WO2018123361A1 - Multi-split air conditioner control device, multi-split air conditioner, multi-split air conditioner control method, and multi-split air conditioner control program - Google Patents

Multi-split air conditioner control device, multi-split air conditioner, multi-split air conditioner control method, and multi-split air conditioner control program Download PDF

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Publication number
WO2018123361A1
WO2018123361A1 PCT/JP2017/041936 JP2017041936W WO2018123361A1 WO 2018123361 A1 WO2018123361 A1 WO 2018123361A1 JP 2017041936 W JP2017041936 W JP 2017041936W WO 2018123361 A1 WO2018123361 A1 WO 2018123361A1
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WIPO (PCT)
Prior art keywords
heat exchanger
air conditioner
volume
defrosting
refrigerant
Prior art date
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PCT/JP2017/041936
Other languages
French (fr)
Japanese (ja)
Inventor
正幸 瀧川
隆博 加藤
達弘 安田
知宏 阪口
Original Assignee
三菱重工サーマルシステムズ株式会社
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Application filed by 三菱重工サーマルシステムズ株式会社 filed Critical 三菱重工サーマルシステムズ株式会社
Priority to EP17885879.1A priority Critical patent/EP3473946A4/en
Publication of WO2018123361A1 publication Critical patent/WO2018123361A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F24F11/42—Defrosting; Preventing freezing of outdoor units
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature

Definitions

  • the present invention relates to a control device for a multi-type air conditioner, a multi-type air conditioner, a control method for the multi-type air conditioner, and a control program for the multi-type air conditioner.
  • the defrosting operation is to remove (defrost) frost adhering to the heat exchanger by allowing a high-temperature and high-pressure refrigerant to flow into the heat exchanger.
  • the defrosting operation of a multi-type air conditioner constituted by a plurality of heat exchangers when the volume of each heat exchanger is different, the refrigerant flow rate required for defrosting is different for each heat exchanger.
  • Patent Document 1 discloses that the temperatures of the heat exchangers detected by the heat exchange temperature detecting means are compared and the refrigerant flow rate is controlled by the opening of the electric expansion valve.
  • Patent Document 2 discloses that the temperatures of the upper and lower paths of the heat exchanger are detected and the refrigerant flow rate is adjusted by the opening of the expansion valve in accordance with the temperature difference.
  • the present invention has been made in view of such circumstances, and is a multi-type air conditioner control device, a multi-type air conditioner, and a multi-type air capable of shortening the defrosting time in heat exchangers having different volumes. It is an object of the present invention to provide a control method for a conditioner and a control program for a multi-type air conditioner.
  • the control device for a multi-type air conditioner, the multi-type air conditioner, the control method for the multi-type air conditioner, and the control program for the multi-type air conditioner of the present invention employ the following means.
  • the control apparatus for a multi-type air conditioner according to the first aspect of the present invention includes: an outdoor unit including a plurality of heat exchangers, wherein the volume of at least one heat exchanger is different from the volume of other heat exchangers; A plurality of the heat exchangers, each of which includes a flow rate adjusting device for adjusting the flow rate of the refrigerant supplied to the heat exchanger. During the frost operation, the refrigerant flow rate supplied to each heat exchanger is adjusted by the control of the flow rate adjusting device according to the volumes of the plurality of heat exchangers.
  • the control device for the multi-type air conditioner including the outdoor unit including a plurality of heat exchangers having different volumes of at least one heat exchanger and the plurality of indoor units is used during the defrosting operation.
  • the refrigerant flow rate is controlled according to the volume of each heat exchanger.
  • the defrosting completion timing is different, a loss of refrigerant that is circulated to prevent re-frosting occurs. Therefore, by controlling the refrigerant flow rate according to the volume of each heat exchanger, the defrosting of each heat exchanger is completed substantially simultaneously. Thereby, it is not necessary to circulate a refrigerant
  • the defrosting of each heat exchanger is completed almost simultaneously, and the defrosting operation is completed early.
  • the volume of each heat exchanger is a numerical value that can be acquired in advance, can be controlled from the start of the defrosting operation, and the time required for defrosting can be shortened.
  • the flow rate adjusting device includes an electric expansion valve
  • the plurality of heat exchangers each include a temperature sensor that detects a heat exchanger temperature of the heat exchanger, and all the heat exchangers
  • the valve opening degree determination control for determining the opening degrees of the electric expansion valves of the plurality of heat exchangers so that the heat exchanger temperature reaches the defrosting completion temperature that is the reference value for completion of defrosting at substantially the same time. Good.
  • the defrosting is completed when the refrigerant flow rate required for defrosting varies depending on the volume, so that the same refrigerant flow rate is obtained.
  • the timing to do is different.
  • the refrigerant flow rate is controlled according to the volume of the heat exchanger because the opening of the electric expansion valve is adjusted and the refrigerant flow rate is controlled so that the heat exchanger temperature of each heat exchanger reaches the defrosting completion temperature at the same time. In doing so, the opening degree of the electric expansion valve is set for each heat exchanger based on the defrosting completion temperature.
  • the ratio of the refrigerant flow rate of each heat exchanger is determined in advance so that the heat exchangers reach the defrosting completion temperature substantially simultaneously, and the opening degree of each electric expansion valve is set based on the ratio. . Even in a multi-type air conditioner provided with a plurality of heat exchangers having different volumes, the defrosting of each heat exchanger is completed at the same time, so that the refrigerant flow rate required for the defrosting can be reduced.
  • the opening degree of the electric expansion valve of the heat exchanger may be a minimum opening degree.
  • the timing of defrosting completion may be different due to various factors.
  • the heat exchanger by which defrost was completed ie, the heat exchanger whose heat exchanger temperature became more than defrost completion temperature
  • the opening degree of the electric expansion valve is made into the minimum opening degree.
  • the minimum opening is an opening that allows a very small amount of refrigerant to flow in so that the outdoor heat exchanger that has completed defrosting does not refrost, and is, for example, about 60 pulses.
  • the said electric drive of this heat exchanger may be gradually increased.
  • the refrigerant flow rate is minimized, so that there is a possibility of refrosting.
  • the heat exchanger temperature of the corresponding heat exchanger becomes lower than the defrosting completion temperature, it is assumed that there is a possibility of refrosting, and the opening degree of the electric expansion valve is gradually increased. Thereby, frost formation of the heat exchanger can be prevented by increasing the refrigerant flow rate.
  • the opening degree of the electric expansion valve of the heat exchanger may be fully opened.
  • the timing of defrosting completion may be different due to various factors.
  • the electric expansion valves of the other heat exchangers have the minimum opening, and there is a margin in the refrigerant supply amount. There will be. However, if the opening degree of the electric expansion valve of the heat exchanger that has not been defrosted remains the same, the supply of the refrigerant flow rate does not increase and defrosting takes time.
  • the opening degree of the electric expansion valve of the heat exchanger is fully opened.
  • the maximum amount of surplus refrigerant can be supplied to the heat exchanger that has not been defrosted, and the time required for defrosting can be shortened.
  • the valve opening determination control may be performed at the time of shipment from a factory or during a trial operation, and the opening of the electric expansion valve may be stored in a storage unit.
  • the control for determining the opening degree of the electric expansion valve serving as a reference is performed at the time of shipment from the factory or at the time of trial operation, and the opening degree is stored in the storage means.
  • the refrigerant flow rate can be properly stored at the time of trial operation before starting normal air-conditioning operation or at the time of valve opening determination control performed at the time of shipment from the factory. Therefore, since the refrigerant flow rate is supplied based on the reference opening during normal air conditioning operation, defrosting can be completed simultaneously even in an air conditioner having a plurality of heat exchangers with different volumes.
  • the multi-type air conditioner according to the second aspect of the present invention includes an outdoor unit including a plurality of heat exchangers having a volume of at least one heat exchanger different from that of other heat exchangers, and a plurality of indoor units And a control device according to any of the above.
  • a control method for a multi-type air conditioner includes: an outdoor unit including a plurality of heat exchangers, wherein the volume of at least one heat exchanger is different from the volume of other heat exchangers; A plurality of heat exchangers, each of the plurality of heat exchangers including a flow rate adjusting device for adjusting a flow rate of refrigerant supplied to the heat exchanger. A step of adjusting the flow rate of the refrigerant supplied to each of the heat exchangers according to the volume of the plurality of heat exchangers during the frost operation is controlled by the flow rate adjusting device.
  • a control program for a multi-type air conditioner includes: an outdoor unit including a plurality of the heat exchangers, wherein the volume of at least one heat exchanger is different from the volume of other heat exchangers; A plurality of heat exchangers, each of which includes a flow rate adjusting device for adjusting a flow rate of refrigerant supplied to the heat exchanger. A step of adjusting the flow rate of the refrigerant supplied to each of the heat exchangers according to the volume of the plurality of heat exchangers during the frost operation by the control of the flow rate adjusting device;
  • the flow rate of each refrigerant is adjusted by controlling the flow rate adjusting device based on the volume of each heat exchanger having a different volume, so that the defrosting of each heat exchanger is completed almost simultaneously. By making it, defrosting time can be shortened.
  • Embodiments of a control device for a multi-type air conditioner, a multi-type air conditioner, a control method for a multi-type air conditioner, and a control program for a multi-type air conditioner according to the present invention will be described below with reference to the drawings. explain.
  • FIG. 1 shows a refrigerant circuit diagram during heating operation of the multi-type air conditioner according to the present embodiment.
  • a plurality of indoor units 3A and 3B are connected to a single outdoor unit 2 in parallel.
  • the plurality of indoor units 3 ⁇ / b> A and 3 ⁇ / b> B are connected in parallel to each other via a branching device 6 between a gas side pipe 4 and a liquid side pipe 5 connected to the outdoor unit 2.
  • the outdoor unit 2 includes an inverter-driven compressor 10 that compresses the refrigerant, a four-way switching valve 12 that switches the circulation direction of the refrigerant, and a plurality of outdoor heat exchangers (heat exchangers) 13A that exchange heat between the refrigerant and the outside air.
  • an inverter-driven compressor 10 that compresses the refrigerant
  • a four-way switching valve 12 that switches the circulation direction of the refrigerant
  • a plurality of outdoor heat exchangers (heat exchangers) 13A that exchange heat between the refrigerant and the outside air.
  • outdoor heat exchanger temperature sensors 14A, 14B and 14C for detecting the heat exchanger temperatures of the outdoor heat exchangers 13A, 13B and 13C, and the outdoor heat exchangers 13A, 13B and 13C
  • Outdoor expansion valves (electric expansion valves: EEVH) (flow rate adjusting devices) 15A, 15B and 15C for adjusting the flow rate of each refrigerant, a receiver 16 for storing liquid refrigerant, and a supercooling heat exchanger 17 for supercooling the liquid refrigerant.
  • EEVH electric expansion valves
  • a supercooling expansion valve (EEVSC) 18 that controls the amount of refrigerant diverted to the supercooling heat exchanger 17, and a liquid component separated from the refrigerant gas sucked into the compressor 10, and only the gas component is compressed.
  • accumulator 19 and to be taken to 10 side, a gas-side operation valve 20, and a liquid-side operation valve 21.
  • the volumes of the outdoor heat exchangers 13A, 13B, and 13C are different.
  • FIG. 1 and FIG. 2 illustrate the case where three outdoor heat exchangers 13A, 13B, and 13C are installed, the number of installed units can be arbitrarily determined.
  • each outdoor heat exchanger 13 either A, B or C is added at the end, and when not distinguishing each outdoor heat exchanger 13, A, B or C is omitted.
  • each outdoor heat exchanger temperature sensor 14 it attaches either A, B, or C to the end, and when not distinguishing each outdoor heat exchanger temperature sensor 14, A, B, or C is used. Omitted.
  • the above devices on the outdoor unit 2 side are sequentially connected via a refrigerant pipe 22 to constitute a known outdoor refrigerant circuit 23. Further, the outdoor unit 2 is provided with an outdoor fan (not shown) that blows outside air to each outdoor heat exchanger 13.
  • the gas side pipe 4 and the liquid side pipe 5 are refrigerant pipes connected to the gas side operation valve 20 and the liquid side operation valve 21 of the outdoor unit 2, and are connected to the outdoor unit 2 and to it during installation on site.
  • the pipe length is appropriately set according to the distance between the plurality of indoor units 3A and 3B.
  • a plurality of branching devices 6 are provided in the middle of the gas side piping 4 and the liquid side piping 5, and an appropriate number of indoor units 3 ⁇ / b> A and 3 ⁇ / b> B are connected via the branching devices 6. Thereby, one sealed refrigeration cycle (refrigerant circuit) 7 is configured.
  • the indoor units 3 ⁇ / b> A and 3 ⁇ / b> B exchange or heat indoor air with a refrigerant to cool or heat the indoor unit 3 ⁇ / b> A through an indoor heat exchanger 30, an indoor expansion valve (EEVC) 31, and an indoor heat exchanger 30.
  • An indoor fan 32 that circulates indoor air and an indoor controller 33 are provided, and are connected to the branching device 6 via branch gas side pipes 4A and 4B and branch liquid side pipes 5A and 5B on the indoor side.
  • the control device 50 acquires a set value, a refrigerant temperature, and the like by the indoor controller 33, and performs switching control of the four-way switching valve 12, opening / closing of each valve, opening degree control, and the like.
  • the control device 50 includes, for example, a CPU (Central Processing Unit), a RAM (Random Access Memory), a ROM (Read Only Memory), and a computer-readable storage medium.
  • a series of processes for realizing various functions is stored in a storage medium or the like in the form of a program as an example, and the CPU reads the program into a RAM or the like to execute information processing / arithmetic processing. As a result, various functions are realized.
  • the program is preinstalled in a ROM or other storage medium, provided in a state stored in a computer-readable storage medium, or distributed via wired or wireless communication means. Etc. may be applied.
  • Examples of the computer-readable storage medium include a magnetic disk, a magneto-optical disk, a CD-ROM, a DVD-ROM, and a semiconductor memory.
  • the heating operation is performed as follows.
  • the high-temperature and high-pressure refrigerant gas compressed and discharged by the compressor 10 is circulated to the gas-side operation valve 20 side through the four-way switching valve 12.
  • the high-pressure gas refrigerant is led out from the outdoor unit 2 through the gas side operation valve 20 and the gas side pipe 4, and is supplied to the plurality of indoor units 3A and 3B through the branching unit 6, the indoor side branching gas side pipes 4A and 4B. be introduced.
  • the high-temperature and high-pressure refrigerant gas introduced into the indoor units 3A and 3B is heat-exchanged with the indoor air circulated through the indoor fan 32 in the indoor heat exchanger 30, and the heated indoor air is blown into the room. It is used for heating.
  • the refrigerant condensed and liquefied in the indoor heat exchanger 30 reaches the branching device 6 through the indoor expansion valve 31 and the branch liquid side pipes 5A and 5B, and is merged with the refrigerant from other indoor units. After that, it returns to the outdoor unit 2.
  • the opening degree of the indoor expansion valve 31 is set to the indoor controller so that the refrigerant outlet temperature or the refrigerant subcooling degree of the indoor heat exchanger 30 functioning as a condenser becomes the control target value. 33 is controlled.
  • the refrigerant that has returned to the outdoor unit 2 passes through the liquid side operation valve 21, reaches the supercooling heat exchanger 17, and flows through the liquid refrigerant pipe side in part. Heat exchange with the adiabatic expanded refrigerant provides a degree of supercooling. Thereafter, the amount of circulation is adjusted by flowing into the receiver 16 and once stored. This liquid refrigerant is supplied to each outdoor expansion valve 15 and adiabatically expanded, and then flows into each outdoor heat exchanger 13.
  • each outdoor heat exchanger 13 the outside air blown from the outdoor fan and the refrigerant are heat-exchanged, and the refrigerant absorbs heat from the outside air and is evaporated and gasified.
  • This refrigerant is introduced from each outdoor heat exchanger 13 through the four-way switching valve 12 and the refrigerant gas from the supercooling heat exchanger 17 and then introduced into the accumulator 19.
  • the liquid component contained in the refrigerant gas is separated, and only the gas component is sucked into the compressor 10 and compressed again in the compressor 10.
  • the heating operation is performed by repeating the above cycle.
  • each outdoor heat exchanger 13 may be frosted.
  • the heating capacity is reduced.
  • the defrosting operation is performed by switching the four-way switching valve 12.
  • the defrosting operation is generally activated when the temperature detected by the outdoor heat exchanger temperature sensor 14 of each outdoor heat exchanger 13 is equal to or lower than a certain temperature.
  • the temperature at which the defrosting operation is performed varies depending on each multi-type air conditioner 1, for example, a value around 0 ° C.
  • FIG. 2 shows a refrigerant circuit diagram during the defrosting operation of the multi-type air conditioner according to the present embodiment.
  • the defrosting operation is performed as follows.
  • the high-temperature and high-pressure refrigerant gas compressed and discharged by the compressor 10 is circulated to the outdoor heat exchanger 13 side by the four-way switching valve 12, and is heat-exchanged with the outdoor air blown by the outdoor fan in each outdoor heat exchanger 13. Is condensed and liquefied.
  • the liquid refrigerant passes through each outdoor expansion valve 15 and is temporarily stored in the receiver 16. In this way, defrosting is performed by the high-temperature and high-pressure refrigerant gas flowing into each outdoor heat exchanger 13.
  • the liquid refrigerant whose circulation amount is adjusted by the receiver 16 reaches the supercooling heat exchanger 17 and is supercooled in the same manner as in heating.
  • This liquid refrigerant is guided from the outdoor unit 2 to the liquid side pipe 5 through the liquid side operation valve 21, and is divided into the branch liquid side pipes 5A and 5B of the indoor units 3A and 3B via the branching unit 6. .
  • the liquid refrigerant divided into the branch liquid side pipes 5A and 5B flows into the indoor units 3A and 3B, is adiabatically expanded by the indoor expansion valve 31, and flows into the indoor heat exchanger 30 as a gas-liquid two-phase flow.
  • the refrigerant gas merged in the gas side pipe 4 returns to the outdoor unit 2 again, merges with the refrigerant gas from the supercooling heat exchanger 17 through the gas side operation valve 20 and the four-way switching valve 12, and then accumulator 19. To be introduced. In the accumulator 19, the liquid component contained in the refrigerant gas is separated, and only the gas component is sucked into the compressor 10. This refrigerant is compressed again in the compressor 10, and the defrosting operation is performed by repeating the above cycle.
  • the defrosting operation is generally completed when the temperature detected by the all-outdoor heat exchanger temperature sensor 14 of the all-outdoor heat exchanger 13 becomes equal to or higher than a certain temperature due to the defrosting operation.
  • the temperature used as the reference value for the completion of the defrosting operation that is, the defrosting completion temperature differs depending on each multi-type air conditioner 1, it is, for example, a value around 9 ° C.
  • FIG. 3 is a block diagram schematically illustrating the refrigerant flow rate during the defrosting operation of each heat exchanger of the multi-type air conditioner according to the first embodiment of the present invention.
  • FIG. 4 is a block diagram showing an outline of the refrigerant flow rate at the completion of defrosting of each heat exchanger of the multi-type air conditioner according to the first embodiment of the present invention.
  • the opening degree of the outdoor expansion valve 15 corresponding to the volume of each outdoor heat exchanger 13 is first determined by the control device 50, and the valve opening degree setting control to be set is performed. Since each outdoor heat exchanger 13 has a different volume, each outdoor heat exchanger 13 is controlled so that the defrosting of each outdoor heat exchanger 13 is completed substantially simultaneously, that is, the defrosting completion temperature is reached almost simultaneously.
  • the flow rate of the refrigerant flowing into each outdoor heat exchanger 13 is determined by the ratio. Based on the determined refrigerant flow rates, the opening degree of each outdoor expansion valve 15 of each outdoor heat exchanger 13 is determined, and the opening degree is set in each outdoor expansion valve 15. After the opening degree of the outdoor expansion valve 15 is set, the defrosting operation is started.
  • the volume of each outdoor heat exchanger 13 can be calculated from the inner diameter, length, and number of tubes. In this embodiment, as shown in FIGS. 3 and 4, it is assumed that the volume of the outdoor heat exchanger 13A is the largest, the volume of the outdoor heat exchanger 13B, and the volume of the outdoor heat exchanger 13C are the smallest. As shown in FIG. 3, since the volume of the outdoor heat exchanger 13A is the largest, the refrigerant flow rate determined based on each volume ratio is set so that the amount of refrigerant flowing into the outdoor heat exchanger 13A is maximized.
  • the opening degree of the outdoor expansion valve 15A is set. Similarly, the opening degrees of the outdoor expansion valves 15B and 15C are set simultaneously based on the volume ratios of the outdoor heat exchangers 13B and 13C. When the opening degree of each outdoor expansion valve 15 is set, the defrosting operation is performed.
  • the outdoor heat of all the outdoor heat exchangers 13 is controlled by controlling the opening degree of each outdoor expansion valve 15 according to each refrigerant flow rate obtained based on the volume ratio of each outdoor heat exchanger 13.
  • the heat exchanger temperatures detected by the exchanger temperature sensor 14 reach the defrosting completion temperature almost simultaneously, and the defrosting is completed.
  • the opening degree of the outdoor expansion valve 15 corresponding to the volume of each outdoor heat exchanger 13 is first determined and set at the start of the defrosting operation.
  • the determination and setting of the opening degree of the outdoor expansion valve 15 may be performed at the time of shipment from the factory or during a trial operation, and the opening degree of the outdoor expansion valve 15 may be stored in a storage unit (not shown) of the control device 50.
  • a multi-type air conditioner including an outdoor unit 2 including a plurality of outdoor heat exchangers 13 having different volumes of at least one outdoor heat exchanger 13 and a plurality of indoor units 3A and 3B.
  • 1 control apparatus 50 controls a refrigerant
  • the refrigerant flow rate is controlled according to the volume of each outdoor heat exchanger 13 so that the defrosting of each outdoor heat exchanger 13 is completed almost simultaneously, thereby preventing the refrigerant from re-frosting.
  • the refrigerant flow rate required for defrosting can be reduced.
  • each outdoor heat exchanger 13 is distributed by each outdoor expansion valve 15, so that the defrosting of each outdoor heat exchanger 13 is completed almost simultaneously and the defrosting operation is performed early. finish.
  • the volume of each outdoor heat exchanger 13 is a numerical value that can be acquired in advance. In the present embodiment, control can be performed from the start of the defrosting operation, and the time required for defrosting can be shortened. it can.
  • the defrosting is completed when the refrigerant flow rate required for defrosting is different due to the difference in volume, so that the same refrigerant flow rate is obtained.
  • the timing is different.
  • the refrigerant flow rate is controlled by adjusting the opening of each outdoor expansion valve 15 so that the heat exchanger temperature of each outdoor heat exchanger 13 reaches the defrosting completion temperature at the same time.
  • the opening degree of the outdoor expansion valve 15 is set for each outdoor heat exchanger 13 with reference to the defrosting completion temperature.
  • the ratio of the refrigerant flow rate of each outdoor heat exchanger 13 is determined in advance based on the volume ratio of each outdoor heat exchanger 13 so that each outdoor heat exchanger 13 reaches the defrosting completion temperature substantially simultaneously. Based on this, the opening degree of each outdoor expansion valve 15 is set. Even in an air conditioner provided with a plurality of outdoor heat exchangers 13 having different volumes, the defrosting of the outdoor heat exchangers 13 is completed at the same time, so that the refrigerant flow rate required for defrosting can be reduced.
  • the valve opening determination control of each outdoor expansion valve 15 serving as a reference is performed at the time of shipment from the factory or at the time of trial operation, and the opening is stored in the storage means. It can be appropriately stored during the valve opening determination control that is performed at the time of trial operation before starting the air-conditioning operation or at the time of shipment from the factory. Accordingly, since the refrigerant flow rate is supplied based on the reference opening during normal air-conditioning operation, the defrosting operation can be started quickly, and a plurality of outdoor heat exchangers 13 having different volumes are provided. Also in the multi-type air conditioner 1, defrosting can be completed substantially simultaneously.
  • the opening degree of the outdoor expansion valve is set based on the volume ratio of each outdoor heat exchanger at the start of the defrosting operation, and the defrosting is completed almost simultaneously.
  • the opening degree of the outdoor expansion valve is controlled. Since the other points are the same as in the first embodiment, the same components are denoted by the same reference numerals and the description thereof is omitted.
  • FIG. 5 is a flowchart showing the control of the electric expansion valve during the defrosting operation by the control device for the multi-type air conditioner according to the second embodiment of the present invention.
  • the opening degree of each outdoor expansion valve 15 corresponding to the volume of each outdoor heat exchanger 13 is set (S101). After the opening degree of each outdoor expansion valve 15 is set, the defrosting operation is started.
  • each heat exchanger temperature is detected by the outdoor heat exchanger temperature sensor 14 of each outdoor heat exchanger 13 (S102).
  • a defrosting completion temperature for example, 9 ° C.
  • step S103 determines with heat exchanger temperature having reached defrost completion temperature in step S103. If it is determined in step S103 that the heat exchanger temperature has not reached the defrosting completion temperature, the process proceeds to step S107.
  • the determination in step S103 is performed on each outdoor heat exchanger 13 in parallel.
  • the opening of the outdoor expansion valve 15A is set to the minimum opening (S104).
  • the minimum opening is an opening that allows a small amount of refrigerant to flow in such a degree that the outdoor heat exchanger 13 that has completed defrosting does not re-frost, and is, for example, about 60 pulses.
  • the process proceeds to step S110.
  • step S110 when it is determined in step S110 that the heat exchanger temperature of the outdoor heat exchanger 13A is lower than the defrosting completion temperature, the opening degree of the outdoor expansion valve 15A is gradually increased (S106). Re-frosting of the outdoor heat exchanger 13A is prevented by gradually increasing the opening of the outdoor expansion valve 15A. Specifically, for example, control for increasing the opening degree of the outdoor expansion valve 15A by x pulses / 20 s is performed n times. When the gradually increasing control of the opening degree of the outdoor expansion valve 15A is completed, the process proceeds to step S110.
  • step S107 when it is determined in step S103 that, for example, the heat exchanger temperature of the outdoor heat exchanger 13A has not reached the defrosting completion temperature, the opening degree of the outdoor expansion valve 15A is maintained (S107).
  • step S108 whether the heat exchanger temperature has reached the defrosting completion temperature in all the outdoor heat exchangers 13 (in this case, the outdoor heat exchanger 13B and the outdoor heat exchanger 13C) other than the outdoor heat exchanger 13A It is determined whether or not (S108). When it determines with the heat exchanger temperature of all the other outdoor heat exchangers 13 having reached defrost completion temperature in step S108, it changes to step S109. If it is determined in step S108 that the heat exchanger temperatures of all other outdoor heat exchangers 13 have not reached the defrosting completion temperature, the process returns to step S107.
  • step S108 for example, the heat exchanger temperature reaches the defrosting completion temperature in all the outdoor heat exchangers 13 (outdoor heat exchanger 13B and outdoor heat exchanger 13C) other than the outdoor heat exchanger 13A. Is determined as the maximum opening degree (S109). That is, the maximum opening means full opening. Then, the process proceeds to step S110.
  • step S110 it is determined whether or not all the outdoor heat exchangers 13 have reached the defrosting completion temperature. When it determines with the heat exchanger temperature in all the outdoor heat exchangers 13 having reached defrost completion temperature in step S110, a defrost operation is complete
  • FIG. 6 is a block diagram showing the refrigerant flow rate at the time of uniform defrosting of each heat exchanger of the multi-type air conditioner according to the second embodiment of the present invention.
  • steps S104 and S109 in the flowchart of FIG. As shown, the opening degree of the outdoor expansion valve 15B of the outdoor heat exchanger 13B and the outdoor expansion valve 15C of the outdoor heat exchanger 13C are set to the minimum opening degree, and the opening degree of the outdoor expansion valve 15A of the outdoor heat exchanger 13A. Is the maximum opening, that is, fully open.
  • the control device for a multi-type air conditioner the multi-type air conditioner, the control method for the multi-type air conditioner, and the control program for the multi-type air conditioner according to the present embodiment, Has the effect of. Even in the case where control is performed so that defrosting is completed at the same time in a plurality of outdoor heat exchangers 13 having different volumes, the timing of defrosting completion may be different due to various factors. When the outdoor heat exchanger 13 in which defrosting is completed earlier than the other outdoor heat exchangers 13 is present, it is unnecessary and unnecessary to supply the same amount of refrigerant flow as before completion of defrosting.
  • the opening of the outdoor expansion valve 15 is set to the minimum opening.
  • coolant flow volume can be minimized, more refrigerant
  • the timing of defrosting completion may be different due to various factors.
  • the outdoor expansion valve 15 of the other outdoor heat exchanger 13 has a minimum opening. There is a margin in the amount of refrigerant supplied. However, if the opening degree of the electric expansion valve of the outdoor heat exchanger 13 that has not been defrosted remains unchanged and the supply of the refrigerant flow rate does not increase, defrosting takes time.
  • the flow rate adjustment device is an outdoor expansion valve (electric expansion valve).
  • any other device may be used as long as the device has a function that allows the control device 50 to adjust the flow rate. Also good.

Abstract

This multi-split air conditioner control device is provided with: an outdoor unit provided with a plurality of outdoor heat exchangers (13) among which the volume of at least one outdoor heat exchanger (13) is different from the volume of another outdoor heat exchanger (13); and a plurality of indoor units. Each of the plurality of outdoor heat exchangers (13) is provided with an outdoor expansion valve (15) for adjusting the flow rate of refrigerant being supplied to the outdoor heat exchanger (13), and the flow rate of the refrigerant supplied to each of the plurality of outdoor heat exchangers (13) is adjusted by controlling the outdoor expansion valves (15) according to the volumes of the plurality of outdoor heat exchangers (13).

Description

マルチ型空気調和機の制御装置、マルチ型空気調和機、マルチ型空気調和機の制御方法及びマルチ型空気調和機の制御プログラムMulti-type air conditioner control device, multi-type air conditioner, control method for multi-type air conditioner, and control program for multi-type air conditioner
　本発明は、マルチ型空気調和機の制御装置、マルチ型空気調和機、マルチ型空気調和機の制御方法及びマルチ型空気調和機の制御プログラムに関するものである。 The present invention relates to a control device for a multi-type air conditioner, a multi-type air conditioner, a control method for the multi-type air conditioner, and a control program for the multi-type air conditioner.
　マルチ型空気調和機において、熱交換器に着霜した場合、除霜運転が行われる。除霜運転は、高温・高圧の冷媒を熱交換器に流入させることで熱交換器に付着した霜を除去（除霜）するものである。複数の熱交換器によって構成されるマルチ型空気調和機の除霜運転では、各熱交換器の容積が違う場合、除霜に要する冷媒流量が各熱交換器によって異なる。除霜に要する冷媒流量が適切に分配されず例えば全ての各熱交換器における冷媒流量が略等しい場合は、除霜が完了した熱交換器に冷媒が流れ続け、除霜が完了していない熱交換器への冷媒流量は変わらない。その結果、除霜運転が長期化する場合があった。
　そこで、各熱交換器の除霜に要する冷媒流量を適切に分配する制御が検討されている。
　例えば、特許文献１には、熱交温度検出手段により検出された各熱交換器の温度を比較し、電動膨張弁の開度により冷媒流量を制御することが開示されている。また、特許文献２には、熱交換器の上パス及び下パスの夫々の温度を検出し、温度差に応じて膨張弁の開度により冷媒流量を調整することが開示されている。 In the multi-type air conditioner, when the heat exchanger is frosted, a defrosting operation is performed. The defrosting operation is to remove (defrost) frost adhering to the heat exchanger by allowing a high-temperature and high-pressure refrigerant to flow into the heat exchanger. In the defrosting operation of a multi-type air conditioner constituted by a plurality of heat exchangers, when the volume of each heat exchanger is different, the refrigerant flow rate required for defrosting is different for each heat exchanger. If the refrigerant flow required for defrosting is not properly distributed, for example, if the refrigerant flow rate in all the heat exchangers is approximately equal, the refrigerant continues to flow through the heat exchanger that has completed defrosting, and heat that has not been defrosted. The refrigerant flow to the exchanger is not changed. As a result, the defrosting operation may be prolonged.
Therefore, control for appropriately distributing the refrigerant flow rate required for defrosting each heat exchanger has been studied.
For example, Patent Document 1 discloses that the temperatures of the heat exchangers detected by the heat exchange temperature detecting means are compared and the refrigerant flow rate is controlled by the opening of the electric expansion valve. Patent Document 2 discloses that the temperatures of the upper and lower paths of the heat exchanger are detected and the refrigerant flow rate is adjusted by the opening of the expansion valve in accordance with the temperature difference.
特開平５－３２２３８８号公報JP-A-5-322388 特開２００２－８９９８０号公報JP 2002-89980 A
　上記特許文献１及び２に開示された発明では、いずれも熱交換器の温度を検出し、この温度に基づき膨張弁の開度を調節し、各熱交換器（または熱交換器内の上下パス）の冷媒流量を調整している。しかし、各熱交換器の温度を検知し膨張弁を調整するため、膨張弁の応答遅れにより除霜を効果的に均一化することが困難であり、除霜時間の短縮につながっていなかった。 In each of the inventions disclosed in Patent Documents 1 and 2, the temperature of the heat exchanger is detected, the opening of the expansion valve is adjusted based on this temperature, and each heat exchanger (or the upper and lower paths in the heat exchanger) is detected. ) Refrigerant flow rate is adjusted. However, since the temperature of each heat exchanger is detected and the expansion valve is adjusted, it is difficult to effectively equalize the defrost due to the response delay of the expansion valve, and the defrost time has not been shortened.
　本発明は、このような事情に鑑みてなされたものであって、容積の異なる熱交換器における除霜時間を短縮可能なマルチ型空気調和機の制御装置、マルチ型空気調和機、マルチ型空気調和機の制御方法及びマルチ型空気調和機の制御プログラムを提供することを目的とする。 The present invention has been made in view of such circumstances, and is a multi-type air conditioner control device, a multi-type air conditioner, and a multi-type air capable of shortening the defrosting time in heat exchangers having different volumes. It is an object of the present invention to provide a control method for a conditioner and a control program for a multi-type air conditioner.
　上記課題を解決するために、本発明のマルチ型空気調和機の制御装置、マルチ型空気調和機、マルチ型空気調和機の制御方法及びマルチ型空気調和機の制御プログラムは以下の手段を採用する。
　本発明の第一態様に係るマルチ型空気調和機の制御装置は、少なくとも一つの熱交換器の容積が他の熱交換器の容積と異なる複数の前記熱交換器を備えた室外機と、複数の室内機と、を備えたマルチ型空気調和機の制御装置であって、複数の前記熱交換器は、夫々、該熱交換器に供給される冷媒流量を調整する流量調整装置を備え、除霜運転時に、複数の前記熱交換器の前記容積に応じて各前記熱交換器に供給される冷媒流量を前記流量調整装置の制御により調整する。 In order to solve the above problems, the control device for a multi-type air conditioner, the multi-type air conditioner, the control method for the multi-type air conditioner, and the control program for the multi-type air conditioner of the present invention employ the following means. .
The control apparatus for a multi-type air conditioner according to the first aspect of the present invention includes: an outdoor unit including a plurality of heat exchangers, wherein the volume of at least one heat exchanger is different from the volume of other heat exchangers; A plurality of the heat exchangers, each of which includes a flow rate adjusting device for adjusting the flow rate of the refrigerant supplied to the heat exchanger. During the frost operation, the refrigerant flow rate supplied to each heat exchanger is adjusted by the control of the flow rate adjusting device according to the volumes of the plurality of heat exchangers.
　本態様によれば、少なくとも一つの熱交換器の容積が異なる複数の熱交換器を備えた室外機と、複数の室内機とを備えたマルチ型空気調和機の制御装置が、除霜運転時に各熱交換器の容積に応じて冷媒流量を制御する。これにより、各熱交換器の除霜を略同時に完了することができる。例えば容積の異なる複数の熱交換器に同量の冷媒が供給された場合に、一の熱交換器のみ除霜が完了しても、この熱交換器に対して再着霜を防止するため冷媒を循環させておく必要がある。すなわち、除霜の完了タイミングが異なると、再着霜防止のために循環させる分の冷媒のロスが発生する。そこで、各熱交換器の容積に応じて冷媒流量を制御することで、各熱交換器の除霜が略同時に完了する。これにより、冷媒を再着霜防止のために循環させる必要がなく、除霜に必要とする冷媒流量を低減することができる。
　また、除霜が完了した熱交換器に冷媒が流れ続けると、除霜中の熱交換器に対する冷媒流量が制限されることから除霜運転が長期化する場合がある。しかし本態様によれば、流量調整装置により各熱交換器が必要とする冷媒流量がそれぞれ分配されるため、各熱交換器の除霜が略同時に完了し除霜運転が早期に終了する。
　また、熱交換器温度により制御する場合は、除霜による熱交換器温度が安定するまでに時間を要し、また着霜の有無が温度に反映されるまでに時間を要すると考えられる。これに対して各熱交換器の容積は事前に取得可能な数値であり、除霜運転開始時から制御を行うことができ、除霜に必要な時間を短縮することができる。 According to this aspect, the control device for the multi-type air conditioner including the outdoor unit including a plurality of heat exchangers having different volumes of at least one heat exchanger and the plurality of indoor units is used during the defrosting operation. The refrigerant flow rate is controlled according to the volume of each heat exchanger. Thereby, defrosting of each heat exchanger can be completed substantially simultaneously. For example, when the same amount of refrigerant is supplied to a plurality of heat exchangers having different volumes, even if defrosting is completed for only one heat exchanger, the refrigerant is used to prevent re-frosting on this heat exchanger. Must be circulated. That is, if the defrosting completion timing is different, a loss of refrigerant that is circulated to prevent re-frosting occurs. Therefore, by controlling the refrigerant flow rate according to the volume of each heat exchanger, the defrosting of each heat exchanger is completed substantially simultaneously. Thereby, it is not necessary to circulate a refrigerant | coolant in order to prevent re-frost formation, and the refrigerant | coolant flow volume required for a defrost can be reduced.
In addition, if the refrigerant continues to flow through the heat exchanger that has been defrosted, the refrigerant flow to the heat exchanger that is being defrosted is limited, so the defrosting operation may be prolonged. However, according to this aspect, since the flow rate of the refrigerant required by each heat exchanger is distributed by the flow rate adjusting device, the defrosting of each heat exchanger is completed almost simultaneously, and the defrosting operation is completed early.
Moreover, when controlling by heat exchanger temperature, it is thought that time is required until the heat exchanger temperature by defrost is stabilized, and it takes time until the presence or absence of frost formation is reflected in temperature. On the other hand, the volume of each heat exchanger is a numerical value that can be acquired in advance, can be controlled from the start of the defrosting operation, and the time required for defrosting can be shortened.
　上記第一態様では、前記流量調整装置は、電動膨張弁を備え、複数の前記熱交換器は、該熱交換器の熱交換器温度を検知する温度センサを夫々備え、全ての前記熱交換器の前記熱交換器温度が除霜完了の基準値となる除霜完了温度に略同時に到達するように複数の前記熱交換器の前記電動膨張弁の開度を決定する弁開度決定制御としてもよい。 In the first aspect, the flow rate adjusting device includes an electric expansion valve, and the plurality of heat exchangers each include a temperature sensor that detects a heat exchanger temperature of the heat exchanger, and all the heat exchangers As the valve opening degree determination control for determining the opening degrees of the electric expansion valves of the plurality of heat exchangers so that the heat exchanger temperature reaches the defrosting completion temperature that is the reference value for completion of defrosting at substantially the same time. Good.
　本態様によれば、容積の異なる複数の熱交換器が備えられた空気調和機において、容積の違いにより除霜に必要となる冷媒流量が異なることで、同一の冷媒流量とすると除霜が完了するタイミングが異なる。各熱交換器の熱交換器温度が同時に除霜完了温度に到達するように電動膨張弁の開度を調整し冷媒流量の制御を行うことから、熱交換器の容積に応じて冷媒流量を制御する際に、除霜完了温度を基準として各熱交換器に対し電動膨張弁の開度を設定する。具体的には、各熱交換器が略同時に除霜完了温度に到達するように、事前に各熱交換器の冷媒流量の比を決定し、これに基づき各電動膨張弁の開度を設定する。容積の異なる複数の熱交換器が備えられたマルチ型空気調和機においても、各熱交換器の除霜が同時に完了するため、除霜に必要とする冷媒流量を低減することができる。 According to this aspect, in the air conditioner provided with a plurality of heat exchangers having different volumes, the defrosting is completed when the refrigerant flow rate required for defrosting varies depending on the volume, so that the same refrigerant flow rate is obtained. The timing to do is different. The refrigerant flow rate is controlled according to the volume of the heat exchanger because the opening of the electric expansion valve is adjusted and the refrigerant flow rate is controlled so that the heat exchanger temperature of each heat exchanger reaches the defrosting completion temperature at the same time. In doing so, the opening degree of the electric expansion valve is set for each heat exchanger based on the defrosting completion temperature. Specifically, the ratio of the refrigerant flow rate of each heat exchanger is determined in advance so that the heat exchangers reach the defrosting completion temperature substantially simultaneously, and the opening degree of each electric expansion valve is set based on the ratio. . Even in a multi-type air conditioner provided with a plurality of heat exchangers having different volumes, the defrosting of each heat exchanger is completed at the same time, so that the refrigerant flow rate required for the defrosting can be reduced.
　上記第一態様では、一以上の前記熱交換器の前記熱交換器温度が前記除霜完了温度以上となった場合、該熱交換器の前記電動膨張弁の開度を最小開度としてもよい。 In the first aspect, when the heat exchanger temperature of one or more of the heat exchangers is equal to or higher than the defrosting completion temperature, the opening degree of the electric expansion valve of the heat exchanger may be a minimum opening degree. .
　容積の異なる複数の熱交換器において、同時に除霜が完了するように制御を行う場合でも、様々な要因により除霜完了のタイミングが異なる場合が考えられる。他の熱交換器よりも早く除霜が完了した熱交換器が存在する場合、除霜完了前と同じ量の冷媒流量の供給は必要がなく、無駄である。そこで、本態様では、除霜が完了した熱交換器、すなわち熱交換器温度が除霜完了温度以上となった熱交換器については、その電動膨張弁の開度を最小開度とする。これにより、冷媒流量を最小化することができ、他の除霜が完了していない熱交換器へ冷媒をより多く供給することができ、複数の熱交換器全体の除霜にかかる時間を早めることができる。また、膨張弁を全閉ではなく最小開度とすることから、再着霜を最小限に防ぐことができる。
　ここで、最小開度とは、除霜が完了した室外熱交換器が再着霜しない程度の微量の冷媒を流入させる程度の開度であり、例えば６０パルス程度である。 Even in the case where control is performed so that defrosting is completed at the same time in a plurality of heat exchangers having different volumes, the timing of defrosting completion may be different due to various factors. When there is a heat exchanger in which defrosting is completed earlier than other heat exchangers, it is unnecessary to supply the same amount of refrigerant flow as before completion of defrosting, which is useless. So, in this aspect, about the heat exchanger by which defrost was completed, ie, the heat exchanger whose heat exchanger temperature became more than defrost completion temperature, the opening degree of the electric expansion valve is made into the minimum opening degree. Thereby, a refrigerant | coolant flow volume can be minimized, more refrigerant | coolants can be supplied to the heat exchanger which has not completed the other defrosting, and the time concerning the defrosting of the whole several heat exchanger is advanced. be able to. In addition, since the expansion valve is set to the minimum opening instead of being fully closed, re-frosting can be prevented to the minimum.
Here, the minimum opening is an opening that allows a very small amount of refrigerant to flow in so that the outdoor heat exchanger that has completed defrosting does not refrost, and is, for example, about 60 pulses.
　上記第一態様では、前記熱交換器の前記電動膨張弁の開度を最小開度とした後、前記熱交換器温度が前記除霜完了温度未満となった場合、該熱交換器の前記電動膨張弁の開度を漸増させるとしてもよい。 In said 1st aspect, after making the opening degree of the said electric expansion valve of the said heat exchanger into the minimum opening degree, when the said heat exchanger temperature becomes less than the said defrost completion temperature, the said electric drive of this heat exchanger The opening degree of the expansion valve may be gradually increased.
　除霜が完了し電動膨張弁の開度を最小開度とした熱交換器において、冷媒流量が最小となるため再着霜する虞がある。これに対し、本態様では、該当の熱交換器の熱交換器温度が除霜完了温度未満となると、再着霜する虞があるとし、電動膨張弁の開度を漸増させる。これにより、冷媒流量が増加していくことで熱交換器の着霜を防ぐことができる。 In the heat exchanger in which the defrosting is completed and the opening degree of the electric expansion valve is set to the minimum opening degree, the refrigerant flow rate is minimized, so that there is a possibility of refrosting. On the other hand, in this aspect, when the heat exchanger temperature of the corresponding heat exchanger becomes lower than the defrosting completion temperature, it is assumed that there is a possibility of refrosting, and the opening degree of the electric expansion valve is gradually increased. Thereby, frost formation of the heat exchanger can be prevented by increasing the refrigerant flow rate.
　上記第一態様では、一の前記熱交換器の前記熱交換器温度のみが前記除霜完了温度未満である場合、該熱交換器の前記電動膨張弁の開度を全開とするとしてもよい。 In the first aspect, when only the heat exchanger temperature of one of the heat exchangers is lower than the defrosting completion temperature, the opening degree of the electric expansion valve of the heat exchanger may be fully opened.
　容積の異なる複数の熱交換器において、同時に除霜が完了するように制御を行う場合でも、様々な要因により除霜完了のタイミングが異なる場合が考えられる。他の熱交換器が全て除霜完了し、除霜完了していない熱交換器が一台のみ存在する場合、他の熱交換器の電動膨張弁は最小開度となり冷媒の供給量には余裕があることになる。しかし、除霜完了していない熱交換器の電動膨張弁の開度が変わらず一定であれば冷媒流量の供給は増えず除霜に時間がかかる。そこで本態様では、除霜完了していない熱交換器が一台のみとなった場合は、その熱交換器の電動膨張弁の開度を全開とする。これにより、余剰の冷媒を除霜が完了していない熱交換器へ最大量供給することでき、除霜にかかる時間を短縮することができる。 Even in the case where control is performed so that defrosting is completed at the same time in a plurality of heat exchangers having different volumes, the timing of defrosting completion may be different due to various factors. When all the other heat exchangers have been defrosted and there is only one heat exchanger that has not been defrosted, the electric expansion valves of the other heat exchangers have the minimum opening, and there is a margin in the refrigerant supply amount. There will be. However, if the opening degree of the electric expansion valve of the heat exchanger that has not been defrosted remains the same, the supply of the refrigerant flow rate does not increase and defrosting takes time. Therefore, in this aspect, when only one heat exchanger has not been defrosted, the opening degree of the electric expansion valve of the heat exchanger is fully opened. As a result, the maximum amount of surplus refrigerant can be supplied to the heat exchanger that has not been defrosted, and the time required for defrosting can be shortened.
　上記第一態様では、前記弁開度決定制御は、工場からの出荷時または試運転時に実施され、前記電動膨張弁の開度が記憶手段に記憶されるとしてもよい。 In the first aspect, the valve opening determination control may be performed at the time of shipment from a factory or during a trial operation, and the opening of the electric expansion valve may be stored in a storage unit.
　本態様によれば、基準となる電動膨張弁の弁開度の決定制御が、工場からの出荷時または試運転時に実施され、その開度が記憶手段に記憶される。これにより、冷媒流量を、通常の空調運転を開始する前の試運転時や、工場からの出荷時等に実施される弁開度の決定制御時に、適正に記憶させることができる。従って、通常の空調運転時に、その基準となる開度に基づいて冷媒流量が供給されるため、容積の異なる複数の熱交換器を有する空調機においても除霜を同時に完了させることができる。 According to this aspect, the control for determining the opening degree of the electric expansion valve serving as a reference is performed at the time of shipment from the factory or at the time of trial operation, and the opening degree is stored in the storage means. Thus, the refrigerant flow rate can be properly stored at the time of trial operation before starting normal air-conditioning operation or at the time of valve opening determination control performed at the time of shipment from the factory. Therefore, since the refrigerant flow rate is supplied based on the reference opening during normal air conditioning operation, defrosting can be completed simultaneously even in an air conditioner having a plurality of heat exchangers with different volumes.
　本発明の第二態様に係るマルチ型空気調和機は、少なくとも一つの熱交換器の容積が他の熱交換器の容積と異なる複数の前記熱交換器を備えた室外機と、複数の室内機と、上述のいずれかに記載の制御装置とを備える。 The multi-type air conditioner according to the second aspect of the present invention includes an outdoor unit including a plurality of heat exchangers having a volume of at least one heat exchanger different from that of other heat exchangers, and a plurality of indoor units And a control device according to any of the above.
　本発明の第三態様に係るマルチ型空気調和機の制御方法は、少なくとも一つの熱交換器の容積が他の熱交換器の容積と異なる複数の前記熱交換器を備えた室外機と、複数の室内機と、を備えたマルチ型空気調和機の制御方法であって、前記複数の熱交換器は、夫々、該熱交換器に供給される冷媒流量を調整する流量調整装置を備え、除霜運転時に、複数の前記熱交換器の前記容積に応じて各前記熱交換器に供給される冷媒流量を前記流量調整装置の制御により調整する工程を備える。 A control method for a multi-type air conditioner according to the third aspect of the present invention includes: an outdoor unit including a plurality of heat exchangers, wherein the volume of at least one heat exchanger is different from the volume of other heat exchangers; A plurality of heat exchangers, each of the plurality of heat exchangers including a flow rate adjusting device for adjusting a flow rate of refrigerant supplied to the heat exchanger. A step of adjusting the flow rate of the refrigerant supplied to each of the heat exchangers according to the volume of the plurality of heat exchangers during the frost operation is controlled by the flow rate adjusting device.
　本発明の第四態様に係るマルチ型空気調和機の制御プログラムは、少なくとも一つの熱交換器の容積が他の熱交換器の容積と異なる複数の前記熱交換器を備えた室外機と、複数の室内機と、を備えたマルチ型空気調和機の制御プログラムであって、前記複数の熱交換器は、夫々、該熱交換器に供給される冷媒流量を調整する流量調整装置を備え、除霜運転時に、複数の前記熱交換器の前記容積に応じて各前記熱交換器に供給される冷媒流量を前記流量調整装置の制御により調整するステップを備える。 A control program for a multi-type air conditioner according to a fourth aspect of the present invention includes: an outdoor unit including a plurality of the heat exchangers, wherein the volume of at least one heat exchanger is different from the volume of other heat exchangers; A plurality of heat exchangers, each of which includes a flow rate adjusting device for adjusting a flow rate of refrigerant supplied to the heat exchanger. A step of adjusting the flow rate of the refrigerant supplied to each of the heat exchangers according to the volume of the plurality of heat exchangers during the frost operation by the control of the flow rate adjusting device;
　本発明によれば、除霜運転において、容積の異なる各熱交換器の容積に基づき流量調整装置の制御を行うことにより各冷媒流量を調整するので、各熱交換器の除霜を略同時に完了させることで除霜時間を短縮することができる。 According to the present invention, in the defrosting operation, the flow rate of each refrigerant is adjusted by controlling the flow rate adjusting device based on the volume of each heat exchanger having a different volume, so that the defrosting of each heat exchanger is completed almost simultaneously. By making it, defrosting time can be shortened.
本発明の第１実施形態に係るマルチ型空気調和機の暖房運転を示した冷媒回路図である。It is the refrigerant circuit figure which showed the heating operation of the multi type air conditioner which concerns on 1st Embodiment of this invention. 本発明の第１実施形態に係るマルチ型空気調和機の除霜運転を示した冷媒回路図である。It is the refrigerant circuit figure which showed the defrost operation of the multi type air conditioner which concerns on 1st Embodiment of this invention. 本発明の第１実施形態に係るマルチ型空気調和機の各熱交換器の除霜運転時の冷媒流量を示したブロック図である。It is the block diagram which showed the refrigerant | coolant flow rate at the time of the defrost driving | operation of each heat exchanger of the multi type air conditioner which concerns on 1st Embodiment of this invention. 本発明の第１実施形態に係るマルチ型空気調和機の各熱交換器の除霜完了時の冷媒流量を示したブロック図である。It is the block diagram which showed the refrigerant | coolant flow rate at the time of completion | finish of defrosting of each heat exchanger of the multi type air conditioner which concerns on 1st Embodiment of this invention. 本発明の第２実施形態に係るマルチ型空気調和機の制御装置による除霜運転時の電動膨張弁の制御を示したフローチャートである。It is the flowchart which showed control of the electric expansion valve at the time of the defrost operation by the control apparatus of the multi type air conditioner which concerns on 2nd Embodiment of this invention. 本発明の第２実施形態に係るマルチ型空気調和機の各熱交換器の除霜均一化時の冷媒流量を示したブロック図である。It is the block diagram which showed the refrigerant | coolant flow rate at the time of defrost uniformization of each heat exchanger of the multi type air conditioner which concerns on 2nd Embodiment of this invention.
　以下に、本発明に係るマルチ型空気調和機の制御装置、マルチ型空気調和機、マルチ型空気調和機の制御方法及びマルチ型空気調和機の制御プログラムの一実施形態について、図面を参照して説明する。 DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of a control device for a multi-type air conditioner, a multi-type air conditioner, a control method for a multi-type air conditioner, and a control program for a multi-type air conditioner according to the present invention will be described below with reference to the drawings. explain.
〔第１実施形態〕
　以下、本発明の第１実施形態について、図１乃至図４を用いて説明する。
　図１には、本実施形態に係るマルチ型空気調和機の暖房運転時の冷媒回路図が示されている。
　マルチ型空気調和機１は、１台の室外機２に、複数台の室内機３Ａ及び３Ｂが並列に接続されたものである。複数台の室内機３Ａ及び３Ｂは、室外機２に接続されているガス側配管４と液側配管５との間に分岐器６を介して互いに並列に接続されている。 [First Embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 to 4.
FIG. 1 shows a refrigerant circuit diagram during heating operation of the multi-type air conditioner according to the present embodiment.
In the multi-type air conditioner 1, a plurality of indoor units 3A and 3B are connected to a single outdoor unit 2 in parallel. The plurality of indoor units 3 </ b> A and 3 </ b> B are connected in parallel to each other via a branching device 6 between a gas side pipe 4 and a liquid side pipe 5 connected to the outdoor unit 2.
　室外機２は、冷媒を圧縮するインバータ駆動の圧縮機１０と、冷媒の循環方向を切換える四方切換弁１２と、冷媒と外気とを熱交換させる複数の室外熱交換器（熱交換器）１３Ａ、１３Ｂ及び１３Ｃと、室外熱交換器１３Ａ、１３Ｂ及び１３Ｃの各熱交換器温度を検出する室外熱交換器温度センサ（温度センサ）１４Ａ、１４Ｂ及び１４Ｃと、室外熱交換器１３Ａ、１３Ｂ及び１３Ｃの各冷媒流量を調整する室外膨張弁（電動膨張弁：ＥＥＶＨ）（流量調整装置）１５Ａ、１５Ｂ及び１５Ｃと、液冷媒を貯留するレシーバ１６と、液冷媒に過冷却を与える過冷却熱交換器１７と、過冷却熱交換器１７に分流される冷媒量を制御する過冷却用膨張弁（ＥＥＶＳＣ）１８と、圧縮機１０に吸入される冷媒ガスから液分を分離し、ガス分のみを圧縮機１０側に吸入させるアキュームレータ１９と、ガス側操作弁２０と、液側操作弁２１とを備えている。
　本実施形態では、各室外熱交換器１３Ａ、１３Ｂ及び１３Ｃの容積はそれぞれ異なる。 The outdoor unit 2 includes an inverter-driven compressor 10 that compresses the refrigerant, a four-way switching valve 12 that switches the circulation direction of the refrigerant, and a plurality of outdoor heat exchangers (heat exchangers) 13A that exchange heat between the refrigerant and the outside air. 13B and 13C, outdoor heat exchanger temperature sensors (temperature sensors) 14A, 14B and 14C for detecting the heat exchanger temperatures of the outdoor heat exchangers 13A, 13B and 13C, and the outdoor heat exchangers 13A, 13B and 13C Outdoor expansion valves (electric expansion valves: EEVH) (flow rate adjusting devices) 15A, 15B and 15C for adjusting the flow rate of each refrigerant, a receiver 16 for storing liquid refrigerant, and a supercooling heat exchanger 17 for supercooling the liquid refrigerant. And a supercooling expansion valve (EEVSC) 18 that controls the amount of refrigerant diverted to the supercooling heat exchanger 17, and a liquid component separated from the refrigerant gas sucked into the compressor 10, and only the gas component is compressed. And accumulator 19 and to be taken to 10 side, a gas-side operation valve 20, and a liquid-side operation valve 21.
In the present embodiment, the volumes of the outdoor heat exchangers 13A, 13B, and 13C are different.
　図１及び図２では、３台の室外熱交換器１３Ａ、１３Ｂ及び１３Ｃが設置されている場合について例示しているが、設置台数については任意に決定することができる。
　以下の説明において、各室外熱交換器１３を区別する場合は、末尾にＡ、ＢまたはＣのいずれかを付し、各室外熱交換器１３を区別しない場合は、Ａ、ＢまたはＣを省略する。また、各室外熱交換器温度センサ１４を区別する場合は、末尾にＡ、ＢまたはＣのいずれかを付し、各室外熱交換器温度センサ１４を区別しない場合は、Ａ、ＢまたはＣを省略する。また、各室外膨張弁１５を区別する場合は、末尾にＡ、ＢまたはＣのいずれかを付し、各室外膨張弁１５を区別しない場合は、Ａ、ＢまたはＣを省略する。 Although FIG. 1 and FIG. 2 illustrate the case where three outdoor heat exchangers 13A, 13B, and 13C are installed, the number of installed units can be arbitrarily determined.
In the following description, when distinguishing each outdoor heat exchanger 13, either A, B or C is added at the end, and when not distinguishing each outdoor heat exchanger 13, A, B or C is omitted. To do. Moreover, when distinguishing each outdoor heat exchanger temperature sensor 14, it attaches either A, B, or C to the end, and when not distinguishing each outdoor heat exchanger temperature sensor 14, A, B, or C is used. Omitted. Moreover, when distinguishing each outdoor expansion valve 15, either A, B, or C is attached | subjected to the end, and when not distinguishing each outdoor expansion valve 15, A, B, or C is abbreviate | omitted.
　室外機２側の上記各機器は、冷媒配管２２を介して順次接続され、公知の室外側冷媒回路２３を構成している。また、室外機２には、各室外熱交換器１３に対して外気を送風する室外ファン（図示せず）が設けられている。 The above devices on the outdoor unit 2 side are sequentially connected via a refrigerant pipe 22 to constitute a known outdoor refrigerant circuit 23. Further, the outdoor unit 2 is provided with an outdoor fan (not shown) that blows outside air to each outdoor heat exchanger 13.
　ガス側配管４及び液側配管５は、室外機２のガス側操作弁２０及び液側操作弁２１に接続される冷媒配管であり、現場での据え付け施工時に、室外機２とそれに接続される複数台の室内機３Ａ及び３Ｂとの間の距離に応じて、その配管長が適宜設定されるようになっている。ガス側配管４及び液側配管５の途中には、複数の分岐器６が設けられ、該分岐器６を介して適宜台数の室内機３Ａ及び３Ｂが接続されている。これによって、密閉された１系統の冷凍サイクル（冷媒回路）７が構成されている。 The gas side pipe 4 and the liquid side pipe 5 are refrigerant pipes connected to the gas side operation valve 20 and the liquid side operation valve 21 of the outdoor unit 2, and are connected to the outdoor unit 2 and to it during installation on site. The pipe length is appropriately set according to the distance between the plurality of indoor units 3A and 3B. A plurality of branching devices 6 are provided in the middle of the gas side piping 4 and the liquid side piping 5, and an appropriate number of indoor units 3 </ b> A and 3 </ b> B are connected via the branching devices 6. Thereby, one sealed refrigeration cycle (refrigerant circuit) 7 is configured.
　室内機３Ａ及び３Ｂは、室内空気を冷媒と熱交換させて冷却又は加熱し、室内の空調に供する室内熱交換器３０と、室内膨張弁（ＥＥＶＣ）３１と、室内熱交換器３０を介して室内空気を循環させる室内ファン３２と、室内コントローラ３３とを備えており、室内側の分岐ガス側配管４Ａ及び４Ｂ及び分岐液側配管５Ａ及び５Ｂを介して分岐器６に接続されている。 The indoor units 3 </ b> A and 3 </ b> B exchange or heat indoor air with a refrigerant to cool or heat the indoor unit 3 </ b> A through an indoor heat exchanger 30, an indoor expansion valve (EEVC) 31, and an indoor heat exchanger 30. An indoor fan 32 that circulates indoor air and an indoor controller 33 are provided, and are connected to the branching device 6 via branch gas side pipes 4A and 4B and branch liquid side pipes 5A and 5B on the indoor side.
　制御装置５０は、室内コントローラ３３による設定値や冷媒温度等を取得し、四方切換弁１２の切替制御、各弁の開閉又は開度の制御等を行う。
　制御装置５０は、例えば、ＣＰＵ（Central　Processing　Unit）、ＲＡＭ（Random　Access　Memory）、ＲＯＭ（Read　Only　Memory）、及びコンピュータ読み取り可能な記憶媒体等から構成されている。そして、各種機能を実現するための一連の処理は、一例として、プログラムの形式で記憶媒体等に記憶されており、このプログラムをＣＰＵがＲＡＭ等に読み出して、情報の加工・演算処理を実行することにより、各種機能が実現される。なお、プログラムは、ＲＯＭやその他の記憶媒体に予めインストールしておく形態や、コンピュータ読み取り可能な記憶媒体に記憶された状態で提供される形態、有線又は無線による通信手段を介して配信される形態等が適用されてもよい。コンピュータ読み取り可能な記憶媒体とは、磁気ディスク、光磁気ディスク、ＣＤ－ＲＯＭ、ＤＶＤ－ＲＯＭ、半導体メモリ等である。 The control device 50 acquires a set value, a refrigerant temperature, and the like by the indoor controller 33, and performs switching control of the four-way switching valve 12, opening / closing of each valve, opening degree control, and the like.
The control device 50 includes, for example, a CPU (Central Processing Unit), a RAM (Random Access Memory), a ROM (Read Only Memory), and a computer-readable storage medium. A series of processes for realizing various functions is stored in a storage medium or the like in the form of a program as an example, and the CPU reads the program into a RAM or the like to execute information processing / arithmetic processing. As a result, various functions are realized. The program is preinstalled in a ROM or other storage medium, provided in a state stored in a computer-readable storage medium, or distributed via wired or wireless communication means. Etc. may be applied. Examples of the computer-readable storage medium include a magnetic disk, a magneto-optical disk, a CD-ROM, a DVD-ROM, and a semiconductor memory.
　上記のマルチ型空気調和機１において、暖房運転は、以下のように行われる。
　圧縮機１０により圧縮され、吐出された高温高圧の冷媒ガスは、四方切換弁１２を介してガス側操作弁２０側に循環される。この高圧ガス冷媒は、ガス側操作弁２０、ガス側配管４を経て室外機２から導出され、分岐器６、室内側の分岐ガス側配管４Ａ及び４Ｂを経て複数台の室内機３Ａ及び３Ｂに導入される。 In the multi-type air conditioner 1 described above, the heating operation is performed as follows.
The high-temperature and high-pressure refrigerant gas compressed and discharged by the compressor 10 is circulated to the gas-side operation valve 20 side through the four-way switching valve 12. The high-pressure gas refrigerant is led out from the outdoor unit 2 through the gas side operation valve 20 and the gas side pipe 4, and is supplied to the plurality of indoor units 3A and 3B through the branching unit 6, the indoor side branching gas side pipes 4A and 4B. be introduced.
　室内機３Ａ及び３Ｂに導入された高温高圧の冷媒ガスは、室内熱交換器３０で室内ファン３２を介して循環される室内空気と熱交換され、これにより加熱された室内空気は室内に吹出されて暖房に供される。一方、室内熱交換器３０で凝縮液化された冷媒は、室内膨張弁３１、分岐液側配管５Ａ及び５Ｂを経て分岐器６に至り、他の室内機からの冷媒と合流され、液側配管５を経て室外機２に戻る。なお、暖房時、室内機３Ａ及び３Ｂでは、凝縮器として機能する室内熱交換器３０の冷媒出口温度又は冷媒過冷却度が制御目標値となるように、室内膨張弁３１の開度が室内コントローラ３３を介して制御される。 The high-temperature and high-pressure refrigerant gas introduced into the indoor units 3A and 3B is heat-exchanged with the indoor air circulated through the indoor fan 32 in the indoor heat exchanger 30, and the heated indoor air is blown into the room. It is used for heating. On the other hand, the refrigerant condensed and liquefied in the indoor heat exchanger 30 reaches the branching device 6 through the indoor expansion valve 31 and the branch liquid side pipes 5A and 5B, and is merged with the refrigerant from other indoor units. After that, it returns to the outdoor unit 2. During heating, in the indoor units 3A and 3B, the opening degree of the indoor expansion valve 31 is set to the indoor controller so that the refrigerant outlet temperature or the refrigerant subcooling degree of the indoor heat exchanger 30 functioning as a condenser becomes the control target value. 33 is controlled.
　室外機２に戻った冷媒は、液側操作弁２１を経て過冷却熱交換器１７に至り液冷媒配管側を流通される過程で、液冷媒配管から一部分流され、過冷却用膨張弁１８で断熱膨張された冷媒と熱交換されて過冷却度が付与される。その後、レシーバ１６に流入され、いったん貯留されることにより循環量が調整される。この液冷媒は、各室外膨張弁１５に供給されて断熱膨張された後、各室外熱交換器１３に流入される。 The refrigerant that has returned to the outdoor unit 2 passes through the liquid side operation valve 21, reaches the supercooling heat exchanger 17, and flows through the liquid refrigerant pipe side in part. Heat exchange with the adiabatic expanded refrigerant provides a degree of supercooling. Thereafter, the amount of circulation is adjusted by flowing into the receiver 16 and once stored. This liquid refrigerant is supplied to each outdoor expansion valve 15 and adiabatically expanded, and then flows into each outdoor heat exchanger 13.
　各室外熱交換器１３では、室外ファンから送風される外気と冷媒とが熱交換され、冷媒は外気から吸熱して蒸発ガス化される。この冷媒は、各室外熱交換器１３から四方切換弁１２を経て、過冷却熱交換器１７からの冷媒ガスと合流された後、アキュームレータ１９に導入される。アキュームレータ１９では、冷媒ガス中に含まれている液分が分離されてガス分のみが圧縮機１０に吸入され、圧縮機１０において再び圧縮される。以上のサイクルを繰り返すことによって暖房運転が行われる。 In each outdoor heat exchanger 13, the outside air blown from the outdoor fan and the refrigerant are heat-exchanged, and the refrigerant absorbs heat from the outside air and is evaporated and gasified. This refrigerant is introduced from each outdoor heat exchanger 13 through the four-way switching valve 12 and the refrigerant gas from the supercooling heat exchanger 17 and then introduced into the accumulator 19. In the accumulator 19, the liquid component contained in the refrigerant gas is separated, and only the gas component is sucked into the compressor 10 and compressed again in the compressor 10. The heating operation is performed by repeating the above cycle.
　マルチ型空気調和機１における暖房運転時において、例えば外気温が低く湿度が高い場合、各室外熱交換器１３を流れる冷媒は各室外膨張弁１５により減圧されることで冷媒温度が低下するため、各室外熱交換器１３が着霜する虞がある。室外熱交換器１３が着霜すると、暖房能力が低下するため、この場合、四方切換弁１２を切り替えることにより、除霜運転を行う。
　除霜運転は、一般的には各室外熱交換器１３のいずれかの室外熱交換器温度センサ１４の検出温度が一定温度以下となった場合に作動するとしている。除霜運転作動となる温度は、各マルチ型空気調和機１によって異なるが、例えば０℃前後の値である。 At the time of heating operation in the multi-type air conditioner 1, for example, when the outside air temperature is low and the humidity is high, the refrigerant flowing through each outdoor heat exchanger 13 is decompressed by each outdoor expansion valve 15, thereby reducing the refrigerant temperature. Each outdoor heat exchanger 13 may be frosted. When the outdoor heat exchanger 13 is frosted, the heating capacity is reduced. In this case, the defrosting operation is performed by switching the four-way switching valve 12.
The defrosting operation is generally activated when the temperature detected by the outdoor heat exchanger temperature sensor 14 of each outdoor heat exchanger 13 is equal to or lower than a certain temperature. The temperature at which the defrosting operation is performed varies depending on each multi-type air conditioner 1, for example, a value around 0 ° C.
　図２には、本実施形態に係るマルチ型空気調和機の除霜運転時の冷媒回路図が示されている。
　上記のマルチ型空気調和機１において、除霜運転は、以下のように行われる。
　圧縮機１０で圧縮され、吐出された高温高圧の冷媒ガスは、四方切換弁１２により室外熱交換器１３側に循環され、各室外熱交換器１３で室外ファンにより送風される外気と熱交換されて凝縮液化される。この液冷媒は、各室外膨張弁１５を通過し、レシーバ１６内にいったん貯留される。
　このように、高温高圧の冷媒ガスが各室外熱交換器１３に流れることにより、除霜が行われる。 FIG. 2 shows a refrigerant circuit diagram during the defrosting operation of the multi-type air conditioner according to the present embodiment.
In the multi-type air conditioner 1 described above, the defrosting operation is performed as follows.
The high-temperature and high-pressure refrigerant gas compressed and discharged by the compressor 10 is circulated to the outdoor heat exchanger 13 side by the four-way switching valve 12, and is heat-exchanged with the outdoor air blown by the outdoor fan in each outdoor heat exchanger 13. Is condensed and liquefied. The liquid refrigerant passes through each outdoor expansion valve 15 and is temporarily stored in the receiver 16.
In this way, defrosting is performed by the high-temperature and high-pressure refrigerant gas flowing into each outdoor heat exchanger 13.
　レシーバ１６で循環量が調整された液冷媒は、過冷却熱交換器１７に至り、暖房時の場合と同様に過冷却が付与される。この液冷媒は、液側操作弁２１を経て室外機２から液側配管５へと導かれ、分岐器６を介して各室内機３Ａ及び３Ｂの分岐液側配管５Ａ及び５Ｂへと分流される。 The liquid refrigerant whose circulation amount is adjusted by the receiver 16 reaches the supercooling heat exchanger 17 and is supercooled in the same manner as in heating. This liquid refrigerant is guided from the outdoor unit 2 to the liquid side pipe 5 through the liquid side operation valve 21, and is divided into the branch liquid side pipes 5A and 5B of the indoor units 3A and 3B via the branching unit 6. .
　分岐液側配管５Ａ及び５Ｂに分流された液冷媒は、各室内機３Ａ及び３Ｂに流入し、室内膨張弁３１で断熱膨張され、気液二相流となって室内熱交換器３０に流入される。室内熱交換器３０では、冷媒はガス化され、分岐ガス側配管４Ａ及び４Ｂを経て分岐器６に至り、他の室内機からの冷媒ガスとガス側配管４で合流される。 The liquid refrigerant divided into the branch liquid side pipes 5A and 5B flows into the indoor units 3A and 3B, is adiabatically expanded by the indoor expansion valve 31, and flows into the indoor heat exchanger 30 as a gas-liquid two-phase flow. The In the indoor heat exchanger 30, the refrigerant is gasified, reaches the branching device 6 through the branch gas side pipes 4 </ b> A and 4 </ b> B, and merges with the refrigerant gas from the other indoor units in the gas side pipe 4.
　ガス側配管４で合流された冷媒ガスは、再び室外機２に戻り、ガス側操作弁２０、四方切換弁１２を経て、過冷却熱交換器１７からの冷媒ガスと合流された後、アキュームレータ１９に導入される。アキュームレータ１９では、冷媒ガス中に含まれている液分が分離され、ガス分のみが圧縮機１０に吸入される。この冷媒は、圧縮機１０において再び圧縮され、以上のサイクルを繰り返すことによって除霜運転が行われる。
　除霜運転は、一般的には除霜運転により全室外熱交換器１３の全室外熱交換器温度センサ１４の検出温度が一定温度以上となった場合に完了するとしている。除霜運転完了の基準値となる温度、すなわち除霜完了温度は、各マルチ型空気調和機１によって異なるが、例えば９℃前後の値である。 The refrigerant gas merged in the gas side pipe 4 returns to the outdoor unit 2 again, merges with the refrigerant gas from the supercooling heat exchanger 17 through the gas side operation valve 20 and the four-way switching valve 12, and then accumulator 19. To be introduced. In the accumulator 19, the liquid component contained in the refrigerant gas is separated, and only the gas component is sucked into the compressor 10. This refrigerant is compressed again in the compressor 10, and the defrosting operation is performed by repeating the above cycle.
The defrosting operation is generally completed when the temperature detected by the all-outdoor heat exchanger temperature sensor 14 of the all-outdoor heat exchanger 13 becomes equal to or higher than a certain temperature due to the defrosting operation. Although the temperature used as the reference value for the completion of the defrosting operation, that is, the defrosting completion temperature differs depending on each multi-type air conditioner 1, it is, for example, a value around 9 ° C.
　次に、図３及び４を用いて除霜運転時の室外膨張弁の開度制御について説明する。
　図３には、本発明の第１実施形態に係るマルチ型空気調和機の各熱交換器の除霜運転時の冷媒流量の概略がブロック図に示されている。
　また、図４には、本発明の第１実施形態に係るマルチ型空気調和機の各熱交換器の除霜完了時の冷媒流量の概略がブロック図に示されている。 Next, the opening degree control of the outdoor expansion valve during the defrosting operation will be described with reference to FIGS.
FIG. 3 is a block diagram schematically illustrating the refrigerant flow rate during the defrosting operation of each heat exchanger of the multi-type air conditioner according to the first embodiment of the present invention.
FIG. 4 is a block diagram showing an outline of the refrigerant flow rate at the completion of defrosting of each heat exchanger of the multi-type air conditioner according to the first embodiment of the present invention.
　除霜運転の開始にあたり、制御装置５０により、まず各室外熱交換器１３の容積に応じた室外膨張弁１５の開度が決定され、設定される弁開度設定制御が行われる。各室外熱交換器１３は、それぞれ容積が異なっており、各室外熱交換器１３の除霜を略同時に完了させるように、すなわち除霜完了温度にほぼ同時に到達するように制御するため、各容積比率により各室外熱交換器１３に流入する冷媒流量を決定する。決定された各冷媒流量に基づき、各室外熱交換器１３の各室外膨張弁１５の開度を決定し、その開度を各室外膨張弁１５に設定する。室外膨張弁１５の開度が設定された後、除霜運転は開始される。
　各室外熱交換器１３の容積は、管の内径、長さ及び本数により算出が可能である。本実施形態では、図３及び４に示すように、室外熱交換器１３Ａの容積が最も大きく、次いで室外熱交換器１３Ｂの容積、そして室外熱交換器１３Ｃの容積が最も小さいとする。
　図３に示されるように、室外熱交換器１３Ａの容積が最も大きいことから、室外熱交換器１３Ａに流入する冷媒の量が最も大きくなるように各容積比率に基づき求められる冷媒流量に応じた室外膨張弁１５Ａの開度が設定される。同様に、室外熱交換器１３Ｂ及び１３Ｃの各容積比率に基づき室外膨張弁１５Ｂ及び１５Ｃの開度も同時に設定される。各室外膨張弁１５の開度が設定されると、除霜運転が行われる。 At the start of the defrosting operation, the opening degree of the outdoor expansion valve 15 corresponding to the volume of each outdoor heat exchanger 13 is first determined by the control device 50, and the valve opening degree setting control to be set is performed. Since each outdoor heat exchanger 13 has a different volume, each outdoor heat exchanger 13 is controlled so that the defrosting of each outdoor heat exchanger 13 is completed substantially simultaneously, that is, the defrosting completion temperature is reached almost simultaneously. The flow rate of the refrigerant flowing into each outdoor heat exchanger 13 is determined by the ratio. Based on the determined refrigerant flow rates, the opening degree of each outdoor expansion valve 15 of each outdoor heat exchanger 13 is determined, and the opening degree is set in each outdoor expansion valve 15. After the opening degree of the outdoor expansion valve 15 is set, the defrosting operation is started.
The volume of each outdoor heat exchanger 13 can be calculated from the inner diameter, length, and number of tubes. In this embodiment, as shown in FIGS. 3 and 4, it is assumed that the volume of the outdoor heat exchanger 13A is the largest, the volume of the outdoor heat exchanger 13B, and the volume of the outdoor heat exchanger 13C are the smallest.
As shown in FIG. 3, since the volume of the outdoor heat exchanger 13A is the largest, the refrigerant flow rate determined based on each volume ratio is set so that the amount of refrigerant flowing into the outdoor heat exchanger 13A is maximized. The opening degree of the outdoor expansion valve 15A is set. Similarly, the opening degrees of the outdoor expansion valves 15B and 15C are set simultaneously based on the volume ratios of the outdoor heat exchangers 13B and 13C. When the opening degree of each outdoor expansion valve 15 is set, the defrosting operation is performed.
　各室外熱交換器１３の容積比率に基づき求められる各冷媒流量に応じた各室外膨張弁１５の開度の制御により、図４に示されるように、全ての室外熱交換器１３の各室外熱交換器温度センサ１４の検出する各熱交換器温度が除霜完了温度に略同時に到達し、除霜が完了する。 As shown in FIG. 4, the outdoor heat of all the outdoor heat exchangers 13 is controlled by controlling the opening degree of each outdoor expansion valve 15 according to each refrigerant flow rate obtained based on the volume ratio of each outdoor heat exchanger 13. The heat exchanger temperatures detected by the exchanger temperature sensor 14 reach the defrosting completion temperature almost simultaneously, and the defrosting is completed.
　ここで、本実施形態では、除霜運転の開始にあたりまず各室外熱交換器１３の容積に応じた室外膨張弁１５の開度を決定し、設定することとした。
　この室外膨張弁１５の開度の決定及び設定は、工場からの出荷時または試運転時に実施し、室外膨張弁１５の開度が制御装置５０の図示しない記憶手段に記憶されることとしてもよい。 Here, in this embodiment, the opening degree of the outdoor expansion valve 15 corresponding to the volume of each outdoor heat exchanger 13 is first determined and set at the start of the defrosting operation.
The determination and setting of the opening degree of the outdoor expansion valve 15 may be performed at the time of shipment from the factory or during a trial operation, and the opening degree of the outdoor expansion valve 15 may be stored in a storage unit (not shown) of the control device 50.
　以上、説明してきたように、本実施形態に係るマルチ型空気調和機の制御装置、マルチ型空気調和機、マルチ型空気調和機の制御方法及びマルチ型空気調和機の制御プログラムによれば、以下の作用効果を奏する。
　本実施形態によれば、少なくとも一つの室外熱交換器１３の容積が異なる複数の室外熱交換器１３を備えた室外機２と、複数の室内機３Ａ及び３Ｂとを備えたマルチ型空気調和機１の制御装置５０が、除霜運転時に各室外熱交換器１３の容積に応じて冷媒流量を制御する。これにより、各室外熱交換器１３の除霜を略同時に完了することができる。例えば容積の異なる複数の室外熱交換器１３に同量の冷媒が供給された場合に、一の室外熱交換器１３のみ除霜が完了しても、この室外熱交換器１３に対して再着霜を防止するため冷媒を循環させておく必要がある。すなわち、除霜の完了タイミングが異なると、再着霜防止のために循環させる分の冷媒のロスが発生する。そこで本実施形態では、各室外熱交換器１３の容積に応じて冷媒流量を制御することで、各室外熱交換器１３の除霜が略同時に完了することにより、冷媒を再着霜防止のために循環させる必要がなく、除霜に必要とする冷媒流量を低減することができる。 As described above, according to the control device for a multi-type air conditioner, the multi-type air conditioner, the control method for the multi-type air conditioner, and the control program for the multi-type air conditioner according to the present embodiment, Has the effect of.
According to the present embodiment, a multi-type air conditioner including an outdoor unit 2 including a plurality of outdoor heat exchangers 13 having different volumes of at least one outdoor heat exchanger 13 and a plurality of indoor units 3A and 3B. 1 control apparatus 50 controls a refrigerant | coolant flow volume according to the volume of each outdoor heat exchanger 13 at the time of a defrost operation. Thereby, defrosting of each outdoor heat exchanger 13 can be completed substantially simultaneously. For example, when the same amount of refrigerant is supplied to a plurality of outdoor heat exchangers 13 having different volumes, even if the defrosting is completed for only one outdoor heat exchanger 13, it is reattached to the outdoor heat exchanger 13. It is necessary to circulate the refrigerant in order to prevent frost. That is, if the defrosting completion timing is different, a loss of refrigerant that is circulated to prevent re-frosting occurs. Therefore, in the present embodiment, the refrigerant flow rate is controlled according to the volume of each outdoor heat exchanger 13 so that the defrosting of each outdoor heat exchanger 13 is completed almost simultaneously, thereby preventing the refrigerant from re-frosting. The refrigerant flow rate required for defrosting can be reduced.
　また、除霜が完了した室外熱交換器１３に冷媒が流れ続けると、除霜中の室外熱交換器１３に対する冷媒流量が制限されることから除霜運転が長期化する。本実施形態では、各室外膨張弁１５により各室外熱交換器１３が必要とする冷媒流量がそれぞれ分配されるため、各室外熱交換器１３の除霜が略同時に完了し除霜運転が早期に終了する。
　また、熱交換器温度により制御する場合は、除霜による熱交換器温度が安定するまでに時間を要し、また着霜の有無が温度に反映されるまでに時間を要すると考えられる。これに対して各室外熱交換器１３の容積は事前に取得可能な数値であり、本実施形態では除霜運転開始時から制御を行うことができ、除霜に必要な時間を短縮することができる。 Moreover, if a refrigerant | coolant continues flowing into the outdoor heat exchanger 13 in which defrost was completed, since the refrigerant | coolant flow volume with respect to the outdoor heat exchanger 13 in defrosting will be restrict | limited, defrost operation will be prolonged. In the present embodiment, the refrigerant flow required by each outdoor heat exchanger 13 is distributed by each outdoor expansion valve 15, so that the defrosting of each outdoor heat exchanger 13 is completed almost simultaneously and the defrosting operation is performed early. finish.
Moreover, when controlling by heat exchanger temperature, it is thought that time is required until the heat exchanger temperature by defrost is stabilized, and it takes time until the presence or absence of frost formation is reflected in temperature. On the other hand, the volume of each outdoor heat exchanger 13 is a numerical value that can be acquired in advance. In the present embodiment, control can be performed from the start of the defrosting operation, and the time required for defrosting can be shortened. it can.
　容積の異なる複数の室外熱交換器１３が備えられたマルチ型空気調和機１において、容積の違いにより除霜に必要となる冷媒流量が異なることで、同一の冷媒流量とすると除霜が完了するタイミングが異なる。本実施形態によれば、各室外熱交換器１３の熱交換器温度が同時に除霜完了温度に到達するように各室外膨張弁１５の開度を調整し冷媒流量の制御を行うことから、各室外熱交換器１３の容積に応じて冷媒流量を制御する際に、除霜完了温度を基準として各室外熱交換器１３に対し室外膨張弁１５の開度を設定する。具体的には、各室外熱交換器１３が略同時に除霜完了温度に到達するように、事前に各室外熱交換器１３の冷媒流量の比を各室外熱交換器１３の容積比率をもとに決定し、これに基づき各室外膨張弁１５の開度を設定する。容積の異なる複数の室外熱交換器１３が備えられた空気調和機においても、各室外熱交換器１３の除霜が同時に完了するため、除霜に必要とする冷媒流量を低減することができる。 In the multi-type air conditioner 1 provided with a plurality of outdoor heat exchangers 13 having different volumes, the defrosting is completed when the refrigerant flow rate required for defrosting is different due to the difference in volume, so that the same refrigerant flow rate is obtained. The timing is different. According to this embodiment, the refrigerant flow rate is controlled by adjusting the opening of each outdoor expansion valve 15 so that the heat exchanger temperature of each outdoor heat exchanger 13 reaches the defrosting completion temperature at the same time. When the refrigerant flow rate is controlled according to the volume of the outdoor heat exchanger 13, the opening degree of the outdoor expansion valve 15 is set for each outdoor heat exchanger 13 with reference to the defrosting completion temperature. Specifically, the ratio of the refrigerant flow rate of each outdoor heat exchanger 13 is determined in advance based on the volume ratio of each outdoor heat exchanger 13 so that each outdoor heat exchanger 13 reaches the defrosting completion temperature substantially simultaneously. Based on this, the opening degree of each outdoor expansion valve 15 is set. Even in an air conditioner provided with a plurality of outdoor heat exchangers 13 having different volumes, the defrosting of the outdoor heat exchangers 13 is completed at the same time, so that the refrigerant flow rate required for defrosting can be reduced.
　本実施形態では、基準となる各室外膨張弁１５の弁開度決定制御が、工場からの出荷時または試運転時に実施されその開度が記憶手段に記憶されるため、各冷媒流量を、通常の空調運転を開始する前の試運転時や工場からの出荷時等に実施される弁開度決定制御時に適正に記憶させることができる。従って、通常の空調運転時に、その基準となる開度に基づいて冷媒流量が供給されるため、除霜運転を迅速に開始することができ、また容積の異なる複数の室外熱交換器１３を有するマルチ型空気調和機１においても除霜を略同時に完了させることができる。 In the present embodiment, the valve opening determination control of each outdoor expansion valve 15 serving as a reference is performed at the time of shipment from the factory or at the time of trial operation, and the opening is stored in the storage means. It can be appropriately stored during the valve opening determination control that is performed at the time of trial operation before starting the air-conditioning operation or at the time of shipment from the factory. Accordingly, since the refrigerant flow rate is supplied based on the reference opening during normal air-conditioning operation, the defrosting operation can be started quickly, and a plurality of outdoor heat exchangers 13 having different volumes are provided. Also in the multi-type air conditioner 1, defrosting can be completed substantially simultaneously.
〔第２実施形態〕
　以下、本発明の第２実施形態について、図５及び６を用いて説明する。
　上記した第１実施形態では、除霜運転の開始にあたり各室外熱交換器の容積比率に基づき室外膨張弁の開度を設定し除霜を略同時に完了させるとしたが、本実施形態では、除霜運転が同時に完了しない場合に室外膨張弁の開度を制御するものである。その他の点については第１実施形態と同様であるので、同様の構成については同一符号を付しその説明は省略する。 [Second Embodiment]
Hereinafter, a second embodiment of the present invention will be described with reference to FIGS.
In the first embodiment described above, the opening degree of the outdoor expansion valve is set based on the volume ratio of each outdoor heat exchanger at the start of the defrosting operation, and the defrosting is completed almost simultaneously. When the frost operation is not completed at the same time, the opening degree of the outdoor expansion valve is controlled. Since the other points are the same as in the first embodiment, the same components are denoted by the same reference numerals and the description thereof is omitted.
　図５には、本発明の第２実施形態に係るマルチ型空気調和機の制御装置による除霜運転時の電動膨張弁の制御がフローチャートに示されている。 FIG. 5 is a flowchart showing the control of the electric expansion valve during the defrosting operation by the control device for the multi-type air conditioner according to the second embodiment of the present invention.
　除霜運転の開始にあたり、まず各室外熱交換器１３の容積に応じた各室外膨張弁１５の開度が設定される（Ｓ１０１）。各室外膨張弁１５の開度が設定された後、除霜運転は開始される。 When starting the defrosting operation, first, the opening degree of each outdoor expansion valve 15 corresponding to the volume of each outdoor heat exchanger 13 is set (S101). After the opening degree of each outdoor expansion valve 15 is set, the defrosting operation is started.
　次に、各室外熱交換器１３の室外熱交換器温度センサ１４により、各熱交換器温度を検出する（Ｓ１０２）。
　次に、ステップＳ１０２にて検出された各熱交換器温度が除霜完了温度（例えば９℃）に到達したか否かを判定する（Ｓ１０３）。ステップＳ１０３にて熱交換器温度が除霜完了温度に到達したと判定された場合は、ステップＳ１０４へ遷移する。ステップＳ１０３にて熱交換器温度が除霜完了温度に到達していないと判定された場合は、ステップＳ１０７へ遷移する。ステップＳ１０３の判定は、各室外熱交換器１３に対して各々並行して行われる。 Next, each heat exchanger temperature is detected by the outdoor heat exchanger temperature sensor 14 of each outdoor heat exchanger 13 (S102).
Next, it is determined whether or not each heat exchanger temperature detected in step S102 has reached a defrosting completion temperature (for example, 9 ° C.) (S103). When it determines with heat exchanger temperature having reached defrost completion temperature in step S103, it changes to step S104. If it is determined in step S103 that the heat exchanger temperature has not reached the defrosting completion temperature, the process proceeds to step S107. The determination in step S103 is performed on each outdoor heat exchanger 13 in parallel.
　ステップＳ１０３にて例えば室外熱交換器１３Ａの熱交換器温度が除霜完了温度に到達したと判定された場合は、室外膨張弁１５Ａの開度を最小開度とする（Ｓ１０４）。最小開度とは、除霜が完了した室外熱交換器１３が再着霜しない程度の微量の冷媒を流入させる程度の開度であり、例えば６０パルス程度である。次に、ステップＳ１１０へ遷移する。 If it is determined in step S103 that, for example, the heat exchanger temperature of the outdoor heat exchanger 13A has reached the defrosting completion temperature, the opening of the outdoor expansion valve 15A is set to the minimum opening (S104). The minimum opening is an opening that allows a small amount of refrigerant to flow in such a degree that the outdoor heat exchanger 13 that has completed defrosting does not re-frost, and is, for example, about 60 pulses. Next, the process proceeds to step S110.
　ステップＳ１１０にて例えば室外熱交換器１３Ａの熱交換器温度が除霜完了温度を下回ると判定された場合は、室外膨張弁１５Ａの開度を漸増させる（Ｓ１０６）。室外膨張弁１５Ａの開度を徐々に増加させることで室外熱交換器１３Ａの再着霜を防ぐ。具体的には、例えば室外膨張弁１５Ａの開度をｘパルス／２０ｓずつ増加させる制御をｎ回行う。
　室外膨張弁１５Ａの開度の漸増制御が完了すると、ステップＳ１１０へ遷移する。 For example, when it is determined in step S110 that the heat exchanger temperature of the outdoor heat exchanger 13A is lower than the defrosting completion temperature, the opening degree of the outdoor expansion valve 15A is gradually increased (S106). Re-frosting of the outdoor heat exchanger 13A is prevented by gradually increasing the opening of the outdoor expansion valve 15A. Specifically, for example, control for increasing the opening degree of the outdoor expansion valve 15A by x pulses / 20 s is performed n times.
When the gradually increasing control of the opening degree of the outdoor expansion valve 15A is completed, the process proceeds to step S110.
　一方、ステップＳ１０３にて例えば室外熱交換器１３Ａの熱交換器温度が除霜完了温度に到達していないと判定された場合は、室外膨張弁１５Ａの開度を維持する（Ｓ１０７）。
　次に、室外熱交換器１３Ａ以外の他の全ての室外熱交換器１３（この場合、室外熱交換器１３Ｂ及び室外熱交換器１３Ｃ）にて熱交換器温度が除霜完了温度に到達したか否かを判定する（Ｓ１０８）。ステップＳ１０８にて他の全ての室外熱交換器１３の熱交換器温度が除霜完了温度に到達したと判定された場合は、ステップＳ１０９へ遷移する。ステップＳ１０８にて他の全ての室外熱交換器１３の熱交換器温度が除霜完了温度に到達していないと判定された場合は、ステップＳ１０７へ戻る。 On the other hand, when it is determined in step S103 that, for example, the heat exchanger temperature of the outdoor heat exchanger 13A has not reached the defrosting completion temperature, the opening degree of the outdoor expansion valve 15A is maintained (S107).
Next, whether the heat exchanger temperature has reached the defrosting completion temperature in all the outdoor heat exchangers 13 (in this case, the outdoor heat exchanger 13B and the outdoor heat exchanger 13C) other than the outdoor heat exchanger 13A It is determined whether or not (S108). When it determines with the heat exchanger temperature of all the other outdoor heat exchangers 13 having reached defrost completion temperature in step S108, it changes to step S109. If it is determined in step S108 that the heat exchanger temperatures of all other outdoor heat exchangers 13 have not reached the defrosting completion temperature, the process returns to step S107.
　ステップＳ１０８にて例えば室外熱交換器１３Ａ以外の他の全ての室外熱交換器１３（室外熱交換器１３Ｂ及び室外熱交換器１３Ｃ）にて熱交換器温度が除霜完了温度に到達していると判定された場合は、室外膨張弁１５Ａの開度を最大開度とする（Ｓ１０９）。最大開度とはすなわち全開を意味する。
　その後、ステップＳ１１０へ遷移する。 In step S108, for example, the heat exchanger temperature reaches the defrosting completion temperature in all the outdoor heat exchangers 13 (outdoor heat exchanger 13B and outdoor heat exchanger 13C) other than the outdoor heat exchanger 13A. Is determined as the maximum opening degree (S109). That is, the maximum opening means full opening.
Then, the process proceeds to step S110.
　ステップＳ１１０では、全ての室外熱交換器１３にて除霜完了温度に到達したか否かが判定される。ステップＳ１１０にて全ての室外熱交換器１３における熱交換器温度が除霜完了温度に到達したと判定された場合は、除霜運転を終了する。
　一方、ステップＳ１１０にて全ての室外熱交換器１３における熱交換器温度が除霜完了温度に到達していないと判定された場合は、ステップＳ１０６へ戻る。 In step S110, it is determined whether or not all the outdoor heat exchangers 13 have reached the defrosting completion temperature. When it determines with the heat exchanger temperature in all the outdoor heat exchangers 13 having reached defrost completion temperature in step S110, a defrost operation is complete | finished.
On the other hand, when it determines with the heat exchanger temperature in all the outdoor heat exchangers 13 not having reached defrost completion temperature in step S110, it returns to step S106.
　図６には、本発明の第２実施形態に係るマルチ型空気調和機の各熱交換器の除霜均一化時の冷媒流量がブロック図に示されている。
　図６に示されるように、室外熱交換器１３Ｂ及び室外熱交換器１３Ｃの除霜が完了し、室外熱交換器１３Ａが除霜中である場合は、図５のフローチャートのステップＳ１０４及びステップＳ１０９で示したように、室外熱交換器１３Ｂの室外膨張弁１５Ｂ及び室外熱交換器１３Ｃの室外膨張弁１５Ｃの開度が最小開度とされ、室外熱交換器１３Ａの室外膨張弁１５Ａの開度が最大開度つまり全開とされる。これにより、室外熱交換器１３Ｂ及び室外熱交換器１３Ｃには再着霜が防止される程度の微量の冷媒が流入し、室外熱交換器１３Ｂ及び室外熱交換器１３Ｃに流入しない分の冷媒が室外熱交換器１３Ａに流入することで室外熱交換器１３Ａの除霜にかかる時間が短縮され、ひいては全室外熱交換器１３の除霜時間が短縮される。 FIG. 6 is a block diagram showing the refrigerant flow rate at the time of uniform defrosting of each heat exchanger of the multi-type air conditioner according to the second embodiment of the present invention.
As shown in FIG. 6, when the defrosting of the outdoor heat exchanger 13B and the outdoor heat exchanger 13C is completed and the outdoor heat exchanger 13A is being defrosted, steps S104 and S109 in the flowchart of FIG. As shown, the opening degree of the outdoor expansion valve 15B of the outdoor heat exchanger 13B and the outdoor expansion valve 15C of the outdoor heat exchanger 13C are set to the minimum opening degree, and the opening degree of the outdoor expansion valve 15A of the outdoor heat exchanger 13A. Is the maximum opening, that is, fully open. As a result, a small amount of refrigerant that prevents re-frosting flows into the outdoor heat exchanger 13B and the outdoor heat exchanger 13C, and the amount of refrigerant that does not flow into the outdoor heat exchanger 13B and the outdoor heat exchanger 13C. By flowing into the outdoor heat exchanger 13A, the time required for the defrosting of the outdoor heat exchanger 13A is shortened, and as a result, the defrosting time of all the outdoor heat exchangers 13 is shortened.
　以上、説明してきたように、本実施形態に係るマルチ型空気調和機の制御装置、マルチ型空気調和機、マルチ型空気調和機の制御方法及びマルチ型空気調和機の制御プログラムによれば、以下の作用効果を奏する。
　容積の異なる複数の室外熱交換器１３において、同時に除霜が完了するように制御を行う場合でも、様々な要因により除霜完了のタイミングが異なる場合が考えられる。他の室外熱交換器１３よりも早く除霜が完了した室外熱交換器１３が存在する場合、除霜完了前と同じ量の冷媒流量の供給は必要がなく、無駄である。そこで、除霜が完了した室外熱交換器１３、すなわち熱交換器温度が除霜完了温度以上となった室外熱交換器１３については、その室外膨張弁１５の開度を最小開度とする。これにより、冷媒流量を最小化することができ、他の除霜が完了していない室外熱交換器１３へ冷媒をより多く供給することができ、複数の室外熱交換器１３全体の除霜にかかる時間を早めることができる。また、室外膨張弁１５を全閉ではなく最小開度とすることから、再着霜を最小限に防ぐことができる。 As described above, according to the control device for a multi-type air conditioner, the multi-type air conditioner, the control method for the multi-type air conditioner, and the control program for the multi-type air conditioner according to the present embodiment, Has the effect of.
Even in the case where control is performed so that defrosting is completed at the same time in a plurality of outdoor heat exchangers 13 having different volumes, the timing of defrosting completion may be different due to various factors. When the outdoor heat exchanger 13 in which defrosting is completed earlier than the other outdoor heat exchangers 13 is present, it is unnecessary and unnecessary to supply the same amount of refrigerant flow as before completion of defrosting. Therefore, for the outdoor heat exchanger 13 in which the defrosting is completed, that is, for the outdoor heat exchanger 13 in which the heat exchanger temperature is equal to or higher than the defrosting completion temperature, the opening of the outdoor expansion valve 15 is set to the minimum opening. Thereby, a refrigerant | coolant flow volume can be minimized, more refrigerant | coolants can be supplied to the outdoor heat exchanger 13 which has not completed other defrosting, and the defrosting of the several outdoor heat exchanger 13 whole is carried out. This time can be accelerated. Further, since the outdoor expansion valve 15 is set to the minimum opening instead of being fully closed, re-frosting can be minimized.
　除霜が完了し室外膨張弁１５の開度を最小開度とした室外熱交換器１３において、冷媒流量を最小とするため再着霜する虞がある。これに対し、該当の室外熱交換器１３の熱交換器温度が除霜完了温度未満となると、再着霜する虞があるとし、室外膨張弁１５の開度を漸増させる。これにより、冷媒流量が増加していくことで室外熱交換器１３の着霜を防ぐことができる。 In the outdoor heat exchanger 13 in which the defrosting is completed and the opening of the outdoor expansion valve 15 is set to the minimum opening, there is a risk of refrosting in order to minimize the refrigerant flow rate. On the other hand, if the heat exchanger temperature of the corresponding outdoor heat exchanger 13 is lower than the defrosting completion temperature, it is assumed that there is a risk of re-frosting, and the opening degree of the outdoor expansion valve 15 is gradually increased. Thereby, the frost formation of the outdoor heat exchanger 13 can be prevented by increasing the refrigerant flow rate.
　容積の異なる複数の室外熱交換器１３において、同時に除霜が完了するように制御を行う場合でも、様々な要因により除霜完了のタイミングが異なる場合が考えられる。他の室外熱交換器１３が全て除霜完了し、除霜完了していない室外熱交換器１３が一台のみ存在する場合、他の室外熱交換器１３の室外膨張弁１５は最小開度となり冷媒の供給量には余裕があることになる。しかし、除霜完了していない室外熱交換器１３の電動膨張弁の開度が変わらず一定であれば冷媒流量の供給は増えず除霜に時間がかかる。そこで、除霜完了していない室外熱交換器１３が一台のみとなった場合は、その室外熱交換器１３の室外膨張弁１５の開度を全開とする。これにより、余剰の冷媒を除霜が完了していない室外熱交換器１３へ最大量供給することでき、除霜にかかる時間を短縮することができる。 Even in the case where control is performed so that defrosting is completed at the same time in a plurality of outdoor heat exchangers 13 having different volumes, the timing of defrosting completion may be different due to various factors. When all the other outdoor heat exchangers 13 have been defrosted and there is only one outdoor heat exchanger 13 that has not been defrosted, the outdoor expansion valve 15 of the other outdoor heat exchanger 13 has a minimum opening. There is a margin in the amount of refrigerant supplied. However, if the opening degree of the electric expansion valve of the outdoor heat exchanger 13 that has not been defrosted remains unchanged and the supply of the refrigerant flow rate does not increase, defrosting takes time. Therefore, when there is only one outdoor heat exchanger 13 that has not been defrosted, the degree of opening of the outdoor expansion valve 15 of the outdoor heat exchanger 13 is fully opened. Thereby, the maximum amount of excess refrigerant can be supplied to the outdoor heat exchanger 13 where defrosting has not been completed, and the time required for defrosting can be shortened.
　以上、本発明の各実施形態について図面を参照して詳述してきたが、具体的な構成はこの実施形態に限られるものではなく、本発明の要旨を逸脱しない範囲の設計変更なども含まれる。 As mentioned above, although each embodiment of the present invention has been described in detail with reference to the drawings, the specific configuration is not limited to this embodiment, and includes design changes and the like within a scope not departing from the gist of the present invention. .
　たとえば、上述した各実施形態においては流量調整装置を室外膨張弁（電動膨張弁）であるとしたが、制御装置５０により流量を調整できる機能を備えた装置であれば、他の装置を用いるとしてもよい。 For example, in each of the above-described embodiments, the flow rate adjustment device is an outdoor expansion valve (electric expansion valve). However, any other device may be used as long as the device has a function that allows the control device 50 to adjust the flow rate. Also good.
１　マルチ型空気調和機
２　室外機
３　室内機
１０　圧縮機
１２　四方切換弁
１３　室外熱交換器（熱交換器）
１４　室外熱交換器温度センサ（温度センサ）
１５　室外膨張弁（流量調整装置）
５０　制御装置 DESCRIPTION OF SYMBOLS 1 Multi type air conditioner 2 Outdoor unit 3 Indoor unit 10 Compressor 12 Four-way switching valve 13 Outdoor heat exchanger (heat exchanger)
14 Outdoor heat exchanger temperature sensor (temperature sensor)
15 Outdoor expansion valve (flow control device)
50 Control device

Claims (9)

  1. 　少なくとも一つの熱交換器の容積が他の熱交換器の容積と異なる複数の前記熱交換器を備えた室外機と、
    　複数の室内機と、
    を備えたマルチ型空気調和機の制御装置であって、
    　複数の前記熱交換器は、夫々、該熱交換器に供給される冷媒流量を調整する流量調整装置を備え、
    　除霜運転時に、複数の前記熱交換器の前記容積に応じて各前記熱交換器に供給される冷媒流量を前記流量調整装置の制御により調整するマルチ型空気調和機の制御装置。     An outdoor unit comprising a plurality of the heat exchangers, the volume of at least one heat exchanger being different from the volume of other heat exchangers;
    Multiple indoor units,
    A multi-type air conditioner control device comprising:
    Each of the plurality of heat exchangers includes a flow rate adjusting device that adjusts the flow rate of the refrigerant supplied to the heat exchanger,
    The control apparatus of the multi-type air conditioner which adjusts the refrigerant | coolant flow volume supplied to each said heat exchanger according to the said volume of the said several heat exchanger by control of the said flow volume adjustment apparatus at the time of a defrost operation.
  2. 　前記流量調整装置は、電動膨張弁を備え、
    　複数の前記熱交換器は、該熱交換器の熱交換器温度を検知する温度センサを夫々備え、
    　全ての前記熱交換器の前記熱交換器温度が除霜完了の基準値となる除霜完了温度に略同時に到達するように複数の前記熱交換器の前記電動膨張弁の開度を決定する弁開度決定制御を行う請求項１に記載のマルチ型空気調和機の制御装置。     The flow rate adjusting device includes an electric expansion valve,
    Each of the plurality of heat exchangers includes a temperature sensor that detects a heat exchanger temperature of the heat exchanger,
    A valve that determines the opening degrees of the electric expansion valves of the plurality of heat exchangers so that the heat exchanger temperatures of all the heat exchangers reach the defrosting completion temperature that is the reference value for completion of defrosting substantially simultaneously. The control apparatus of the multi type air conditioner of Claim 1 which performs opening degree determination control.
  3. 　一以上の前記熱交換器の前記熱交換器温度が前記除霜完了温度以上となった場合、該熱交換器の前記電動膨張弁の開度を最小開度とする請求項２に記載のマルチ型空気調和機の制御装置。 The multi of claim 2, wherein when the heat exchanger temperature of one or more of the heat exchangers is equal to or higher than the defrosting completion temperature, the opening degree of the electric expansion valve of the heat exchanger is set to a minimum opening degree. Type air conditioner control device.
  4. 　前記熱交換器の前記電動膨張弁の開度を最小開度とした後、前記熱交換器温度が前記除霜完了温度未満となった場合、該熱交換器の前記電動膨張弁の開度を漸増させる請求項３に記載のマルチ型空気調和機の制御装置。 After the opening degree of the electric expansion valve of the heat exchanger is set to the minimum opening degree, when the heat exchanger temperature becomes lower than the defrosting completion temperature, the opening degree of the electric expansion valve of the heat exchanger is set. The control device for a multi-type air conditioner according to claim 3, which is gradually increased.
  5. 　一の前記熱交換器の前記熱交換器温度のみが前記除霜完了温度未満である場合、該熱交換器の前記電動膨張弁の開度を全開とする請求項３または請求項４に記載のマルチ型空気調和機の制御装置。 The opening degree of the electric expansion valve of the heat exchanger is fully opened when only the heat exchanger temperature of the one heat exchanger is lower than the defrosting completion temperature. Multi-type air conditioner control device.
  6. 　前記弁開度決定制御は、工場からの出荷時または試運転時に実施され、前記電動膨張弁の開度が記憶手段に記憶される請求項２から請求項５のいずれかに記載のマルチ型空気調和機の制御装置。 The multi-type air conditioning according to any one of claims 2 to 5, wherein the valve opening determination control is performed at the time of shipment from a factory or at the time of trial operation, and the opening of the electric expansion valve is stored in a storage means. Machine control device.
  7. 　少なくとも一つの熱交換器の容積が他の熱交換器の容積と異なる複数の前記熱交換器を備えた室外機と、
    　複数の室内機と、
    　請求項１から請求項６のいずれかに記載の制御装置と
    を備えたマルチ型空気調和機。     An outdoor unit comprising a plurality of the heat exchangers, the volume of at least one heat exchanger being different from the volume of other heat exchangers;
    Multiple indoor units,
    The multi-type air conditioner provided with the control apparatus in any one of Claims 1-6.
  8. 　少なくとも一つの熱交換器の容積が他の熱交換器の容積と異なる複数の前記熱交換器を備えた室外機と、
    　複数の室内機と、
    を備えたマルチ型空気調和機の制御方法であって、
    　複数の前記熱交換器は、夫々、該熱交換器に供給される冷媒流量を調整する流量調整装置を備え、
    　除霜運転時に、複数の前記熱交換器の前記容積に応じて各前記熱交換器に供給される冷媒流量を前記流量調整装置の制御により調整する工程を備えるマルチ型空気調和機の制御方法。     An outdoor unit comprising a plurality of the heat exchangers, the volume of at least one heat exchanger being different from the volume of other heat exchangers;
    Multiple indoor units,
    A control method for a multi-type air conditioner comprising:
    Each of the plurality of heat exchangers includes a flow rate adjusting device that adjusts the flow rate of the refrigerant supplied to the heat exchanger,
    The control method of a multi-type air conditioner provided with the process of adjusting the refrigerant | coolant flow volume supplied to each said heat exchanger according to the said volume of the said some heat exchanger by control of the said flow volume adjustment apparatus at the time of a defrost operation.
  9. 　少なくとも一つの熱交換器の容積が他の熱交換器の容積と異なる複数の前記熱交換器を備えた室外機と、
    　複数の室内機と、
    を備えたマルチ型空気調和機の制御プログラムであって、
    　複数の前記熱交換器は、夫々、該熱交換器に供給される冷媒流量を調整する流量調整装置を備え、
    　除霜運転時に、複数の前記熱交換器の前記容積に応じて各前記熱交換器に供給される冷媒流量を前記流量調整装置の制御により調整するステップを備えるマルチ型空気調和機の制御プログラム。     An outdoor unit comprising a plurality of the heat exchangers, the volume of at least one heat exchanger being different from the volume of other heat exchangers;
    Multiple indoor units,
    A multi-type air conditioner control program comprising:
    Each of the plurality of heat exchangers includes a flow rate adjusting device that adjusts the flow rate of the refrigerant supplied to the heat exchanger,
    A control program for a multi-type air conditioner, comprising a step of adjusting a flow rate of refrigerant supplied to each heat exchanger according to the volume of a plurality of heat exchangers during the defrosting operation by control of the flow rate adjusting device.
PCT/JP2017/041936 2016-12-28 2017-11-22 Multi-split air conditioner control device, multi-split air conditioner, multi-split air conditioner control method, and multi-split air conditioner control program WO2018123361A1 (en)

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