EP1933102B1 - Air conditioner refrigerant circuit - Google Patents

Air conditioner refrigerant circuit Download PDF

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Publication number
EP1933102B1
EP1933102B1 EP08003787A EP08003787A EP1933102B1 EP 1933102 B1 EP1933102 B1 EP 1933102B1 EP 08003787 A EP08003787 A EP 08003787A EP 08003787 A EP08003787 A EP 08003787A EP 1933102 B1 EP1933102 B1 EP 1933102B1
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EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
temperature
gas line
liquid
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
EP08003787A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1933102A1 (en
Inventor
Hidehiko Kataoka
Shinichi Sakamoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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Publication date
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Publication of EP1933102A1 publication Critical patent/EP1933102A1/en
Application granted granted Critical
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Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B43/02—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
    • 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
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    • 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 an air conditioner refrigerant circuit, and more particularly to an air conditioner refrigerant circuit that connects an outdoor unit refrigerant circuit that includes a compressor, a four way directional control valve, and an outdoor heat exchanger that is disposed inside the outdoor device, with an indoor heat exchanger that is disposed inside an indoor unit, by means of liquid line piping and gas line piping.
  • An air conditioner refrigerant circuit is a system in which a compressor, a four way directional control valve, and a outdoor heat exchanger disposed inside an outdoor unit are connected, by means of refrigerant piping, to an indoor heat exchanger disposed inside an indoor unit, and which forms a circulatory route for refrigerant.
  • a high pressure receiver (hereinafter referred to as a "receiver") that temporarily stores liquid refrigerant condensed by the outdoor heat exchanger is provided in the refrigerant circuit, and the amount of refrigerant inside the outdoor heat exchanger that functions as a condenser, and the amount of refrigerant inside the indoor heat exchanger that functions as an vaporizer, changes, there are times when the refrigerant circuit is constructed such that the change in the amount of refrigerant is absorbed by the receiver.
  • a liquid line shut off valve is provided on the liquid line piping that is connected to the outdoor heat exchanger
  • a gas line shut off valve is provided on the gas line piping that is connected to the four way directional control valve
  • the receiver is serially disposed between the liquid line shut off valve and the outdoor heat exchanger.
  • a decompression circuit such as an electric valve or the like is provided for each indoor heat exchanger.
  • the amount of refrigerant supplied to each indoor heat exchanger can be controlled at a suitable level by means of the decompression circuit provided for each indoor heat exchanger.
  • the air conditioner refrigerant circuit is constructed so that an adjustment in the amount of refrigerant takes place by means of the receiver, and is returned to the compressor.
  • the four way directional control valve is operated and the refrigerant cycle takes place.
  • the surplus refrigerant used during heating is stored in the receiver, it is necessary to provide decompression circuits, such as electric valves or the like, between the receiver and the indoor heat exchangers. Because of this, there is a danger that the pressure differential before and after the decompression circuits used for distribution that correspond to each indoor heat exchanger will become small, and that the flow of refrigerant inside the indoor heat exchangers will worsen.
  • the air conditioner refrigerant circuit according to the present invention has the features defined in the preamble of claim 1. Embodiments of the invention are named in the dependent claims.
  • FIG. 1 we will consider a situation in which a plurality of indoor units 200A, 200B, etc. are connected to an outdoor unit 100 via branching units 300A, 300B, etc.
  • the outdoor unit 100 is comprised of a compressor 101, a four way directional control valve 102, an outdoor heat exchanger 103, an accumulator 105, and the like.
  • a discharge thermistor 109 for detecting the discharge line temperature is provided on the discharge side of the compressor 101.
  • an outside air thermistor 111 for detecting the outside air temperature, and an outdoor heat exchange thermistor 112 for detecting the temperature of the outdoor heat exchanger 103 are provided in the outdoor unit 100.
  • a fan 106 for drawing in outside air and exchanging heat between the outside air and the refrigerant that flows inside the outdoor heat exchanger 103, and a fan motor 104 for rotationally driving the fan 106, are provided.
  • a liquid line connector port 114 that is connected to the outdoor heat exchanger 103, and a gas line connector port 115 that is connected to the four way directional control valve 102, is provided in the outdoor unit 100.
  • a liquid line shut off valve 116 and a gas line shut off valve 117 are installed on the inside of each connecting port.
  • a receiver 121 is provided in the outdoor unit 121, which temporarily stores surplus refrigerant liquid from the outdoor heat exchanger 103 when it functions as a condenser during air conditioning.
  • the receiver 121 comprises a liquid line connector 122 and a gas line connector 123.
  • the liquid line connector 122 is connected to liquid line piping 131 between the outdoor heat exchanger 103 and the liquid line shut off valve 116, and the gas line connector 123 is connected to gas line piping 132 between the four way directional control valve 102 and the gas line shut off valve 117.
  • branching units 300A, 300B, etc. are connected to the liquid line connector port 114 and the gas line connector port 115 on the outside unit 100. Because the branching units 300A, 300B, etc. each have an identical construction, a description of the branching unit 300A will be provided, and a description of the other branching units will be omitted.
  • the branching unit 300A is comprised of an outdoor liquid line connector port 301 that is connected to the liquid line connector port 114 on the outdoor unit 100, and an outdoor gas line connector port 303 that is connected to the gas line connector port 115 on the outdoor unit 100.
  • the branching unit 300A is comprised of a liquid line branching circuit that branches on the inside of the outdoor liquid line connector port 301, and on the other side thereof, indoor liquid line connector ports 302 are provided which are connected to a number of indoor units.
  • the branching unit 300A is comprised of a gas line branching circuit that branches on the inside of the outdoor liquid line connector port 303, and on the other side thereof, indoor liquid line connector ports 304 are provided which are connected to a number of indoor units.
  • indoor liquid line connector ports 302A, 302B, and 302C, and indoor gas line connector ports 304A, 304B, and 304C are provided for three connected indoor units.
  • Electric valves 305A - 305C for decompressing the pressurized refrigerant that passes therethrough, and liquid line thermistors 306A - 306C for detecting the temperature of the refrigerant temperature that passes therethrough, are each provided along the branching circuit that spans between the outdoor liquid connector port 301 inside the branching unit 300A to each indoor liquid line connector port 302A - 302C.
  • gas line thermistors 307A - 307C for detecting the temperature of the refrigerant that passes therethrough are each provided along the branching circuit that spans between the outdoor gas connector port 303 inside the branching unit 300A to each indoor gas line connector port 304A - 304C.
  • a plurality of indoor units 200 are connected to each branching unit 300A, 300B, etc.
  • Each indoor unit 200A - 200F is an indoor unit for use with a multi unit, and any of them can be used as a paired unit.
  • indoor device 200A will be described when used as a paired unit.
  • Indoor unit 200A is comprised of an indoor heat exchanger 201, and refrigerant piping connected to this indoor heat exchanger 201 is lead to the outdoor unit via a liquid connector port 204 and a gas connector port 205. Further, this indoor device 200A is comprised of a room temperature thermistor 202 for detecting the indoor temperature, and an indoor heat exchange thermistor 203 for detecting the temperature of the indoor heat exchanger 201.
  • gas line connector 123 of the receiver 121 can be constructed so that it connects the gas line between the four way directional control valve 102 and the accumulator 105.
  • capillaries 124, 125 for decompression are respectively installed on the liquid line connector 122 and the gas line connector 123 of the receiver 121. Electric valves for decompression may respectively provided thereon instead of the capillaries 124, 125.
  • the first embodiment it is possible to provide functional components that shut off the flow of refrigerant to the liquid line connector 122 and the gas line connector 123 of the receiver 121.
  • magnetic valves 126, 127 used as refrigerant shut offs are installed on the liquid line connector 122 and the gas line connector 123 of the receiver 121.
  • the first embodiment it is possible to provide functional components that have a decompression function and a refrigerant shut off function in the liquid line connector 121 and the gas line connector 122 of the receiver 121.
  • functional components that have a decompression function and a refrigerant shut off function in the liquid line connector 121 and the gas line connector 122 of the receiver 121.
  • this type of functional components it is possible to employ a combination of electric valves or capillaries that have a decompression function and a shut off function, and magnetic valves.
  • a liquid line electric valve (EVL) 128 is provided in the liquid line connector 122 of the receiver 121, and a gas line electric valve (EVG) 129 is provided in the gas line connector 123 of the receiver 121.
  • a capillary for venting gas between the receiver 121 and the gas line piping 132.
  • a gas recovery capillary 130 can be provided which is connected with the gas line piping 132 between the four way directional control valve 102 and the gas shut off valve 117, and serves to collect gaseous refrigerant from the receiver 121.
  • a gas recovery capillary is provided in the piping between the four way directional control valve that becomes continuous low pressure piping, and the accumulator.
  • the gas recovery capillary is connected to a continuous low pressure line, the flow rate characteristics of the capillary must be made smaller, and the result of this is that it becomes difficult to improve refrigerant collection efficiency during pump down operations.
  • gas refrigerant inside the receiver 121 can return to the inlet of the accumulator via the gas recovery capillary 130 during pump down operations, it becomes easy to store liquid refrigerant in the receiver 121, and during normal operations, the flow of refrigerant from the gas recovery capillary 130 can be interrupted during cooling operations by shutting liquid line electric valve 128. Further, high pressure can be maintained inside the receiver 121 during heating operations, the back flow of refrigerant from the liquid line electric valve 128 can be prevented, and it becomes possible to handle surplus refrigerant during heating operations.
  • a gas line electric valve 129 having a decompression function and a refrigerant shut off function is provided on the gas line connector 123 of the receiver 121.
  • An auxiliary heat exchanger 133 is provided between the gas line electric valve 129 and the portion that connects with the gas line piping 132.
  • auxiliary heat exchanger 133 When the refrigerant circuit in the first to fifth embodiments is employed and cooling operations take place, when surplus refrigerant is discharged from the receiver, it is necessary to control the speed of refrigerant discharge in order to prevent liquid from suddenly backing up toward the accumulator.
  • auxiliary heat exchanger 133 By providing this type of auxiliary heat exchanger 133, it becomes possible to eliminate the occurrence of a sudden liquid backup toward the accumulator, and improve the speed of refrigerant discharge, because the liquid refrigerant vaporizes by means of this auxiliary heat exchanger 133.
  • the auxiliary heat exchanger 133 functions as a condenser, it becomes possible to improve the speed in which surplus refrigerant is stored in receiver 121.
  • liquid line electric valve 128 and the gas line electric valve 129 connected to the receiver 121, and providing the auxiliary heat exchanger 133 between the liquid line electric valve 129 and the gas line electric valve 132, it becomes possible to control the state of the refrigerant in the outlet of the outdoor heat exchanger 103 (liquid line piping 131). Because of this, when the temperature of the discharge pipe is high, the quantity of refrigerant discharged from the receiver 121 is made large in order to cool it, and when there is liquid refrigerant in the accumulator 105, it becomes possible to control the discharge temperature by reducing the quantity of refrigerant discharge from the receiver 121.
  • the condensing ability of the auxiliary heat exchanger 133 can be enlarged by enlarging the opening of the gas line electric valve 129, and this can contribute to a decrease in the high pressure.
  • auxiliary heat exchanger 133 when the auxiliary heat exchanger 133 is disposed on the gas line connector 123 of the receiver 121, it is possible to provide the auxiliary heat exchanger 133 inside the outdoor heat exchanger 103, and, it is possible to place it on the lowermost portion of the outdoor heat exchanger 103.
  • This seventh embodiment is shown in Fig. 7 .
  • the auxiliary heat exchanger 133 connected to the gas line connector 123 of the receiver 121 is provided inside the outdoor heat exchanger 103, and, is disposed on the lowermost portion of the outdoor heat exchanger 103.
  • This subcooling heat exchanger is a device for placing refrigerant from the outlet of the outdoor heat exchanger into the supercooled state during cooling.
  • the configuration shown in Fig. 8 will be considered, in which the auxiliary heat exchanger in the seventh embodiment is disposed in the outdoor heat exchanger and is adjacent to the subcooling heat exchanger.
  • a subcooling heat exchanger 134 is disposed below the outdoor heat exchanger 103, and below that, the auxiliary heat exchanger 133 is disposed on the lowermost portion of the outdoor heat exchanger 103.
  • cooling abilities can be increased by means of the subcooling heat exchanger 134 disposed adjacent thereto, and the degree to which the refrigerant from the outlet of the outdoor heat exchanger 103 is supercooled can be increased.
  • the outdoor heat exchanger 103 for example, as shown in Fig. 10 , is composed of a plurality of cooling lines 171 that have one end thereof bent back, and a plurality of heat radiating fins 172, which are metallic plate members that have insertion holes formed therein for inserting the cooling lines 171.
  • Distributors 173, 174 are provided on both ends of each cooling line 171.
  • each cooling line 171 functions as a vaporizer, one end thereof serves as a refrigerant port, and when each cooling line 171 functions as a condenser, the other end serves as a refrigerant port.
  • Fig. 9 shows an enlarged lateral view of only the lower portion of this type of outdoor heat exchanger 103.
  • a pipe plate 175 that supports both ends of cooling lines 171 is provided on the side surface of the outdoor heat exchanger 103.
  • This pipe plate 175 is formed into approximately the same shape as the heat radiating fins 172, and has insertion holes 176 formed therein for inserting the cooling lines 171.
  • the cooling lines 171 disposed between the distributors 173, 174 are inserted into each insertion hole 176.
  • the distributor 174 on the outdoor heat exchanger 103 is connected to the four way directional control valve 102, and the distributor 173 is connected to the subcooling heat exchanger 134.
  • the subcooling heat exchanger 134 is comprised of an SC cooling line 177, one end of which is connected to the distributor 173, and the other end thereof is connected to the liquid shut off valve 116.
  • the auxiliary heat exchanger 133 is comprised of an auxiliary cooling line 178, one end of which is connected to the gas line electric valve 129, and the other end thereof is connected to the gas line piping 132.
  • the SC cooling line 177 is disposed on the downwind side (the left side of Fig. 9 ), and the auxiliary cooling line 178 is disposed on the upwind side (the right side of Fig. 9 ).
  • heat exchange can not only occur by means of the thermal conduction of the SC cooling line 177, the heat radiating fins 172, and the auxiliary cooling line 178, but the heat radiated outward by the airflow produced by the fan 106 can be used, the efficiency of the subcooling heat exchanger 134 is increased, and refreezing in the lower portion of the outdoor heat exchanger 103 can be prevented.
  • Fig. 11 The preferred embodiment of the present invention is shown in Fig. 11 .
  • the outdoor device 100 is comprised of an outdoor refrigerant circuit, which is comprised of a compressor 101, a four way directional control valve 102, a heat exchanger 103, an accumulator 105, and the like.
  • a discharge pressure protection switch 108 for detecting an abnormal rise in the discharge pressure is provided on the discharge side of the compressor 101, and an inlet pressure sensor 110 for detecting the inlet pressure is provided on the inlet side of the compressor 101.
  • an oil separator 107 for separating the lubricating oil that is included in the refrigerant and returning it to the accumulator 105 is provided on the discharge side of the compressor 101.
  • a discharge line thermistor 109 for detecting the temperature on the discharge side of the compressor 101 is installed in the oil separator 107.
  • a discharge - intake capillary 141 for adjusting the discharge pressure and the inlet pressure, and a discharge - intake electric valve (EVP) 142 for controlling capacity, are provided in a discharge - intake bypass that connects the outlet side of the oil separator 107 and the inlet side of the accumulator 105.
  • an outside air thermistor 111 for detecting the outside air temperature, and an outdoor heat exchange thermistor 112 for detecting the temperature of the outdoor heat exchanger 103 are provided in the outdoor unit 100.
  • the outdoor unit 100 comprises a liquid line connector port 114 that is connected to the outdoor heat exchanger 103, and a gas line connector port 115 that is connected to the four way directional control valve 102.
  • a liquid line shut off valve 116 and a gas line shut off valve 117 are provided on the inner sides of each connector port.
  • a receiver 121 is provided in the outdoor unit 100, which temporarily stores surplus refrigerant from the outdoor heat exchanger 103 when it functions as a condenser during cooling operations.
  • the receiver 121 is comprised of a liquid line connector 122 and a gas line connector 123.
  • the liquid line connector 122 is connected to liquid line piping 131 between the outdoor heat exchanger 103 and the liquid line shut off valve 116, and the gas line connector 123 is connected to gas line piping 132 between the four way directional control valve 102 and the gas line shut off valve 117.
  • a liquid line electric valve (EVL) 128 having a decompression function and a refrigerant cut-off function is provided in the liquid line connector 122 on the receiver 121, and a gas line electric valve (EVG) 129 is provided on the gas line connector 123 on the receiver 121.
  • An auxiliary heat exchanger 133 is provided in between the gas line electric valve 129 and a portion that connects to the gas line piping 132. As shown in Fig. 9 , the auxiliary heat exchanger 133 is constructed by placing an auxiliary cooling line 178 in the lowermost portion of the outdoor heat exchanger 103. A subcooling heat exchanger 134 is disposed on the liquid line outlet of the outdoor heat exchanger 103. As shown in Fig. 9 , the subcooling heat exchanger 134 can be constructed so that it is disposed adjacent to the auxiliary heat exchanger 133, by positioning an SC cooling line 177 on the downwind side of the auxiliary cooling line 178 of the auxiliary heat exchanger 133.
  • a gas recovery capillary 130 for collecting gaseous refrigerant from the receiver 121 is provided, and is connected to the gas line piping 132 in between the four way directional control valve 102 and the gas shut off valve 117.
  • a plurality of branching units 300A, 300B, etc. are connected to the liquid line connector port 144 and the gas line connector port 115 on the outdoor unit 100. Because each outdoor unit 300A, 300B, etc. are constructed identically, a description of the branching unit 300A will be provided, and a description of the other branching units will be omitted.
  • the branching unit 300A is comprised of an outdoor liquid line connector port 301 that is connected to the liquid line connector port 114 on the outdoor unit 100, and an outdoor gas line connector port 303 that is connected to the gas line connector port 115 on the outdoor unit 100.
  • the branching unit 300A is comprised of a liquid line branching circuit that branches on the inner side of the outdoor liquid line connector port 301, and on the opposite end thereof, indoor liquid line connector ports 302 for a number of connected indoor units are provided.
  • the branching unit 300A is comprised of a gas line branching circuit that branches on the inner side of the outdoor gas line connector port 303, and on the opposite end thereof, indoor gas line connector ports 304 for a number of connected indoor units are provided.
  • indoor liquid line connector ports 302A, 302B, and 302C, and indoor gas line connector ports 304A, 304B, and 304C will be provided.
  • an electric valve 308 for use as a bypass is provided between the outdoor liquid line connector port 301 and the outdoor gas line connector port 303.
  • Electric valves 305A - 305C for decompressing the pressurized refrigerant that passes therethrough, and liquid line thermistors 306A - 306C for detecting the temperature of the refrigerant that passes therethrough, are each provided in the branching circuit that spans between the outdoor liquid line connector port 301 inside the branching unit 300A and each indoor liquid line connector port 302A - 302C.
  • gas line thermistors 307A - 307C for detecting the temperature of the refrigerant that passes therethrough are each provided in the branching circuit that spans between the outdoor gas line connector port 303 inside the branching unit 300A and each indoor gas line connector port 307A - 307C.
  • a plurality of indoor units 200 are connected to each branching unit 300A, 300B, etc. As illustrated in the figure, three indoor units can be connected to each branching unit 300A, 300B, etc., with the indoor units 200A - 200C connected to the branching unit 300A, and the indoor units 200D - 200F connected to the branching unit 300B.
  • Each indoor unit 200A - 200F can be used either as an indoor unit for multi unit use, or as an indoor unit for paired unit use.
  • the indoor unit 200A will be described as an indoor unit for paired unit use.
  • the indoor device 200A is comprised of an indoor heat exchanger 201, and refrigerant piping that is connected to this indoor heat exchanger 201 is lead to the outdoor unit via a liquid line connector port 204 and a gas line connector port 205. Further, a room temperature thermistor 202 for detecting the indoor room temperature, and an indoor heat exchange thermistor 203 for detecting the temperature of the indoor heat exchanger 201 are provided in the indoor unit 200A.
  • the discharge - intake bypass electric valve 142 is opened wide, a rise in the discharge pressure during heating operations is prevented, and freezing of the low pressure piping during cooling operations is prevented.
  • the overall system can be controlled with the liquid line electric valve 128 by controlling the opening and closing thereof when the gas line electric valve 129 is in the open state and there is surplus refrigerant in the receiver 121.
  • the liquid line electric valve 128 distinguishes between the presence or absence of surplus refrigerant, and controls the surplus refrigerant in the outdoor unit SC control.
  • the gas line electric valve 129 stores surplus refrigerant in the receiver 121 by opening to a predetermined aperture when it is necessary to handle surplus refrigerant.
  • the gas line electric valve 129 controls the overall system by controlling the opening and closing thereof when the liquid line electric valve 128 is in the open state and there is surplus refrigerant in the receiver 121.
  • FIG. 12 A working example during heating operations is shown in Fig. 12 .
  • Step S1 it is determined in Step S1 whether or not there is not surplus refrigerant in the refrigerant circuit, and whether or not there is no need to control capacity.
  • Step S2 the discharge - intake bypass electric valve 142 is placed in the fully closed state, the liquid line electric valve 128 is placed in the fully open state, and the gas line electric valve 129 is placed in the fully closed state.
  • each indoor heat exchanger 201 in each indoor unit functions as a condenser.
  • the electric valves 305A - 305C, 305D - 305F that are inside the branching units 300A, 300B are constructed such that the apertures thereof are respectively controlled in accordance with the settings in each indoor unit, and refrigerant is distributed to each indoor heat exchanger 201.
  • the electric valve 308 used as a bypass is in the fully closed state.
  • the appropriate amount of refrigerant can be distributed to each indoor heat exchanger 201 by means of the electric valves 305A - 305C, 305D - 305F disposed inside the branching units 300A, 300B. Further, because surplus refrigerant is not produced in the circuit, the receiver 121 is placed in the non-operational state, and control of any of the discharge - intake bypass electric valve 142, the liquid line electric valve 128, and the gas line electric valve 128 is not required.
  • Step S3 it is determined whether or not there is surplus refrigerant in the refrigerant circuit, and whether or not capacity control is unnecessary.
  • the process moves to Step S4.
  • Step S4 the discharge - intake electric valve 142 is placed in the fully closed position, the gas line electric valve 129 is opened a fixed amount, and the liquid line electric valve 128 is controlled in response to the target discharge line temperature.
  • the outdoor unit 100 in situations when only the indoor units 200A - 200C connected to the branching units 300A operate, it is possible for the outdoor unit 100 to generate surplus refrigerant.
  • the refrigerant that was condensed by the auxiliary heat exchanger 133 by opening the gas line electric valve 129 a fixed amount can be introduced and stored in the receiver 121. Because the refrigerant that passes through the gas line electric valve 129 is condensed by the auxiliary heat exchanger 133, the temperature thereof will not exceed the heat resistant temperature of a standard electric valve, and it becomes possible to select a gas line electric valve 129 that is inexpensive.
  • the aperture of the liquid line electric valve 128 in response to the target discharge line temperature, the surplus refrigerant inside the receiver 121 can be adjusted, and the overall system can be controlled by controlling the intake superheating.
  • Step S5 it is determined whether or not there is surplus refrigerant in the refrigerant circuit, and whether or not there is a need to control capacity. For example, when there is surplus refrigerant in the refrigerant circuit, and the peak-cut control is in the suspend zone even though the operational frequency of the compressor 101 is at the lower limit, it will be determined that that there is surplus refrigerant and that capacity control is necessary, and the process will move to Step S6.
  • Step S6 the discharge - intake electric valve 142 is maintained in the closed state, and the aperture of the gas line electric valve 129 is controlled so that the peak-cut control remains stable in a no-change zone.
  • the aperture of the liquid line electric valve 128 is controlled in response to the target discharge line temperature.
  • the condensing capability of the auxiliary heat exchanger 133 is improved by opening the gas line electric valve 129, and the aperture of the gas line electric valve 129 is controlled so that the peak-cut control remains stable in a no-change zone. Because of this, refrigerant condensed via the auxiliary heat exchanger 133 is introduced into the receiver 121, surplus refrigerant is collected in the receiver 121, the high pressure refrigerant capacity is stabilized, and control of the operational frequency of the compressor 101 is stabilized in the no-change zone of the peak-cut control. In addition, because the gas line electric valve 129 is open, the control of the overall system (intake superheating control) occurs by adjusting the surplus refrigerant inside the receiver 121 by controlling the aperture of the liquid line valve 128 in response to the target discharge line temperature.
  • Step S7 it is determined whether or not the peak-cut control is still in the suspend zone even though the gas line electric valve 129 is completely open.
  • the peak-cut control is in the suspend zone even though the number of operational cycles of the compressor 101 is below a lower limit, and the peak-cut control is still in the suspend zone even though the gas line electric valve 129 is completely open, then the process moves to Step S8.
  • Step S8 the aperture of the discharge - intake bypass electric valve 142 is controlled so that the operational frequency of the compressor 101 remains stable in a no-change zone of the peak-cut control.
  • the gas line electric valve 129 is in the fully open state, and the aperture of the liquid line electric valve 128 is controlled in response to the target discharge line temperature.
  • the control of the overall system occurs by adjusting the surplus refrigerant inside the receiver 121 by controlling the aperture of the liquid line electric valve 128 in response to the target discharge line temperature.
  • FIG. 17 A working example during cooling operations is shown in Fig. 17 .
  • Step S11 it is determined at Step S11 whether or not there is surplus refrigerant in the refrigerant circuit, and whether or not capacity control is unnecessary.
  • the process moves to Step S12.
  • Step S12 the discharge - intake bypass electric valve 142 is placed into the fully closed state, the gas line electric valve 129 is placed in the fully open state, and the liquid line electric valve 128 for conducting SC control by means of the subcooling heat exchanger 134 is placed in the fully open state.
  • the outdoor heat exchanger 103 functions as a condenser, and the indoor heat exchangers 201 in each indoor unit function as vaporizers.
  • the electric valves 305A - 305C, 305D - 305F inside the branching units 300A, 300B are constructed such that each respective aperture thereof is controlled in accordance with the settings in each indoor unit, and refrigerant is distributed to each indoor heat exchanger 201.
  • the bypass electric valve 308 is placed in the fully open state.
  • refrigerant can be appropriately distributed to each indoor heat exchanger 201 by means of the electric valves 305A - 305C, 305D - 305F disposed inside the branching units 300A, 300B. Further, because surplus refrigerant is not generated inside the circuit, the receiver is placed into a non-operational state, and none of the discharge - intake bypass electric valve 142, liquid line electric valve 128, or the gas line electric valve 129 need be controlled.
  • Step S13 it is determined whether or not there is surplus refrigerant in the refrigerant circuit, and whether or not capacity control is unnecessary.
  • the process moves to Step S14.
  • Step S14 the discharge - intake bypass electric valve 142 is placed in the fully closed state, and the liquid line electric valve 128 is opened to a degree in which SC control by means of the subcooling heat exchanger 134 becomes possible (not fully open). Further, the aperture of the gas line electric valve 129 is controlled, and the overall system is controlled (intake superheating control), in order to place the discharge line temperature of the compressor 101 at the desired temperature.
  • surplus refrigerant can be introduced to and stored in the receiver 121 by opening the liquid line electric valve 128.
  • the aperture of the gas line electric valve 129 to correspond with the target discharge line temperature, the surplus refrigerant inside the receiver 121 can be adjusted, and the overall system can be controlled due to the control of intake superheating.
  • Step S15 it is determined whether or not there is surplus refrigerant in the refrigerant circuit, and whether or not capacity control is necessary.
  • Step S16 For example, when there are few indoor units operating, there is a surplus of refrigerant, and the freezing prevention control is in the suspend zone even though the operational frequency of the compressor 101 is at a lower limit, it is determined that capacity control is necessary and the process moves to Step S16.
  • the aperture of the discharge - intake bypass electric valve 142 is controlled so that control of the number of cycles of the compressor 101 stabilizes in an antifreeze control no-change zone.
  • the aperture of the liquid line electric valve 128 is controlled (not fully opened) in order to handle the surplus refrigerant from the liquid line piping 131, and the liquid refrigerant is stored in the receiver 121.
  • the amount of refrigerant inside the receiver 121 is adjusted by controlling the aperture of the gas line electric valve 129 to correspond with the target discharge line temperature, thereby controlling the overall system.
  • This type of operational state will be attained when, from amongst the connected indoor units 200C, only the indoor unit 200C is in the operational state, and this indoor unit 200C has a small capacity.
  • the aperture of the electric valve 305C corresponding to the indoor heat exchanger 201 of the operational indoor unit is controlled in response to the indoor temperature setting and the like, and the other electric valves 305A, 305B, and the electric valves 305D - 305F inside the branching unit 300B, are placed in the closed state.
  • the aperture of the discharge - intake bypass electric valve 142 can be controlled, the number of cycles of the compressor 101 can be stabilized, surplus refrigerant can be handled by adjusting the aperture of the liquid line electric valve 128, and the overall system can be controlled by adjusting the aperture of the gas line electric valve 129.
  • Step S17 it is determined whether or not the outside air temperature is lower than a predetermined temperature.
  • the outside air temperature is below a predetermined temperature, and when the liquid line electric valve 128 is placed in the fully closed state, there is a danger that the pressure inside the receiver 121 will become lower than the intake pressure of the compressor 101, and the liquid refrigerant stored in the receiver 121 will not be able to drain out. In this situation, there is a danger that a refrigerant shortage will occur in the refrigerant circuit.
  • the process moves to Step S18.
  • the pressure inside the receiver 121 is made higher than the pressure inside the gas line piping 132 by opening the aperture of the liquid line electric valve 128 to a predetermined degree, and the liquid refrigerant inside the receiver 121 is discharged into the auxiliary heat exchanger 133. Further, because the liquid line electric valve 128 is open, by controlling the aperture of the gas line electric valve 129, the target discharge line temperature can be controlled, and the overall system can be controlled. Moreover, the intake pressure of the compressor 101 can be increased by controlling the discharge - intake bypass electric valve 142 in order to prevent freezing.
  • the antifreeze control by controlling the aperture of the discharge - intake bypass electric valve 142, the indoor unit vaporization temperature is stably controlled in a no-change antifreeze control area.
  • the discharge - intake bypass electric valve 142 is placed in the fully closed state
  • the liquid line electric valve 128 is placed in the fully closed state
  • the gas line electric valve is placed in the fully opened state
  • the outside heat exchanger 103 is made to function as a condenser, and defrost operations take place.
  • the outdoor heat exchanger 103 is presumed to be thawed out, and the defrost operation ends. Heating operations will occur following this type of defrost operation, because defrost operations generally occur in the wintertime.
  • liquid refrigerant returns to the accumulator 105 because the ventilation fan inside the indoor unit 200 stops, and because the indoor heat exchanger 201 is not made to function as a vaporizer at the maximum level. In other words, the liquid refrigerant accumulates and backs up. Thus, after the completion of this type of defrost operation, it is difficult to promptly start heating operations, and the startup capabilities of the heater worsen.
  • liquid line electric valve 128 is opened, and the aperture of the gas line electric valve 129 is controlled so that the amount of refrigerant that the compressor 101 takes in is equivalent thereto. Because of this, liquid refrigerant can be introduced to and stored in the receiver 121, and will not accumulate and back up in the accumulator 105. Thus, the startup capabilities of the heater after the completion of defrost operations can be improved.
  • the gas line electric valve 129 when the gas line electric valve 129 is provided in the gas line connector 123 of the receiver 121, by controlling the opening and closing of the gas line electric valve 129, the surplus refrigerant in the receiver 121 that is injected back into the compressor 101 as a liquid can be adjusted. In this way, the discharge line temperature can be controlled. Further, when the liquid line electric valve 128 is provided in the liquid line connector 122 of the receiver, and the gas line electric valve 129 is provided in the gas line connector 123 of the receiver, during both cooling and heating, the amount of liquid refrigerant injected from the receiver 121 to the compressor 101 can be adjusted, and operational efficiency can be improved.
  • the target discharge line temperature is determined from the indoor heat exchanger temperature and the outdoor heat exchanger temperature, and the apertures of the liquid line electric valve 128 and the gas line electric valve 129 are adjusted so that the actual discharge line temperature comes close to the target discharge line temperature.
  • the amount of adjustment in the liquid line electric valve 128 and the gas line electric valve 129 can be determined, and each electric valve can be driven, from a table that corresponds the deviation between the target discharge line temperature and the actual discharge line temperature with the amount of change in the discharge temperature per unit of time.
  • the table that corresponds the deviation between the target discharge line temperature and the actual discharge line with the amount of change in the discharge temperature per unit of time can be a fuzzy table.
  • Step S21 it is determined whether or not control condition 1 is satisfied in order to begin target discharge line temperature control by means of the outside electric valves.
  • Control condition 1 is determined based upon the flow chart shown in Fig. 25 .
  • Step S41 it is determined whether or not the air conditioner is operating normally. If the air conditioner is in normal cooling operations or normal heating operations, then the process moves to Step S44, and if not, then the process moves to Step S42.
  • Step S42 it is determined whether or not the air conditioner is in a test mode.
  • the process moves to Step S44, and if not, the process moves to Step S43.
  • Step S43 it is determined whether or not the air conditioner is in defrost preheating operation.
  • the process moves to Step S44, and if not, the process moves to Step S49.
  • Step S44 it is determined whether or not the electric valves 305 inside the branching unit 300 are being controlled when the room in which heating or cooling is occurring changes.
  • the electric valves 305 inside each branching unit 300 are being controlled when the room in which heating or cooling is taking place is changed immediately after any of the indoor units 200 begin operating, or immediately after any of the indoor units 200 cease operation, then the process moves to Step S49, and if not, the process moves to Step S45.
  • Step S45 it is determined whether or not control is occurring during a change in the operational frequency.
  • the air conditioning load changes in the indoor units 200 during operation, and when control is occurring during a change in the number of operational cycles of the compressor 101, the process moves to Step S49, and if not, the process moves to Step S46.
  • Step S46 it is determined whether or not discharge line high temperature control is occurring.
  • the apertures of the liquid line valve 128 and the gas line valve 129 open a fixed amount, and discharge line high temperature control occurs such that the liquid refrigerant inside the receiver 121 backs up into the accumulator 103.
  • this type of discharge line high temperature control occurs, the process moves to Step S49, and if it does not, the process moves to Step S47.
  • Step S47 it is determined whether or not discharge line thermistor removal control is occurring.
  • the discharge temperature detected by the discharge line thermistor 109 does not rise above a predetermined temperature, even though the air conditioner runs for a fixed period of time from startup, there is a possibility that the discharge line thermistor 109 has been removed, or that it is due to environmental conditions, such as the outside air temperature being unusually cold.
  • the discharge temperature will be estimated from other temperature sensors and the like, a test operation will be run, and it will be confirmed that the discharge line thermistor 109 has in fact not been removed.
  • this operational control instigates the discharge line thermistor omission control, and this discharge line thermistor removal control occurs, the process moves to Step S49. If not, the process moves to Step S48.
  • Step S48 the apertures of the electric valves 128, 129 inside the outdoor device 100 are controlled, the target discharge line temperature control mode is set, and at Step S49, a mode in which this control does not occur is set.
  • Step S21 when control condition 1 is satisfied, and the target discharge line temperature control mode has been set by means of the outdoor unit electric valves, the process moves to Step S23.
  • Step S22 When the mode in which this control does not occur is set, the process moves to Step S22.
  • Step S22 a flag that shows whether or not a sampling timer has started for the first time is set initially to be on, and the process returns to the overall control main routine.
  • Step S23 the sampling timer is started.
  • This sampling timer counts the sampling timing of the discharge line temperature data in order to control the discharge line temperature.
  • Step S24 it is determined whether or not the sampling time counted exceeds a predetermined sampling time TTHS1.
  • This sampling time TTHS1 can be set in a range between 0 to 255 x 100 msec. For example, it can be set at 20 seconds.
  • Step S24 when it is determined that the count value of the sampling timer exceeds the sampling time TTHS1, the process moves to Step S25.
  • Step S25 the target discharge line temperature DOSET is determined.
  • the target discharge temperature DOSET is determined, as described above, the average value of the previous target discharge line temperature and the current target discharge line temperature is used (temporary target discharge line temperature) in order to minimize fluctuations due to disturbances.
  • the method of determining the temporary target discharge line temperature DOSETN is shown in Fig. 26 and 27 .
  • the determination of the temporary discharge line temperature DOSETN during cooling operations can be performed by means of the flow chart in Fig. 26 .
  • Step S51 it is determined whether or not the desired operational frequency FMK for the compressor 101 exceeds a condensing temperature correction coefficient switching frequency FEVFDC for calculating the target discharge line temperature during cooling operations.
  • FEVFDC condensing temperature correction coefficient switching frequency
  • a condensing temperature correction coefficient KEVFD is set to be a condensing temperature correction coefficient KEVFDC for calculating the target discharge line temperature during high frequency cooling.
  • the condensing temperature correction coefficient KEVFDC is set to be a condensing temperature correction coefficient KEVFDC1 for calculating the target discharge line temperature during low frequency cooling.
  • Step S54 it is determined whether or not the lowest temperature of a indoor heat exchanger operating in a room DCMNU is equal to or above a vaporizing temperature threshold for calculating the target discharge line temperature during cooling DZC.
  • the process moves to Step S55. If not, the process moves to Step S56.
  • the lowest temperature of a indoor heat exchanger operating in a room DCMNU is set as a vaporizing temperature DZ.
  • the current vaporizing temperature DZ is set to be the vaporizing temperature threshold for calculating the target discharge line temperature DZC.
  • intercept points DSHC are established for calculating the target discharge line temperature during cooling.
  • Step S58 it is determined whether or not the aperture EVP of the discharge - intake electric valve 142 is equal to or greater than a predetermined value EVPMIN.
  • EVPMIN a predetermined value
  • a target discharge line temperature correction value DEVP is set to be a target discharge line temperature value during cooling operations capacity control DEVPC.
  • the value of the target discharge line temperature correction value DEVP is set to zero.
  • the value of the temporary target discharge line temperature DOSETN is calculated from the condensing temperature correction coefficient for calculating the target discharge line temperature KEVFD, the outdoor heat exchanger temperature DE, a vaporizing temperature correction coefficient for calculating the target discharge line temperature during cooling KEVFDEC, the minimum indoor heat exchanger temperature (vaporizing temperature) DZ, the intercept points for calculating the target discharge line temperature during cooling DSHC, and the target discharge line temperature correction value DEVP.
  • DOSETN KEVFD x DE - KEVFDEC x DZ + DSHC - DEVP.
  • Step S71 it is determined whether or not a desired operational frequency FMK for the compressor 101 exceeds a condensing temperature correction coefficient switching frequency for calculating the target discharge line temperature during heating operations FEVFDW.
  • a desired operational frequency FMK for the compressor 101 exceeds a condensing temperature correction coefficient switching frequency for calculating the target discharge line temperature during heating operations FEVFDW.
  • a condensing temperature correction coefficient KEVFD is set to be a condensing temperature correction coefficient for calculating the target discharge line temperature during high frequency heating KEVFDW.
  • the condensing temperature correction coefficient KEVFD is set to be a condensing temperature correction coefficient for calculating the target discharge line temperature during low frequency heating KEVFDW1.
  • Step S74 it is determined whether or not the outdoor heat exchanger temperature DE is equal to or above a vaporizing temperature threshold for calculating the target discharge line temperature during heating DZW.
  • the process moves to Step S75. If not, the process moves to Step S76.
  • the lowest temperature of a indoor heat exchanger operating in a room DCMNU is set as a vaporizing temperature DZ.
  • the vaporizing temperature DZ is set to be the vaporizing temperature threshold for calculating the target discharge line temperature during heating DZW.
  • an intercept point for calculating the target discharge line temperature during heating DSHW is established.
  • the outdoor temperature DOA is smaller than an intercept point switching outside air temperature for calculating the target discharge line temperature during low temperature heating DOASH1
  • the intercept point for calculating the target discharge line temperature during heating DSHW is set as the intercept point for calculating the target discharge line temperature during low temperature heating DSHW1.
  • the value of the intercept point for calculating the target discharge line temperature during heating DSHW is set to be an intercept point for calculating the target discharge line temperature during moderate temperature heating DSHW2.
  • the value of the intercept point for calculating the target discharge line temperature during heating DSHW is set to be an intercept point for calculating the target discharge line temperature during high temperature heating DSHW3.
  • Step S78 it is determined whether or not the aperture EVP of the discharge - intake electric valve 142 is equal to or greater than a predetermined value EVPMIN.
  • EVPMIN a predetermined value
  • a target discharge line temperature correction value DEVP is set to be a target discharge line temperature value during heating operations capacity control DEVPW.
  • the value of the target discharge line temperature correction value DEVP is set to zero.
  • the value of the temporary target discharge line temperature DOSETN is calculated from the condensing temperature correction coefficient for calculating the target discharge line temperature KEVFD, the maximum indoor heat exchanger temperature DCMXT, a vaporizing temperature correction coefficient for calculating the target discharge line temperature during heating KEVFDEW, the vaporizing temperature DZ, the intercept point for calculating the target discharge line temperature during heating DSHC, and the target discharge line temperature correction value DEVP.
  • DOSETN KEVFD x DCMXT - KEVFDEW x DZ + DSHW - DEVP.
  • Step S91 it is determined whether or not the first time flag is on. Because a target discharge line temperature control mode is set by the outdoor unit electric valves, the first time flag indicates the first time the value of the sampling timer has exceeded the sampling time TTHS1. When the first time flag is on, the process moves to Step S92, and when it is not, the process moves to Step S93.
  • the target discharge line temperature DOSET is set as the temporary target discharge line temperature DOSETN.
  • the previous target discharge line temperature DOSETZ is set as the temporary target discharge line temperature.
  • DOSET DOSETN
  • DOSETZ DOSETN
  • Step S93 the average of the temporary target discharge line temperature DOSETN and the previous target discharge line temperature DOSETZ is calculated, and the target discharge line temperature DOSET is set to this value.
  • the previous target discharge line temperature DOSETZ is set to the temporary target discharge line temperature.
  • DOSET DOSETN + DOSETZ / 2
  • DOSETZ DOSETN
  • the largest and smallest values for the discharge line temperature during normal operations are considered, and are set as the upper and lower limits for the target discharge line temperature DOSETN.
  • the target discharge line temperature DOSET requested is controlled so as to be within these upper and lower limits.
  • the current discharge line temperature DO is detected.
  • the current discharge line temperature DO can be detected by reading the discharge line temperature thermistor 109.
  • the variation in the discharge line temperature EDO is calculated.
  • the discharge line temperature variation EDO the target discharge line temperature DOSET - the discharge line temperature DO.
  • amount of change in the discharge line temperature dDO is calculated.
  • the amount of change in the discharge line temperature the previous discharge line temperature DOZ - the current discharge line temperature DO.
  • Step S29 the discharge line temperature EDO and amount of change in the discharge line temperature dDO is used to search the fuzzy table, and the value for the amount of change in the electric valves PEVHN is determined.
  • Step S32 it is determined whether or not the air conditioner is in cooling operation mode.
  • the process moves to Step S33, and if not, the process moves to Step S34.
  • the amount of change in the electric valves PEVHN is corrected by means of a cooling correction coefficient KPOTD.
  • PEVHN KPOTD ⁇ PEVHN
  • the electric valve cumulative pulse PHNA is calculated based upon the amount of change in the electric valves PEVHN.
  • PHNA PHNA + PEVHN
  • Step S35 an integral part and fractional part of the electric valve cumulative pulse PHNA are each calculated, with the integral part set as PHN and the fractional part set as PHNA.
  • Step S36 it is determined whether or not the control condition 2 has been satisfied.
  • Step S101 it is determined whether or not the operational mode is set to cooling operations.
  • the process moves to Step S102, and if not, the process proceeds in the direction of D (Step S37 of Fig. 4 ).
  • Step S102 it is determined whether or not an indicator signal has been received from the connected branching unit 300 that indicates that the apertures of the electric valves 305 are at a minimum, which corresponds to the air conditioning in all rooms being halted.
  • an indicator signal has been received from the connected branching unit 300 that indicates that the apertures of the electric valves 305 are at a minimum, which corresponds to the air conditioning in all rooms being halted
  • the process proceeds in the direction of C (Step S38 of Fig. 24 ).
  • Step S103 the process moves to Step S103.
  • Step S103 it is determined whether or not a gas line electric valve aperture EVG is equal to or larger than a predetermined valve EVGMIN.
  • the process proceeds in the direction of C (Step S38 of Fig. 24 ), and if not, it proceeds in the direction of D (Step S37 of Fig. 24 ).
  • Step S37 the desired apertures of the electric valves are changed.
  • the gas line electric valve aperture EVG EVG - an electric valve change pulse PHN
  • the liquid line electric valve aperture EVL EVL - PHN.
  • Step S38 the desired aperture of the gas line electric valve is changed.
  • the gas line electric valve aperture EVG EVG + the electric valve change pulse PHN.
  • Step S39 the first time flag is placed in the off state, the sampling timer is reset, and the process moves to Step S21.
  • the appropriate discharge line temperature of the compressor 101 can be set by controlling the apertures of the liquid line electric valve 128 and the gas line electric valve 129 connected to the receiver 121.
  • the liquid injection amount can be appropriately controlled during not only cooling but also during heating, and it becomes possible to increase reliability and operational efficiency regardless of the operational mode.
  • a refrigerant circuit can be provided that minimizes the occurrence of refrigerant high-low drift even though a plurality of indoor units are placed in different vertical intervals, and in which cost reductions can be provided.
  • the air conditioner of the present invention by controlling the refrigerant opening and closing means connected to the receiver, the discharge line temperature of the compressor can be controlled, and reliability and operational efficiency can be improved.

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)
EP08003787A 2000-07-13 2001-07-12 Air conditioner refrigerant circuit Expired - Lifetime EP1933102B1 (en)

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
EP01947994A EP1300637B1 (en) 2000-07-13 2001-07-12 Refrigerant circuit of air conditioner

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP01947994A Division EP1300637B1 (en) 2000-07-13 2001-07-12 Refrigerant circuit of air conditioner

Publications (2)

Publication Number Publication Date
EP1933102A1 EP1933102A1 (en) 2008-06-18
EP1933102B1 true EP1933102B1 (en) 2009-11-18

Family

ID=18708920

Family Applications (2)

Application Number Title Priority Date Filing Date
EP01947994A Expired - Lifetime EP1300637B1 (en) 2000-07-13 2001-07-12 Refrigerant circuit of air conditioner
EP08003787A Expired - Lifetime EP1933102B1 (en) 2000-07-13 2001-07-12 Air conditioner refrigerant circuit

Family Applications Before (1)

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EP01947994A Expired - Lifetime EP1300637B1 (en) 2000-07-13 2001-07-12 Refrigerant circuit of air conditioner

Country Status (8)

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EP (2) EP1300637B1 (ko)
JP (1) JP3584862B2 (ko)
KR (1) KR100474400B1 (ko)
CN (1) CN1162665C (ko)
AT (2) ATE415601T1 (ko)
AU (1) AU766170B2 (ko)
DE (2) DE60136707D1 (ko)
WO (1) WO2002006738A1 (ko)

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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
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KR100564444B1 (ko) * 2003-10-20 2006-03-29 엘지전자 주식회사 에어컨의 액 냉매 누적 방지 장치 및 방법
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JP5212537B1 (ja) * 2011-12-13 2013-06-19 ダイキン工業株式会社 冷凍装置
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Publication number Publication date
KR100474400B1 (ko) 2005-03-09
JP2002022306A (ja) 2002-01-23
EP1933102A1 (en) 2008-06-18
AU766170B2 (en) 2003-10-09
WO2002006738A1 (fr) 2002-01-24
DE60140584D1 (de) 2009-12-31
ATE449295T1 (de) 2009-12-15
EP1300637A1 (en) 2003-04-09
JP3584862B2 (ja) 2004-11-04
DE60136707D1 (de) 2009-01-08
CN1386184A (zh) 2002-12-18
CN1162665C (zh) 2004-08-18
AU6951201A (en) 2002-01-30
ATE415601T1 (de) 2008-12-15
EP1300637A4 (en) 2006-12-20
KR20020035137A (ko) 2002-05-09
EP1300637B1 (en) 2008-11-26

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