control device 40 flows into the heat exchangers 25a and 25b between the heat medium, receives the amount of heat supplied to the living space 7 through the indoor unit 3 from the refrigerant side, and pumps again. It is sucked into 31a and 31b.
  • the air conditioning load required in the living space 7 is the temperature detected by the temperature sensor 55a, or the temperature detected by the temperature sensor 55b and the temperature of the heat medium flowing out from the use side heat exchanger 35. This can be covered by controlling the flow rate of the heat medium flow switching device 40 so as to keep the difference at the target value.
  • the outlet temperature of the heat exchanger related to heat medium 25 the temperature of either the temperature sensor 55a or the temperature sensor 55b may be used, or the average temperature thereof may be used.
  • the refrigerant is flowing into both of the heat exchangers 25a and 25b, and the pumps 31a and 31b for transporting the heat medium are also operated, so that they are connected to the branch ports.
  • the pumps 31a and 31b for transporting the heat medium are also operated, so that they are connected to the branch ports.
  • FIG. 5 is a diagram showing the flow of the heat medium during the air removal operation mode of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the air removal operation mode is a mode in which, for example, the secondary side circuit 30 is filled with a heat medium during construction (installation) of the air conditioner 100 (before operation by the actual air conditioning operation described above).
  • the heat medium is caused to flow in the pipe 5 by the pressurization of the pump 31.
  • the heat medium sucked into the pumps 31a and 31b and pressurized and flowed out passes through the heat medium flow switching flow rate adjusting device 40 and flows into the use side heat exchangers 35a to 35d.
  • the blowers included in the indoor units 3a to 3d may be stopped so that the heat exchange between the heat medium and the indoor air is not actively performed in the use side heat exchangers 35a to 35d.
  • the heat medium that has passed through the use side heat exchangers 35a to 35d returns to the heat medium flow switching flow control device 40, passes through the heat exchangers between heat mediums 25a and 25b, and is sucked into the pumps 31a and 31b again.
  • the air removal valves 41 and 42 are opened, and the air in the heat medium is removed from the air removal valves 41 and 42.
  • the air removal valves 41 and 42 are closed when the air removal operation mode is completed.
  • the operation of the primary side circuit 20 is not performed here, for example, in the air removal operation mode, the operation may be performed in the same manner as in the heating only operation mode.
  • the operation may be performed in the same manner as in the heating only operation mode.
  • FIG. 6 is a diagram illustrating a flow in the air removal operation mode performed by the control device 50 according to Embodiment 1 of the present invention. Based on FIG. 6, the content of the process which the control apparatus 50 performs in the air removal operation mode is demonstrated.
  • the control device 50 starts the air removal operation mode (step S1). After the operation is started, the air removal valves 41 and 42 in the secondary circuit are opened (step S2). Thereafter, the pumps 31a and 31b are stopped for a predetermined time (for example, 10 seconds) and driven intermittently (step S3).
  • control is performed to determine whether or not the air in the secondary circuit 30 has been exhausted during step S3 based on the rotational speeds of the pumps 31a and 31b (step S4).
  • the pumps 31a and 31b use water pumps that can use, for example, water, antifreeze, a mixture of water and antifreeze, or a mixture of water and an additive having a high anticorrosive effect. Occurs, causing the pumps 31a and 31b to idle. Therefore, when air is inhaled, the rotational speed of the pumps 31a and 31b temporarily increases as compared to the normal rotational speed.
  • FIG. 7 is a diagram showing the relationship between the rotational speeds of the pumps 31a and 31b and the operation time of the air removal operation during the air removal operation according to Embodiment 1 of the present invention.
  • the rotational speed N of the pumps 31a and 31b temporarily increases as compared to the normal rotational speed Na.
  • the control device 50 constantly acquires the rotational speed N of the pumps 31a and 31b, if a large amount of air remains in the secondary circuit 30, the rotational speed Nb when air is sucked in is frequently detected.
  • the frequency of detecting the rotational speed Nb decreases.
  • the control device 50 completes the air removal operation when the generation interval (elapsed time Tx) of the rotation speed Nb when the air of the pumps 31a and 31b is sucked becomes equal to or longer than a preset time interval (Te). To do. In other words, the control device 50 can be said to complete the air removal operation when the generation of the rotational speed Nb when the air of the pumps 31a and 31b is sucked does not continue within a preset time (Te).
  • Tr the time taken to make a round of the secondary circuit 30 after the air bubbles are discharged from the pumps 31a and 31b.
  • step S4 After the end of step S4, it is determined whether or not a predetermined time (for example, 20 minutes) has elapsed since the start of step S3 (step S5). If it is determined that the predetermined time has not elapsed, the processes of steps S3 to S5 are repeated. On the other hand, if it is determined that the predetermined time has elapsed, the intermittent operation in step S3 is terminated, and the process proceeds to step S6.
  • a predetermined time for example, 20 minutes
  • step S6 the individual indoor unit operation is started (step S6).
  • step S6 the opening degree of the heat medium flow switching flow rate adjusting device 40a is maximized, the heat medium flow switching flow rate adjusting devices 40b, 40c, and 40d are closed, and the heat medium does not flow toward the indoor units 3b, 3c, and 3d. Like that. Further, after the operation of the indoor unit 3a, the same operation is performed for each of the indoor units 3b, 3c, and 3d. For this reason, the path length in the secondary side circuit 30 becomes short, and the flow rate of the heat medium with respect to the output can be increased.
  • step S6 control is performed to determine whether or not the air in the secondary circuit 30 has been exhausted based on the rotational speed N of the pumps 31a and 31b (step S7).
  • step S7 the same calculation as in step S4 described above is performed, and when Tx ⁇ Te is established, the air removal operation is terminated (step S13).
  • Tx ⁇ Te is not established in step S7, it is determined whether or not a predetermined time (for example, the number of specified branches ⁇ 10 minutes) has elapsed since the start of step S6 (step S8). If it is determined that the predetermined time has not elapsed, steps S6 to S8 are repeated. If it is determined that the predetermined time has elapsed, the individual indoor unit operation in step S6 is terminated, and the process proceeds to step S9.
  • a predetermined time for example, the number of specified branches ⁇ 10 minutes
  • step S8 When step S8 is completed, all the indoor units 3a to 3d are heated by maximizing the openings of all the heat medium flow switching flow rate adjusting devices 40a to 40d (step S9). For this reason, the primary side circuit 20 is also operated in the heating only operation mode.
  • whether or not to drive the blower (not shown) of the indoor unit 3 is not particularly limited.
  • step S9 control is performed to determine whether or not the air in the secondary circuit 30 has been exhausted based on the rotational speed N of the pumps 31a and 31b (step S10).
  • step S10 the same calculation as in steps S4 and S7 described above is performed, and when Tx ⁇ Te is satisfied, the air removal operation is terminated (step S13).
  • step S10 when Tx ⁇ Te is not established in step S10, it is determined whether or not a predetermined time (for example, 20 minutes) has elapsed since the start of step S9 (step S11). If it is determined that the predetermined time has not elapsed, the processes of steps S9 to S11 are repeated.
  • a predetermined time for example, 20 minutes
  • step S12 control is performed to determine whether or not the air in the secondary circuit 30 has been exhausted based on the rotational speed N of the pumps 31a and 31b (step S12). That is, in step S12, it is determined again whether Tx ⁇ Te is satisfied. If Tx ⁇ Te is established, the operation in the air removal operation mode is completed (step S13). When Tx ⁇ Te is not established, the process proceeds to step S3 and the operation is resumed.
  • the control device 50 when the secondary circuit 30 is installed, the control device 50 automatically determines the completion of the air removal operation. It can be carried out.
  • the air removal valves 41 and 42 are opened, the pumps 31a and 31b are driven to circulate the heat medium, and the inside of the secondary circuit 30
  • the control apparatus 50 which performs the air removal operation which extracts the air of this, and determines completion of air removal operation based on the rotation speed of pump 31a, 31b is provided. According to this, the completion of the air removal operation is determined based on the number of rotations of the pumps 31a and 31b, and the determination to complete the air removal operation is quantitatively performed. And prolonged construction time can be avoided.
  • the control device 50 determines the completion of the air removal operation based on the generation of the rotational speed Nb when the air of the pumps 31a and 31b is sucked. According to this, since the determination to complete the air removal operation is quantitatively made based on the generation of the rotational speed Nb when the air of the pumps 31a and 31b is sucked, the residual air in the secondary circuit 30 and the construction Prolonged time can be avoided.
  • the control device 50 completes the air removal operation when the generation interval (elapsed time Tx) of the rotational speed Nb when the air of the pumps 31a and 31b is sucked becomes equal to or longer than a preset time interval (Te). According to this, since the determination to complete the air removal operation is quantitatively performed based on the relational expression of Tx ⁇ Te, it is possible to avoid the remaining of air in the secondary circuit 30 and the lengthening of the construction time. .
  • 1 Heat source device 2 relay unit, 3 (3a, 3b, 3c, 3d) indoor unit, 4 refrigerant pipe, 4a, 4b refrigerant connection pipe, 5 pipe, 6 outdoor space, 7 residential space, 8 non-residential space, 9 Building, 10 compressor, 11 first refrigerant flow switching device, 12 heat source side heat exchanger, 13a, 13b, 13c, 13d check valve, 19 accumulator, 20 primary side circuit, 25 (25a, 25b) heat Inter-medium heat exchanger, 26 (26a, 26b) throttle device, 27, 29 switchgear, 28 (28a, 28b) second refrigerant flow switching device, 30 secondary circuit, 31 (31a, 31b) pump, 35 (35a, 35b, 35c, 35d) User side heat exchanger, 40 (40a, 40b, 40c, 40d) Heat medium flow switching flow control device, 41, 42 Air removal valve, 0 controller, 55 (55a, 55b) a temperature sensor, 100 an air conditioner.

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Abstract

In order to quantitatively make a determination for ending an air removal operation, and to prevent air from remaining in a heat medium circulation circuit and prevent an increase in the installation time, an air-conditioning device is equipped with: a primary-side circuit 20, formed by connecting by means of piping a compressor 10, a heat-source-side heat exchanger 12, throttle devices 26, and the heat-source-side and refrigerant-side of inter-heat-medium heat exchangers 25; and a secondary-side circuit 30, formed by connecting by means of piping the heat-medium side of the inter-heat-medium heat exchangers 25, pumps 31, and usage-side heat exchangers 35. The secondary-side circuit 30 has air removal valves 41 and 42 for discharging air in the circuit. Furthermore, a control device 50 is provided for executing an air removal operation, in which the air removal valves 41 and 42 are opened and the pumps 31 are driven, thereby circulating the heat medium and removing air from within the secondary-side circuit 30 when the secondary-side circuit 30 is installed, and for determining the end of the air removal operation on the basis of the rotational frequency of the pumps 31.

Description

空気調和装置Air conditioner
　本発明は、たとえばビル用マルチエアコンなどに適用する施工時に熱媒体循環回路内から空気を抜く空気調和装置に関する。 The present invention relates to an air conditioner that extracts air from a heat medium circulation circuit during construction applied to, for example, a building multi-air conditioner.
　たとえば室外機と中継ユニットとの間を配管接続して構成する冷凍サイクル回路（以下、１次側回路と称する）を循環する熱源側冷媒と、中継ユニットと室内機との間を配管接続して構成する熱媒体循環回路（以下、２次側回路と称する）を循環する屋内側冷媒と、を熱交換させる空気調和装置がある。 For example, by connecting a pipe between the heat source side refrigerant circulating in a refrigeration cycle circuit (hereinafter referred to as a primary side circuit) configured by connecting a pipe between the outdoor unit and the relay unit, and between the relay unit and the indoor unit. There is an air conditioner that exchanges heat with an indoor-side refrigerant that circulates in a heat medium circulation circuit (hereinafter referred to as a secondary circuit).
　そして、このような構成の空気調和装置をビル用マルチエアコンなどに適用する際、熱媒体の搬送動力を低減させるようにして省エネルギーを図っているものがある（たとえば、特許文献１参照）。 When applying an air conditioner having such a configuration to a building multi-air conditioner or the like, there is one that saves energy by reducing the conveyance power of the heat medium (see, for example, Patent Document 1).
　特許文献１に開示された技術において、室内機との間を配管接続して構成する２次側回路を循環する屋内側冷媒は、水や水にブラインを混ぜた溶液を用いている。ここで、特に屋内側の循環回路の施工過程では、回路内に空気が混入し易い。２次側回路の水またはブライン溶液に空気が混入することによって故障が生じる可能性がある。よって、空気調和装置を稼働する前の段階で、２次側回路内の空気を除去する運転（以下、空気除去運転と称する）を行う必要があった（たとえば、特許文献２参照）。 In the technology disclosed in Patent Document 1, an indoor refrigerant that circulates in a secondary circuit configured by connecting a pipe to an indoor unit uses water or a solution obtained by mixing brine with water. Here, especially in the construction process of the circulation circuit on the indoor side, air is likely to enter the circuit. Failure can occur due to air entering the water or brine solution of the secondary circuit. Therefore, it is necessary to perform an operation for removing air in the secondary circuit (hereinafter referred to as an air removal operation) before operating the air conditioner (see, for example, Patent Document 2).
国際公開第２０１０／０４９９９８号International Publication No. 2010/049998 国際公開第２０１４／０８３６８２号International Publication No. 2014/083682
　特許文献２に開示された技術において、２次側回路内の空気を除去する空気除去運転を完了するか否かは、作業者の目視によって空気の排出量を確認して判断していた。
　ここで、作業者の目視による空気の排出量の確認は、個人差によって判断にばらつきが生じる。このため、空気が２次側回路内に残留したり、空気除去運転に時間をかけすぎることによって施工時間が長期化したりする課題があった。 In the technique disclosed in Patent Document 2, whether or not to complete the air removal operation for removing the air in the secondary circuit has been determined by checking the amount of air discharged by the operator's visual observation.
Here, the operator's visual confirmation of the air discharge amount varies depending on individual differences. For this reason, there existed a subject that construction time was prolonged because air remained in a secondary side circuit or it took time for air removal operation too much.
　本発明は上述の課題を解決するためのものであり、空気除去運転を完了する判断を定量的に行い、熱媒体循環回路内の空気の残留や施工時間の長期化を回避することを目的とする。 The present invention is intended to solve the above-described problems, and quantitatively determines the completion of the air removal operation, and aims to avoid air remaining in the heat medium circulation circuit and prolonged construction time. To do.
　本発明に係る空気調和装置は、熱源側冷媒を圧縮する圧縮機、前記熱源側冷媒を熱交換させる熱源側熱交換器、前記熱源側冷媒を圧力調整する絞り装置および前記熱源側冷媒と熱媒体との熱交換を行う熱媒体間熱交換器の熱源側冷媒側を配管接続して構成された冷媒循環回路と、前記熱媒体間熱交換器の熱媒体側、前記熱媒体を循環させるポンプおよび前記熱媒体と空調対象空間の空気との熱交換を行う利用側熱交換器を配管接続して構成された熱媒体循環回路と、を備え、前記熱媒体循環回路は、内部の空気を放出させる空気除去弁を有し、前記熱媒体循環回路を施工したときに前記空気除去弁を開弁して前記ポンプを駆動させて前記熱媒体を循環させて前記熱媒体循環回路内の空気を抜く空気除去運転を実行し、前記空気除去運転の完了を、前記ポンプの回転数に基づいて判定を行う制御装置を備えるものである。 An air conditioner according to the present invention includes a compressor that compresses a heat source side refrigerant, a heat source side heat exchanger that exchanges heat with the heat source side refrigerant, a throttling device that adjusts the pressure of the heat source side refrigerant, and the heat source side refrigerant and heat medium A refrigerant circulation circuit configured by pipe-connecting a heat source side refrigerant side of a heat exchanger related to heat medium that performs heat exchange with the heat medium, a heat medium side of the heat exchanger related to heat medium, a pump for circulating the heat medium, and A heat medium circulation circuit configured by pipe connection of a use side heat exchanger that exchanges heat between the heat medium and the air in the air-conditioning target space, and the heat medium circulation circuit releases internal air Air that has an air removal valve, opens the air removal valve when the heat medium circulation circuit is installed, drives the pump to circulate the heat medium, and removes air from the heat medium circulation circuit The removal operation is executed and the air removal operation is completed. The one in which a control device for determining on the basis of the rotational speed of the pump.
　本発明に係る空気調和装置によれば、空気除去運転の完了を、ポンプの回転数に基づいて判定を行い、空気除去運転を完了する判断を定量的に行うので、熱媒体循環回路内の空気の残留や施工時間の長期化を回避することができる。 According to the air conditioner of the present invention, the completion of the air removal operation is determined based on the number of revolutions of the pump, and the determination to complete the air removal operation is quantitatively performed. It is possible to avoid residuals and prolonged construction time.
本発明の実施の形態１に係る空気調和装置の設置例を示す概略図である。It is the schematic which shows the example of installation of the air conditioning apparatus which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る空気調和装置の構成を示す概略回路図である。It is a schematic circuit diagram which shows the structure of the air conditioning apparatus which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る空気調和装置の混在運転モード時における冷媒の流れを示す冷媒回路図である。It is a refrigerant circuit diagram which shows the flow of the refrigerant | coolant at the time of the mixed operation mode of the air conditioning apparatus which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る空気調和装置の全暖房運転モード時における冷媒の流れを示す冷媒回路図である。It is a refrigerant circuit diagram which shows the flow of the refrigerant | coolant at the time of the heating only operation mode of the air conditioning apparatus which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る空気調和装置の空気除去運転モード時における熱媒体の流れを示す図である。It is a figure which shows the flow of the heat medium at the time of the air removal operation mode of the air conditioning apparatus which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る制御装置が行う空気除去運転モード時におけるフローを説明する図である。It is a figure explaining the flow in the air removal operation mode which the control apparatus which concerns on Embodiment 1 of this invention performs. 本発明の実施の形態１に係る空気除去運転時におけるポンプの回転数と空気除去運転の運転時間の関係を示す図である。It is a figure which shows the relationship between the rotation speed of the pump at the time of the air removal driving | operation which concerns on Embodiment 1 of this invention, and the driving | running time of air removal driving | operation.
実施の形態１．
　図１は、本発明の実施の形態１に係る空気調和装置１００の設置例を示す概略図である。
　図１に基づいて、空気調和装置１００の構成について説明する。この空気調和装置１００は、熱源側冷媒を循環させる１次側回路２０および水や不凍液などの熱媒体を循環させる２次側回路３０を利用し、冷房運転または暖房運転を実行するものである。ここで、図１を含め、以下の図面では各構成部材の大きさの関係が実際のものとは異なる場合がある。また、添字で区別している複数の同種の機器などについて、特に区別したり、特定したりする必要がない場合には、添字を省略して記載する場合もある。また、温度、圧力などの高低については、特に絶対的な値との関係で高低などが定まっているものではなく、システム、装置などにおける状態、動作などにおいて相対的に定まるものとする。 Embodiment 1 FIG.
FIG. 1 is a schematic diagram illustrating an installation example of an air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
Based on FIG. 1, the structure of the air conditioning apparatus 100 is demonstrated. The air conditioner 100 performs a cooling operation or a heating operation using a primary side circuit 20 that circulates a heat source side refrigerant and a secondary side circuit 30 that circulates a heat medium such as water or antifreeze. Here, in the following drawings including FIG. 1, the size relationship of each component may be different from the actual one. In addition, when there is no need to distinguish or identify a plurality of similar devices that are distinguished by subscripts, the subscripts may be omitted. In addition, the level of temperature, pressure, etc. is not particularly determined in relation to absolute values, but is relatively determined in terms of the state and operation of the system, apparatus, and the like.
　図１に示すように、本実施の形態の空気調和装置１００は、たとえば熱源機である１台の熱源装置１と、複数台の室内機３と、熱源装置１と室内機３との間に介在する中継ユニット２と、を有している。
　中継ユニット２は、熱源側冷媒と熱媒体とで熱交換を行うものである。熱源装置１と中継ユニット２とは、熱源側冷媒を導通する冷媒配管４で接続される。中継ユニット２と室内機３とは、熱媒体を導通する配管５で接続される。冷媒配管４および配管５を有することにより、熱源装置１で生成された冷熱あるいは温熱を室内機３に配送する。
　なお、熱源装置１、室内機３および中継ユニット２の接続台数を図示した台数に限定するものではない。 As shown in FIG. 1, an air conditioner 100 according to the present embodiment includes, for example, one heat source device 1 that is a heat source device, a plurality of indoor units 3, and between the heat source device 1 and the indoor unit 3. And an intervening relay unit 2.
The relay unit 2 performs heat exchange between the heat source side refrigerant and the heat medium. The heat source device 1 and the relay unit 2 are connected by a refrigerant pipe 4 that conducts the heat source side refrigerant. The relay unit 2 and the indoor unit 3 are connected by a pipe 5 that conducts the heat medium. By having the refrigerant pipe 4 and the pipe 5, cold heat or hot heat generated by the heat source device 1 is delivered to the indoor unit 3.
The number of connected heat source devices 1, indoor units 3, and relay units 2 is not limited to the illustrated number.
　熱源装置１は、通常、ビルなどの建物９の外の空間である室外空間６に配置され、中継ユニット２を介して室内機３に冷熱または温熱を供給する。
　室内機３は、冷房用空気あるいは暖房用空気を搬送できる建物９の内部の居室やサーバールームなどの居住空間７に配置され、空調対象域となる居住空間７に冷房用空気あるいは暖房用空気を供給する。
　中継ユニット２は、熱源装置１および室内機３とは別体として、室外空間６および居住空間７とは別の位置である非居住空間８に配置され、熱源装置１と室内機３とを接続し、熱源装置１から供給される冷熱または温熱を室内機３に伝達する。 The heat source device 1 is normally disposed in an outdoor space 6 that is a space outside a building 9 such as a building, and supplies cold or hot heat to the indoor unit 3 via the relay unit 2.
The indoor unit 3 is disposed in a living space 7 such as a living room or a server room in a building 9 that can carry cooling air or heating air, and the cooling air or heating air is supplied to the living space 7 that is an air-conditioning target area. Supply.
The relay unit 2 is disposed separately from the heat source device 1 and the indoor unit 3 in a non-residential space 8 that is a position different from the outdoor space 6 and the residential space 7, and connects the heat source device 1 and the indoor unit 3. Then, the cold or warm heat supplied from the heat source device 1 is transmitted to the indoor unit 3.
　１次側回路２０の熱源側冷媒としては、たとえばＲ－２２、Ｒ－１３４ａ、Ｒ３２などの単一冷媒、Ｒ－４１０Ａ、Ｒ－４０４Ａなどの擬似共沸混合冷媒、Ｒ－４０７Ｃなどの非共沸混合冷媒、化学式内に二重結合を含む、ＣＦ３ＣＦ＝ＣＨ２などの地球温暖化係数が比較的小さい値とされている冷媒やその混合物、あるいはＣＯ２やプロパンなどの自然冷媒を用いることができる。 Examples of the heat source side refrigerant of the primary side circuit 20 include single refrigerants such as R-22, R-134a, and R32, pseudo-azeotropic refrigerant mixtures such as R-410A and R-404A, and non-common refrigerants such as R-407C. Use boiling refrigerants, refrigerants that contain double bonds in the chemical formula, such as CF 3 CF═CH 2, etc., which have a relatively low global warming potential, or mixtures thereof, or natural refrigerants such as CO 2 or propane be able to.
　一方、２次側回路３０の熱媒体としては、たとえば水、不凍液、水と不凍液の混合液、水と防食効果が高い添加剤の混合液などを用いることができる。 On the other hand, as the heat medium of the secondary side circuit 30, for example, water, an antifreeze solution, a mixed solution of water and antifreeze solution, a mixed solution of water and an additive having a high anticorrosion effect, or the like can be used.
　室外空間６は、建物９の外部に存在する場所、たとえば図１に示すような屋上を想定している。
　非居住空間８は、建物９の内部ではあるが居住空間７とは別の空間、たとえば廊下の上などの人が常時存在しない場所や、共用ゾーンの天井裏、エレベータなどがある共用部、機械室、電算室、倉庫などを想定している。
　居住空間７は、建物９の内部であって、常に人が存在する場所や一時的にも多数あるいは小数の人が存在する場所、たとえばオフィス、教室、会議室、食堂、サーバールームなどを想定している。 The outdoor space 6 assumes a place existing outside the building 9, for example, a rooftop as shown in FIG.
The non-residential space 8 is a space inside the building 9 but different from the residential space 7, for example, a place where there is no person at all times, such as on the corridor, a common zone with a ceiling in the common zone, an elevator, etc. A room, a computer room, a warehouse, etc. are assumed.
The living space 7 is assumed to be an interior of the building 9 where there are always people or where there are many or a small number of people temporarily, such as offices, classrooms, conference rooms, canteens, server rooms, etc. ing.
　熱源装置１と中継ユニット２とは、２本の冷媒配管４を用いて接続されている。また、中継ユニット２と各室内機３とは、それぞれ２本の配管５で接続されている。このように、熱源装置１を２本の冷媒配管４で中継ユニット２に接続し、室内機３を２本の配管５で中継ユニット２に接続することにより、空気調和装置１００の施工が容易になる。 The heat source device 1 and the relay unit 2 are connected using two refrigerant pipes 4. The relay unit 2 and each indoor unit 3 are connected by two pipes 5 respectively. Thus, the construction of the air conditioner 100 is facilitated by connecting the heat source device 1 to the relay unit 2 through the two refrigerant pipes 4 and connecting the indoor unit 3 to the relay unit 2 through the two pipes 5. Become.
　図２は、本発明の実施の形態１に係る空気調和装置１００の構成を示す概略回路図である。
　図２に示すように、熱源装置１と中継ユニット２とが、中継ユニット２に備えられている熱媒体間熱交換器２５ａ、２５ｂを介して冷媒配管４で接続されている。
　また、中継ユニット２と室内機３とが、配管５で接続されている。 FIG. 2 is a schematic circuit diagram showing the configuration of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
As shown in FIG. 2, the heat source device 1 and the relay unit 2 are connected by the refrigerant pipe 4 via the heat exchangers 25 a and 25 b provided in the relay unit 2.
Further, the relay unit 2 and the indoor unit 3 are connected by a pipe 5.
［熱源装置（室外ユニット）１］
　熱源装置１には、圧縮機１０と、四方弁などの第１冷媒流路切替装置１１と、熱源側熱交換器１２と、アキュムレーター１９とが冷媒配管４で直列に接続されて搭載されている。
　また、熱源装置１には、冷媒用接続配管４ａ、４ｂおよび逆止弁１３ａ、１３ｂ、１３ｃ、１３ｄが設けられている。冷媒用接続配管４ａ、４ｂおよび逆止弁１３ａ、１３ｂ、１３ｃ、１３ｄを設けることで、室内機３の要求する運転にかかわらず、中継ユニット２に流入させる熱源側冷媒の流れを一定方向にすることができる。 [Heat source device (outdoor unit) 1]
In the heat source device 1, a compressor 10, a first refrigerant flow switching device 11 such as a four-way valve, a heat source side heat exchanger 12, and an accumulator 19 are connected and connected in series through a refrigerant pipe 4. Yes.
Further, the heat source device 1 is provided with refrigerant connection pipes 4a and 4b and check valves 13a, 13b, 13c and 13d. By providing the refrigerant connection pipes 4a and 4b and the check valves 13a, 13b, 13c, and 13d, the flow of the heat source side refrigerant flowing into the relay unit 2 is made to be a constant direction regardless of the operation requested by the indoor unit 3. be able to.
　圧縮機１０は、熱源側冷媒を吸入し、その熱源側冷媒を圧縮して高温・高圧の状態にして１次側回路２０に搬送するものであり、たとえば容量制御可能なインバータ圧縮機などで構成するとよい。
　第１冷媒流路切替装置１１は、暖房運転時における熱源側冷媒の流れと冷房運転時における熱源側冷媒の流れとを切り替えるものである。 The compressor 10 sucks the heat-source-side refrigerant, compresses the heat-source-side refrigerant, transfers the heat-source-side refrigerant to a primary side circuit 20 in a high temperature / high pressure state, and includes, for example, an inverter compressor capable of capacity control. Good.
The first refrigerant flow switching device 11 switches the flow of the heat source side refrigerant during the heating operation and the flow of the heat source side refrigerant during the cooling operation.
　熱源側熱交換器１２は、暖房運転時には蒸発器として機能し、冷房運転時には凝縮器（または放熱器）として機能し、図示省略のファンなどの送風機から供給される空気の流体と熱源側冷媒との間で熱交換を行い、その熱源側冷媒を蒸発ガス化または凝縮液化する。
　アキュムレーター１９は、圧縮機１０の吸入側に設けられており、暖房運転時と冷房運転時の違いによる余剰冷媒、または過渡的な運転の変化に対する余剰冷媒を蓄えるものである。 The heat source side heat exchanger 12 functions as an evaporator during heating operation, functions as a condenser (or radiator) during cooling operation, and includes a fluid of air supplied from a blower such as a fan (not shown), a heat source side refrigerant, and the like. The heat source side refrigerant is evaporated and condensed or liquefied.
The accumulator 19 is provided on the suction side of the compressor 10 and stores excess refrigerant due to a difference between the heating operation and the cooling operation, or excess refrigerant with respect to a transient change in operation.
　逆止弁１３ｃは、中継ユニット２と第１冷媒流路切替装置１１との間における冷媒配管４に設けられ、所定の方向（中継ユニット２から熱源装置１への方向）のみに熱源側冷媒の流れを許容する。逆止弁１３ａは、熱源側熱交換器１２と中継ユニット２との間における冷媒配管４に設けられ、所定の方向（熱源装置１から中継ユニット２への方向）のみに熱源側冷媒の流れを許容する。逆止弁１３ｄは、冷媒用接続配管４ａに設けられ、暖房運転時において圧縮機１０から吐出された熱源側冷媒を中継ユニット２に流通させる。逆止弁１３ｂは、冷媒用接続配管４ｂに設けられ、暖房運転時において中継ユニット２から戻ってきた熱源側冷媒を圧縮機１０の吸入側に流通させる。 The check valve 13c is provided in the refrigerant pipe 4 between the relay unit 2 and the first refrigerant flow switching device 11, and the heat source side refrigerant is only in a predetermined direction (direction from the relay unit 2 to the heat source device 1). Allow flow. The check valve 13a is provided in the refrigerant pipe 4 between the heat source side heat exchanger 12 and the relay unit 2, and allows the flow of the heat source side refrigerant only in a predetermined direction (direction from the heat source device 1 to the relay unit 2). Allow. The check valve 13d is provided in the refrigerant connection pipe 4a and causes the heat source side refrigerant discharged from the compressor 10 to flow through the relay unit 2 during the heating operation. The check valve 13 b is provided in the refrigerant connection pipe 4 b and distributes the heat source side refrigerant returned from the relay unit 2 during the heating operation to the suction side of the compressor 10.
　冷媒用接続配管４ａは、熱源装置１内において、第１冷媒流路切替装置１１と逆止弁１３ｃとの間における冷媒配管４と、逆止弁１３ａと中継ユニット２との間における冷媒配管４と、を接続する。冷媒用接続配管４ｂは、熱源装置１内において、逆止弁１３ｃと中継ユニット２との間における冷媒配管４と、熱源側熱交換器１２と逆止弁１３ａとの間における冷媒配管４と、を接続する。
　なお、図２では、冷媒用接続配管４ａ、４ｂおよび逆止弁１３ａ、１３ｂ、１３ｃ、１３ｄを設けた場合を例に示しているが、これに限定するものではなく、これらを必ずしも設ける必要はない。 In the heat source device 1, the refrigerant connection pipe 4 a includes a refrigerant pipe 4 between the first refrigerant flow switching device 11 and the check valve 13 c, and a refrigerant pipe 4 between the check valve 13 a and the relay unit 2. And connect. In the heat source device 1, the refrigerant connection pipe 4b includes a refrigerant pipe 4 between the check valve 13c and the relay unit 2, a refrigerant pipe 4 between the heat source side heat exchanger 12 and the check valve 13a, Connect.
In addition, in FIG. 2, the case where the refrigerant connection pipes 4a and 4b and the check valves 13a, 13b, 13c and 13d are provided is shown as an example. However, the present invention is not limited to this, and it is not always necessary to provide them. Absent.
［室内機（室内ユニット）３］
　室内機３には、それぞれ利用側熱交換器３５が搭載されている。この利用側熱交換器３５は、配管５によって中継ユニット２の熱媒体流路切替流量調整装置４０に接続する。この利用側熱交換器３５は、図示省略のファンなどの送風機から供給される空気と熱媒体との間で熱交換を行い、居住空間７に供給するための暖房用空気あるいは冷房用空気を生成する。 [Indoor unit (indoor unit) 3]
Each indoor unit 3 is equipped with a use side heat exchanger 35. The use side heat exchanger 35 is connected to the heat medium flow switching flow rate adjusting device 40 of the relay unit 2 by the pipe 5. The use side heat exchanger 35 exchanges heat between air supplied from a blower such as a fan (not shown) and a heat medium, and generates heating air or cooling air to be supplied to the living space 7. To do.
　図２では、４台の室内機３が中継ユニット２に接続されている場合を例に示し、紙面上側から室内機３ａ、室内機３ｂ、室内機３ｃ、室内機３ｄとして図示している。また、室内機３ａ、３ｂ、３ｃ、３ｄに応じて、利用側熱交換器３５も、紙面上側から利用側熱交換器３５ａ、利用側熱交換器３５ｂ、利用側熱交換器３５ｃ、利用側熱交換器３５ｄとして図示している。なお、図１と同様に、室内機３の接続台数を図２に示す４台に限定するものではない。 FIG. 2 shows an example in which four indoor units 3 are connected to the relay unit 2, and are illustrated as an indoor unit 3a, an indoor unit 3b, an indoor unit 3c, and an indoor unit 3d from the upper side of the drawing. Further, in accordance with the indoor units 3a, 3b, 3c, and 3d, the use side heat exchanger 35 is also used from the upper side of the page with the use side heat exchanger 35a, the use side heat exchanger 35b, the use side heat exchanger 35c, and the use side heat. It is illustrated as an exchanger 35d. As in FIG. 1, the number of connected indoor units 3 is not limited to the four shown in FIG.
［中継ユニット２］
　中継ユニット２には、２つの熱媒体間熱交換器２５と、２つの絞り装置２６と、２つの開閉装置（開閉装置２７、開閉装置２９）と、２つの第２冷媒流路切替装置２８と、２つの熱媒体搬送装置であるポンプ３１と、４つの熱媒体流路切替流量調整装置４０と、２つの空気除去弁４１、４２と、が搭載されている。 [Relay unit 2]
The relay unit 2 includes two heat exchangers for heat medium 25, two expansion devices 26, two switch devices (switch devices 27, switch devices 29), and two second refrigerant flow switching devices 28. A pump 31 that is two heat medium transfer devices, four heat medium flow switching flow rate adjustment devices 40, and two air removal valves 41 and 42 are mounted.
　２つの熱媒体間熱交換器２５（熱媒体間熱交換器２５ａ、２５ｂ）は、暖房運転をしている室内機３に対して温熱を供給する際には凝縮器（放熱器）として、冷房運転をしている室内機３に対して冷熱を供給する際には蒸発器として機能し、熱源側冷媒と熱媒体とで熱交換を行い、熱源装置１で生成され熱源側冷媒に貯えられた冷熱または温熱を熱媒体に伝達する。
　熱媒体間熱交換器２５ａは、１次側回路２０における絞り装置２６ａと第２冷媒流路切替装置２８ａとの間に設けられ、冷房暖房混在運転モード時において熱媒体の冷却に供する。また、熱媒体間熱交換器２５ｂは、１次側回路２０における絞り装置２６ｂと第２冷媒流路切替装置２８ｂとの間に設けられ、冷房暖房混在運転モード時において熱媒体の加熱に供する。 The two heat exchangers for heat medium 25 (heat exchangers for heat medium 25a, 25b) serve as condensers (heat radiators) for cooling when supplying heat to the indoor unit 3 that is performing the heating operation. When supplying cold heat to the indoor unit 3 in operation, it functions as an evaporator, performs heat exchange between the heat source side refrigerant and the heat medium, and is generated by the heat source device 1 and stored in the heat source side refrigerant. Transfers cold or warm heat to the heat medium.
The heat exchanger related to heat medium 25a is provided between the expansion device 26a and the second refrigerant flow switching device 28a in the primary circuit 20, and serves to cool the heat medium in the cooling / heating mixed operation mode. Further, the heat exchanger related to heat medium 25b is provided between the expansion device 26b and the second refrigerant flow switching device 28b in the primary circuit 20, and serves to heat the heat medium in the cooling / heating mixed operation mode.
　２つの絞り装置２６（絞り装置２６ａ、２６ｂ）は、減圧弁や膨張弁としての機能を有し、熱源側冷媒を減圧して膨張させる。
　絞り装置２６ａは、冷房運転時の熱源側冷媒の流れにおいて熱媒体間熱交換器２５ａの上流側に設けられている。絞り装置２６ｂは、冷房運転時の熱源側冷媒の流れにおいて熱媒体間熱交換器２５ｂの上流側に設けられている。２つの絞り装置２６は、開度が可変に制御可能なもの、たとえば電子式膨張弁などで構成するとよい。 The two expansion devices 26 (the expansion devices 26a and 26b) have functions as pressure reducing valves and expansion valves, and expand the heat source side refrigerant by reducing the pressure.
The expansion device 26a is provided on the upstream side of the heat exchanger related to heat medium 25a in the flow of the heat source side refrigerant during the cooling operation. The expansion device 26b is provided on the upstream side of the heat exchanger related to heat medium 25b in the flow of the heat source side refrigerant during the cooling operation. The two throttling devices 26 may be configured by a device whose opening degree can be variably controlled, for example, an electronic expansion valve.
　２つの開閉装置（開閉装置２７、２９）は、通電により開閉動作が可能な電磁弁などで構成され、冷媒配管４を開閉するものである。つまり、２つの開閉装置２７、２９は、運転モードに応じて開閉が制御され、熱源側冷媒の流路を切り替えている。
　開閉装置２７は、熱源側冷媒の入口側における冷媒配管４に設けられている。開閉装置２９は、熱源側冷媒の入口側の冷媒配管４と出口側の冷媒配管４とを接続した配管に設けられている。
　なお、開閉装置２７、２９は、冷媒流路の切り替えが可能なものであればよく、たとえば電子式膨張弁などの開度を可変に制御できるものを用いてもよい。 The two opening / closing devices (opening / closing devices 27, 29) are configured by electromagnetic valves or the like that can be opened / closed by energization, and open / close the refrigerant pipe 4. That is, the opening and closing of the two opening / closing devices 27 and 29 is controlled according to the operation mode, and the flow path of the heat source side refrigerant is switched.
The opening / closing device 27 is provided in the refrigerant pipe 4 on the inlet side of the heat source side refrigerant. The opening / closing device 29 is provided in a pipe connecting the refrigerant pipe 4 on the inlet side of the heat source side refrigerant and the refrigerant pipe 4 on the outlet side.
The opening / closing devices 27 and 29 may be any devices that can switch the refrigerant flow path. For example, an electronic expansion valve or the like that can variably control the opening degree may be used.
　２つの第２冷媒流路切替装置２８（第２冷媒流路切替装置２８ａ、２８ｂ）は、たとえば四方弁などで構成され、運転モードに応じて熱媒体間熱交換器２５が凝縮器または蒸発器として作用するよう、熱源側冷媒の流れを切り替える。
　第２冷媒流路切替装置２８ａは、冷房運転時の熱源側冷媒の流れにおいて熱媒体間熱交換器２５ａの下流側に設けられている。第２冷媒流路切替装置２８ｂは、冷房運転モード時の熱源側冷媒の流れにおいて熱媒体間熱交換器２５ｂの下流側に設けられている。 The two second refrigerant flow switching devices 28 (second refrigerant flow switching devices 28a and 28b) are constituted by, for example, a four-way valve or the like, and the heat exchanger related to heat medium 25 is a condenser or an evaporator depending on the operation mode. The flow of the heat source side refrigerant is switched so as to act as
The second refrigerant flow switching device 28a is provided on the downstream side of the heat exchanger related to heat medium 25a in the flow of the heat source side refrigerant during the cooling operation. The second refrigerant flow switching device 28b is provided on the downstream side of the heat exchanger related to heat medium 25b in the flow of the heat source side refrigerant in the cooling operation mode.
　２つのポンプ３１（ポンプ３１ａ、３１ｂ）は、配管５を導通する熱媒体を２次側回路３０に循環させる。
　ポンプ３１ａは、熱媒体間熱交換器２５ａと熱媒体流路切替流量調整装置４０との間における配管５に設けられている。ポンプ３１ｂは、熱媒体間熱交換器２５ｂと熱媒体流路切替流量調整装置４０との間における配管５に設けられている。
　２つのポンプ３１は、たとえば容量制御可能なポンプなどで構成し、室内機３における負荷の大きさによってその流量を調整できるようにしておくとよい。 The two pumps 31 (pumps 31 a and 31 b) circulate the heat medium that conducts the pipe 5 to the secondary circuit 30.
The pump 31 a is provided in the pipe 5 between the heat exchanger related to heat medium 25 a and the heat medium flow switching flow control device 40. The pump 31 b is provided in the pipe 5 between the heat exchanger related to heat medium 25 b and the heat medium flow switching flow control device 40.
The two pumps 31 may be configured by, for example, capacity-controllable pumps, and the flow rate thereof may be adjusted according to the load in the indoor unit 3.
　２つの空気除去弁４１、４２は施工時に２次側回路３０の空気を抜くために使用される。なお、空気除去弁の接続数を図２に示す２個に限定するものではない。 The two air removal valves 41 and 42 are used to evacuate the secondary circuit 30 during construction. The number of connected air removal valves is not limited to two as shown in FIG.
　４つの熱媒体流路切替流量調整装置４０（熱媒体流路切替流量調整装置４０ａ～４０ｄ）は、一つの駆動装置と弁体などで構成され、熱媒体の流路を熱媒体間熱交換器２５ａと熱媒体間熱交換器２５ｂとの間で切り替えると共に各分岐へ対する熱媒体の流量を調整する。熱媒体流路切替流量調整装置４０は、室内機３の設置台数に応じた個数（ここでは４つ）が設けられるようになっており、それぞれが相互に連結することも可能とした構造である。さらに、この熱媒体流路切替流量調整装置４０は、その内部にて、一方が熱媒体間熱交換器２５ａに、他方が熱媒体間熱交換器２５ｂに、それぞれ接続されており、利用側熱交換器３５にも接続されている。
　なお、室内機３に対応させて、紙面上側から熱媒体流路切替流量調整装置４０ａ、熱媒体流路切替流量調整装置４０ｂ、熱媒体流路切替流量調整装置４０ｃ、熱媒体流路切替流量調整装置４０ｄとして図示している。また、熱媒体流路の切替には、一方から他方への完全な切替だけでなく、一方から他方への部分的な切替も含んでいるものとする。 The four heat medium flow path switching flow rate adjusting devices 40 (heat medium flow path switching flow rate adjusting devices 40a to 40d) are composed of one drive device and a valve body, and the heat medium flow path is used as a heat exchanger between heat mediums. It switches between 25a and the heat exchanger between heat media 25b, and adjusts the flow rate of the heat medium to each branch. The number of heat medium flow switching flow rate adjusting devices 40 according to the number of indoor units 3 installed (here, four) is provided, and each of them can be connected to each other. . Further, in the heat medium flow switching flow rate adjusting device 40, one of them is connected to the heat exchanger related to heat medium 25a and the other is connected to the heat exchanger related to heat medium 25b. It is also connected to the exchanger 35.
In correspondence with the indoor unit 3, from the upper side of the page, the heating medium channel switching flow rate adjustment device 40a, the heating medium channel switching flow rate adjustment device 40b, the heating medium channel switching flow rate adjustment device 40c, and the heating medium channel switching flow rate adjustment are adjusted. Illustrated as device 40d. The switching of the heat medium flow path includes not only complete switching from one to the other but also partial switching from one to the other.
　また、熱媒体流路切替流量調整装置４０は、流量調整も可能であり、開口面積を調整することで、配管５に流れる熱媒体の流量を制御する。熱媒体流路切替流量調整装置４０は、一方が利用側熱交換器３５に、他方が熱媒体間熱交換器２５に、それぞれ接続されている。すなわち、熱媒体流路切替流量調整装置４０は、室内機３へ流入する熱媒体の温度および流出する熱媒体の温度により室内機３に流入する熱媒体の量を調整し、室内負荷に応じた最適な熱媒体量を室内機３に提供可能とする。 Further, the heat medium flow switching flow rate adjusting device 40 can also adjust the flow rate, and controls the flow rate of the heat medium flowing through the pipe 5 by adjusting the opening area. One of the heat medium flow switching flow rate adjusting devices 40 is connected to the use side heat exchanger 35 and the other is connected to the heat exchanger related to heat medium 25. That is, the heat medium flow switching flow rate adjusting device 40 adjusts the amount of the heat medium flowing into the indoor unit 3 according to the temperature of the heat medium flowing into the indoor unit 3 and the temperature of the heat medium flowing out, according to the indoor load. An optimal amount of heat medium can be provided to the indoor unit 3.
　なお、室内機３において、停止やサーモＯＦＦなどの負荷を必要としていないとき、または、メンテナンスなどにより、熱媒体の流路を遮断したい場合、熱媒体流路切替流量調整装置４０を全閉にすることにより、室内機３への熱媒体供給を止めることができる。 When the indoor unit 3 does not require a load such as stop or thermo OFF, or when it is desired to shut off the heat medium flow path due to maintenance or the like, the heat medium flow path switching flow rate adjustment device 40 is fully closed. As a result, the supply of the heat medium to the indoor unit 3 can be stopped.
　また、中継ユニット２には、熱媒体間熱交換器２５の出口側における熱媒体の温度を検出するための温度センサー５５（温度センサー５５ａ、５５ｂ）が設けられている。温度センサー５５で検出された情報（温度情報）は、空気調和装置１００の動作を統括制御する制御装置５０に送られ、圧縮機１０の駆動周波数、図示省略の送風機の回転数、第１冷媒流路切替装置１１の切り替え、ポンプ３１の駆動周波数、第２冷媒流路切替装置２８の切り替え、熱媒体の流路の切り替え、室内機３の熱媒体流量の調整などの制御に利用されることになる。
　なお、制御装置５０が中継ユニット２内に搭載されている状態を例に示しているが、これに限定するものではなく、熱源装置１または室内機３、あるいは、各ユニットに通信可能に搭載するようにしてもよい。 In addition, the relay unit 2 is provided with a temperature sensor 55 ( temperature sensors 55a and 55b) for detecting the temperature of the heat medium on the outlet side of the heat exchanger related to heat medium 25. Information (temperature information) detected by the temperature sensor 55 is sent to a control device 50 that performs overall control of the operation of the air-conditioning apparatus 100, and the driving frequency of the compressor 10, the rotational speed of the blower (not shown), the first refrigerant flow It is used for control such as switching of the path switching device 11, driving frequency of the pump 31, switching of the second refrigerant flow switching device 28, switching of the flow path of the heat medium, adjustment of the heat medium flow rate of the indoor unit 3. Become.
In addition, although the state in which the control device 50 is mounted in the relay unit 2 is shown as an example, the present invention is not limited to this, and the control device 50 is mounted to be communicable with the heat source device 1 or the indoor unit 3 or each unit. You may do it.
　制御装置５０は、マイコンなどで構成され、各種検出手段での検出情報およびリモコンからの指示に基づいて、圧縮機１０の駆動周波数、送風機の回転数（ＯＮ／ＯＦＦ含む）、第１冷媒流路切替装置１１の切り替え、ポンプ３１の駆動、絞り装置２６の開度、開閉装置２７、２９の開閉、第２冷媒流路切替装置２８の切り替え、熱媒体流路切替流量調整装置４０の切り替えおよび駆動など、各アクチュエーター（ポンプ３１、絞り装置２６）を制御するようになっている。
　本実施の形態では、制御装置５０は、後述する空気除去運転モードにて、ポンプ３１ａ、３１ｂの回転数Ｎを常時取得し、空気を吸入したときの回転数Ｎｂが検知されるとタイマを起動して次の回転数Ｎｂまでの回転数Ｎｂ間の発生間隔を検知する。 The control device 50 is constituted by a microcomputer or the like, and based on detection information from various detection means and instructions from a remote controller, the driving frequency of the compressor 10, the rotational speed of the blower (including ON / OFF), the first refrigerant flow path. Switching of the switching device 11, driving of the pump 31, opening of the expansion device 26, opening and closing of the switching devices 27 and 29, switching of the second refrigerant flow switching device 28, switching and driving of the heat medium flow switching flow rate adjusting device 40 Etc., each actuator (pump 31, throttle device 26) is controlled.
In the present embodiment, the control device 50 constantly acquires the rotation speed N of the pumps 31a and 31b in the air removal operation mode described later, and starts a timer when the rotation speed Nb when air is sucked is detected. Then, the generation interval between the rotation speeds Nb up to the next rotation speed Nb is detected.
　熱媒体を導通する配管５は、熱媒体間熱交換器２５ａに接続されるものと、熱媒体間熱交換器２５ｂに接続されるものと、で構成されている。配管５は、中継ユニット２に接続される室内機３の台数に応じて分岐（ここでは、各４分岐）されている。そして、配管５は、熱媒体流路切替流量調整装置４０で接続されている。熱媒体流路切替流量調整装置４０を制御することで、熱媒体間熱交換器２５ａからの熱媒体を利用側熱交換器３５に流入させるか、熱媒体間熱交換器２５ｂからの熱媒体を利用側熱交換器３５に流入させるかが決定される。 The pipe 5 that conducts the heat medium is composed of one that is connected to the heat exchanger related to heat medium 25a and one that is connected to the heat exchanger related to heat medium 25b. The pipe 5 is branched (here, four branches each) according to the number of indoor units 3 connected to the relay unit 2. The pipe 5 is connected by a heat medium flow switching flow rate adjusting device 40. By controlling the heat medium flow switching flow rate adjusting device 40, the heat medium from the heat exchanger related to heat medium 25a flows into the use side heat exchanger 35, or the heat medium from the heat exchanger related to heat medium 25b is used as the heat medium. Whether to flow into the use side heat exchanger 35 is determined.
　そして、空気調和装置１００では、圧縮機１０、第１冷媒流路切替装置１１、熱源側熱交換器１２、開閉装置２７、開閉装置２９、第２冷媒流路切替装置２８、熱媒体間熱交換器２５の冷媒流路、絞り装置２６、およびアキュムレーター１９を、冷媒配管４で接続して１次側回路２０を構成している。
　また、熱媒体間熱交換器２５の熱媒体流路、ポンプ３１、熱媒体流路切替流量調整装置４０、利用側熱交換器３５を、配管５で接続して２次側回路３０を構成している。
　さらに、熱媒体間熱交換器２５のそれぞれに複数台の利用側熱交換器３５が並列に接続され、２次側回路３０を複数系統としている。 In the air conditioner 100, the compressor 10, the first refrigerant flow switching device 11, the heat source side heat exchanger 12, the switching device 27, the switching device 29, the second refrigerant flow switching device 28, and heat exchange between heat media. The refrigerant flow path of the container 25, the expansion device 26, and the accumulator 19 are connected by the refrigerant pipe 4 to constitute the primary side circuit 20.
Further, the secondary medium circuit 30 is configured by connecting the heat medium flow path of the heat exchanger 25 between the heat medium 25, the pump 31, the heat medium flow path switching flow rate adjusting device 40, and the use side heat exchanger 35 with the pipe 5. ing.
Further, a plurality of use side heat exchangers 35 are connected in parallel to each of the heat exchangers 25 between heat mediums, and the secondary side circuit 30 has a plurality of systems.
　よって、空気調和装置１００では、熱源装置１と中継ユニット２とが、中継ユニット２に設けられている熱媒体間熱交換器２５ａ、２５ｂを介して接続され、中継ユニット２と室内機３とが、熱媒体間熱交換器２５ａ、２５ｂを介して接続されている。すなわち、空気調和装置１００では、熱媒体間熱交換器２５ａ、２５ｂで１次側回路２０を循環する熱源側冷媒と２次側回路３０を循環する熱媒体とが熱交換する。このような構成を用いることで、空気調和装置１００は、室内負荷に応じた最適な冷房運転または暖房運転を実現することができる。 Therefore, in the air conditioner 100, the heat source device 1 and the relay unit 2 are connected via the heat exchangers 25a and 25b provided in the relay unit 2, and the relay unit 2 and the indoor unit 3 are connected. Are connected via heat exchangers 25a and 25b. That is, in the air conditioner 100, the heat source side refrigerant circulating in the primary circuit 20 and the heat medium circulating in the secondary circuit 30 exchange heat in the intermediate heat exchangers 25a and 25b. By using such a configuration, the air conditioner 100 can realize an optimal cooling operation or heating operation according to the indoor load.
　次に、各運転モードによる１次側回路２０および２次側回路３０の流れについて説明する。 Next, the flow of the primary side circuit 20 and the secondary side circuit 30 in each operation mode will be described.
［混在運転モード］
　図３は、本発明の実施の形態１に係る空気調和装置１００の混在運転モード時における冷媒の流れを示す冷媒回路図である。図３では、利用側熱交換器３５のうちのいずれかで温熱負荷が発生し、利用側熱交換器３５のうちの残りで冷熱負荷が発生している場合である混在運転のうち、暖房主体運転モードについて説明する。
　なお、図３では、太線で表された配管が熱源側冷媒の循環する配管を示している。また、図３では、流れ方向を実線矢印で示している。 [Mixed operation mode]
FIG. 3 is a refrigerant circuit diagram illustrating a refrigerant flow in the mixed operation mode of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. In FIG. 3, in the mixed operation in which the thermal load is generated in any of the use side heat exchangers 35 and the cold load is generated in the remaining of the use side heat exchangers 35, the heating main The operation mode will be described.
In addition, in FIG. 3, the pipe | tube represented by the thick line has shown the piping through which the heat source side refrigerant | coolant circulates. Moreover, in FIG. 3, the flow direction is shown by the solid line arrow.
　図３に示す暖房主体運転モードの場合、熱源装置１では、第１冷媒流路切替装置１１を、圧縮機１０から吐出された熱源側冷媒を、熱源側熱交換器１２を経由させずに中継ユニット２へ流入させるように切り替える。
　中継ユニット２では、ポンプ３１ａ、３１ｂを駆動させ、熱媒体流路切替流量調整装置４０ａ～４０ｄを開放し、熱媒体間熱交換器２５ａと冷熱負荷が発生している利用側熱交換器３５との間を、熱媒体間熱交換器２５ｂと温熱負荷が発生している利用側熱交換器３５との間を、それぞれ熱媒体が循環するようにしている。また、第２冷媒流路切替装置２８ａは冷房側、第２冷媒流路切替装置２８ｂは暖房側に切り替えられており、絞り装置２６ａは全開、開閉装置２７は閉、開閉装置２９は閉となっている。 In the heating main operation mode shown in FIG. 3, in the heat source device 1, the first refrigerant flow switching device 11 relays the heat source side refrigerant discharged from the compressor 10 without passing through the heat source side heat exchanger 12. Switch to flow into unit 2.
In the relay unit 2, the pumps 31a and 31b are driven, the heat medium flow switching flow rate adjusting devices 40a to 40d are opened, the heat exchanger 25a between the heat medium and the use side heat exchanger 35 generating the cooling load, The heat medium is circulated between the heat exchanger 25b between the heat medium and the use side heat exchanger 35 where the heat load is generated. The second refrigerant flow switching device 28a is switched to the cooling side, the second refrigerant flow switching device 28b is switched to the heating side, the expansion device 26a is fully opened, the opening / closing device 27 is closed, and the opening / closing device 29 is closed. ing.
　始めに、１次側回路２０における熱源側冷媒の流れについて説明する。
　低温・低圧の冷媒が圧縮機１０によって圧縮され、高温・高圧のガス冷媒となって吐出される。圧縮機１０から吐出された高温・高圧のガス冷媒は、第１冷媒流路切替装置１１を通り、冷媒用接続配管４ａを導通し、逆止弁１３ｄを通過し、熱源装置１から流出する。熱源装置１から流出した高温・高圧のガス冷媒は、冷媒配管４を通って中継ユニット２に流入する。中継ユニット２に流入した高温・高圧のガス冷媒は、第２冷媒流路切替装置２８ｂを通って凝縮器として作用する熱媒体間熱交換器２５ｂに流入する。 First, the flow of the heat source side refrigerant in the primary side circuit 20 will be described.
The low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, conducts the refrigerant connection pipe 4 a, passes through the check valve 13 d, and flows out of the heat source device 1. The high-temperature and high-pressure gas refrigerant that has flowed out of the heat source device 1 flows into the relay unit 2 through the refrigerant pipe 4. The high-temperature and high-pressure gas refrigerant that has flowed into the relay unit 2 flows through the second refrigerant flow switching device 28b into the heat exchanger related to heat medium 25b that acts as a condenser.
　熱媒体間熱交換器２５ｂに流入したガス冷媒は、２次側回路３０を循環する熱媒体に放熱しながら凝縮液化し、液冷媒となる。熱媒体間熱交換器２５ｂから流出した液冷媒は、絞り装置２６ｂで膨張させられて低圧二相冷媒となる。この低圧二相冷媒は、絞り装置２６ａを介して蒸発器として作用する熱媒体間熱交換器２５ａに流入する。熱媒体間熱交換器２５ａに流入した低圧二相冷媒は、２次側回路３０を循環する熱媒体から吸熱することで蒸発し、熱媒体を冷却する。この低圧二相冷媒は、熱媒体間熱交換器２５ａから流出し、第２冷媒流路切替装置２８ａを介して中継ユニット２から流出し、冷媒配管４を通って再び熱源装置１へ流入する。 The gas refrigerant that has flowed into the heat exchanger related to heat medium 25b is condensed and liquefied while dissipating heat to the heat medium circulating in the secondary circuit 30, and becomes liquid refrigerant. The liquid refrigerant flowing out of the heat exchanger related to heat medium 25b is expanded by the expansion device 26b and becomes a low-pressure two-phase refrigerant. This low-pressure two-phase refrigerant flows into the heat exchanger related to heat medium 25a acting as an evaporator via the expansion device 26a. The low-pressure two-phase refrigerant flowing into the heat exchanger related to heat medium 25a evaporates by absorbing heat from the heat medium circulating in the secondary circuit 30 and cools the heat medium. The low-pressure two-phase refrigerant flows out of the heat exchanger related to heat medium 25a, flows out of the relay unit 2 through the second refrigerant flow switching device 28a, and flows into the heat source device 1 again through the refrigerant pipe 4.
　熱源装置１に流入した低温・低圧の二相冷媒は、逆止弁１３ｂを通って、蒸発器として作用する熱源側熱交換器１２に流入する。そして、熱源側熱交換器１２に流入した冷媒は、熱源側熱交換器１２で外気から吸熱して、低温・低圧のガス冷媒となる。熱源側熱交換器１２から流出した低温・低圧のガス冷媒は、第１冷媒流路切替装置１１およびアキュムレーター１９を介して圧縮機１０へ再度吸入される。 The low-temperature and low-pressure two-phase refrigerant that has flowed into the heat source device 1 flows into the heat source side heat exchanger 12 that acts as an evaporator through the check valve 13b. And the refrigerant | coolant which flowed into the heat source side heat exchanger 12 absorbs heat from external air in the heat source side heat exchanger 12, and turns into a low temperature and low pressure gas refrigerant. The low-temperature and low-pressure gas refrigerant flowing out from the heat source side heat exchanger 12 is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
　なお、絞り装置２６ｂは、熱媒体間熱交換器２５ｂの出口冷媒のサブクール（過冷却度）が目標値になるように開度が制御される。なお、絞り装置２６ｂを全開とし、絞り装置２６ａで、サブクールを制御するようにしてもよい。 The opening degree of the expansion device 26b is controlled so that the subcooling (supercooling degree) of the outlet refrigerant of the heat exchanger related to heat medium 25b becomes a target value. Note that the expansion device 26b may be fully opened, and the subcool may be controlled by the expansion device 26a.
　次に、２次側回路３０における熱媒体の流れについて説明する。
　暖房主体運転モードでは、熱媒体間熱交換器２５ｂで熱源側冷媒の温熱が熱媒体に伝えられ、暖められた熱媒体がポンプ３１ｂによって配管５内を流動させられる。ポンプ３１ｂで加圧されて流出した暖められた熱媒体は、温熱負荷が発生している利用側熱交換器３５に熱媒体流路切替流量調整装置４０を介して流入する。
　また、暖房主体運転モードでは、熱媒体間熱交換器２５ａで熱源側冷媒の冷熱が熱媒体に伝えられ、冷やされた熱媒体がポンプ３１ａによって配管５内を流動させられる。ポンプ３１ａで加圧されて流出した冷やされた熱媒体は、冷熱負荷が発生している利用側熱交換器３５に熱媒体流路切替流量調整装置４０を介して流入する。 Next, the flow of the heat medium in the secondary side circuit 30 will be described.
In the heating main operation mode, the heat of the heat source side refrigerant is transmitted to the heat medium in the heat exchanger related to heat medium 25b, and the heated heat medium is caused to flow in the pipe 5 by the pump 31b. The heated heat medium that has been pressurized and discharged by the pump 31b flows into the use-side heat exchanger 35 where the thermal load is generated via the heat medium flow switching flow rate adjusting device 40.
Further, in the heating main operation mode, the cold heat of the heat source side refrigerant is transmitted to the heat medium in the intermediate heat exchanger 25a, and the cooled heat medium is caused to flow in the pipe 5 by the pump 31a. The cooled heat medium that has been pressurized and flowed out by the pump 31a flows into the use-side heat exchanger 35 where the cold load is generated via the heat medium flow switching flow rate adjusting device 40.
　このとき、熱媒体流路切替流量調整装置４０は、接続されている室内機３が暖房運転モードであるときは、熱媒体間熱交換器２５ｂおよびポンプ３１ｂが接続されている方向に切り替えられ、接続されている室内機３が冷房運転モードであるときは、熱媒体間熱交換器２５ａおよびポンプ３１ａが接続されている方向に切り替えられる。すなわち、熱媒体流路切替流量調整装置４０によって、室内機３へ供給する熱媒体を暖房用または冷房用に切り替えることを可能としている。 At this time, when the connected indoor unit 3 is in the heating operation mode, the heat medium flow switching flow rate adjustment device 40 is switched to the direction in which the heat exchanger related to heat medium 25b and the pump 31b are connected, When the connected indoor unit 3 is in the cooling operation mode, the indoor unit 3 is switched to the direction in which the heat exchanger related to heat medium 25a and the pump 31a are connected. That is, the heat medium flow switching device 40 can switch the heat medium supplied to the indoor unit 3 for heating or cooling.
　利用側熱交換器３５では、熱媒体が室内空気から吸熱することによる居住空間７の冷房運転、または、熱媒体が室内空気に放熱することによる居住空間７の暖房運転を行う。このとき、熱媒体流路切替流量調整装置４０の作用によって熱媒体の流量が室内にて必要とされる空調負荷を賄うのに必要な流量に制御されて利用側熱交換器３５に流入する。 In the use side heat exchanger 35, the cooling operation of the living space 7 by the heat medium absorbing heat from the indoor air or the heating operation of the living space 7 by the heat medium radiating heat to the indoor air is performed. At this time, the flow rate of the heat medium is controlled to a flow rate necessary to cover the air conditioning load required indoors by the action of the heat medium flow switching flow rate adjusting device 40 and flows into the use side heat exchanger 35.
　冷房運転に利用され、利用側熱交換器３５を通過し若干温度が上昇した熱媒体は、熱媒体流路切替流量調整装置４０を通って、熱媒体間熱交換器２５ａに流入し、再びポンプ３１ａへ吸い込まれる。暖房運転に利用され、利用側熱交換器３５を通過し若干温度が低下した熱媒体は、熱媒体流路切替流量調整装置４０を通って、熱媒体間熱交換器２５ｂへ流入し、再びポンプ３１ｂへ吸い込まれる。
　このとき、熱媒体流路切替流量調整装置４０は、接続されている室内機３が暖房運転モードであるときは、熱媒体間熱交換器２５ｂおよびポンプ３１ｂが接続されている方向に切り替えられ、接続されている室内機３が冷房運転モードであるときは、熱媒体間熱交換器２５ａおよびポンプ３１ａが接続されている方向に切り替えられる。 The heat medium that has been used for the cooling operation and has passed through the use-side heat exchanger 35 and whose temperature has risen slightly passes through the heat medium flow switching flow rate adjusting device 40 and flows into the heat exchanger related to heat medium 25a, and is again pumped. It is sucked into 31a. The heat medium that has been used for the heating operation and has passed through the use-side heat exchanger 35 and has slightly decreased in temperature passes through the heat medium flow switching flow adjustment device 40 and flows into the heat exchanger related to heat medium 25b, and is again pumped. It is sucked into 31b.
At this time, when the connected indoor unit 3 is in the heating operation mode, the heat medium flow switching flow rate adjustment device 40 is switched to the direction in which the heat exchanger related to heat medium 25b and the pump 31b are connected, When the connected indoor unit 3 is in the cooling operation mode, the indoor unit 3 is switched to the direction in which the heat exchanger related to heat medium 25a and the pump 31a are connected.
　この間、暖かい熱媒体と冷たい熱媒体とは、熱媒体流路切替流量調整装置４０の作用により、混合することなく、それぞれ温熱負荷、冷熱負荷がある利用側熱交換器３５へ導入される。これにより、暖房運転モードで利用された熱媒体を暖房用途として冷媒から熱を与えている熱媒体間熱交換器２５ｂへと流入させ、冷房運転モードで利用された熱媒体を冷房用途として冷媒が熱を受け取っている熱媒体間熱交換器２５ａへと流入させ、再度それぞれが冷媒と熱交換を行った後、ポンプ３１ａ、３１ｂへと搬送される。 During this time, the warm heat medium and the cold heat medium are introduced into the use-side heat exchanger 35 having a heat load and a heat load, respectively, without being mixed by the action of the heat medium flow switching flow control device 40. As a result, the heat medium used in the heating operation mode is caused to flow into the heat exchanger related to heat medium 25b, which gives heat from the refrigerant for heating use, and the heat medium used in the cooling operation mode is used for cooling use. The heat is introduced into the heat exchanger related to heat medium 25a that receives the heat, and each heat exchanges again with the refrigerant, and then is transferred to the pumps 31a and 31b.
　なお、居住空間７にて必要とされる空調負荷は、暖房側においては温度センサー５５ｂで検出された温度と利用側熱交換器３５から流出した熱媒体の温度との差を、冷房側においては利用側熱交換器３５から流出した熱媒体の温度と温度センサー５５ａで検出された温度との差を目標値として保つように制御することにより、賄うことができる。 The air conditioning load required in the living space 7 is the difference between the temperature detected by the temperature sensor 55b on the heating side and the temperature of the heat medium flowing out from the use side heat exchanger 35 on the cooling side. This can be covered by controlling the difference between the temperature of the heat medium flowing out from the use side heat exchanger 35 and the temperature detected by the temperature sensor 55a as a target value.
［全暖房運転モード］
　図４は、本発明の実施の形態１に係る空気調和装置１００の全暖房運転モード時における冷媒の流れを示す冷媒回路図である。図４では、利用側熱交換器３５ａ～３５ｄの全部で温熱負荷が発生している場合を例に全暖房運転モードについて説明する。なお、図４では、流れ方向を実線矢印で示している。 [Heating operation mode]
FIG. 4 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 according to Embodiment 1 of the present invention is in the heating only operation mode. In FIG. 4, the heating only operation mode will be described by taking as an example a case where a heating load is generated in all of the use side heat exchangers 35a to 35d. In FIG. 4, the flow direction is indicated by a solid arrow.
　図４に示す全暖房運転モードの場合には、熱源装置１では、第１冷媒流路切替装置１１を、圧縮機１０から吐出された熱源側冷媒が熱源側熱交換器１２を経由せずに中継ユニット２へ流入するように切り替える。
　中継ユニット２では、ポンプ３１ａ、３１ｂを駆動させ、熱媒体流路切替流量調整装置４０ａ～４０ｄを開放し、熱媒体間熱交換器２５ａ、２５ｂのそれぞれと利用側熱交換器３５ａ～３５ｄとの間を熱媒体が循環するようにしている。また、第２冷媒流路切替装置２８ａおよび第２冷媒流路切替装置２８ｂは暖房側に切り替えられ、開閉装置２７は閉、開閉装置２９は開となっている。 In the heating only operation mode shown in FIG. 4, in the heat source device 1, the heat source side refrigerant discharged from the compressor 10 does not pass through the heat source side heat exchanger 12 in the first refrigerant flow switching device 11. It switches so that it may flow into relay unit 2.
In the relay unit 2, the pumps 31a and 31b are driven, the heat medium flow switching flow rate adjusting devices 40a to 40d are opened, and the heat exchangers 25a and 25b between the heat medium and the use side heat exchangers 35a to 35d are connected. The heat medium circulates between them. The second refrigerant flow switching device 28a and the second refrigerant flow switching device 28b are switched to the heating side, the opening / closing device 27 is closed, and the opening / closing device 29 is open.
　始めに、１次側回路２０における熱源側冷媒の流れについて説明する。
　低温・低圧の冷媒が圧縮機１０によって圧縮され、高温・高圧のガス冷媒となって吐出される。圧縮機１０から吐出された高温・高圧のガス冷媒は、第１冷媒流路切替装置１１を通り、冷媒用接続配管４ａを導通し、逆止弁１３ｄを通過し、熱源装置１から流出する。熱源装置１から流出した高温・高圧のガス冷媒は、冷媒配管４を通って中継ユニット２に流入する。中継ユニット２に流入した高温・高圧のガス冷媒は、分岐されて第２冷媒流路切替装置２８ａ、２８ｂのそれぞれを通って、熱媒体間熱交換器２５ａ、２５ｂのそれぞれに流入する。 First, the flow of the heat source side refrigerant in the primary side circuit 20 will be described.
The low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, conducts the refrigerant connection pipe 4 a, passes through the check valve 13 d, and flows out of the heat source device 1. The high-temperature and high-pressure gas refrigerant that has flowed out of the heat source device 1 flows into the relay unit 2 through the refrigerant pipe 4. The high-temperature and high-pressure gas refrigerant that has flowed into the relay unit 2 is branched, passes through the second refrigerant flow switching devices 28a and 28b, and flows into the heat exchangers 25a and 25b, respectively.
　熱媒体間熱交換器２５ａ、２５ｂに流入した高温・高圧のガス冷媒は、２次側回路３０を通る熱媒体に放熱しながら凝縮液化し、高圧の液冷媒となる。熱媒体間熱交換器２５ａ、２５ｂから流出した液冷媒は、絞り装置２６ａ、２６ｂで膨張させられ、低温・低圧の二相冷媒となる。これらの二相冷媒は、合流した後、開閉装置２９を通って、中継ユニット２から流出し、冷媒配管４を通って再び熱源装置１に流入する。熱源装置１に流入した冷媒は、冷媒用接続配管４ｂを導通し、逆止弁１３ｂを通過して、蒸発器として作用する熱源側熱交換器１２に流入する。 The high-temperature and high-pressure gas refrigerant that has flowed into the intermediate heat exchangers 25a and 25b is condensed and liquefied while dissipating heat to the heat medium passing through the secondary circuit 30, and becomes a high-pressure liquid refrigerant. The liquid refrigerant flowing out from the heat exchangers 25a and 25b is expanded by the expansion devices 26a and 26b, and becomes a low-temperature and low-pressure two-phase refrigerant. These two-phase refrigerants merge, flow out of the relay unit 2 through the opening / closing device 29, and flow into the heat source device 1 again through the refrigerant pipe 4. The refrigerant flowing into the heat source device 1 is conducted through the refrigerant connection pipe 4b, passes through the check valve 13b, and flows into the heat source side heat exchanger 12 that functions as an evaporator.
　そして、熱源側熱交換器１２に流入した熱源側冷媒は、熱源側熱交換器１２で室外空間６の空気（以下、外気と称する）から吸熱して、低温・低圧のガス冷媒となる。熱源側熱交換器１２から流出した低温・低圧のガス冷媒は、第１冷媒流路切替装置１１およびアキュムレーター１９を介して圧縮機１０に再度吸入される。 The heat-source-side refrigerant that has flowed into the heat-source-side heat exchanger 12 absorbs heat from the air in the outdoor space 6 (hereinafter referred to as “outside air”) by the heat-source-side heat exchanger 12, and becomes a low-temperature / low-pressure gas refrigerant. The low-temperature and low-pressure gas refrigerant flowing out from the heat source side heat exchanger 12 is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
　このとき、絞り装置２６は、熱媒体間熱交換器２５と絞り装置２６との間を流れる熱源側冷媒の圧力を飽和温度に換算した値と、熱媒体間熱交換器２５の出口側の温度との差として得られるサブクール（過冷却度）が一定になるように開度が制御される。なお、熱媒体間熱交換器２５の中間位置の温度が測定できる場合は、その中間位置での温度を換算した飽和温度の代わりに用いてもよい。この場合、圧力センサーを設置しなくて済み、安価にシステムを構成できる。 At this time, the expansion device 26 has a value obtained by converting the pressure of the heat-source-side refrigerant flowing between the heat exchanger related to heat medium 25 and the expansion device 26 into a saturation temperature, and the temperature on the outlet side of the heat exchanger related to heat medium 25. The degree of opening is controlled so that the subcool (degree of supercooling) obtained as a difference from the above becomes constant. In addition, when the temperature of the intermediate position of the heat exchanger 25 between heat media can be measured, you may use it instead of the saturation temperature which converted the temperature in the intermediate position. In this case, it is not necessary to install a pressure sensor, and the system can be configured at low cost.
　次に、２次側回路３０における熱媒体の流れについて説明する。
　全暖房運転モードでは、熱媒体間熱交換器２５ａ、２５ｂの双方で熱源側冷媒の温熱が熱媒体に伝えられ、暖められた熱媒体がポンプ３１ａ、３１ｂによって配管５内を流動させられる。ポンプ３１ａ、３１ｂで加圧されて流出した熱媒体は、熱媒体流路切替流量調整装置４０を介して、利用側熱交換器３５ａ～３５ｄに流入する。そして、熱媒体が利用側熱交換器３５ａ～３５ｄで室内空気に放熱することで、居住空間７の暖房を行う。 Next, the flow of the heat medium in the secondary side circuit 30 will be described.
In the heating only operation mode, the heat of the heat source side refrigerant is transmitted to the heat medium in both the heat exchangers 25a and 25b, and the heated heat medium is caused to flow in the pipe 5 by the pumps 31a and 31b. The heat medium pressurized and discharged by the pumps 31a and 31b flows into the use side heat exchangers 35a to 35d via the heat medium flow switching flow rate adjusting device 40. The living space 7 is heated by the heat medium radiating heat to the indoor air by the use side heat exchangers 35a to 35d.
　それから、熱媒体は、利用側熱交換器３５ａ～３５ｄから流出して熱媒体流路切替流量調整装置４０に再度流入する。このとき、熱媒体流路切替流量調整装置４０の流量調整作用によって熱媒体の流量が室内にて必要とされる空調負荷を賄うのに必要な流量に制御されて利用側熱交換器３５ａ～３５ｄに流入する。熱媒体流路切替流量調整装置４０から流出した熱媒体は、熱媒体間熱交換器２５ａ、２５ｂに流入し、室内機３を通じて居住空間７に供給した分の熱量を冷媒側から受け取り、再びポンプ３１ａ、３１ｂに吸い込まれる。 Then, the heat medium flows out of the use side heat exchangers 35a to 35d and flows into the heat medium flow switching flow rate adjusting device 40 again. At this time, the heat medium flow switching device 40 controls the flow rate of the heat medium to a flow rate necessary to cover the air conditioning load required in the room, so that the use side heat exchangers 35a to 35d are used. Flow into. The heat medium that has flowed out of the heat medium flow switching flow control device 40 flows into the heat exchangers 25a and 25b between the heat medium, receives the amount of heat supplied to the living space 7 through the indoor unit 3 from the refrigerant side, and pumps again. It is sucked into 31a and 31b.
　なお、居住空間７にて必要とされる空調負荷は、温度センサー５５ａで検出された温度、あるいは、温度センサー５５ｂで検出された温度と利用側熱交換器３５から流出した熱媒体の温度との差を目標値に保つように熱媒体流路切替流量調整装置４０によって制御することにより、賄うことができる。熱媒体間熱交換器２５の出口温度は、温度センサー５５ａまたは温度センサー５５ｂのどちらの温度を使用してもよいし、これらの平均温度を使用してもよい。 The air conditioning load required in the living space 7 is the temperature detected by the temperature sensor 55a, or the temperature detected by the temperature sensor 55b and the temperature of the heat medium flowing out from the use side heat exchanger 35. This can be covered by controlling the flow rate of the heat medium flow switching device 40 so as to keep the difference at the target value. As the outlet temperature of the heat exchanger related to heat medium 25, the temperature of either the temperature sensor 55a or the temperature sensor 55b may be used, or the average temperature thereof may be used.
　このとき、前述の通り、熱媒体間熱交換器２５ａ、２５ｂの双方に冷媒は流入していると共に、それぞれに熱媒体を搬送するポンプ３１ａ、３１ｂも動作をしているため、分岐口に接続されている複数の室内機３に対しては、それぞれの熱媒体間熱交換器２５により熱交換を行った熱媒体を各室内負荷に応じて適切に搬送する必要がある。 At this time, as described above, the refrigerant is flowing into both of the heat exchangers 25a and 25b, and the pumps 31a and 31b for transporting the heat medium are also operated, so that they are connected to the branch ports. For the plurality of indoor units 3, it is necessary to appropriately transport the heat medium subjected to heat exchange by the heat exchangers 25 between the heat mediums according to each indoor load.
［空気除去運転モード］
　図５は、本発明の実施の形態１に係る空気調和装置１００の空気除去運転モード時における熱媒体の流れを示す図である。空気除去運転モードとは、たとえば空気調和装置１００の施工（設置）時（前述した実際の冷暖房運転による運用前）において、２次側回路３０に熱媒体の充填を行うモードである。 [Air removal operation mode]
FIG. 5 is a diagram showing the flow of the heat medium during the air removal operation mode of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. The air removal operation mode is a mode in which, for example, the secondary side circuit 30 is filled with a heat medium during construction (installation) of the air conditioner 100 (before operation by the actual air conditioning operation described above).
　ここで、空気除去運転モードでは、１次側回路２０の運転は任意であるため、ここでは１次側回路２０についての運転は行わず、２次側回路３０のみ運転させるものとして説明する。したがって、図５に基づいて２次側回路３０における熱媒体の流れについて説明する。 Here, since the operation of the primary circuit 20 is arbitrary in the air removal operation mode, the operation of the primary circuit 20 is not performed here, and only the secondary circuit 30 is operated. Therefore, the flow of the heat medium in the secondary circuit 30 will be described with reference to FIG.
　空気除去運転モードでは、熱媒体はポンプ３１の加圧によって配管５内を流動させられることになる。ポンプ３１ａ、３１ｂに吸い込まれ、加圧されて流出した熱媒体は、熱媒体流路切替流量調整装置４０を通過して利用側熱交換器３５ａ～３５ｄに流入する。ここで、例えば、室内機３ａ～３ｄが有する送風機を停止状態とし、利用側熱交換器３５ａ～３５ｄにおいて熱媒体と室内空気との熱交換を積極的には行わないようにしてもよい。
　利用側熱交換器３５ａ～３５ｄを通過した熱媒体は、熱媒体流路切替流量調整装置４０に戻り、熱媒体間熱交換器２５ａ、２５ｂを通過し、再びポンプ３１ａ、３１ｂに吸い込まれる。 In the air removal operation mode, the heat medium is caused to flow in the pipe 5 by the pressurization of the pump 31. The heat medium sucked into the pumps 31a and 31b and pressurized and flowed out passes through the heat medium flow switching flow rate adjusting device 40 and flows into the use side heat exchangers 35a to 35d. Here, for example, the blowers included in the indoor units 3a to 3d may be stopped so that the heat exchange between the heat medium and the indoor air is not actively performed in the use side heat exchangers 35a to 35d.
The heat medium that has passed through the use side heat exchangers 35a to 35d returns to the heat medium flow switching flow control device 40, passes through the heat exchangers between heat mediums 25a and 25b, and is sucked into the pumps 31a and 31b again.
　また、空気除去運転モードでは、空気除去弁４１、４２を開弁し、空気除去弁４１、４２から熱媒体内の空気を除去する。空気除去弁４１、４２は、空気除去運転モードが完了すると、閉じられる。 In the air removal operation mode, the air removal valves 41 and 42 are opened, and the air in the heat medium is removed from the air removal valves 41 and 42. The air removal valves 41 and 42 are closed when the air removal operation mode is completed.
　また、ここでは１次側回路２０の運転を行っていないが、たとえば空気除去運転モードにおいて、全暖房運転モードと同じように運転を行うようにしてもよい。熱媒体の温度を高くすることで、熱媒体中に含まれる空気の析出を促すことができ、さらに効率よく回路内の空気を抜くことができる。 In addition, although the operation of the primary side circuit 20 is not performed here, for example, in the air removal operation mode, the operation may be performed in the same manner as in the heating only operation mode. By increasing the temperature of the heat medium, precipitation of air contained in the heat medium can be promoted, and the air in the circuit can be extracted more efficiently.
　図６は、本発明の実施の形態１に係る制御装置５０が行う空気除去運転モード時におけるフローを説明する図である。図６に基づいて制御装置５０が空気除去運転モード時において行う処理の内容について説明する。 FIG. 6 is a diagram illustrating a flow in the air removal operation mode performed by the control device 50 according to Embodiment 1 of the present invention. Based on FIG. 6, the content of the process which the control apparatus 50 performs in the air removal operation mode is demonstrated.
　制御装置５０は、施工者などが空気除去運転モード用のスイッチをＯＮにしたものと判断すると空気除去運転モードを開始する（ステップＳ１）。
　運転開始後、２次側回路内の空気除去弁４１、４２を開弁する（ステップＳ２）。
　その後、ポンプ３１ａ、３１ｂを所定時間（例えば１０秒）停止させ、間欠的に駆動させる（ステップＳ３）。 When it is determined that the installer or the like has turned on the switch for the air removal operation mode, the control device 50 starts the air removal operation mode (step S1).
After the operation is started, the air removal valves 41 and 42 in the secondary circuit are opened (step S2).
Thereafter, the pumps 31a and 31b are stopped for a predetermined time (for example, 10 seconds) and driven intermittently (step S3).
　ここで、ステップＳ３中に２次側回路３０内の空気が抜けきったか否かをポンプ３１ａ、３１ｂの回転数により判定する制御を行う（ステップＳ４）。
　ポンプ３１ａ、３１ｂは、たとえば水、不凍液、水と不凍液の混合液、水と防食効果が高い添加剤の混合液などが使用できる水ポンプを使用するため、空気を吸入するとケース内に空気の隙間が生じてポンプ３１ａ、３１ｂが空回りする。そのため、空気を吸入するとポンプ３１ａ、３１ｂの回転数は、正常回転数に比して空気を吸入したときの回転数が一時的に上昇する。 Here, control is performed to determine whether or not the air in the secondary circuit 30 has been exhausted during step S3 based on the rotational speeds of the pumps 31a and 31b (step S4).
The pumps 31a and 31b use water pumps that can use, for example, water, antifreeze, a mixture of water and antifreeze, or a mixture of water and an additive having a high anticorrosive effect. Occurs, causing the pumps 31a and 31b to idle. Therefore, when air is inhaled, the rotational speed of the pumps 31a and 31b temporarily increases as compared to the normal rotational speed.
　図７は、本発明の実施の形態１に係る空気除去運転時におけるポンプ３１ａ、３１ｂの回転数と空気除去運転の運転時間の関係を示す図である。
　図７に示すように、空気を吸入するとポンプ３１ａ、３１ｂの回転数Ｎは、正常回転数Ｎａに比して空気を吸入したときの回転数Ｎｂが一時的に上昇する。
　制御装置５０がポンプ３１ａ、３１ｂの回転数Ｎを常時取得しているとき、２次側回路３０内に空気が大量に残っていると、空気を吸入したときの回転数Ｎｂを頻発して検知し、２次側回路３０内の空気が抜けていくと、この回転数Ｎｂを検知する頻度は減少していく。
　そこで、回転数Ｎｂが検知されてから制御装置５０のタイマを起動し、経過時間Ｔｘをカウントする。Ｔｘが一定時間（Ｔｅ）以上経過すると（Ｔｘ≧Ｔｅが成立したとき）、２次側回路３０内に空気が残っていないと判断して、空気除去運転を終了する（ステップＳ１３）。
　すなわち、制御装置５０は、空気除去運転を、ポンプ３１ａ、３１ｂの空気を吸入したときの回転数Ｎｂの発生間隔（経過時間Ｔｘ）が予め設定した時間間隔（Ｔｅ）以上になったときに完了する。言い換えると、制御装置５０は、空気除去運転を、ポンプ３１ａ、３１ｂの空気を吸入したときの回転数Ｎｂの発生が予め設定した時間（Ｔｅ）内に連続しないときに完了するともいえる。 FIG. 7 is a diagram showing the relationship between the rotational speeds of the pumps 31a and 31b and the operation time of the air removal operation during the air removal operation according to Embodiment 1 of the present invention.
As shown in FIG. 7, when air is inhaled, the rotational speed N of the pumps 31a and 31b temporarily increases as compared to the normal rotational speed Na.
When the control device 50 constantly acquires the rotational speed N of the pumps 31a and 31b, if a large amount of air remains in the secondary circuit 30, the rotational speed Nb when air is sucked in is frequently detected. When the air in the secondary circuit 30 is released, the frequency of detecting the rotational speed Nb decreases.
Therefore, after the rotation speed Nb is detected, the timer of the control device 50 is started and the elapsed time Tx is counted. When Tx elapses for a certain time (Te) or more (when Tx ≧ Te is established), it is determined that no air remains in the secondary circuit 30, and the air removal operation is terminated (step S13).
That is, the control device 50 completes the air removal operation when the generation interval (elapsed time Tx) of the rotation speed Nb when the air of the pumps 31a and 31b is sucked becomes equal to or longer than a preset time interval (Te). To do. In other words, the control device 50 can be said to complete the air removal operation when the generation of the rotational speed Nb when the air of the pumps 31a and 31b is sucked does not continue within a preset time (Te).
　ここで、判定時間Ｔｅを定義する。空気の気泡がポンプ３１ａ、３１ｂより吐出されてから、２次側回路３０を一周する時間をＴｒとするとＴｅ＝Ｔｒ×３とする。
　このとき、Ｔｒは、ポンプ３１ａ、３１ｂの回転数Ｎから求められる水の流量Ｇｒと、中継ユニット２から最遠方に設置された室内機３に接続されている配管５の長さＬと、配管５の断面積Ｓから、Ｔｒ＝Ｌ／（Ｇｒ／Ｓ）とする。 Here, the determination time Te is defined. Te = Tr × 3, where Tr is the time taken to make a round of the secondary circuit 30 after the air bubbles are discharged from the pumps 31a and 31b.
At this time, Tr is the flow rate Gr of water obtained from the rotational speed N of the pumps 31a and 31b, the length L of the pipe 5 connected to the indoor unit 3 installed farthest from the relay unit 2, and the pipe. From the cross-sectional area S of 5, Tr = L / (Gr / S).
　ステップＳ４の終了後、ステップＳ３を開始してから所定時間（たとえば２０分）経過したか否かを判断する（ステップＳ５）。
　所定時間を経過していないと判断すると、ステップＳ３～Ｓ５の処理を繰り返し行う。一方、所定時間経過したものと判断するとステップＳ３の間欠運転を終了し、ステップＳ６に移行する。 After the end of step S4, it is determined whether or not a predetermined time (for example, 20 minutes) has elapsed since the start of step S3 (step S5).
If it is determined that the predetermined time has not elapsed, the processes of steps S3 to S5 are repeated. On the other hand, if it is determined that the predetermined time has elapsed, the intermittent operation in step S3 is terminated, and the process proceeds to step S6.
　ステップＳ５を終了すると、個別室内機運転を開始する（ステップＳ６）。
　ステップＳ６では、熱媒体流路切替流量調整装置４０ａの開度を最大にし、熱媒体流路切替流量調整装置４０ｂ、４０ｃ、４０ｄを閉じて室内機３ｂ、３ｃ、３ｄ側に熱媒体が流れないようにする。また、室内機３ａの運転後、室内機３ｂ、３ｃ、３ｄのそれぞれについても同じ動作を行う。このため、２次側回路３０における経路長が短くなり、出力に対する熱媒体の流速を高くすることができる。 When step S5 is completed, the individual indoor unit operation is started (step S6).
In step S6, the opening degree of the heat medium flow switching flow rate adjusting device 40a is maximized, the heat medium flow switching flow rate adjusting devices 40b, 40c, and 40d are closed, and the heat medium does not flow toward the indoor units 3b, 3c, and 3d. Like that. Further, after the operation of the indoor unit 3a, the same operation is performed for each of the indoor units 3b, 3c, and 3d. For this reason, the path length in the secondary side circuit 30 becomes short, and the flow rate of the heat medium with respect to the output can be increased.
　次に、ステップＳ６中に２次側回路３０内の空気が抜けきったか否かをポンプ３１ａ、３１ｂの回転数Ｎにより判定する制御を行う（ステップＳ７）。
　ステップＳ７は前述のステップＳ４と同様の計算を行い、Ｔｘ≧Ｔｅが成立したとき、空気除去運転を終了する（ステップＳ１３）。
　ステップＳ７にてＴｘ≧Ｔｅが成立しないとき、ステップＳ６を開始してから所定時間（たとえば仕様分岐数×１０分）経過したか否かを判断する（ステップＳ８）。
　所定時間を経過していないと判断すると、ステップＳ６～Ｓ８の処理を繰り返し行う。所定時間経過したものと判断すると、ステップＳ６の個別室内機運転を終了し、ステップＳ９に移行する。 Next, in step S6, control is performed to determine whether or not the air in the secondary circuit 30 has been exhausted based on the rotational speed N of the pumps 31a and 31b (step S7).
In step S7, the same calculation as in step S4 described above is performed, and when Tx ≧ Te is established, the air removal operation is terminated (step S13).
When Tx ≧ Te is not established in step S7, it is determined whether or not a predetermined time (for example, the number of specified branches × 10 minutes) has elapsed since the start of step S6 (step S8).
If it is determined that the predetermined time has not elapsed, steps S6 to S8 are repeated. If it is determined that the predetermined time has elapsed, the individual indoor unit operation in step S6 is terminated, and the process proceeds to step S9.
　ステップＳ８を終了すると、全ての熱媒体流路切替流量調整装置４０ａ～４０ｄの開度を最大にさせて、全室内機３ａ～３ｄにおいて暖房を行う（ステップＳ９）。
　このため、１次側回路２０についても全暖房運転モードでの運転を行う。ここで、室内機３の送風機（図示せず）を駆動させるか否かについては、特に限定しない。 When step S8 is completed, all the indoor units 3a to 3d are heated by maximizing the openings of all the heat medium flow switching flow rate adjusting devices 40a to 40d (step S9).
For this reason, the primary side circuit 20 is also operated in the heating only operation mode. Here, whether or not to drive the blower (not shown) of the indoor unit 3 is not particularly limited.
　次に、ステップＳ９中に２次側回路３０内の空気が抜けきったか否かをポンプ３１ａ、３１ｂの回転数Ｎにより判定する制御を行う（ステップＳ１０）。
　ステップＳ１０は前述のステップＳ４、Ｓ７と同様の計算を行い、Ｔｘ≧Ｔｅが成立したとき、空気除去運転を終了する（ステップＳ１３）。 Next, in step S9, control is performed to determine whether or not the air in the secondary circuit 30 has been exhausted based on the rotational speed N of the pumps 31a and 31b (step S10).
In step S10, the same calculation as in steps S4 and S7 described above is performed, and when Tx ≧ Te is satisfied, the air removal operation is terminated (step S13).
　次に、ステップＳ１０にてＴｘ≧Ｔｅが成立しないとき、ステップＳ９を開始してから所定時間（たとえば２０分）経過したかを判断する（ステップＳ１１）。
　所定時間を経過していないと判断すると、ステップＳ９～Ｓ１１の処理を繰り返し行う。 Next, when Tx ≧ Te is not established in step S10, it is determined whether or not a predetermined time (for example, 20 minutes) has elapsed since the start of step S9 (step S11).
If it is determined that the predetermined time has not elapsed, the processes of steps S9 to S11 are repeated.
　所定時間が経過したとき、２次側回路３０内の空気が抜けきったか否かをポンプ３１ａ、３１ｂの回転数Ｎにより判定する制御を行う（ステップＳ１２）。すなわち、ステップＳ１２では、再度Ｔｘ≧Ｔｅが成立したか否かの判定を行う。
　Ｔｘ≧Ｔｅが成立したならば空気除去運転モードによる運転を完了する（ステップＳ１３）。
　Ｔｘ≧Ｔｅが成立しないとき、ステップＳ３に移行して運転を再開する。 When a predetermined time has elapsed, control is performed to determine whether or not the air in the secondary circuit 30 has been exhausted based on the rotational speed N of the pumps 31a and 31b (step S12). That is, in step S12, it is determined again whether Tx ≧ Te is satisfied.
If Tx ≧ Te is established, the operation in the air removal operation mode is completed (step S13).
When Tx ≧ Te is not established, the process proceeds to step S3 and the operation is resumed.
　以上のように、実施の形態１の空気調和装置１００によれば、２次側回路３０を施工したときに、空気除去運転の完了を制御装置５０により自動で判定するため、効率良く空気除去を行うことができる。 As described above, according to the air conditioner 100 of the first embodiment, when the secondary circuit 30 is installed, the control device 50 automatically determines the completion of the air removal operation. It can be carried out.
　以上説明した本実施の形態では、２次側回路３０を施工したときに空気除去弁４１、４２を開弁してポンプ３１ａ、３１ｂを駆動させて熱媒体を循環させて２次側回路３０内の空気を抜く空気除去運転を実行し、空気除去運転の完了を、ポンプ３１ａ、３１ｂの回転数に基づいて判定を行う制御装置５０を備える。これによれば、空気除去運転の完了を、ポンプ３１ａ、３１ｂの回転数に基づいて判定を行い、空気除去運転を完了する判断を定量的に行うので、２次側回路３０内の空気の残留や施工時間の長期化を回避することができる。 In the present embodiment described above, when the secondary circuit 30 is constructed, the air removal valves 41 and 42 are opened, the pumps 31a and 31b are driven to circulate the heat medium, and the inside of the secondary circuit 30 The control apparatus 50 which performs the air removal operation which extracts the air of this, and determines completion of air removal operation based on the rotation speed of pump 31a, 31b is provided. According to this, the completion of the air removal operation is determined based on the number of rotations of the pumps 31a and 31b, and the determination to complete the air removal operation is quantitatively performed. And prolonged construction time can be avoided.
　制御装置５０は、空気除去運転の完了を、ポンプ３１ａ、３１ｂの空気を吸入したときの回転数Ｎｂの発生に基づいて判定を行う。これによれば、空気除去運転を完了する判断をポンプ３１ａ、３１ｂの空気を吸入したときの回転数Ｎｂの発生に基づいて定量的に行うので、２次側回路３０内の空気の残留や施工時間の長期化を回避することができる。 The control device 50 determines the completion of the air removal operation based on the generation of the rotational speed Nb when the air of the pumps 31a and 31b is sucked. According to this, since the determination to complete the air removal operation is quantitatively made based on the generation of the rotational speed Nb when the air of the pumps 31a and 31b is sucked, the residual air in the secondary circuit 30 and the construction Prolonged time can be avoided.
　制御装置５０は、空気除去運転を、ポンプ３１ａ、３１ｂの空気を吸入したときの回転数Ｎｂの発生間隔（経過時間Ｔｘ）が予め設定した時間間隔（Ｔｅ）以上になったときに完了する。これによれば、空気除去運転を完了する判断をＴｘ≧Ｔｅの関係式に基づいて定量的に行うので、２次側回路３０内の空気の残留や施工時間の長期化を回避することができる。 The control device 50 completes the air removal operation when the generation interval (elapsed time Tx) of the rotational speed Nb when the air of the pumps 31a and 31b is sucked becomes equal to or longer than a preset time interval (Te). According to this, since the determination to complete the air removal operation is quantitatively performed based on the relational expression of Tx ≧ Te, it is possible to avoid the remaining of air in the secondary circuit 30 and the lengthening of the construction time. .
　１　熱源装置、２　中継ユニット、３（３ａ、３ｂ、３ｃ、３ｄ）　室内機、４　冷媒配管、４ａ、４ｂ　冷媒用接続配管、５　配管、６　室外空間、７　居住空間、８　非居住空間、９　建物、１０　圧縮機、１１　第１冷媒流路切替装置、１２　熱源側熱交換器、１３ａ、１３ｂ、１３ｃ、１３ｄ　逆止弁、１９　アキュムレーター、２０　１次側回路、２５（２５ａ、２５ｂ）　熱媒体間熱交換器、２６（２６ａ、２６ｂ）　絞り装置、２７、２９　開閉装置、２８（２８ａ、２８ｂ）　第２冷媒流路切替装置、３０　２次側回路、３１（３１ａ、３１ｂ）　ポンプ、３５（３５ａ、３５ｂ、３５ｃ、３５ｄ）　利用側熱交換器、４０（４０ａ、４０ｂ、４０ｃ、４０ｄ）　熱媒体流路切替流量調整装置、４１、４２　空気除去弁、５０　制御装置、５５（５５ａ、５５ｂ）　温度センサー、１００　空気調和装置。 1 Heat source device, 2 relay unit, 3 (3a, 3b, 3c, 3d) indoor unit, 4 refrigerant pipe, 4a, 4b refrigerant connection pipe, 5 pipe, 6 outdoor space, 7 residential space, 8 non-residential space, 9 Building, 10 compressor, 11 first refrigerant flow switching device, 12 heat source side heat exchanger, 13a, 13b, 13c, 13d check valve, 19 accumulator, 20 primary side circuit, 25 (25a, 25b) heat Inter-medium heat exchanger, 26 (26a, 26b) throttle device, 27, 29 switchgear, 28 (28a, 28b) second refrigerant flow switching device, 30 secondary circuit, 31 (31a, 31b) pump, 35 (35a, 35b, 35c, 35d) User side heat exchanger, 40 (40a, 40b, 40c, 40d) Heat medium flow switching flow control device, 41, 42 Air removal valve, 0 controller, 55 (55a, 55b) a temperature sensor, 100 an air conditioner.

Claims (3)

  1. 　熱源側冷媒を圧縮する圧縮機、前記熱源側冷媒を熱交換させる熱源側熱交換器、前記熱源側冷媒を圧力調整する絞り装置および前記熱源側冷媒と熱媒体との熱交換を行う熱媒体間熱交換器の熱源側冷媒側を配管接続して構成する冷媒循環回路と、
    　前記熱媒体間熱交換器の熱媒体側、前記熱媒体を循環させるポンプおよび前記熱媒体と空調対象空間の空気との熱交換を行う利用側熱交換器を配管接続して構成された熱媒体循環回路と、
    を備え、
    　前記熱媒体循環回路は、内部の空気を放出させる空気除去弁を有し、
    　前記熱媒体循環回路を施工したときに前記空気除去弁を開弁して前記ポンプを駆動させて前記熱媒体を循環させて前記熱媒体循環回路内の空気を抜く空気除去運転を実行し、前記空気除去運転の完了を、前記ポンプの回転数に基づいて判定を行う制御装置を備える空気調和装置。     A compressor that compresses the heat source side refrigerant, a heat source side heat exchanger that exchanges heat with the heat source side refrigerant, a throttling device that adjusts the pressure of the heat source side refrigerant, and a heat medium that exchanges heat between the heat source side refrigerant and the heat medium A refrigerant circulation circuit configured by pipe connection of the heat source side refrigerant side of the heat exchanger;
    A heat medium configured by pipe-connecting a heat medium side of the heat exchanger between the heat medium, a pump for circulating the heat medium, and a use side heat exchanger for exchanging heat between the heat medium and the air in the air conditioning target space A circulation circuit;
    With
    The heat medium circulation circuit has an air removal valve that discharges internal air,
    When the heat medium circulation circuit is installed, the air removal valve is opened and the pump is driven to circulate the heat medium to remove the air in the heat medium circulation circuit, An air conditioner including a control device that determines completion of an air removal operation based on the number of rotations of the pump.
  2. 　前記制御装置は、前記空気除去運転の完了を、前記ポンプの空気を吸入したときの回転数の発生に基づいて判定を行う請求項１に記載の空気調和装置。 The air conditioner according to claim 1, wherein the control device determines completion of the air removal operation based on generation of a rotation speed when the air of the pump is sucked.
  3. 　前記制御装置は、前記空気除去運転を、前記ポンプの空気を吸入したときの回転数の発生間隔が予め設定した時間間隔以上になったときに完了する請求項１または２に記載の空気調和装置。 3. The air conditioner according to claim 1, wherein the control device completes the air removal operation when a generation interval of a rotation speed when the air of the pump is sucked becomes equal to or longer than a preset time interval. .
PCT/JP2015/060391 2015-04-01 2015-04-01 Air-conditioning device WO2016157481A1 (en)

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