WO2002006738A1 - Circuit de refroidissement pour conditionneur d'air - Google Patents

Circuit de refroidissement pour conditionneur d'air Download PDF

Info

Publication number
WO2002006738A1
WO2002006738A1 PCT/JP2001/006061 JP0106061W WO0206738A1 WO 2002006738 A1 WO2002006738 A1 WO 2002006738A1 JP 0106061 W JP0106061 W JP 0106061W WO 0206738 A1 WO0206738 A1 WO 0206738A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
pipe
heat exchanger
circuit
valve
Prior art date
Application number
PCT/JP2001/006061
Other languages
English (en)
Japanese (ja)
Inventor
Hidehiko Kataoka
Shinichi Sakamoto
Original Assignee
Daikin Industries, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to DE60136707T priority Critical patent/DE60136707D1/de
Priority to EP01947994A priority patent/EP1300637B1/fr
Priority to AU69512/01A priority patent/AU766170B2/en
Publication of WO2002006738A1 publication Critical patent/WO2002006738A1/fr

Links

Classifications

    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/04—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for withdrawing non-condensible gases
    • F25B43/043—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for withdrawing non-condensible gases for compression type systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
    • 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
    • F25B2313/0232—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses
    • 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
    • F25B2313/02331—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during cooling
    • 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
    • F25B2313/02334—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0311—Pressure sensors near the expansion valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor 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
    • F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
    • F25B2345/006—Details for charging or discharging refrigerants; Service stations therefor characterised by charging or discharging 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
    • 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
    • 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
    • F25B2400/0415—Refrigeration circuit bypassing means for the receiver
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • 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
    • F25B2400/16—Receivers
    • 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
    • F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
    • 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
    • F25B2600/02—Compressor control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2523—Receiver 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
    • F25B2700/1931—Discharge 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
    • F25B2700/193—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
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost

Definitions

  • the present invention relates to a refrigerant circuit of an air conditioner, particularly, an outdoor unit-side refrigerant circuit including a compressor, a four-way switching valve, and an outdoor heat exchanger disposed in an outdoor unit, and an indoor heat exchanger disposed in an indoor unit.
  • the present invention relates to a refrigerant circuit of an air conditioner, wherein the refrigerant circuit is connected by a liquid pipe side pipe and a gas pipe side pipe.
  • the refrigerant circuit of an air conditioner is configured by connecting a compressor, a four-way switching valve, and an outdoor heat exchanger disposed in an outdoor unit to an indoor heat exchanger disposed in an indoor unit by refrigerant piping. Yes, constitutes a refrigerant circulation path.
  • the refrigerant circulation direction is changed by the four-way switching valve so that the outdoor heat exchanger functions as a condenser and the indoor heat exchanger functions as an evaporator. Controlled.
  • a high-pressure receiver (hereinafter referred to as a receiver) that temporarily stores the refrigerant liquid condensed in the outdoor heat exchanger is provided in the refrigerant circuit, and the amount of refrigerant in the outdoor heat exchanger that functions as a condenser is determined.
  • the receiver may absorb the change in the amount of refrigerant in some cases.
  • a liquid pipe closing valve is installed on the liquid pipe side pipe connected to the outdoor heat exchanger, and a gas pipe closing valve is installed on the gas pipe side pipe connected to the four-way switching valve.
  • a serial receiver is placed between the shut-off valve and the outdoor heat exchanger.
  • the amount of refrigerant supplied to each indoor heat exchanger is reduced by a pressure reducing circuit provided for each indoor heat exchanger. Can be controlled to an appropriate amount.
  • the amount of refrigerant in the outdoor heat exchanger and the amount of refrigerant in each indoor heat exchanger fluctuates, the amount of refrigerant is adjusted by the receiver and returned to the compressor.
  • the refrigerant is circulated by controlling the four-way switching valve so that the indoor heat exchanger functions as a condenser and the outdoor heat exchanger functions as an evaporator.
  • a pressure reducing circuit such as a motor-operated valve between the receiver and the outdoor heat exchanger in order to store excess refrigerant in the receiver during heating. For this reason, the pressure difference before and after the pressure reducing circuit for distribution corresponding to each indoor heat exchanger becomes small, and the flow of the refrigerant in the indoor heat exchanger may be deteriorated.
  • a refrigerant circuit which is less likely to cause a difference in elevation of a refrigerant even when there is a difference in elevation between installation locations of a plurality of indoor units, thereby enabling cost reduction.
  • the purpose is to do. Disclosure of the invention
  • the refrigerant circuit of the air conditioner according to the present invention includes an outdoor unit-side refrigerant circuit including a compressor, a four-way switching valve, and an outdoor heat exchanger disposed in the outdoor unit, and an indoor heat exchanger disposed in the indoor unit.
  • a refrigerant circuit of the air conditioner which is connected by a liquid pipe side pipe and a gas pipe side pipe, wherein a bypass circuit for bypassing the liquid pipe side pipe and the gas pipe side pipe is provided.
  • a liquid receiving circuit for recovering the liquid refrigerant is provided.
  • the air conditioner further includes a liquid pipe closing valve and a gas pipe closing valve disposed in the outdoor unit and provided between the outdoor unit side refrigerant circuit and the indoor heat exchanger, and the bypass circuit includes a four-way switching valve and a gas pipe.
  • Gas pipe side piping between the shut-off valve, and between the outdoor heat exchanger and the liquid pipe shut-off valve
  • the liquid receiving circuit is provided between the receiver and the liquid pipe, and the receiver is provided in the bypass circuit and collects the liquid refrigerant.
  • the liquid pipe connecting pipe and the gas pipe are connected from the receiver to the liquid pipe.
  • a refrigerant opening / closing means provided on the gas pipe side connection pipe connected to the gas pipe.
  • the refrigerant opening / closing means can be constituted by a functional component capable of depressurizing the refrigerant, and specifically, can be constituted by an electric valve or a cabin.
  • the refrigerant enclosing means can be configured by a functional component capable of shutting off the flow of the refrigerant, and can be configured by, for example, any one of an electric valve, a solenoid valve, and a check valve.
  • the refrigerant enclosing means can be configured with a function having a function of depressurizing the refrigerant and a function of shutting off the flow of the refrigerant, and can be configured with a motor-operated valve or a combination of a capillary and an electromagnetic valve.
  • a configuration may be further provided with a gas venting gallery that is inserted between a gas pipe side pipe between the four-way switching valve and the gas pipe and the receiver.
  • the refrigerant opening / closing means provided on the gas pipe side connection pipe of the receiver is preferably a pressure reducing circuit using an electric valve.
  • the auxiliary heat exchanger is preferably provided below the outdoor heat exchanger.
  • the outdoor heat exchanger may include a subcool heat exchanger located on the liquid pipe side, and the auxiliary heat exchanger and the subcool heat exchanger may be arranged adjacent to each other.
  • the auxiliary heat exchanger is arranged on the windward side of the subcool heat exchanger.
  • a configuration in which a pressure reducing circuit is provided in the liquid pipe side pipe between the outdoor unit side refrigerant circuit and the indoor heat exchanger can be provided.
  • the pressure reducing circuit corresponds to a plurality of connected indoor units. It can be constituted by a partial pressure electric valve provided.
  • the pressure reducing circuit may be provided in a refrigerant branch unit disposed between the outdoor unit-side refrigerant circuit and the indoor heat exchanger.
  • An outdoor unit-side refrigerant circuit including a unit, an indoor heat exchanger disposed in the indoor unit and connected to the outdoor unit-side refrigerant circuit via a liquid pipe side pipe and a gas pipe side pipe, a liquid pipe side pipe and a gas pipe
  • a receiver disposed on a bypass circuit for bypassing the side pipe and recovering excess refrigerant on the refrigerant circuit; a liquid pipe side connection pipe connected from the receiver to the liquid pipe side pipe and a gas pipe connected to the gas pipe side pipe
  • a refrigerant circuit including refrigerant switching means disposed on the side connection pipe, and controlling the temperature of the discharge pipe of the compressor to a predetermined value by controlling the opening and closing of the refrigerant switching means. Suggest a machine.
  • the medium opening / closing means provided on the gas pipe side connection pipe of the receiver can be constituted by a pressure reducing circuit using an electric valve.
  • FIG. 1 is a schematic configuration diagram of a first embodiment of the present invention.
  • FIG. 2 is a schematic configuration diagram of a second embodiment of the present invention.
  • FIG. 3 is a schematic configuration diagram of a third embodiment of the present invention.
  • FIG. 4 is a schematic configuration diagram of a fourth embodiment of the present invention.
  • FIG. 5 is a schematic configuration diagram of a fifth embodiment of the present invention.
  • FIG. 6 is a schematic configuration diagram of a sixth embodiment of the present invention.
  • FIG. 5 is a schematic configuration diagram of a second embodiment of the present invention.
  • FIG. 8 is a schematic configuration diagram of an eighth embodiment of the present invention.
  • FIG. 9 is a schematic configuration diagram of a ninth embodiment of the present invention.
  • FIG. 10 is a simplified explanatory view of an outdoor heat exchanger.
  • FIG. 11 is a configuration diagram of the embodiment.
  • Fig. 12 is a control flowchart during heating operation.
  • FIG. 13 is an explanatory diagram showing an operation example during the heating operation.
  • FIG. 14 is an explanatory diagram showing an operation example during the heating operation.
  • FIG. 15 is an explanatory diagram showing an operation example during the heating operation.
  • FIG. 16 is an explanatory diagram showing an operation example during the heating operation.
  • Figure 17 is a control flowchart for cooling operation.
  • FIG. 18 is an explanatory diagram showing an operation example during cooling operation.
  • FIG. 19 is an explanatory diagram showing an operation example during cooling operation.
  • FIG. 20 is an explanatory diagram showing an operation example during cooling operation.
  • FIG. 21 is an explanatory diagram showing an operation example during cooling operation.
  • FIG. 22 is an explanatory diagram showing an operation example during cooling operation.
  • Fig. 23 is a flowchart of the target discharge pipe temperature control using the outdoor unit electric valve.
  • Fig. 24 is a flowchart of target discharge pipe temperature control using an outdoor unit electric valve.
  • FIG. 25 is a flowchart of control condition (1).
  • FIG. 26 is a flowchart of calculating a temporary target discharge pipe temperature during cooling.
  • Fig. 27 is a flowchart for calculating the temporary target discharge pipe temperature during heating.
  • Figure 28 is a flowchart for calculating the target discharge pipe temperature.
  • Fig. 29 is a flowchart of control condition (1).
  • a plurality of indoor units 200A, 200B, ... are connected to the outdoor unit 100 via branch units 300A, 300B, ...
  • the outdoor unit 100 is provided with a compressor 101, a four-way switching valve 102, an outdoor heat exchanger 103, an accumulator 105, and the like.
  • the discharge side of the compressor 101 is provided with a discharge pipe temperature sensor 109 for detecting a discharge pipe temperature.
  • the outdoor unit 100 has an external air temperature sensor 111 for detecting the temperature of the outdoor air, and an outdoor heat exchanger 110 for detecting the temperature of the outdoor heat exchanger 103. 1 and 2 are provided.
  • a fan 106 for sucking outside air and exchanging heat between the sucked outside air and the refrigerant flowing inside the outdoor heat exchanger 103, and a fan motor for rotating and driving the fan 106.
  • One night and 104 are provided.
  • the outdoor unit 100 has a liquid pipe connection port 114 connected to the outdoor heat exchanger 103, and a four-way switching valve. 1 0 2 A connected gas pipe connection port 115 is provided. Further, a liquid pipe closing valve 1 16 and a gas pipe closing valve 1 17 are provided inside each connection port.
  • the outdoor unit 100 is provided with a receiver 122 that temporarily stores excess refrigerant liquid from the outdoor heat exchanger 103 that functions as a condenser during the cooling operation.
  • the receiver 12 1 has a liquid pipe side connection pipe 122 and a gas pipe side connection pipe 123.
  • the liquid pipe side connection pipe 1 2 2 is connected to the liquid pipe side pipe section 1 3 1 between the outdoor heat exchanger 103 and the liquid pipe closing valve 1 16 and the gas pipe side connection pipe 1 2 3 Is connected to a gas pipe side piping section 132 between the four-way switching valve 102 and the gas pipe closing valve 117.
  • a plurality of branch units 300OA, 300B ⁇ ⁇ ⁇ are connected to the liquid pipe connection port 114 and the gas pipe connection port 115 of the outdoor unit 100. Since each of the branch units 300A and 300B has the same configuration, only the branch unit 300OA will be described, and description of the other units will be omitted.
  • the branch unit 300 A is connected to the liquid pipe connection port 301 of the outdoor unit 100 and to the liquid pipe connection port 301 of the outdoor unit 100, and to the gas pipe connection port 115 of the outdoor unit 100.
  • An outdoor gas pipe connection port 303 to be connected is provided.
  • the branch unit 30 OA is provided with a liquid pipe side branching path that branches inside the outdoor liquid pipe connection port 301, and at the tip thereof, the indoor liquid pipe connection port of the number of indoor units to be connected. 302 is provided.
  • a gas pipe-side branch path that branches inside the outdoor gas pipe connection port 303 is provided, and at the tip thereof, there are provided indoor gas pipe connection ports 304 of the number of indoor units to be connected. ing.
  • three indoor units are connected, and the indoor liquid pipe connection ports 302 A, 302 B, 302 C and the indoor gas pipe connection ports 304 A, 304 B, 304 C shall be provided.
  • the refrigerant pressure passing through the inside is There are motorized valves for reducing the pressure, 300 A to 300 C, and liquid tubes for detecting the temperature of the refrigerant passing through the inside, and 300 A to 300 C, respectively. . Also, the refrigerant passing through the inside of the branch from the outdoor gas pipe connection port 303 in the branch unit 30 OA to each of the indoor gas pipe connection ports 304 A to 304 C is provided. There is a gas line for detecting the temperature. A plurality of indoor units 200 are connected to each branch unit 300A, 30OB.
  • each branch unit 300A, 300B ⁇ the number of indoor units that can be connected to each branch unit 300A, 300B ⁇ is three, indoor units 200A to 200C are connected to branch unit 30OA, and indoor units are connected to branch unit 300B. It is assumed that 200D to 20 OF are connected.
  • Each of the indoor units 200A to 20OF can be used either as a multi-unit indoor unit or a pair-unit indoor unit.
  • a pair-unit indoor unit is used as the indoor unit 20OA will be described.
  • the indoor unit 20OA includes an indoor heat exchanger 201, and refrigerant piping connected to the indoor heat exchanger 201 is connected to the outdoor unit via a liquid pipe connection port 204 and a gas pipe connection port 205. Derived.
  • the indoor unit 20 OA includes a room temperature sensor 202 for detecting the indoor temperature and an indoor heat exchange sensor 203 for detecting the temperature of the indoor heat exchanger 201. .
  • a liquid tube thermistor for detecting the temperature of the refrigerant flowing inside is provided in the liquid tube side piping section. In such a case, it is possible to omit the liquid tube thermistors in the branch units 300A and 300B.
  • the gas pipe side connection pipe 123 of the receiver 121 may be configured to be connected to a gas pipe section between the four-way switching valve 102 and the accumulator 105.
  • the receiver 121 is provided in a bypass circuit connecting the liquid pipe closing valve 116 and the gas pipe closing valve 117 of the outdoor unit 100, and the excess refrigerant is recovered by the receiver 121.
  • the refrigerant is distributed by the electric valves 305 A to 305 C, 305 D to 305 F in the branching units 300 A, 300 B
  • the refrigerant is connected to the liquid pipe side connection pipe 122 and the gas pipe side connection pipe 123 of the receiver 122. It is conceivable to provide a functional component that blocks the flow. Motorized valves, solenoid valves, check valves, etc. can be considered as functional components that block the flow of refrigerant.
  • the surplus refrigerant can be reliably collected in the receiver 121, and the distribution of refrigerant by the electric valves in the branch units 30OA, 300B And the occurrence of height difference drift can be prevented.
  • ⁇ Fourth embodiment Provide functional components having a decompression function and a refrigerant shutoff function before and after the receiver>
  • the liquid pipe side connection pipe 122 and the gas pipe side connection pipe 123 of the receiver 122 with functional components having a decompression function and a refrigerant cutoff function.
  • a functional component it is conceivable to use a motor-operated valve having a pressure reducing function and a shut-off function, or a combination of a cab and a solenoid valve.
  • the liquid tube motorized valve (EVL) 1 28 is provided on the liquid tube side connection tube 122 of the receiver 121, and the gas tube motorized valve (EVL) is mounted on the gas tube side connection tube 123 of the receiver 121.
  • EVG) 1 2 9 is provided.
  • the gas venting capillaries are provided between the receiver 12 1 and the gas pipe side piping section 13 2. May be provided. In this case, as shown in FIG. 5, gaseous refrigerant is supplied from the receiver 12 21 to the gas pipe side piping section 13 2 between the four-way switching valve 102 and the gas shutoff valve 1 17.
  • a degassing capillary 130 can be provided for recovery.
  • a gas venting capillary is provided in the pipe between the four-way switching valve and the accumulator which is always a low-pressure pipe.
  • the refrigerant flows from the high-pressure side to the low-pressure side, resulting in reduced efficiency during normal operation.
  • the degassing cavities are always connected to the low-pressure pipe, so the flow characteristics of the cavities need to be reduced. It is difficult to improve the recovery efficiency.
  • the gaseous medium in the receiver 12 1 can be returned to the accumulator suction side through the degassing cavity 130, and the liquid refrigerant can be transferred to the receiver 1. It is possible to make it easier to store the refrigerant in the refrigerant pipe 1, and close the liquid pipe motor valve 128 during normal operation to shut off the refrigerant flow from the gas venting cabinet 130 during cooling operation.
  • the inside of the receiver 122 can be maintained at a high pressure, and the backflow of the refrigerant from the liquid-tube electric valve 128 can be prevented, and the excess refrigerant can be treated during the heating operation.
  • the gas pipe side connection pipe 1 2 3 of the receiver 1 2 A gas-tube motorized valve 12 9 with the function is provided.
  • An auxiliary heat exchanger 13 is provided between the gas pipe motorized valve 12 9 and the connection to the gas pipe side piping section 13 2.
  • the auxiliary heat exchanger 133 functions as a condenser, so that the speed of storing the excess refrigerant in the receiver 122 can be increased.
  • a liquid pipe motor valve 1 28 and a gas pipe motor valve 12 9 connected to the receiver 1 2 1 are provided, and auxiliary heat exchange between the gas pipe motor valve 12 9 and the gas pipe piping section 13 2 is provided.
  • the provision of the heat exchanger 133 makes it possible to control the state of the refrigerant at the outlet of the outdoor heat exchanger 103 (the liquid pipe piping section 131) during the cooling operation.
  • the receiver 1 2 1 It is possible to control the discharge pipe temperature by reducing the amount of refrigerant discharged from the pipe. In addition, it is possible to adjust the rate at which excess refrigerant is stored during the heating operation, and since the condensing capacity of the auxiliary heat exchangers 133 is variable, the conditions under which high pressure is likely to increase, such as heating overload operation In this case, the condensing capacity of the auxiliary heat exchanger 133 is increased by increasing the opening of the gas pipe motorized valve 129, which can contribute to a decrease in high pressure.
  • the auxiliary heat exchanger 13 is connected to the gas pipe side connection pipe 12 3 of the receiver 12 1.
  • FIG. 7 shows the seventh embodiment.
  • the auxiliary heat exchanger 133 connected to the gas pipe side connection pipe 123 of the receiver 122 is provided inside the outdoor heat exchanger 103, and the auxiliary heat exchanger 103 is connected to the outside heat exchanger 103. Located at the bottom.
  • the condensed water after the defrost operation may re-freeze on the bottom frame of 0 and develop to the outdoor heat exchanger 103, which may cause a decrease in operating performance.
  • the auxiliary heat exchanger 133 By arranging the auxiliary heat exchanger 133 at the lowermost portion of the outdoor heat exchanger 103 as in the seventh embodiment, the auxiliary heat exchanger 133 during the heating operation at a low outside air temperature can be provided.
  • the refrigerant flowing through the water can prevent re-icing of the condensed water, and can prevent the performance of the outdoor heat exchanger 103 from lowering.
  • a subcool heat exchanger 13 4 is located at the lower part of the outdoor heat exchanger 103, and an auxiliary heat exchanger is located at the lower part and at the lowest layer of the outdoor heat exchanger 103. Place 1 3 3
  • the cooling capacity of the adjacent subcool heat exchangers 13 4 can be increased by the evaporation capacity of the auxiliary heat exchangers 13 3, and the refrigerant at the outlet of the outdoor heat exchanger 10 3 can be cooled.
  • the degree of supercooling can be increased.
  • an auxiliary heat exchanger is arranged on the windward side of a subcool heat exchanger>
  • the cooling pipe of the auxiliary heat exchanger is arranged on the windward side of the cooling pipe of the subcool heat exchanger. Is considered.
  • the outdoor heat exchanger 103 is provided with a plurality of cooling pipes 17 1 turned back at one end and a communication for passing the cooling pipes 17 1.
  • a plurality of heat dissipating fins 1 and 2 made of a metal plate member having holes formed therein are provided.
  • Distributors 173 and 174 are provided at both ends of each cooling pipe 171, one of which serves as a refrigerant inlet when functioning as an evaporator, and another when functioning as a condenser. The one functions as a refrigerant inlet.
  • FIG. 9 shows a side view in which only the lower end portion of such an outdoor heat exchanger 103 is enlarged.
  • a tube sheet 175 supporting both ends of the cooling pipe 171 is provided on the side surface of the outdoor heat exchanger 103.
  • This tube sheet 17 5 is almost the same as the radiation fin 17 2 It has the same shape, and has a through hole 176 through which the cooling pipe 171 passes.
  • the cooling pipes 171, which are arranged between the distributors 173 and 174, are connected to the respective communication holes 176.
  • the distributor 1 ⁇ 4 of the outdoor heat exchanger 103 is connected to the four-way selector valve 102, and the distributor 173 is connected to the sub-cooler heat exchanger 133.
  • the subcool heat exchanger 134 has an SC reject pipe 177 that has one end connected to the distributor 1 ⁇ 3 and the other end connected to the liquid shutoff valve 116.
  • the auxiliary heat exchanger 1 33 has one end connected to the gas pipe side motorized valve 12 9, and the other end connected to the gas pipe side piping section 13 2. 8 will be provided.
  • FIG. 11 shows a preferred embodiment of the present invention.
  • the outdoor unit 100 includes an outdoor unit-side refrigerant circuit including a compressor 101, a four-way switching valve 102, an outdoor heat exchanger 103, an accumulator 105, and the like.
  • the discharge side of the compressor 101 is provided with a discharge side pressure protection switch 108 for detecting an abnormal rise in the discharge pressure, and the suction side of the compressor 101 is for detecting the suction pressure.
  • a pressure sensor 110 is provided.
  • An oil separator 107 for separating the lubricating oil contained in the refrigerant and returning it to the accumulator 105 is provided on the discharge side of the compressor 101.
  • This A discharge pipe thermistor 109 for detecting the temperature on the discharge side of the compressor 101 is attached to the filter separator 107.
  • the discharge-suction bypass which connects the outlet side of the oil separation unit 107 and the inlet side of the accumulator 105, has a discharge-suction cabin for adjusting the discharge pressure and suction pressure.
  • An electric discharge-suction electric valve (EVP) 144 for control is provided.
  • the outdoor unit 100 has an outside air temperature sensor for detecting the temperature of the outdoor heat exchanger 103, and an outdoor air heat exchanger for detecting the temperature of the outdoor heat exchanger 103.
  • a fan 106 for sucking outside air and exchanging heat between the sucked outside air and the refrigerant flowing inside the outdoor heat exchanger 103, and a fan motor for rotating the fan 106
  • One night and 104 are provided.
  • the outdoor unit 100 is connected to the liquid pipe connection ports 1 1 4 connected to the outdoor heat exchanger 103, It has a gas pipe connection port 1 15 connected to the switching valve 102, and a liquid pipe closing valve 1 16 and a gas pipe closing valve 1 17 are provided inside each connection port. I have.
  • the outdoor unit 100 is provided with a receiver 122 that temporarily stores excess refrigerant liquid from the outdoor heat exchanger 103 that functions as a condenser during the cooling operation.
  • the receiver 1 2 1 has a liquid pipe side connection pipe 1 2 2 and a gas pipe side connection pipe 1 2 3 .
  • the liquid pipe side connection pipe 1 2 2 has an outdoor heat exchanger 103 and a liquid pipe closed.
  • the gas pipe side connection pipe 1 2 3 is connected to the liquid pipe side pipe section 13 1 between the valve 1 16 and the gas pipe side connection pipe 1 2 3 is the gas pipe between the four way switching valve 10 2 and the gas pipe closing valve 1 17 It is connected to the side piping section 1 32.
  • a liquid tube motorized valve (EVL) 128 having a decompression function and a refrigerant shutoff function is provided in the liquid tube side connection tube 122 of the receiver 122, and the gas tube side connection tube 123 is provided. Is equipped with a gas pipe valve (EVG) 129.
  • An auxiliary heat exchanger 13 is provided between the gas pipe motorized valve 12 9 and the connection to the gas pipe side piping section 13 2.
  • This auxiliary heat exchanger 133 is configured by disposing an auxiliary cooling pipe 178 at the bottom of the outdoor heat exchanger 103 as shown in FIG.
  • a subcool heat exchanger 134 is arranged at the outlet of the outdoor heat exchanger 103 on the liquid tube side.
  • the subcool heat exchanger 13 4 is located on the leeward side of the auxiliary cooling pipe 17 8 of the auxiliary heat exchanger 13 3, and the SC cooling pipe 17 7 is arranged. Therefore, it is possible to adopt a configuration arranged adjacent to the auxiliary heat exchanger 13.
  • Degassing cavities 1 3 0 for collecting gaseous refrigerant from the receiver 1 2 1 toward the gas pipe side piping section 1 32 between the four-way switching valve 102 and the gas shut-off valve 1 17 Is provided.
  • branch units 300A, 300B ⁇ ⁇ ⁇ are connected to the liquid pipe connection port 114 and the gas pipe connection port 115 of the outdoor unit 100. Since each branch unit 300 A, 300 B... Has the same configuration, the branch unit 300 A will be described, and the description of the other units will be omitted.
  • the branch unit 300 A is connected to the liquid pipe surrounding port 114 of the outdoor unit 100, and the outdoor liquid pipe connection port 301 is connected to the gas pipe of the outdoor unit 100.
  • An outdoor gas pipe connection port 303 connected to the connection port 115 is provided.
  • the branch unit 300A is provided with a liquid pipe-side branch passage that branches inside the outdoor liquid pipe connection port 301, and at the tip thereof, the indoor liquid pipes of the number of indoor units to be connected are provided.
  • a connection port 302 is provided.
  • a gas pipe-side branch path that branches inside the outdoor gas pipe connection port 303 is provided, and at the tip thereof, there are provided indoor gas pipe connection ports 304 of the number of indoor units to be connected. ing.
  • the indoor liquid pipe connection ports 302 A, 302 B, 302 C and the indoor gas pipe connection ports 304 A, 304 B, 304 C shall be provided.
  • an electric valve for bypass 308 is provided between the outdoor liquid pipe connection port 301 and the outdoor gas pipe connection port 303.
  • Branch unit 30 In the branch path from the outdoor-side liquid pipe connection port 301 in the OA to each indoor-side liquid pipe connection port 302 A to 302 C, the refrigerant pressure passing through the inside is reduced.
  • Each is provided with a motor-operated valve 300 A to 300 C for pressurizing and a liquid pipe sump 300 A to 300 C for detecting the temperature of the refrigerant passing therethrough.
  • the branching passage from the outdoor-side gas pipe connection port 303 in the branch unit 30 OA to each of the indoor-side gas pipe connection ports 304 A to 304 C passes through the inside.
  • a gas tube thermistor 307 A to 307 C for detecting the medium temperature is provided.
  • a plurality of indoor units 200 are connected to each branch unit 300 A, 300 B.
  • the one shown is connected to each branch unit 300A, 300B
  • the number of possible indoor units is 3, the branch unit 300A is connected to the indoor units 200A to 200C, and the branch unit 300B is connected to the indoor units 200D to 200D.
  • OF shall be connected.
  • Each of the indoor units 200 A to 20 OF can be used as either an indoor unit for a multi-unit or an indoor unit for a pair unit. Will be described.
  • the indoor unit 20OA includes an indoor heat exchanger 201, and refrigerant pipes connected to the indoor heat exchanger 201 include a liquid pipe connection port 204 and a gas pipe connection port 205. Through the outdoor unit.
  • the indoor unit 20 OA includes a room temperature sensor 202 for detecting the indoor temperature and an indoor heat exchanger 210 for detecting the temperature of the indoor heat exchanger 201. 0 and 3.
  • a liquid pipe for detecting the temperature of the refrigerant flowing inside the pipe section on the liquid pipe side is used.
  • thermistors are provided, and in this case, it is possible to omit the liquid tubes in the branch units 300A and 300B.
  • the discharge-suction bypass motor-operated valve 142 is used when the refrigerant capacity of the indoor unit is small (when the number of operating units is small or when the capacity of the indoor heat exchanger of the operating indoor unit is small). To prevent the discharge pressure from increasing during the heating operation, and to prevent the low-pressure piping from freezing during the cooling operation.
  • the liquid pipe motorized valve 128 is controlled to open and close when there is excess refrigerant in the receiver 122 while the gas pipe motorized valve 129 is open, thereby controlling the entire system.
  • the presence or absence of surplus refrigerant is determined, and the surplus refrigerant is controlled in the outdoor unit SC control.
  • the gas pipe motorized valve 12 9 opens the predetermined opening when the surplus refrigerant processing is required during the heating operation to store the surplus refrigerant in the receiver 12 1, and the liquid refrigerant during the cooling operation If there is excess refrigerant in the receiver 121 while the pipe motor valve 128 is open, the entire system is controlled by opening and closing control.
  • Fig. 12 shows an operation example during the heating operation.
  • step S1 it is determined whether or not there is no surplus refrigerant in the refrigerant circuit and it is not necessary to perform capacity control.
  • step S2 the discharge-suction bypass electric valve 142 is fully closed, the liquid pipe electric valve 128 is fully opened, and the gas pipe electric valve 122 is fully closed.
  • the outdoor heat exchanger 103 functions as an evaporator
  • the indoor heat exchanger 201 of each indoor unit functions as a condenser.
  • Each of the motorized valves 300A to 300C and 300D to 300F in the branch unit 300A, 300B is controlled by the opening according to the setting of each indoor unit.
  • the refrigerant is distributed to the indoor heat exchangers 201.
  • the motor-operated valve for bypass 300 is in the fully closed state, so the motor-operated valve 300 A to 300 C, 30 disposed in the branch unit 300A, 300B.
  • the refrigerant distribution to each indoor heat exchanger 201 is appropriately performed by 5D to 305F. Also, since no excess refrigerant is generated in the circuit, the receiver 1 2 1 is not functioning, and the discharge-intake bypass electric valve 1 42, liquid pipe electric valve 1 28, gas pipe electric valve 1 29 are not used for control.
  • step S3 it is determined whether or not there is excess refrigerant on the refrigerant circuit and there is no need to perform capacity control.
  • the process proceeds to step S4.
  • step S4 the discharge / suction bypass electric valve 142 is fully closed, the gas pipe electric valve 122 is fixed, and the liquid pipe electric valve 128 is controlled according to the target discharge pipe temperature. I do. For example, as shown in Fig. 14, when only the indoor units 200A to 200C connected to the branch unit 300A are operating, the capacity of the outdoor unit 100 It is conceivable that excess refrigerant is generated.
  • the refrigerant condensed in the auxiliary heat exchanger 133 can be introduced and stored in the receiver 122 by opening the gas pipe motorized valve 129 at a fixed rate.
  • Refrigerant passing through gas pipe motor valve 1 2 9 is auxiliary Since it is condensed in the heat exchanger 13 3, its temperature does not exceed the heat-resistant temperature of a general motor-operated valve, and it is possible to select an inexpensive gas pipe motor-operated valve 12 9.
  • the degree of opening of the liquid pipe motorized valve 128 in accordance with the target discharge pipe temperature the excess refrigerant in the receiver 121 is adjusted to control the degree of suction superheat, thereby achieving overall system control. can do.
  • step S5 it is determined whether or not there is surplus refrigerant in the refrigerant circuit and it is necessary to perform capacity control. For example, if there is surplus refrigerant in the refrigerant circuit and the peak cut control is in the drooping zone even if the operating frequency of the compressor 101 is at the lower limit frequency, the surplus refrigerant flows and the volume control It is determined that it is necessary to perform step S6, and the process proceeds to step S6.
  • step S6 while the discharge-suction bypass motor-operated valve 142 remains in the fully closed state, the gas pipe motor-operated valve 1229 is controlled so as to be stable in a non-change range in the peak cut control.
  • the opening degree of the liquid pipe motorized valve 128 is controlled in accordance with the target discharge pipe temperature.
  • the condensing capacity of the auxiliary heat exchanger 13 3 is increased, and the gas pipe motorized valve 12 9 is opened so that it becomes stable in the peak cut control unchanged region. Perform degree control.
  • the refrigerant condensed through the auxiliary heat exchanger 13 3 is introduced into the receiver 12 1, excess refrigerant is stored in the receiver 12 1, the refrigerant capacity on the high pressure side is stabilized, and compression is performed. Stabilizes the frequency control of the machine 101 in the unchangeable range of the peak cut control.
  • the overall system control is to control the opening of the liquid pipe motorized valve 128 to correspond to the target discharge pipe temperature. This is performed by adjusting the excess refrigerant in the receiver 122.
  • step S7 it is determined whether or not the gas pipe motorized valve 129/29 is fully open and still in the dripping zone of the peak cut control.
  • Operating frequency of compressor 101 is lower limit frequency Even if the number is reached, if the beak cut control is in the drooping zone, and if the gas pipe motorized valve 12 9 is fully open and still is in the drooping zone of peak cut control, the process proceeds to step S8.
  • step S8 the opening degree of the discharge / suction bypass electric valve 142 is controlled so that the frequency control of the compressor 101 is stabilized in a range where the peak cut control is not changed.
  • the gas pipe motorized valve 129 is fully opened, and the liquid pipe motorized valve 128 performs the control in accordance with the target discharge pipe temperature.
  • the displacement control is performed by controlling the discharge-suction bypass motor-operated valve 142, and the frequency control of the compressor 101 is stabilized in the unchanged range of the peak cut control.
  • the overall system control suction superheat control
  • Figure 1 ⁇ shows an operation example during cooling operation.
  • step S11 it is determined whether or not there is excess refrigerant on the refrigerant circuit and the volume control is not required.
  • the process proceeds to step S12.
  • step S 12 the discharge-suction bypass motorized valve 14 2 is fully closed, the gas pipe motorized valve 12 9 is fully opened, and the liquid pipe motor is operated to perform SC control using the subcool heat exchanger 13 4. Valves 1 2 8 are fully closed.
  • the outdoor heat exchanger 103 functions as a condenser
  • the indoor heat exchanger 201 of each indoor unit functions as an evaporator.
  • Branch unit 30 OA, 300 B The electric valves 3 0 5 A to 3 0 5 C and 3 0 5 D to 3 0 5 F are controlled by the opening according to the setting of each indoor unit, and each indoor heat exchanger 2 0 1 It is configured to distribute refrigerant to the The motor-operated valve for bypass 3008 is in the fully closed state here. Therefore, the motor-operated valve 300 to 300C, 3 disposed in the branch units 300A and 300B.
  • the refrigerant distribution to each of the indoor heat exchangers 201 can be appropriately performed by using 05D to 300F.
  • step S13 it is determined whether or not there is excess refrigerant in the refrigerant circuit and there is no need to perform capacity control. If it is determined that there is surplus refrigerant and it is not necessary to perform capacity control, the process proceeds to step S14.
  • step S14 the discharge-suction bypass motorized valve 142 is fully closed, and the liquid tube motorized valve 128 is opened to the extent that SC control by the subcool heat exchanger 134 is possible. Not fully open).
  • the opening degree of the gas pipe motorized valve 129 is controlled so that the discharge pipe temperature of the compressor 101 becomes the target temperature, and the entire system is controlled (intake superheat control).
  • the liquid refrigerant can be introduced and stored in the receiver 122 by opening the liquid tube motorized valve 128.
  • the excess refrigerant in the receiver 221 is adjusted to control the degree of superheating of the suction system. Control.
  • step S15 there is surplus refrigerant in the refrigerant circuit, and it is necessary to perform capacity control. It is determined whether there is any state. If it is determined that the surplus refrigerant has run out and it is necessary to perform capacity control, the process proceeds to step S16. For example, in a state where the number of operating indoor units is small and there is excess refrigerant, if the anti-freezing control is a drooping zone even when the operating frequency of the compressor 101 reaches the lower limit frequency, the capacity control is performed. It is determined that it is necessary to carry out, and the process proceeds to step S16.
  • step S16 the opening degree control of the discharge-suction bypass electric valve 142 is performed so that the frequency control of the compressor 101 is stabilized in the non-change range of the freeze prevention control.
  • the opening control of the liquid pipe motorized valve 128 is performed (not fully open), and the liquid refrigerant is stored in the receiver 122.
  • the amount of refrigerant in the receiver 122 is adjusted by controlling the degree of gas pipe motor valve 122 corresponding to the target discharge pipe temperature. Controls the entire system.
  • the electric valve 3 0 5 C corresponding to the indoor heat exchanger 2 0 1 of the operating indoor unit performs opening control according to the indoor temperature setting and other electric valves 3 0 5 A, 3 0 5 B and the electric valves 300D to 300F in the branch unit 300B are in a closed state.
  • the opening of the discharge-suction bypass electric valve 142 the frequency control of the compressor 101 is stabilized, and by adjusting the opening of the liquid pipe electric valve 128, the excess refrigerant is obtained.
  • the entire system can be controlled by performing the process and adjusting the opening of the gas pipe motorized valve 129.
  • step S17 it is determined whether or not the outside air temperature is lower than a predetermined temperature. If the liquid pipe motor valve 1 28 is fully closed when the outside air temperature is lower than the predetermined temperature, the pressure in the receiver 1 21 becomes lower than the suction pressure of the compressor 101, The liquid refrigerant accumulated in the receiver 122 may not be able to be drawn. In this case, a shortage of the refrigerant in the refrigerant circuit may occur. Therefore, when it is determined that the outside air temperature is lower than the predetermined temperature assumed to be in such a state, the process proceeds to step S18.
  • step S18 the liquid tube motorized valve 1
  • the pressure in 1 2 1 is made higher than the pressure in the gas pipe piping section 1 32, and the liquid refrigerant in the receiver 1 2 1 is discharged to the auxiliary heat exchanger 1 33 side.
  • the target discharge pipe temperature can be controlled by controlling the degree of the gas pipe motorized valve 122, and the entire system can be controlled. .
  • the electric discharge-by-suction bypass electric valve 142 to prevent freezing, the suction pressure of the compressor 101 can be increased.
  • the liquid tube motorized valve 128 is fully closed so that the liquid refrigerant is not introduced into the receiver 121, but the liquid tube motorized valve 128 is completely closed. Once closed, the liquid refrigerant that has once accumulated cannot be removed. Therefore, by opening the liquid pipe motorized valve 128 at a predetermined opening and controlling the opening of the gas pipe motorized valve 125, the liquid refrigerant is discharged to the auxiliary heat exchanger 133 side, and the entire system Can be configured to be performed.
  • the indoor unit evaporating temperature is configured to be stably controlled in the unchangeable range of the tsunami prevention control. .
  • the outdoor heat exchanger 103 of the outdoor unit 100 may freeze.
  • the defrost operation (defrosting operation) according to the cooling operation can be performed to release the freezing of the outdoor heat exchanger 103.
  • the discharge-suction bypass motorized valve 142 is fully closed, the liquid pipe motorized valve 128 is fully closed, and the gas pipe motorized valve 129 is fully open, and the outdoor
  • the defrost operation is performed by using the heat exchanger 103 as a condenser.
  • the defrost operation is terminated assuming that the freezing of the outdoor heat exchanger 103 has been completed. Since such defrost operation is generally considered to be performed in winter, it is considered that heating operation is performed following this defrost operation.
  • the liquid pipe motorized valve 128 is opened, and the opening of the gas pipe motorized valve 129 is controlled to be equal to the suction amount of the compressor 101.
  • the liquid refrigerant can be introduced into the receiver 122 and stored therein, so that liquid storage and liquid back do not occur in the accumulator 105. Therefore, it is possible to improve the start-up performance of the heating operation after the end of the defrost operation.
  • the gas pipe motorized valve 12 9 when the gas pipe motorized valve 12 9 is provided on the gas pipe side connection pipe 12 3 of the receiver 12 21, the gas pipe motorized valve 12 By controlling the opening and closing of 9, the amount of liquid injection that returns the excess refrigerant in the receiver 121 to the compressor 101 side can be adjusted, whereby the discharge pipe temperature of the compressor 101 can be adjusted. Control can be performed. Also, if the liquid pipe motorized valve 1 28 is provided on the liquid pipe connection pipe 122 of the receiver, and the gas pipe motor valve 129 is provided on the gas pipe connection pipe 123, the cooling Z heating In both cases, the amount of liquid injection from the receiver 121 to the compressor 101 can be adjusted, and the operating efficiency can be improved.
  • the target discharge pipe temperature is obtained from the indoor heat exchanger temperature and the outdoor heat exchanger temperature, and the opening of the liquid pipe motor valve 1 28 and the gas pipe motor valve 12 9 is adjusted so that the actual discharge pipe temperature approaches them. I do.
  • the condensing temperature and the evaporating temperature fluctuate greatly due to disturbance.
  • the average value of the target discharge pipe temperature thus obtained and the target discharge pipe temperature obtained this time temporary target discharge pipe temperature
  • Fig. 23 and Fig. 24 show examples of target discharge pipe temperature control by controlling the degree of opening of the liquid pipe motorized valve 1 28 and gas pipe motorized valve 12 9 connected to the receiver 12 1 in the outdoor unit 100. This will be described based on the flowchart shown in FIG.
  • step S21 it is determined whether control condition 1 for starting target discharge pipe temperature control by the outdoor electric valve is satisfied.
  • Control condition 1 is determined based on the flowchart shown in FIG.
  • step S41 it is determined whether or not normal operation is being performed. If the operation mode of the air conditioner is in the normal cooling operation or the normal heating operation, the process proceeds to step S44. Otherwise, the process proceeds to step S42.
  • step 42 it is determined whether or not a trial operation is being performed. If the operation mode of the air conditioner is during the cooling test operation or the heating test operation, the flow shifts to step S4. Otherwise, the flow shifts to step S43.
  • step S43 it is determined whether or not the heating operation before the defrosting is being performed.
  • the process proceeds to step S44, and otherwise, the process proceeds to step S9.
  • step S444 it is determined whether or not the electric valve 305 in the branch unit 300 is being controlled when the operating room is changed. Immediately after any one of the indoor units 200 is started or when the operating room is changed, such as immediately after the operation is stopped, if the electric valve 305 in each branch unit 300 is controlled, the step is executed. Move to 49, otherwise go to step S45.
  • step S45 it is determined whether or not the frequency change control is being performed. If the operation frequency change control of the compressor 101 based on the change of the air conditioning load in the indoor unit 200 during operation, etc., is performed, the process proceeds to step S49. Otherwise, the process proceeds to step S4. Move to 6.
  • step S46 it is determined whether or not the discharge pipe high temperature control is being performed.
  • Compressor 1 If the discharge pipe temperature of 01 is higher than the predetermined temperature, the liquid pipe motor valve 1 28 and the gas pipe motor valve 1 29 are raised by a fixed amount, and the receiver 1 2 1 The high temperature control of the discharge pipe for backing the liquid refrigerant to the accumulator 105 side is performed. If such discharge pipe high temperature control is being performed, the process proceeds to step S49. Otherwise, the process proceeds to step S47.
  • step S47 it is determined whether or not control is performed at the time of discharge tube thermistor evening. If the discharge pipe temperature detected by the discharge pipe temperature sensor 109 does not exceed the specified value even after a certain period of time has elapsed since the start-up, the discharge pipe temperature error 109 is dropped. However, it may be based on environmental conditions such as abnormally low outside air temperature. In the latter case, since there is no need to perform an inspection with the system down, the discharge pipe temperature is estimated from another temperature sensor, etc., and test operation is continued. Confirm that it has not dropped out. The operation control at this time is referred to as control at the time of discharge pipe error. If the control at the time of discharge pipe error is performed, the process proceeds to step S49. Go to step 48.
  • step S48 the mode is set to control the target discharge pipe temperature by controlling the degree of opening of the motor-operated valves 1228 and 1229 in the outdoor unit 100. In step S49, this control is performed. Set to no mode.
  • step S21 if control condition ⁇ ⁇ is satisfied and the mode of target discharge pipe temperature control by the outdoor unit electric valve is set, the process proceeds to step S23. If the mode is set not to perform this control, the process proceeds to step S22.
  • step S22 a flag indicating whether or not the sampling timer is started for the first time is set to ON in the initial state, and the process returns to the main routine of the overall control.
  • step S23 the sampling time is moved by ⁇ .
  • This sampling timer counts the sampling timing of the discharge pipe temperature control for controlling the discharge pipe temperature.
  • step S24 it is determined whether or not the value for counting the sampling time has exceeded a preset sampling time TTHS1.
  • This sampling time TTHS1 is set in the range of 0 to 255 x 100 msec. For example, it can be set to about 20 sec.
  • step S24 If it is determined in step S24 that the count value of the sampling time has exceeded the sampling time TTHS1, the process proceeds to step S25.
  • step S25 the target discharge pipe temperature D OSET is determined.
  • the temporary target discharge pipe temperature D OSETN during cooling operation can be determined based on the flowchart of FIG.
  • step S51 it is determined whether or not the target operating frequency FMK for the compressor 101 exceeds the cooling-time target discharge pipe temperature calculation condensation temperature correction coefficient switching frequency FEVFDC. If the target frequency FMK> FEVFDC, the process shifts to step S52. Otherwise, the process shifts to step S53.
  • step S52 the condensing temperature correction coefficient KEVFD is set to the condensing temperature correction coefficient KEVFDC for calculating the target discharge pipe temperature during high frequency side cooling.
  • step S53 the condensing temperature correction coefficient KEVFD is set to the condensing temperature correction coefficient KEVFDC1 for calculating the target discharge pipe temperature during low frequency side cooling.
  • step S54 it is determined whether or not the minimum value D CMNU of the indoor heat exchanger temperature in the operating room is equal to or higher than the lower limit temperature DZC for calculating the target discharge pipe temperature during cooling. If the minimum value of the indoor heat exchanger temperature D CMNU is equal to or higher than the evaporating temperature lower limit temperature DZC for calculating the target discharge pipe temperature during cooling, the process proceeds to step S55, otherwise, the process proceeds to step S56. Move to
  • step S55 the minimum value D CMNU of the indoor heat exchanger temperature in the operating room is set as the evaporation temperature DZ.
  • step S56 the evaporating temperature for calculating the target discharge pipe temperature Let the lower limit temperature DZC be the current evaporation temperature DZ.
  • step S57 the target DSC for calculating the discharge pipe temperature at the time of cooling is set based on the number of the indoor units 200 currently operated.
  • the section DSHC1 for one-room operation, the section DSHC2 for two-room operation, and the section DSHC3 for three-room operation are set in the storage area in advance, and one of the values is assigned to DSHC according to the operating conditions at that time.
  • step S58 it is determined whether or not the opening EVP of the discharge-suction electric valve 142 is equal to or greater than a predetermined value EVPMIN. If it is determined that the opening degree EVP of the discharge / suction electric valve 142 is equal to or larger than the predetermined value EVPMIN, the flow shifts to step S59; otherwise, the flow shifts to step S60.
  • step S59 the value of the target discharge pipe temperature correction value DEVP is set to the target discharge pipe temperature correction value DEVPC during the cooling operation capacity control.
  • step S60 the value of the target discharge pipe temperature correction value DEVP is set to 0.
  • step S61 the value of the provisional target discharge pipe temperature DO SETN is converted to the condensation temperature correction coefficient KEVFD for calculating the target discharge pipe temperature, the outdoor heat exchanger temperature DE, and the evaporation temperature correction coefficient KEVFDEC for calculating the target discharge pipe temperature during cooling.
  • KEVFD condensation temperature correction coefficient
  • the target discharge pipe temperature calculation intercept DSHC for cooling
  • step S71 it is determined whether or not the target operating frequency FMK for the compressor 101 has exceeded the condensing temperature correction coefficient switching frequency FEVFDW for heating target discharge pipe temperature calculation. If the target frequency FMK> FEVFDW, the process proceeds to step S72; otherwise, the process proceeds to step S73.
  • step S72 the condensing temperature correction coefficient KEVFD is set to the condensing temperature correction coefficient KEVFDW for calculating the target discharge pipe temperature during high frequency side heating.
  • step S73 the condensation Set the temperature correction coefficient KEVFD to the condensation temperature correction coefficient KEVFDW1 for calculating the target discharge pipe temperature during low-frequency heating.
  • step S74 it is determined whether or not the outdoor heat exchanger temperature DE is equal to or higher than a heating target discharge pipe temperature calculation steaming temperature lower limit temperature DZW. If the outdoor heat exchanger temperature DE is equal to or higher than the lower limit temperature DZW for calculating the target discharge pipe temperature at the time of heating, the process proceeds to step S75, and if not, the process proceeds to step S76.
  • step S75 the outdoor heat exchanger temperature DE is set as the evaporation temperature DZ.
  • step S76 the evaporation temperature DZ is set to the evaporation temperature lower limit temperature DZW for calculating the target discharge pipe temperature during heating.
  • a value of the heating discharge target pipe temperature calculation intercept DSHW is set based on the value of the outdoor temperature DOA.
  • the value of the heating discharge target pipe temperature calculation intercept DSHW is set to the target discharge pipe temperature during low temperature heating.
  • the outdoor temperature DOA is the intercept switching outside air temperature for calculating the target discharge pipe temperature during low-temperature heating! ) 0 ASH1 or more, high temperature heating target discharge pipe temperature calculation intercept switching outside air temperature D 0 A
  • the heating target discharge pipe temperature calculation intercept D SHW value is set to the medium temperature heating target discharge.
  • step S78 it is determined whether or not the opening degree EVP of the discharge-suction electric valve 142 is equal to or greater than a predetermined value EVPMIN. If it is determined that the opening EVP of the discharge-suction electric valve 142 is equal to or larger than the predetermined value EVPMIN, the flow shifts to step S79. Otherwise, the flow shifts to step S80.
  • step S79 the value of the target discharge pipe temperature correction value DEVP is set to the target discharge pipe temperature correction value DEVPW during heating operation capacity control.
  • step S80 the value of the target discharge pipe temperature correction value D EVP is set to 0.
  • step S81 the value of the tentative target discharge pipe temperature D OSETN is set to the condensing temperature correction coefficient KEVFD for calculating the target discharge pipe temperature, the maximum value of the indoor heat exchanger temperature D CMXT, Evaporation temperature correction coefficient for target discharge pipe temperature calculation KEVFDEW, evaporation temperature DZ, intercept DSHW for target discharge pipe temperature calculation during heating, and target discharge pipe temperature correction value DEVP.
  • KEVFD condensing temperature correction coefficient for calculating the target discharge pipe temperature
  • D CMXT the maximum value of the indoor heat exchanger temperature D CMXT
  • Evaporation temperature correction coefficient for target discharge pipe temperature calculation KEVFDEW Evaporation temperature correction coefficient for target discharge pipe temperature calculation KEVFDEW
  • evaporation temperature DZ intercept DSHW for target discharge pipe temperature calculation during heating
  • target discharge pipe temperature correction value DEVP target discharge pipe temperature correction value
  • D0SETN KEVFDXD CMXT-KEV DEWXDZ + DSHW -DEVP.
  • step S91 it is determined whether or not the initial flag is on.
  • the initial flag indicates that the value of the sampling timer has exceeded the sampling timer T THS1 for the first time since the mode of the target discharge pipe temperature control by the outdoor unit electric valve was set. If is turned on, the process proceeds to step S92; otherwise, the process proceeds to step S93.
  • step S92 the temporary target discharge pipe temperature DOSETN is set as it is to the target discharge pipe temperature DOSET. Further, the temporary target discharge pipe temperature DOSETN is set to the previous target discharge pipe temperature DOSETZ.
  • step S93 the average of the temporary target discharge pipe temperature DOSETN and the previous target discharge pipe temperature DOS ETZ is calculated, and this is set as the target discharge pipe temperature DOSET. Further, the tentative target discharge pipe temperature D OSETN is set to the previous target discharge pipe temperature D OSETZ.
  • DOSET (DOSETN + D OSETZ) / 2
  • the upper and lower limits of the target discharge pipe temperature DOSETN are set in advance in consideration of the maximum and minimum values of the discharge pipe temperature that enable normal operation for each operation mode, and are calculated as described above.
  • the target discharge pipe temperature DOSET is controlled so as to be within the range of the upper limit value and the lower limit value.
  • --END Target discharge pipe temperature D OSET- the current discharge pipe temperature D ⁇ is detected.
  • Discharge pipe temperature error By reading the value of 109, the current discharge pipe temperature DO can be detected.
  • the deviation EDO of the discharge pipe temperature is calculated.
  • the discharge pipe temperature deviation EDO the target discharge pipe temperature D OSET—the discharge pipe temperature DO.
  • the change amount d D ⁇ of the discharge pipe temperature is calculated.
  • step S29 a fuzzy table is searched using the discharge pipe temperature deviation EDO and the discharge pipe temperature change dDO, and the value of the motorized valve change PEVHN is determined.
  • step S32 it is determined whether or not the operation mode is the cooling operation mode. If the operation mode is the cooling operation mode, the process proceeds to step S33. Otherwise, the process proceeds to step S34. In step S33, the value of the motor-operated valve change amount PEVHN is corrected by the cooling-time correction coefficient KPOTD.
  • step S34 the motorized valve cumulative pulse: PHNA is calculated based on the value of the motorized valve change amount PEVHN.
  • P HNA P HNA + P EVHN
  • step S35 the integer part and the decimal part of the electric cumulative pulse PHNA are calculated respectively, and the integer part is set to PHN and the decimal part is set to PHNA.
  • step S36 it is determined whether control condition 2 is satisfied.
  • step S101 it is determined whether the operation mode is the heating operation. If it is determined that the operation mode is the heating operation mode, the process proceeds to step S102. Otherwise, the process proceeds to the direction D (step S37 in FIG. 4).
  • step S102 it is determined whether or not a signal is received from the connected branch unit 300 that indicates that the opening of the motor-operated valve 305 corresponding to all the stopped rooms is minimum. If a signal indicating that the opening of the motor-operated valve 305 corresponding to all the stopped rooms is minimum is received, the process proceeds to the direction C (step S38 in FIG. 24). Stay If the condition in step S102 is not satisfied, the flow shifts to step S103.
  • step S103 it is determined whether or not the gas pipe motorized valve opening EVG is equal to or greater than a predetermined value EVGMIN. If the gas pipe motorized valve opening EVG is equal to or larger than the predetermined value EVGMIN, proceed to the direction C (step S38 in FIG. 24), otherwise proceed to the direction D (step S37 in FIG. 24).
  • step S37 the target opening of the motor-operated valve is changed.
  • the gas pipe motorized valve opening EVG EVG-motorized valve change pulse PHN
  • step S38 the target opening of the gas pipe motorized valve is changed.
  • the gas pipe motor connection degree EVG EVG + motor valve change pulse P HN.
  • step S39 the first flag is turned off, the sampling time is reset, and the routine goes to step S21.
  • the liquid injection amount can be continuously controlled, and the discharge pipe of the compressor 101 can be controlled.
  • the temperature can be optimized.
  • the air conditioner according to the present invention by controlling the refrigerant opening / closing means connected to the receiver, it is possible to control the temperature of the discharge pipe of the compressor, thereby improving reliability and operating efficiency. Improvement can be achieved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

L'invention concerne le circuit de refroidissement d'un conditionneur d'air, qui comprend un circuit de refroidissement sur la face d'une unité extérieure ayant un accumulateur (105), un compresseur (101), une vanne sélective à quatre voies (102), ainsi qu'un échangeur thermique extérieur (103) monté dans une unité extérieure (100) et un échangeur thermique intérieur (201) monté dans une unité intérieure (200), en interconnexion par l'intermédiaire d'une ligne latérale de conduite fluidique et d'une ligne latérale de conduite de gaz, un circuit de dérivation pour contourner la ligne latérale de conduite fluidique (131) et la ligne latérale de conduite de gaz (132), un collecteur (121) pour recevoir un fluide réfrigérant installé dans le circuit de dérivation, ainsi qu'une vanne commandée par moteur pour la conduite fluidique (128) et qu'une vanne commandée par moteur pou la conduite de gaz (129), montées à l'avant et à l'arrière du collecteur (121).
PCT/JP2001/006061 2000-07-13 2001-07-12 Circuit de refroidissement pour conditionneur d'air WO2002006738A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE60136707T DE60136707D1 (de) 2000-07-13 2001-07-12 Kältemittelkreislauf für eine klimaanlage
EP01947994A EP1300637B1 (fr) 2000-07-13 2001-07-12 Circuit de refroidissement pour conditionneur d'air
AU69512/01A AU766170B2 (en) 2000-07-13 2001-07-12 Refrigerant circuit of air conditioner

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000213115A JP3584862B2 (ja) 2000-07-13 2000-07-13 空気調和機の冷媒回路
JP2000-213115 2000-07-13

Publications (1)

Publication Number Publication Date
WO2002006738A1 true WO2002006738A1 (fr) 2002-01-24

Family

ID=18708920

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2001/006061 WO2002006738A1 (fr) 2000-07-13 2001-07-12 Circuit de refroidissement pour conditionneur d'air

Country Status (8)

Country Link
EP (2) EP1933102B1 (fr)
JP (1) JP3584862B2 (fr)
KR (1) KR100474400B1 (fr)
CN (1) CN1162665C (fr)
AT (2) ATE449295T1 (fr)
AU (1) AU766170B2 (fr)
DE (2) DE60136707D1 (fr)
WO (1) WO2002006738A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1312876A2 (fr) * 2001-11-19 2003-05-21 RHOSS S.p.A. Unité frigorifique à cycle réversible
US20170010027A1 (en) * 2014-01-27 2017-01-12 Qingdao Hisense Hitachi Air-Conditionung Systems Co., Ltd Heat recovery variable-frequency multi-split heat pump system and control method thereof

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4089139B2 (ja) * 2000-07-26 2008-05-28 ダイキン工業株式会社 空気調和機
JP2004086816A (ja) * 2002-08-29 2004-03-18 Masaru Yokosuka 物品引取依頼情報連絡方法及びシステム
KR100504509B1 (ko) 2003-01-16 2005-08-03 엘지전자 주식회사 차단 가능한 다중 분배기를 갖는 냉난방 동시형멀티공기조화기
KR100564444B1 (ko) * 2003-10-20 2006-03-29 엘지전자 주식회사 에어컨의 액 냉매 누적 방지 장치 및 방법
US7237394B2 (en) * 2004-09-30 2007-07-03 Carrier Corporation Charge management for 100% heat recovery units
JP4575184B2 (ja) 2005-02-09 2010-11-04 三星電子株式会社 空気調和装置
JP4254863B2 (ja) * 2007-01-23 2009-04-15 ダイキン工業株式会社 空気調和装置
JP5385800B2 (ja) * 2010-01-19 2014-01-08 東プレ株式会社 気液分離型冷凍装置
JP5537979B2 (ja) * 2010-02-12 2014-07-02 東芝キヤリア株式会社 空気調和機
CN102032732B (zh) * 2010-12-03 2012-01-11 海信（山东）空调有限公司 具有制冷剂回收功能的空调系统
JP5212537B1 (ja) * 2011-12-13 2013-06-19 ダイキン工業株式会社 冷凍装置
JP5573881B2 (ja) * 2012-04-16 2014-08-20 ダイキン工業株式会社 空気調和機
CN102635927B (zh) * 2012-04-26 2018-05-11 青岛海尔空调电子有限公司 用于空调系统的压力调整装置和方法
WO2015140874A1 (fr) * 2014-03-17 2015-09-24 三菱電機株式会社 Dispositif de climatisation
CN106461279B (zh) * 2014-05-12 2019-01-18 松下知识产权经营株式会社 制冷循环装置
CN104236186A (zh) * 2014-09-30 2014-12-24 宁波奥克斯电气有限公司 热泵多联机的除霜控制方法
EP3508802B1 (fr) * 2015-10-20 2020-04-22 Mitsubishi Electric Corporation Appareil de cycle de réfrigération
US10830515B2 (en) 2015-10-21 2020-11-10 Mitsubishi Electric Research Laboratories, Inc. System and method for controlling refrigerant in vapor compression system
WO2018033827A1 (fr) * 2016-08-18 2018-02-22 Atlas Copco Airpower, Naamloze Vennootschap Procédé de commande de la température de sortie d'une pompe à vide ou d'un compresseur à injection d'huile et pompe à vide ou compresseur à injection d'huile mettant en œuvre un tel procédé
BE1024497B1 (nl) 2016-08-18 2018-03-19 Atlas Copco Airpower Naamloze Vennootschap Een werkwijze voor het regelen van de uitlaattemperatuur van een oliegeïnjecteerde compressor of vacuümpomp en oliegeïnjecteerde compressor of vacuümpomp die een dergelijke werkwijze toepast.
CN106403201B (zh) * 2016-11-10 2019-03-15 广东美的暖通设备有限公司 空调器的新风机换热器积液的控制方法及空调器
CN111207504A (zh) * 2020-01-13 2020-05-29 珠海格力电器股份有限公司 空调系统及冷媒回收控制方法
CN113865063B (zh) * 2021-08-31 2022-11-25 宁波奥克斯电气股份有限公司 多联机系统控制方法、控制装置、多联机系统和存储介质

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5918348A (ja) * 1982-07-20 1984-01-30 松下精工株式会社 空冷ヒ−トポンプ式空気調和機
JPS60114669A (ja) * 1983-11-28 1985-06-21 株式会社東芝 空気調和機
US4720982A (en) * 1985-10-28 1988-01-26 Kabushiki Kaisha Toshiba Multi-type air conditioner with optimum control for each load
JPH07120092A (ja) * 1993-10-20 1995-05-12 Fujitsu General Ltd 空気調和機
JPH08219583A (ja) * 1995-02-08 1996-08-30 Yamaha Motor Co Ltd 空気調和装置
JP2000146322A (ja) * 1998-11-16 2000-05-26 Zexel Corp 冷凍サイクル

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5140827A (en) * 1991-05-14 1992-08-25 Electric Power Research Institute, Inc. Automatic refrigerant charge variation means
US5937660A (en) * 1993-07-26 1999-08-17 Lau; Billy Ying Bui Quick cooling air conditioning system
US5784892A (en) 1996-09-09 1998-07-28 Electric Power Research Institute, Inc. Refrigerant charge variation mechanism
CN1250515A (zh) * 1997-03-17 2000-04-12 大金工业株式会社 空调器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5918348A (ja) * 1982-07-20 1984-01-30 松下精工株式会社 空冷ヒ−トポンプ式空気調和機
JPS60114669A (ja) * 1983-11-28 1985-06-21 株式会社東芝 空気調和機
US4720982A (en) * 1985-10-28 1988-01-26 Kabushiki Kaisha Toshiba Multi-type air conditioner with optimum control for each load
JPH07120092A (ja) * 1993-10-20 1995-05-12 Fujitsu General Ltd 空気調和機
JPH08219583A (ja) * 1995-02-08 1996-08-30 Yamaha Motor Co Ltd 空気調和装置
JP2000146322A (ja) * 1998-11-16 2000-05-26 Zexel Corp 冷凍サイクル

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1312876A2 (fr) * 2001-11-19 2003-05-21 RHOSS S.p.A. Unité frigorifique à cycle réversible
EP1312876A3 (fr) * 2001-11-19 2003-11-19 RHOSS S.p.A. Unité frigorifique à cycle réversible
US20170010027A1 (en) * 2014-01-27 2017-01-12 Qingdao Hisense Hitachi Air-Conditionung Systems Co., Ltd Heat recovery variable-frequency multi-split heat pump system and control method thereof
US10132530B2 (en) * 2014-01-27 2018-11-20 Qingdao Hisense Hitachi Air-conditioning Systems Co., Ltd. Heat recovery variable-frequency multi-split heat pump system and control method thereof

Also Published As

Publication number Publication date
ATE449295T1 (de) 2009-12-15
KR20020035137A (ko) 2002-05-09
JP3584862B2 (ja) 2004-11-04
EP1933102B1 (fr) 2009-11-18
JP2002022306A (ja) 2002-01-23
EP1933102A1 (fr) 2008-06-18
DE60140584D1 (de) 2009-12-31
AU766170B2 (en) 2003-10-09
EP1300637A4 (fr) 2006-12-20
CN1162665C (zh) 2004-08-18
DE60136707D1 (de) 2009-01-08
EP1300637B1 (fr) 2008-11-26
KR100474400B1 (ko) 2005-03-09
ATE415601T1 (de) 2008-12-15
CN1386184A (zh) 2002-12-18
EP1300637A1 (fr) 2003-04-09
AU6951201A (en) 2002-01-30

Similar Documents

Publication Publication Date Title
JP3584862B2 (ja) 空気調和機の冷媒回路
US6986259B2 (en) Refrigerator
EP2211127A1 (fr) Climatiseur de type pompe à chaleur
JP4462387B1 (ja) 冷凍装置
KR20090064417A (ko) 공기 조화 장치
JP5062039B2 (ja) 冷凍装置
JP4548265B2 (ja) 空気調和機
JP3724239B2 (ja) 冷却装置
JP3731065B2 (ja) 空気調和機
JP3709477B2 (ja) 空気調和機の冷媒回路
KR20100064836A (ko) 공기조화기 및 그 운전 방법
JPH0395343A (ja) 空気調和装置の運転制御装置
JP3680261B2 (ja) 空気調和機の冷媒回路
JP2021032440A (ja) 熱源ユニット及び冷凍装置
EP4310416A1 (fr) Système de climatisation multiple hybride
JP2002022296A (ja) 空気調和機
JP3750496B2 (ja) 空気調和機
JP5574638B2 (ja) 冷凍空調装置
KR102422008B1 (ko) 하이브리드 멀티 공조 시스템 및 그의 제어 방법
JP2017101858A (ja) 冷凍装置
JP4453195B2 (ja) 冷凍装置
JP2008111584A (ja) 空気調和装置
JP3168730B2 (ja) 空気調和装置
JP2019066085A (ja) 冷凍装置
JP2009030937A (ja) 冷凍装置

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AU CN KR

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE TR

WWE Wipo information: entry into national phase

Ref document number: 018020038

Country of ref document: CN

WWE Wipo information: entry into national phase

Ref document number: 1020027003261

Country of ref document: KR

121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 69512/01

Country of ref document: AU

WWE Wipo information: entry into national phase

Ref document number: 2001947994

Country of ref document: EP

WWP Wipo information: published in national office

Ref document number: 1020027003261

Country of ref document: KR

WWP Wipo information: published in national office

Ref document number: 2001947994

Country of ref document: EP

WWG Wipo information: grant in national office

Ref document number: 69512/01

Country of ref document: AU

WWG Wipo information: grant in national office

Ref document number: 1020027003261

Country of ref document: KR