WO2016194098A1 - Dispositif de climatisation et dispositif de commande de fonctionnement - Google Patents

Dispositif de climatisation et dispositif de commande de fonctionnement Download PDF

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Publication number
WO2016194098A1
WO2016194098A1 PCT/JP2015/065730 JP2015065730W WO2016194098A1 WO 2016194098 A1 WO2016194098 A1 WO 2016194098A1 JP 2015065730 W JP2015065730 W JP 2015065730W WO 2016194098 A1 WO2016194098 A1 WO 2016194098A1
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WO
WIPO (PCT)
Prior art keywords
heat source
refrigerant
load
refrigerant pipe
source side
Prior art date
Application number
PCT/JP2015/065730
Other languages
English (en)
Japanese (ja)
Inventor
周平 水谷
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP15894133.6A priority Critical patent/EP3306214B1/fr
Priority to PCT/JP2015/065730 priority patent/WO2016194098A1/fr
Priority to JP2017521358A priority patent/JP6501878B2/ja
Priority to CN201580081017.7A priority patent/CN107709887B/zh
Publication of WO2016194098A1 publication Critical patent/WO2016194098A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/07—Exceeding a certain pressure value in a refrigeration component or cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/195—Pressures of the condenser

Definitions

  • the present invention relates to an air conditioner capable of diverting existing piping and an operation control apparatus capable of controlling the air conditioner.
  • an air conditioner capable of diverting existing piping for example, an operation frequency of a compressor, an opening degree of a decompression device, etc. are controlled so that the pressure of the refrigerant in the existing piping does not exceed a pressure resistance reference value.
  • Patent Document 1 Japanese Patent Document 1
  • the load capacity (operating capacity) of the indoor unit is reduced during cooling operation in an environment where the outside air temperature is higher than usual (hereinafter referred to as “high outside air temperature environment”).
  • high outside air temperature environment there is a high possibility that the pressure of the refrigerant in the existing piping will rise more than during normal cooling operation. Therefore, in the air conditioner of Patent Document 1, since the possibility that the refrigerant pressure in the existing pipe exceeds the pressure resistance reference value increases, the frequency of the air conditioner abnormally stopping due to pressure abnormality increases, and the reliability of the air conditioner is increased. There was a problem that sex could not be maintained.
  • the present invention has been made to solve the above-described problem, and is capable of suppressing the pressure of the refrigerant in the existing piping to less than the pressure resistance reference value even during a cooling operation in a high outside air temperature environment. It aims at providing a harmony device and an operation control device.
  • An air conditioner connects a compressor, a heat source side heat exchanger, a pressure reducing device, and a load side heat exchanger via a refrigerant pipe to circulate the refrigerant, and at least the heat source side heat exchanger includes A refrigeration cycle that functions as a radiator and performs a cooling operation in which the load-side heat exchanger functions as an evaporator, the compressor, the heat-source-side heat exchanger, and a heat-source-side unit that houses the decompression device, One or more load-side units that house a load-side heat exchanger and are connected to the heat source-side unit via an existing refrigerant pipe, and a control device that controls the refrigeration cycle, When the outdoor air temperature of the outdoor air supplied to the heat source side heat exchanger exceeds a reference outdoor air temperature during operation and the total load capacity of the one or more load side units decreases with time, the total load capacity And adjusts the opening degree of the pressure reducing device in accordance with a variation value.
  • the operation control apparatus includes a compressor, a heat source side heat exchanger, and a decompression device housed in the heat source side unit, and one or more connected to the heat source side unit via an existing refrigerant pipe.
  • a load side heat exchanger accommodated in the load side unit is connected via a refrigerant pipe to circulate the refrigerant.
  • At least the heat source side heat exchanger functions as a radiator and the load side heat exchanger evaporates.
  • the opening degree of the decompression device is adjusted according to the fluctuation value of the total load capacity.
  • the opening degree of the heat source side pressure reducing device can be adjusted according to the reduction of the total load capacity of one or more load side units, the pressure of the refrigerant in the existing pipe is controlled to be equal to or lower than the pressure resistance reference value. it can. Therefore, according to the present invention, it is possible to provide a highly reliable air conditioning apparatus and operation control apparatus that can reduce the frequency with which the air conditioning apparatus abnormally stops due to pressure abnormality.
  • FIG. 1 is a schematic refrigerant circuit diagram illustrating an example of the air-conditioning apparatus 1 according to Embodiment 1.
  • FIG. 1 the dimensional relationship and shape of each component may be different from the actual one.
  • the air conditioner 1 includes a heat source side unit 100 (heat source unit) that is an outdoor unit, a first load side unit 200a that is an indoor unit arranged in parallel to the heat source side unit 100, and And a second load side unit 200b. Between the heat source side unit 100 and the first load side unit 200a and the second load side unit 200b, a first extended refrigerant pipe 300 (liquid pipe) and a second extended refrigerant pipe 400 (gas) which are existing pipes are provided. Connected by piping). In FIG. 1, two load-side units are connected, but the number of load-side units connected may be one or three or more.
  • the air conditioner 1 includes a compressor 2, a heat source side heat exchanger 3, a heat source side decompression device 4, a first load side decompression device 5a, a second load side decompression device 5b, and a first
  • the load-side heat exchanger 6a and the second load-side heat exchanger 6b, the refrigerant flow switching device 7, and the accumulator 8 have a single refrigeration cycle (refrigerant circuit) for circulating the refrigerant sequentially.
  • the compressor 2 is a variable frequency type fluid machine that is housed in the heat source side unit 100, compresses the sucked low-pressure refrigerant, and discharges it as a high-pressure refrigerant.
  • a scroll compressor whose rotation frequency is controlled by an inverter can be used.
  • the heat source side heat exchanger 3 (outdoor unit heat exchanger) is a heat exchanger that functions as a radiator (condenser) during cooling operation and functions as an evaporator during heating operation, and is accommodated in the heat source side unit 100. Yes.
  • the heat source side heat exchanger 3 performs heat exchange between the refrigerant flowing inside the heat source side heat exchanger 3 and the outside air (for example, outdoor air) blown by a heat source side heat exchanger fan (not shown). Configured.
  • the heat source side heat exchanger 3 can be constituted by, for example, a cross fin type fin-and-tube heat exchanger constituted by a heat transfer tube and a plurality of fins.
  • the first heat source side refrigerant pipe 10 (outdoor unit liquid line) is accommodated in the heat source side unit 100, and one end is connected to the heat source side heat exchanger 3.
  • the other end portion of the first heat source side refrigerant pipe 10 is a first extended refrigerant pipe connection valve 9a (liquid operation valve) provided on the first heat source side refrigerant pipe 10, and the first extended refrigerant. It is connected to the pipe 300.
  • the first extended refrigerant pipe connection valve 9a is composed of, for example, a two-way valve such as a two-way solenoid valve that can be switched between open and closed.
  • the heat source side decompression device 4 expands and decompresses the high-pressure liquid refrigerant flowing from the heat source side heat exchanger 3 during the cooling operation, and flows it into the first extended refrigerant pipe 300 which is an existing pipe.
  • the heat source side decompression device 4 is accommodated in the heat source side unit 100 and is provided in the first heat source side refrigerant pipe 10.
  • an electronic expansion valve such as a linear electronic expansion valve (LEV) whose opening degree can be adjusted in multiple stages or continuously can be used as the heat source side pressure reducing device 4 and is configured as an outdoor electronic expansion valve.
  • LEV linear electronic expansion valve
  • the heat source side decompression device 4 further expands and decompresses the medium-pressure liquid refrigerant or the two-phase refrigerant flowing from the first extended refrigerant pipe 300 into the first heat source side refrigerant pipe 10, It can be configured to flow into the side heat exchanger 3.
  • the first load side decompression device 5a and the second load side decompression device 5b further expand and decompress the medium-pressure liquid refrigerant or two-phase refrigerant flowing from the first extended refrigerant pipe 300 during the cooling operation, It is made to flow in 1 load side heat exchanger 6a and 2nd load side heat exchanger 6b, respectively.
  • the first load-side decompression device 5a is accommodated in the first load-side unit 200a
  • the second load-side decompression device 5b is accommodated in the second load-side unit 200b.
  • the first load-side pressure reducing device 5a and the second load-side pressure reducing device 5b are, for example, electronic expansion valves such as linear electronic expansion valves whose opening degree can be adjusted in multiple stages or continuously, and are used as indoor electronic expansion valves. Composed.
  • the first load side pressure reducing device 5a is adjusted to be closed.
  • the second load side pressure reducing device 5b is adjusted to be closed.
  • the first load-side decompression device 5a expands and decompresses the high-pressure liquid refrigerant flowing from the first load-side heat exchanger 6a during the heating operation, and the first extended refrigerant pipe that is an existing pipe. It can be configured to flow into 300.
  • the second load-side decompression device 5b expands and decompresses the high-pressure liquid refrigerant flowing from the second load-side heat exchanger 6b, and is a first extended refrigerant that is an existing pipe. It can be configured to flow into the pipe 300.
  • the first load side heat exchanger 6a and the second load side heat exchanger 6b are heat exchangers that function as an evaporator during cooling operation and function as a radiator during heating operation.
  • the first load side heat exchanger 6a and the second load side heat exchanger 6b are, for example, a refrigerant flowing inside the first load side heat exchanger 6a and the second load side heat exchanger 6b, and the outside air It is configured to exchange heat with (for example, room air).
  • the 1st load side heat exchanger 6a and the 2nd load side heat exchanger 6b can be constituted as a fin and tube type heat exchanger of the cross fin type constituted by a heat exchanger tube and a plurality of fins, for example. .
  • the first load side heat exchanger 6a is accommodated in the first load side unit 200a, and the second load side heat exchanger 6b is accommodated in the second load side unit 200b. Moreover, in the air conditioning apparatus 1 according to the first embodiment, the first load side heat exchanger 6a and the second load side heat exchanger 6b are blown by air from a fan for load side heat exchanger (not shown). It can be configured to supply outside air.
  • the refrigerant flow switching device 7 switches the refrigerant flow direction in the refrigeration cycle when switching between the cooling operation and the heating operation, and is accommodated in the heat source unit 100.
  • a four-way valve is used as the refrigerant flow switching device 7.
  • a fifth heat source side refrigerant pipe 18 is connected between the refrigerant flow switching device 7 and the heat source side heat exchanger 3.
  • a third heat source side refrigerant pipe 14 (pipe before the accumulator) is connected between the refrigerant flow switching device 7 and the refrigerant inlet of the accumulator 8.
  • a fourth heat source side refrigerant pipe 16 is connected between the refrigerant flow switching device 7 and the discharge port of the compressor 2.
  • a second heat source side refrigerant pipe 12 is connected between the refrigerant flow switching device 7 and the second extended refrigerant pipe 400.
  • the refrigerant flow switching device 7 causes the refrigerant to flow from the second heat source side refrigerant pipe 12 to the third heat source side refrigerant pipe 14, and from the fourth heat source side refrigerant pipe 16 to the fifth heat source side refrigerant.
  • the refrigerant is configured to flow through the pipe 18.
  • the refrigerant flow switching device 7 causes the refrigerant to flow from the fifth heat source side refrigerant pipe 18 to the third heat source side refrigerant pipe 14, and from the fourth heat source side refrigerant pipe 16 to the second heat source side.
  • the refrigerant is configured to flow through the refrigerant pipe 12.
  • the second heat source side refrigerant pipe 12, the third heat source side refrigerant pipe 14, the fourth heat source side refrigerant pipe 16, and the fifth heat source side refrigerant pipe 18 are accommodated in the heat source side unit 100.
  • the second heat source side refrigerant pipe 12 is connected to the second extended refrigerant pipe 400 by a second extended refrigerant pipe connection valve 9b (gas operation valve) provided in the second heat source side refrigerant pipe 12. ing.
  • the second extended refrigerant pipe connection valve 9b is composed of, for example, a two-way valve such as a two-way solenoid valve that can be switched between open and closed.
  • the accumulator 8 is a gas / liquid that prevents a large amount of liquid refrigerant from flowing into the compressor 2 by retaining a refrigerant storage function that stores excess refrigerant and liquid refrigerant that is temporarily generated when the operating state changes. It has a separation function.
  • the accumulator 8 is disposed on the suction pipe side of the compressor 2 and is accommodated in the heat source side unit 100.
  • the heat source side unit 100 is a bypass refrigerant pipe 20 (high / low pressure bypass pipe) branched from the first heat source side refrigerant pipe 10 at a position between the heat source side pressure reducing device 4 and the first extended refrigerant pipe connection valve 9a. It has.
  • the end of the bypass refrigerant pipe 20 is connected to the third heat source side refrigerant pipe 14 at a position between the refrigerant flow switching device 7 and the accumulator 8.
  • the bypass refrigerant pipe 20 is a first heat source side refrigerant pipe 10 that is a refrigerant pipe on the refrigerant outlet side of the heat source side decompression device 4 and a refrigerant pipe that is connected to the refrigerant inlet side of the accumulator 8.
  • This is a refrigerant pipe that bypasses the heat source side refrigerant pipe 14.
  • the bypass refrigerant pipe 20 is provided with an electromagnetic valve 25 that is a valve that opens or closes the flow path when power is supplied or stopped.
  • the solenoid valve 25 causes the refrigerant that has flowed into the first heat source side refrigerant pipe 10 to flow into the accumulator 8. It has a capacity coefficient (CV value) that can reduce the pressure of the high-pressure or medium-pressure refrigerant flowing into the first heat source side refrigerant pipe 10 to a low pressure.
  • the electromagnetic valve 25 is configured by a two-way valve such as a two-way electromagnetic valve capable of switching between opening and closing, for example.
  • the air conditioner 1 includes a first temperature sensor 30, a second temperature sensor 35a, a first pressure sensor 40, and a second pressure sensor 45.
  • the first temperature sensor 30 is an outside air temperature sensor (outdoor temperature sensor) that detects the temperature of the outside air (outdoor air) that is sucked by a heat source side fan (not shown) and blown to the heat source side heat exchanger 3. is there.
  • the 1st temperature sensor 30 is arrange
  • the second temperature sensor 35a is sucked in by a load-side blower fan (not shown) housed in the first load-side unit 200a and is sent to the first load-side heat exchanger 6a.
  • the 2nd temperature sensor 35a When the 2nd temperature sensor 35a is comprised as an outside temperature sensor, the 2nd temperature sensor 35a is arrange
  • the third temperature sensor 35b is sucked in by a load-side fan (not shown) housed in the second load-side unit 200b and is sent to the second load-side heat exchanger 6b. It can be an outside air temperature sensor (indoor unit intake temperature sensor) that detects the temperature.
  • the 3rd temperature sensor 35b is comprised as an outside temperature sensor, the 3rd temperature sensor 35b is arrange
  • the first pressure sensor 40 is a pressure sensor (intermediate pressure sensor) that detects the pressure P of the refrigerant flowing through the first heat source side refrigerant pipe 10 on the refrigerant outlet side of the heat source side decompression device 4 during the cooling operation. . That is, the first pressure sensor 40 is disposed at a position of the first heat source side refrigerant pipe 10 between the heat source side pressure reducing device 4 and the first extended refrigerant pipe connection valve 9a.
  • the second pressure sensor 45 flows out from the outlets of the first load side heat exchanger 6a and the second load side heat exchanger 6b and detects the low pressure of the merged refrigerant. It is a (low pressure sensor) and detects the pressure of the refrigerant flowing out from the outlet of the heat source side heat exchanger 3 during heating operation.
  • the second pressure sensor 45 is disposed in the third heat source side refrigerant pipe 14.
  • the first temperature sensor 30 As a material of the first temperature sensor 30, the second temperature sensor 35a, and the third temperature sensor 35b, a semiconductor (for example, a thermistor) or a metal (for example, a resistance temperature detector) is used. Further, as the first pressure sensor 40 and the second pressure sensor 45, a crystal piezoelectric pressure sensor, a semiconductor sensor, a pressure transducer, or the like is used. In addition, the 1st temperature sensor 30, the 2nd temperature sensor 35a, and the 3rd temperature sensor 35b may be comprised with the same material, and may be comprised with a different material. Also, the first pressure sensor 40 and the second pressure sensor 45 may be made of the same type or different types.
  • control device 500 operation control device that performs overall control of the air-conditioning apparatus 1 according to Embodiment 1 will be described.
  • the control device 500 controls the operation state of the first control unit 50 (outdoor unit side control device) that controls the operation state of the heat source side unit 100 and the first load side unit 200a.
  • a second control unit 55a (indoor unit side control device) and a third control unit 55b (indoor unit side control device) that controls the operating state of the second load side unit 200b are provided.
  • the first control unit 50, the second control unit 55a, and the third control unit 55b include a microcomputer that includes a CPU, a memory (eg, ROM, RAM, etc.), an I / O port, and the like. .
  • the control device 500 connects the first control unit 50, the second control unit 55a, and the third control unit 55b with a communication line 58 to communicate with each other such as transmission and reception of control signals. Configured to be able to do. Note that communication between the first control unit 50 and the second control unit 55a and the third control unit 55b may be performed wirelessly.
  • the first control unit 50 starts and stops the operation of the heat source side unit 100, adjusts the opening degree of the heat source side decompression device 4, opens or closes the electromagnetic valve 25, adjusts the operation frequency of the compressor 2, and the like. It is configured to be able to control the operating state.
  • the first control unit 50 is configured to have a storage unit (not shown) that can store various data such as a control target value.
  • the first control unit 50 also receives an electrical signal of temperature information detected by the first temperature sensor 30 and an electrical signal of pressure information detected by the first pressure sensor 40 and the second pressure sensor 45. Configured as follows.
  • the second control unit 55a is configured to control operation states such as start and stop of the operation of the first load-side unit 200a and adjustment of the opening degree of the first load-side decompression device 5a.
  • the second control unit 55a is configured to measure the load capacity Q1 (operating capacity) of the first load side unit 200a at a predetermined interval (for example, every minute).
  • the second control unit 55a is configured to receive an electrical signal of temperature information detected by the second temperature sensor 35a.
  • the third control unit 55b is configured to control the operation state such as the start and stop of the operation of the second load side unit 200b and the adjustment of the opening degree of the second load side decompression device 5b.
  • the third control unit 55b is configured to measure the load capacity Q2 of the second load-side unit 200b at a predetermined interval (for example, every 1 minute), and the second control unit 55a 3 is configured to receive an electrical signal of temperature information detected by the temperature sensor 35b.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 3.
  • the high-temperature and high-pressure gas refrigerant that has flowed into the heat source side heat exchanger 3 is heat-exchanged by releasing heat to a low-temperature medium such as outdoor air, and becomes a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is expanded and depressurized by the heat source-side decompression device 4 provided in the first heat source-side refrigerant pipe 10 to become a medium-pressure liquid refrigerant or a two-phase refrigerant, and passes through the first extended refrigerant pipe 300. Then, it flows into the heat source side unit 100.
  • the medium-pressure liquid refrigerant or two-phase refrigerant flowing into the first load-side decompression device 5a and the second load-side decompression device 5b is further expanded and decompressed to become a low-temperature and low-pressure two-phase refrigerant.
  • the two-phase refrigerant having a high dryness or the low-temperature and low-pressure gas refrigerant that has flowed out of the first load-side heat exchanger 6a and the second load-side heat exchanger 6b is supplied to the second extended refrigerant pipe 400, the second heat source side.
  • the refrigerant flows into the accumulator 8 via the refrigerant pipe 12, the refrigerant flow switching device 7, and the third heat source side refrigerant pipe 14.
  • the two-phase refrigerant having a high degree of dryness or the low-temperature and low-pressure gas refrigerant is sucked into the compressor 2 after the liquid phase component is removed by the accumulator 8.
  • the refrigerant sucked into the compressor 2 is compressed to become a high-temperature and high-pressure gas refrigerant and is discharged from the compressor 2.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 3 via the fourth heat source side refrigerant pipe 16, the refrigerant flow switching device 7, and the fifth heat source side refrigerant pipe 18. To do. In the cooling operation of the air conditioner 1, the above cycle is repeated.
  • the flow path inside the refrigerant flow switching device 7 is switched from the solid flow path to the dotted flow path as shown in FIG.
  • the high-temperature and high-pressure gas refrigerant flows into the first load-side heat exchanger 6a and the second load-side heat exchanger 6b, releases heat to a low-temperature medium such as indoor air, and the high-pressure liquid refrigerant and Become.
  • the indoor air is heated by the heat dissipation action of the refrigerant.
  • the control device 500 of the air-conditioning apparatus 1 according to Embodiment 1 is configured such that the outdoor air temperature supplied to the heat source side heat exchanger 3 exceeds the reference outdoor air temperature during cooling operation, and one or more load sides When the total load capacity Q of the units (the first load side unit 200a and the second load side unit 200b) decreases with time, the opening degree of the heat source side pressure reducing device 4 according to the fluctuation value of the total load capacity Q Configured to adjust.
  • FIG. 2 is a flowchart showing an example of control processing during cooling operation in the control device 500 of the air-conditioning apparatus 1 according to Embodiment 1.
  • the control process of FIG. 2 may be performed all the time during the cooling operation, or may be performed at any time when a change in the outside air temperature T is detected, for example.
  • step S11 the control device 500 determines whether or not the outside air temperature T detected by the first temperature sensor 30 is higher than the reference outside air temperature T0.
  • the reference outside air temperature T0 is set as a boundary value between the high outside air temperature environment and the normal outside air temperature environment, and is set to 52 ° C., for example.
  • the normal temperature environment refers to an outside air temperature environment in which the pressure of the refrigerant flowing through the existing piping does not exceed the pressure resistance reference value due to the fluctuation of the total load capacity Q.
  • step S12 the control device 500 causes the current load capacity Q1 now in the first load side unit 200a and the current load capacity Q2 now in the second load side unit 200b. And the current total load capacity Qnow is calculated by the following equation (2).
  • Q now Q1 now + Q2 now (2)
  • step S ⁇ b> 13 the control device 500 determines whether or not the current total load capacity Q now is less than the latest total load capacity Q last stored in the storage unit of the control apparatus 500.
  • the control process is terminated and normal cooling operation is continued.
  • the opening degree adjustment value ⁇ D of the heat source side decompression device 4 is calculated in step S14.
  • the correction coefficient K is, for example, a fluctuation value of the total load capacity Q, a fluctuation value of the pressure P detected by the first pressure sensor 40, and an opening adjustment value ⁇ D for canceling the fluctuation of the pressure P. It is a constant that is calculated and determined from the correlation of measured values.
  • the refrigeration cycle to be performed the compressor 2, the heat source side heat exchanger 3, the heat source side unit 100 housing the pressure reducing device (heat source side pressure reducing device 4), and the load side heat exchanger (first load side heat exchanger 6a). , The second load-side heat exchanger 6b), and the existing refrigerant pipe (the first extended refrigerant distribution). 300, one or more load side units (first load side unit 200a, second load side unit 200b) connected to the heat source side unit 100 via the second extended refrigerant pipe 400) and the refrigeration cycle are controlled.
  • the total load capacity in a state where all five indoor units are in operation is 100%.
  • the total load capacity of the indoor units is 20%.
  • the electronic expansion valves of the four stopped indoor units are closed. Therefore, assuming that the refrigerant circulation amount in a state in which all five indoor units are in operation is 100%, the refrigerant pressure that flows into the existing piping is maintained when the four indoor units are stopped.
  • control device 500 opens the electromagnetic valve 25 in step S22.
  • step S23 the control device 500 counts the time M during which the electromagnetic valve 25 is opened, and determines whether or not a certain time M0 has elapsed. When the fixed time M0 has not elapsed, the open state of the solenoid valve 25 is maintained.
  • step S24 the control device 500 closes the electromagnetic valve 25 and ends the control process.
  • the heat source side unit 100 includes the accumulator 8 disposed on the suction pipe side of the compressor 2 and the refrigerant flow of the decompression device (heat source side decompression device 4).
  • Bypass refrigerant pipe 20 that bypasses between the refrigerant pipe on the outlet side (first heat source side refrigerant pipe 10) and the refrigerant pipe (third heat source side refrigerant pipe 14) connected to the refrigerant inlet side of the accumulator 8.
  • a solenoid valve 25 provided in the bypass refrigerant pipe 20, and the control device 500 has a refrigerant pipe (first heat source side) on the refrigerant outlet side of the pressure reducing apparatus (heat source side pressure reducing apparatus 4) during the cooling operation.
  • the pressure of the refrigerant flowing through the refrigerant pipe 10) exceeds the pressure resistance reference value of the existing refrigerant pipe (first extended refrigerant pipe 300)
  • the electromagnetic valve 25 is opened for a certain period of time.
  • control device 500 includes an accumulator 8 disposed on the suction pipe side of the compressor 2 and a refrigerant on the refrigerant outlet side of the decompression device (heat source side decompression device 4).
  • a bypass refrigerant pipe 20 that bypasses between the pipe (first heat source side refrigerant pipe 10) and a refrigerant pipe (third heat source side refrigerant pipe 14) connected to the refrigerant inlet side of the accumulator 8, and a bypass refrigerant
  • the air conditioner 1 that further accommodates the electromagnetic valve 25 provided in the pipe 20 in the heat source side unit 100 is controlled, and the refrigerant pipe (first pipe) on the refrigerant outlet side of the pressure reducing apparatus (heat source side pressure reducing apparatus 4) during cooling operation.
  • a device 500 operation control device
  • the present invention is not limited to the above-described embodiment, and various modifications can be made.
  • the above-described embodiment is not limited to the air conditioner 1 and can be used for a water heater or the like.

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

Abstract

L'invention concerne un dispositif de climatisation (1) équipé d'un dispositif de commande (500) (dispositif de commande de fonctionnement). Si, pendant une opération de refroidissement, la température de l'air extérieur délivré à un échangeur de chaleur (3) côté source de chaleur dépasse une température d'air extérieur de référence, et si la capacité de charge totale d'une ou de plusieurs unités côté charge (une première unité côté charge (200a) et une seconde unité côté charge (200b)) est réduite dans le temps, le dispositif de commande (500) (dispositif de commande de fonctionnement) ajuste le degré d'ouverture d'un dispositif de décompression (dispositif de décompression (4) côté source de chaleur) en fonction de la variation de la capacité de charge totale.
PCT/JP2015/065730 2015-06-01 2015-06-01 Dispositif de climatisation et dispositif de commande de fonctionnement WO2016194098A1 (fr)

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EP15894133.6A EP3306214B1 (fr) 2015-06-01 2015-06-01 Dispositif de climatisation et dispositif de commande de fonctionnement
PCT/JP2015/065730 WO2016194098A1 (fr) 2015-06-01 2015-06-01 Dispositif de climatisation et dispositif de commande de fonctionnement
JP2017521358A JP6501878B2 (ja) 2015-06-01 2015-06-01 空気調和装置及び運転制御装置
CN201580081017.7A CN107709887B (zh) 2015-06-01 2015-06-01 空气调节装置以及运行控制装置

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WO2021065112A1 (fr) * 2019-09-30 2021-04-08 ダイキン工業株式会社 Unité de source de chaleur et dispositif de réfrigération
JP2021081114A (ja) * 2019-11-18 2021-05-27 ダイキン工業株式会社 冷凍装置用の中間ユニットおよび冷凍装置

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FR3097807B1 (fr) * 2019-06-28 2021-07-09 Valeo Systemes Thermiques Procédé de gestion d’un dispositif de gestion thermique pour véhicule automobile
CN111076279A (zh) * 2020-01-08 2020-04-28 珠海格力电器股份有限公司 更新多联机空调系统的控制方法及更新多联空调系统
CN113639412B (zh) * 2021-07-15 2023-03-24 青岛海尔空调器有限总公司 室内换热器的管外自清洁控制方法
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CN115751663A (zh) * 2022-11-28 2023-03-07 贵州电网有限责任公司 一种中央空调外机散热负荷自动调节装置和方法

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JP6501878B2 (ja) 2019-04-17
EP3306214A4 (fr) 2018-06-06
JPWO2016194098A1 (ja) 2017-12-28
CN107709887B (zh) 2020-03-03
CN107709887A (zh) 2018-02-16
EP3306214A1 (fr) 2018-04-11
EP3306214B1 (fr) 2023-10-18

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