EP1965150A1 - Conditionneur d'air - Google Patents

Conditionneur d'air Download PDF

Info

Publication number
EP1965150A1
EP1965150A1 EP06834561A EP06834561A EP1965150A1 EP 1965150 A1 EP1965150 A1 EP 1965150A1 EP 06834561 A EP06834561 A EP 06834561A EP 06834561 A EP06834561 A EP 06834561A EP 1965150 A1 EP1965150 A1 EP 1965150A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
stagnation
air conditioner
compression mechanism
heat source
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.)
Granted
Application number
EP06834561A
Other languages
German (de)
English (en)
Other versions
EP1965150A4 (fr
EP1965150B1 (fr
Inventor
Tadafumi Nishimura
Shinichi Kasahara
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
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
Publication of EP1965150A1 publication Critical patent/EP1965150A1/fr
Publication of EP1965150A4 publication Critical patent/EP1965150A4/fr
Application granted granted Critical
Publication of EP1965150B1 publication Critical patent/EP1965150B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02743—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using three four-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—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
    • 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
    • F25B2400/01—Heaters
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/22—Preventing, detecting or repairing leaks of refrigeration fluids
    • F25B2500/222—Detecting refrigerant leaks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/28—Means for preventing liquid refrigerant entering into 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/04—Refrigerant level
    • 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

Definitions

  • the present invention relates to a refrigerant circuit of an air conditioner and an air conditioner provided therewith.
  • Patent Document 1 An example of a conventional refrigerant leak detector of a refrigeration apparatus is disclosed in Patent Document 1.
  • a condensation refrigerant temperature and an evaporative refrigerant temperature are keep at a fixed value by using condensation refrigerant temperature adjustment means and evaporative refrigerant temperature adjustment means, and a refrigerant leak detection operation for detecting refrigerant leaks in a refrigerating cycle is carried out using temperature difference calculation means for comparing output signals of a discharge refrigerant temperature detector and set values and calculating a temperature difference.
  • the temperature of the condensation refrigerant that flows through a condenser and the temperature of the evaporative refrigerant that flow through an evaporator are kept at a fixed value, whereby the discharge refrigerant temperature under a suitable refrigerant quantity is set to the set value.
  • the set value and the output signal of the discharge refrigerant temperature detector are compared, a judgment is made that a refrigerant leak has not occurred when the value is less than the set value, and a judgment is made that a refrigerant leak has occurred when the value is higher than the set value.
  • An object of the present invention is to solve the stagnation of refrigerant in refrigeration machine oil inside a compressor, and to minimize the prediction error of the refrigerant quantity produced by the difference of solubility of the refrigerant into the oil.
  • the air conditioner according to a first aspect is provided with a refrigerant circuit, a refrigerant stagnation judging means, and an operation controller.
  • the refrigerant circuit is a circuit that includes a heat source unit, refrigerant communication pipes, expansion mechanisms, and a utilization unit.
  • the heat source unit has a compression mechanism and a heat source side heat exchanger.
  • a heat source unit is connected to the refrigerant communication pipes.
  • the utilization unit has a utilization side heat source exchanger and is connected to the refrigerant communication pipe.
  • the refrigerant stagnation judging means can judge whether the refrigerant is stagnant inside the compression mechanism.
  • the operation controller performs a refrigerant de-stagnation operation for eliminating stagnation of the refrigerant in the case that the refrigerant stagnation judging means has judged in advance that the refrigerant is stagnant inside the compression mechanism when a refrigerant quantity judging operation is carried out for judging the refrigerant quantity inside the refrigerant circuit.
  • the refrigerant stagnation judging means makes a judgment in advance whether refrigerant is stagnant in the refrigeration machine oil inside the compression mechanism when the refrigerant quantity judgment operation is carried out.
  • the operation controller performs the refrigerant de-stagnation operation when the refrigerant stagnation judging means judges that refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism.
  • the refrigerant quantity judgment operation can be performed after refrigerant stagnation has been eliminated in refrigeration machine oil inside the compression mechanism. For this reason, the quantity of refrigerant that dissolves into the refrigeration machine oil inside the compression mechanism can be dramatically reduced and error in predicting the refrigerant quantity can be reduced during the refrigerant quantity judgment operation.
  • a more precise refrigerant quantity judgment operation is made possible because the refrigerant stagnation can be eliminated in the refrigeration machine oil inside the compression mechanism during the refrigerant quantity judgment operation.
  • the air conditioner according to a second aspect is the air conditioner according to the first aspect, wherein the refrigerant stagnation judging means makes a judgment on the basis of the temperature inside the compression mechanism.
  • the judgment of the refrigerant stagnation judgment means is performed based on the temperature inside the compression mechanism. Refrigerant more readily stagnates in the refrigeration machine oil when the temperature inside the compression mechanism is low. Therefore, it is possible to determine that refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism when the temperature inside the compression mechanism is low. For this reason, it is possible to judge whether refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism on the basis of the temperature inside the compression mechanism.
  • the air conditioner according to a third aspect is the air conditioner according to the first aspect, wherein the refrigerant stagnation judging means makes a judgment on the basis of the outside air temperature.
  • the refrigerant stagnation judging means judges based on the temperature of the outside air.
  • the refrigerant readily becomes stagnant in the refrigeration machine oil when the temperature inside the compression mechanism is low. Therefore, the temperature inside the compression mechanism can be predicted because the temperature of the outside air can be measured. For this reason, the judgment that refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism is made possible when the temperature inside the compression mechanism can be predicted to be low. Judgment as to whether the refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism is thereby made possible.
  • the air conditioner according to a fourth aspect is the air conditioner according to the first aspect, wherein the refrigerant stagnation judging means makes a judgment on the basis of weather information.
  • the refrigerant stagnation judging means makes a judgment based on weather information obtained via a network connected to the refrigerant stagnation judgment means. Therefore, the outside temperature can be acquired from the weather information, and the temperature inside the compression mechanism can be predicted. It is accordingly possible to determine that the refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism when the temperature inside the compression mechanism can be predicted to be low. Judgment as to whether refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism is thereby made possible.
  • the air conditioner according to a fifth aspect is the air conditioner according to the first aspect, wherein the refrigerant stagnation judgment means makes judgment on the basis of a refrigerant stagnation interval in which the refrigerant is predicted to readily stagnate inside the compression mechanism.
  • the refrigerant stagnation judging means makes a judgment based on a time interval that has been set in advance.
  • the refrigerant readily stagnates in the refrigeration machine oil when the temperature inside the compression mechanism is low.
  • the judgment is made by establishing a time interval in which the temperature inside the compression mechanism is predicted to be low. Therefore, the user sets the time interval in which the temperature inside the compression mechanism is predicted to be low, whereby the refrigerant stagnation can be predicted without measuring the temperature inside the compression mechanism. It is thereby possible to judge whether the refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism. Also, production costs can be reduced because a temperature sensor or the like no longer needs to be installed.
  • the air conditioner according to a sixth aspect is the air conditioner according to any of the first to fifth aspects, wherein the operation controller performs a control for driving the compression mechanism for a first prescribed time as the refrigerant de-stagnation operation.
  • the refrigerant de-stagnation operation is a warm-up operation that is performed by driving a compressor for a first prescribed length of time. Therefore, in the refrigerant de-stagnation operation, a compressor is operated for a first prescribed length of time, whereby the interior of the compression mechanism can be warmed up. For this reason, refrigerant stagnation in the refrigeration machine oil inside the compression mechanism can be eliminated.
  • the air conditioner according to a seventh aspect is the air conditioner according to any of the first to sixth aspects, wherein a plurality of the heat source units is present.
  • the service life of the entire system can be extended without placing the load exclusively on a single unit even during low-load operation, because the heat source units in the system can be placed in a rotation and driven at fixed intervals of time one unit at a time.
  • the air conditioner according to an eighth aspect is the air conditioner according to any of the first to seventh aspects, wherein the compression mechanism has a plurality of compressors.
  • the compression mechanism has a plurality of compressors. Therefore, all of the heat source units can be continuously operated and the pooling of refrigerant and oil in the refrigerant circuit can be prevented to the extent possible even when the operating load of the utilization unit has been reduced because the capacity of the compression mechanism can be varied by controlling the number of compressors. The remaining compressors can handle the load even if one of the compressors malfunctions. For this reason, a complete stoppage of the air conditioner can be avoided.
  • the air conditioner according to a ninth aspect is the air conditioner according to the eighth aspect, wherein the refrigerant de-stagnation operation is an operation for driving at least a compressor that is not driven during the refrigerant quantity judgment operation.
  • the energy that is used can be reduced because all of the compressors are not required to operate. Also, the time required for the refrigerant de-stagnation operation can be reduced.
  • the air conditioner according to a tenth aspect is the air conditioner according to the eighth aspect, wherein the refrigerant de-stagnation operation is an operation in which the operation controller operates all of the compressors one at a time in sequence for a second prescribed time interval.
  • the air conditioner according to an eleventh aspect is the air conditioner according to the first aspect, further comprising a heater for warming the compression mechanism.
  • the refrigerant de-stagnation operation is an operation for warming the compression mechanism using the heater.
  • the refrigerant de-stagnation operation can be performed by warming the compression mechanism using a heater. Therefore, refrigerant stagnation can be eliminated without driving a compressor. For this reason, the time that a compressor is driven can be reduced and the service life of a compressor can be extended because a compressor is not required to be driven during the refrigerant de-stagnation operation.
  • the air conditioner according to a twelfth aspect is the air conditioner according to any of the first to eleventh aspects, wherein the operation controller further performs an oil-return operation immediately after the refrigerant de-stagnation operation.
  • the oil-return operation is an operation for returning oil pooled in the refrigerant circuit to the compression mechanism.
  • an oil-return operation is further carried out after the refrigerant de-stagnation operation. Therefore, oil that is pooled in the refrigerant circuit can be returned to the compression mechanism by further carrying out an oil-return operation.
  • the refrigerant quantity judgment operation can accordingly be carried out with greater precision.
  • the air conditioner according to a thirteenth aspect is the air conditioner according to the twelfth aspect, wherein the oil-return operation is an operation for controlling the refrigerant that flows through the refrigerant circuit so that the refrigerant flows inside the pipes at or above a prescribed rate.
  • the oil-return operation is an operation for controlling the refrigerant so that the refrigerant flows inside the pipes at or above a prescribed rate. Therefore, oil pooled in the refrigerant circuit can be reliably returned to the compression mechanism.
  • the refrigerant quantity judgment operation can accordingly be carried out with greater precision.
  • the refrigerant quantity judging operation can be carried out after the stagnation of refrigerant has been eliminated in the refrigeration machine oil inside the compression mechanism.
  • the quantity of refrigerant that has dissolved in the refrigeration machine oil inside the compression mechanism can accordingly be reduced to the extent possible at the time of the refrigerant quantity judging operation, and the prediction error of the refrigerant quantity can be reduced.
  • a more precise refrigerant quantity judgment operation is made possible because the refrigerant stagnation can be eliminated in the refrigeration machine oil inside the compression mechanism during the refrigerant quantity judgment operation.
  • the refrigerant can be judged to have stagnated in the refrigeration machine oil inside the compression mechanism when the temperature inside the compression mechanism is low. For this reason, the decision as to whether the refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism can be made on the basis of the temperature inside the compression mechanism.
  • the temperature inside the compression mechanism can be predicted because the temperature of the outside air can be measured. Accordingly, it can be judged that the refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism when the temperature inside the compression mechanism can be predicted to be low. It can thereby be judged whether the refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism.
  • the temperature of the outside air can be acquired from weather information and the temperature inside the compression mechanism can be predicted. Accordingly, it can be judged that the refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism when the temperature inside the compression mechanism can be predicted to be low. It can thereby be judged whether the refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism.
  • a user sets a length of time in which the temperature inside the compression mechanism is predicted to be low, whereby refrigerant stagnation can be predicted without measuring the temperature inside the compression mechanism. It is thereby possible to judge whether refrigerant has stagnated in the refrigeration machine oil inside the compression mechanism. Production costs can be reduced because there is no longer a need to install a temperature sensor or the like.
  • the interior of the compression mechanism can be warmed by operating a compressor for a first prescribed length of time. For this reason, refrigerant stagnation in the refrigeration machine oil inside the compression mechanism can be eliminated.
  • the service life of the entire system can be extended without placing the load exclusively on a single unit even during low-load operation because the heat source units in the system can be placed in a rotation and driven at fixed intervals of time one unit at a time.
  • all of the heat source units can be operated continuously and the pooling of refrigerant and oil in the refrigerant circuit can be prevented to the extent possible even when the operating load of the utilization units is low, because the capacity of the compression mechanism can be varied by controlling the number of compressors. The remaining compressors can handle the load even if one of the compressors malfunctions. For this reason, a complete stoppage of the air conditioner can be avoided.
  • the energy that is used can be reduced because all of the compressors are not required to operate. Also, the time required for the refrigerant de-stagnation operation can be reduced.
  • all of the compressors can be driven in advance by operating the compressors for a second prescribed time interval one unit at a time.
  • stagnation of the refrigerant can be eliminated without driving a compressor.
  • the time a compressor is driven can be reduced and the service life of the compressors can be extended because a compressor is not required to be driven during the refrigerant de-stagnation operation.
  • oil that has pooled in the refrigerant circuit can be returned to the compression mechanism by further performing an oil-return operation.
  • the refrigerant quantity judging operation can accordingly be carried out with greater precision.
  • oil that has pooled inside the refrigerant circuit can be reliably returned to the compression mechanism.
  • the refrigerant quantity judging operation can accordingly be carried out with greater precision.
  • FIG. 1 shows a schematic diagram of refrigerant circuit of an air conditioner 1 related to a first embodiment of the present invention.
  • the air conditioner 1 is used for conditioning the air of a building or the like, and has a configuration in which a plurality (three, in the present embodiment) of air-cooled heat source units 2a to 2c and numerous utilization units 3a, 3b, ... are connected in parallel to a liquid refrigerant communication pipe 4 and a gas refrigerant communication pipe 5, respectively. In this case, only two utilization units 3a and 3b are shown.
  • the plurality of heat source units 2a to 2c are provided with compression mechanisms 2 1 a to 21c that each have single variable-capacity compressors 22a to 22c and a plurality (two, in the present embodiment) fixed-capacity compressors 27a to 27c, and 28a to 28c.
  • the utilization units 3a, 3b, ... are mainly composed of utilization side expansion valves 31a, 31b, ... , utilization side heat exchangers 32a, 32b, ... , and pipes that connect thereto, respectively.
  • the utilization side expansion valves 31a, 31b, ... are electrically driven expansion valves connected to the liquid refrigerant communication pipe 4 side (hereinafter referred to as a liquid side) of the utilization side heat exchangers 32a, 32b, ... in order to adjust the refrigerant pressure, adjust the refrigerant flow rate, and perform other operations.
  • the utilization side heat exchangers 32a, 32b, ... are cross-fin tube heat exchangers and are devices for exchanging heat with indoor air.
  • the utilization units 3a, 3b, ... are provided with a indoor fan (not shown) for taking indoor air into the units and discharging air, and can exchange heat between the indoor air and the refrigerant that flows through the utilization side heat exchangers 32a, 32b, ... .
  • the heat source units 2a to 2c are mainly composed of compression mechanisms 21 a to 21 c, four-way switching valves 23a to 23c, heat source side heat exchangers 24a to 24c, liquid side stop valves 25a to 25c, gas side stop valves 26a to 26c, heat source side expansion valves 29a to 29c, and pipes that connect thereto, respectively.
  • the heat source side expansion valves 29a to 29c are electrically driven expansion valves connected to the liquid refrigerant communication pipe 4 side (hereinafter referred to as a liquid side) of the heat source side expansion valves 29a to 29c in order to adjust the refrigerant pressure, adjust the refrigerant flow rate, and perform other operations.
  • the compression mechanisms 21a to 21c have variable-capacity compressors 22a to 22c, two fixed-capacity compressors 27a to 27c and 28a to 28c, and an oil separator (not shown).
  • the compressors 22a to 22c, 27a to 27c, and 28a to 28c are devices for compressing refrigerant gas that has been taken in, and, in the present embodiment, are composed of a single variable-capacity compressor in which the operating capacity can be changed by inverter control, and two fixed-capacity compressors.
  • the four-way switching valves 23a to 23c are valves for switching the direction of the flow of the refrigerant when a switch is made between cooling and heating operations; during cooling operation, are capable of connecting the compression mechanisms 21a to 21c and the gas refrigerant communication pipe 5 side (hereinafter referred to as gas side) of the heat source side heat exchangers 24a to 24c, and connecting a suction side of the compressors 21 a to 21c and the gas refrigerant communication pipe 5 (see the solid lines of the four-way switching valves 23a to 23c of FIG.
  • the heat source side heat exchangers 24a to 24c are cross-fin tube heat exchangers and are devices for exchanging heat between the refrigerant and outside air as a heat source.
  • the heat source units 2a to 2c are provided with an outdoor fan (not shown) for taking outdoor air into the units and discharging air, and can exchange heat between the outdoor air and the refrigerant that flows through the heat source side heat exchangers 24a to 24c.
  • the liquid side stop valves 25a to 25c and the gas side stop valves 26a to 26c of the heat source units 2a to 2c are connected in parallel to the liquid refrigerant communication pipe 4 and the gas refrigerant communication pipe 5.
  • the liquid refrigerant communication pipe 4 is connected between the liquid side of the utilization side heat exchangers 32a, 32b, ... of the utilization units 3a, 3b, ... and the liquid side of the heat source side heat exchangers 24a to 24c of the heat source units 2a to 2c.
  • the gas refrigerant communication pipe 5 is connected between the gas side of the utilization side heat exchangers 32a, 32b, ... of the utilization units 3a, 3b, ... and the four-way switching valves 23a to 23c of the heat source units 2a to 2c.
  • the air conditioner 1 is further provided with refrigerant stagnation judging means 8a to 8c and operation controllers 6a to 6c.
  • the refrigerant stagnation judging means 8a to 8c judges whether refrigerant has stagnated inside the compression mechanisms 21 a to 21c.
  • the operation controllers 6a to 6c carry out in advance a refrigerant de-stagnation operation for resolving stagnation of the refrigerant when the refrigerant has stagnated in the compression mechanisms 21a to 21c when a refrigerant quantity judging operation for judging the of refrigerant quantity inside the refrigerant circuit 7 is carried out.
  • the refrigerant stagnation judging means and the operation controllers 6a to 6c are housed in the heat source units 2a to 2c.
  • Operation control such as that described above can be performed using only the operation controller (6a, in this case) of the heat source unit (2a, in this case) set as the parent device.
  • the operation controllers (6b and 6c, in this case) of the heat source units (2a and 2b, in this case) set as the other subordinate devices can send the operating state of the compression mechanism and other devices and detection data in the various sensors to the parent operation controller 6a, and can function so as to send operation and stop commands to the compression mechanism and other devices via commands from the parent operation controller 6a.
  • temperature sensors 61a to 61c are provided, the temperature of the outside air is measured by the temperature sensors, and the temperature data is sent to the parent operation controller 6a.
  • a judgment is made whether to perform the refrigerant de-stagnation operation.
  • the four-way switching valves 23a to 23c in all of the heat source units 2a to 2c are in the state indicated by the solid lines in FIG. 1 , i.e., the discharge side of the compression mechanisms 2 1 a to 2 1 c is connected to the gas side of the heat source side heat exchangers 24a to 24c, and the suction side of the compression mechanisms 21a to 21c is connected to the gas side of the utilization side heat exchangers 32a, 32b, ... via the gas refrigerant communication pipe 5.
  • the liquid side stop valves 25a to 25c and the gas side stop valves 26a to 26c are opened and the opening position of the utilization side expansion valves 31a, 31 b, ... is adjusted so as to reduce the pressure of the refrigerant.
  • the refrigerant gas is taken into the compression mechanisms 2 1 a to 21c and compressed when the outdoor fans (not shown) of the heat source units 2a to 2c and the indoor fans (not shown) and the compression mechanisms 21a: to 21c of the utilization units 3a, 3b, ... are started up, whereupon the refrigerant gas is sent to the heat source side heat exchangers 24a to 24c via the four-way switching valves 23a to 23c, exchanges heat with the outside air, and is condensed.
  • the condensed refrigerant liquid is merged with the liquid refrigerant communication pipe 4 and sent to the utilization units 3a, 3b, ....
  • the refrigerant fluid sent to the utilization units 3a, 3b, ... is reduced in pressure by the utilization side expansion valves 31a, 31b, ... , is then subjected to heat exchange with indoor air in the utilization side heat exchangers 32a, 32b, ... , and is then caused to evaporate.
  • the evaporated refrigerant gas is sent through the gas refrigerant communication pipe 5 to the heat source units 2a to 2c side.
  • the refrigerant gas that flows through the gas refrigerant communication pipe 5 passes through the four-way switching valves 23a to 23c of the heat source units 2a to 2c, and is thereafter taken into the compression mechanisms 21 a to 21c again.
  • the cooling operation is carried out in this manner.
  • the four-way switching valves 23a to 23c in all of the heat source units 2a to 2c are in the state indicated by the broken lines in FIG. 1 , i.e., the discharge side of the compression mechanisms 21a to 21c is connected to the gas side of the utilization side heat exchangers 32a, 32b, ... via the gas refrigerant communication pipe 5 and the suction side of the compression mechanisms 21 a to 21c is connected to the gas side of the heat source side heat exchangers 24a to 24c.
  • the liquid side stop valves 25a to 25c and the gas side stop valves 26a to 26c are opened and the opening position of the heat source side expansion valves 29a to 29c is adjusted so as to reduce the pressure of the refrigerant.
  • the refrigerant gas is taken into the compression mechanisms 21a to 21c and compressed when the outdoor fans (not shown) of the heat source units 2a to 2c and the indoor fans (not shown) and the compression mechanisms 21a to 21c of the utilization units 3a, 3b, ... are started up, whereupon the refrigerant gas is merged with the gas refrigerant communication pipe 5 via the four-way switching valves 23a to 23c of the heat source units 2a to 2c and sent to the utilization units 3a, 3b, ... side.
  • the refrigerant gas sent to the utilization units 3a, 3b, ... exchanges heat with the indoor air via the utilization side heat exchangers 32a, 32b, ...
  • the condensed refrigerant is merged with the liquid refrigerant communication pipe 4 via the utilization side expansion valves 3 1 a, 31 b, ... , and is sent to the heat source units 2a to 2c side.
  • the refrigerant liquid that flows through the liquid refrigerant communication pipe 4 is made to exchange heat with the outside air via the heat source side heat exchangers 24a to 24c of the heat source units 2a to 2c, and is caused to evaporate.
  • the evaporated refrigerant gas is taken into the compression mechanisms 21a to 21c again via the four-way switching valves 23a to 23c of the heat source units 2a to 2c.
  • the heating operation is carried out in this manner.
  • the refrigerant quantity judging operation includes a refrigerant leakage detection operation and an automatic refrigerant charging operation.
  • FIG. 2 is a flowchart of the refrigerant leak detection operation.
  • the refrigerant leak detection operation which is a refrigerant quantity judging operation, during cooling operation or heating operation in normal operation, whereby detection is performed to determine whether refrigerant inside the refrigerant circuit 7 has leaked to the exterior due to an unknown cause.
  • step S1 a refrigerant quantity judging preparatory operation is carried out prior to refrigerant leak detection operation.
  • the refrigerant quantity judging preparatory operation will be described later.
  • step S2 a judgment is made whether an operation in normal operation such as the cooling operation or the heating operation described above has continued for a fixed length of time (e.g., one month), and the process proceeds to the next step S2 when an operation in normal operation has continued for a fixed length of time.
  • a fixed length of time e.g., one month
  • step S3 when an operation in normal operation has continued for a fixed length of time, the refrigerant circuit 7 enters a state in which the four-way switching valves 23a to 23c of the heat source units 2a to 2c are in the state indicated by the solid lines of FIG. 1 , the utilization side expansion valves 31a, 31b, ... of the utilization units 3a, 3b, ... are opened, the compression mechanisms 21a to 21c and the outdoor fan (not shown) are actuated, and a cooling operation is forcibly carried out in all of the utilization units 3a, 3b, ... .
  • step S4 condensation pressure control by an outdoor fan, overheating control by the utilization side expansion valves 31a, 31b, ... , and evaporation pressure control by the compression mechanisms 21 a to 21c are carried out and the state of the refrigerant that circulates inside the refrigerant circuit 7 is stabilized.
  • step S5 subcooling degree is detected at the outlets of the heat source side heat exchangers 24a to 24c.
  • step S6 the subcooling degree detected in step S5 is used to judge whether the refrigerant quantity is adequate.
  • the adequacy of the refrigerant quantity charged in the refrigerant circuit 7 can be judged when subcooling degree is detected in step S5 by using the subcooling degree of the refrigerant at the outlets of the heat source side heat exchangers 24a to 24c without relation to the mode of the utilization units 3a, 3b, ... and the length of the liquid refrigerant communication pipe 4 and gas refrigerant communication pipe 5.
  • the refrigerant quantity in the heat source side heat exchangers 24a to 24c is at a low level when the quantity of additional refrigerant charging is low and the required refrigerant quantity is not attained (specifically indicating that the subcooling degree detected in step S5 is less than an subcooling degree that corresponds to the refrigerant quantity that is required for condensation pressure of the heat source side heat exchangers 24a to 24c). It is judged that there is no refrigerant leakage when the subcooling degree detected in step S5 is substantially the same degree (e.g., the difference between the detected subcooling degree and the target subcooling degree is less than a prescribed degree) as the target subcooling degree, and the refrigerant leak detection operation is ended.
  • step S5 when the subcooling degree detected in step S5 is a degree that is less than the target subcooling degree (e.g., the difference between the detected subcooling degree and the target subcooling degree is a prescribed degree or greater), it is judged that refrigerant leakage has occurred.
  • the process proceeds to the processing of step S7, and a warning that provides notification that refrigerant leakage has been detected is displayed, whereupon the refrigerant leak detection operation is ended.
  • FIG. 3 is a flowchart of the automatic refrigerant charging operation.
  • a refrigerant circuit 7 is assembled at the installation site by connecting the utilization units 3a, 3b, ... and the heat source units 2a to 2c filled with refrigerant in advance are connected by way of the liquid refrigerant communication pipe 4 and gas refrigerant communication pipe 5, and refrigerant that is lacking is thereafter added and charged in the refrigerant circuit 7 in accordance with the length of the liquid refrigerant communication pipe 4 and the gas refrigerant communication pipe 5.
  • the liquid side stop valves 25a to 25c and the gas side stop valves 26a to 26c of the heat source units 2a to 2c are opened, and the refrigerant charged in advance in the heat source units 2a to 2c is filled into the refrigerant circuit 7.
  • the person who carries out the refrigerant charging work sends a command to carry out an automatic refrigerant charging operation, which is one of the refrigerant quantity judging operation, via remote control or directly to utilization side controllers (not shown) of the utilization units 3a, 3b, ... or to the operation controllers 6a to 6c of the heat source units 2a to 2c, whereupon the automatic refrigerant charging operation is carried out in the sequence of step S11 to step S 14.
  • step S11 the refrigerant quantity judging preparatory operation is carried out prior to the automatic refrigerant charging operation.
  • the refrigerant quantity judging preparatory operation will be described later.
  • step S12 when a command has been issued for the automatic refrigerant charging operation to begin, the refrigerant circuit 7 enters a state in which the four-way switching valves 23a to 23c of the heat source units 2a to 2c are in the state indicated by the solid lines of FIG. 1 , the utilization side expansion valves 31a, 31b, ... of the utilization units 3a, 3b, ... are opened, the compression mechanisms 21a to 21c and the outdoor fan (not shown) are actuated, and a cooling operation is forcibly carried out in all of the utilization units 3a, 3b,
  • step S13 condensation pressure control by an outdoor fan, overheating control by the utilization side expansion valves 31a, 31 b, ... , and evaporation pressure control by the compression mechanisms 21a to 21c are carried out and the state of the refrigerant that circulates inside the refrigerant circuit 7 is stabilized.
  • step S14 subcooling degree is detected at the outlets of the heat source side heat exchangers 24a to 24c.
  • step S 15 the subcooling degree detected in step S 14 is used to judge whether the amount of refrigerant is adequate. Specifically, when the subcooling degree detected in step S 14 is less than the target subcooling degree and refrigerant charging is not completed, the processing of step S 13 and step S 14 is repeated until the subcooling degree reaches the target subcooling degree.
  • the automatic refrigerant charging operation can be carried out when refrigerant is charged during a test operation after onsite installation, and can also be used to perform additional refrigerant charging when the quantity of refrigerant charged in the refrigerant circuit 7 has been reduced due to refrigerant leakage or the like.
  • refrigerant stagnation judging means 8a to 8c judges that the refrigerant has stagnated inside the compression mechanisms 21a to 21c when the temperature detected by temperature sensors 61a to 61 c is lower than a prescribed temperature, and sends a signal indicating the stagnation of the refrigerant to the operation controller 6a.
  • the operation controller 6a which has received a signal from the refrigerant stagnation judging means 8a to 8c, performs -a control (refrigerant de-stagnation operation) preliminarily so that the compressors 22a to 22c, 27a to 27c, and 28a to 28c are sufficiently warmed.
  • the operation controller 6a judges in step S21 whether the temperature inside the compression mechanisms 2 1 a to 21c measured by the temperature sensors 61a to 61c is lower than a prescribed temperature.
  • the process proceeds to step S22, and when the temperature is not lower than the prescribed temperature, the process proceeds to step S23.
  • the refrigerant de-stagnation operation is carried out in step S22 and the process proceeds to step S23.
  • An oil-return operation is carried out in step S23.
  • step S2 the refrigerant quantity judging operation is a refrigerant leak detection operation
  • step S12 the refrigerant quantity judging operation is an automatic refrigerant charging operation.
  • the operation controller 6a issues a drive command to all of the compression mechanisms 21a to 21c of the heat source units 2a to 2c when a signal is received from the refrigerant stagnation judging means 8a to 8c.
  • the operation controllers 6b and 6c which are subordinate devices, receive the commands of the parent operation controller 6a and issue a drive command to the compression mechanisms 21b and 21c.
  • step S32 the compressors 22a to 22c are driven in step S31 and the process proceeds to step S32.
  • step S32 the compressors 22a to 22c are stopped 15 minutes after step S31, the compressors 27a to 27c are driven, and the process proceeds to step S33.
  • step S33 the compressors 27a to 27c are stopped 15 minutes after step S32, the compressors 28a to 28c are driven, and the process proceeds to step S34.
  • step S34 the compressors 28a to 28c are stopped 15 minutes after step S33, and the refrigerant de-stagnation operation is ended.
  • step S23 The oil-return operation of step S23 is carried out when the refrigerant de-stagnation operation described above is ended, or when the temperature of the compressors in step S21 is higher than a prescribed temperature.
  • the oil-return operation will be described with reference to FIG. 6 .
  • step S41 the operation controller 6a issues a command to drive one of the compressors (i.e., compressors 22a to 22c) of the heat source units 2a to 2c.
  • the operation controllers 6b and 6c which are subordinate devices, receive the commands of the parent operation controller 6a and the subordinate operation controllers 6b and 6c issue a drive command to the compression mechanisms 22b and 22c.
  • step S41 the process proceeds to step S42.
  • step S42 the operation controller 6a issues a command to stop after the compressors 22a to 22c have been driven for 5 minutes. The oil pooled in the refrigerant circuit 7 can thereby be returned to the compression mechanisms 21 a to 21 c.
  • the air conditioner of the present invention can eliminate the stagnation of refrigerant in refrigeration machine oil inside a compression mechanism prior to a refrigerant quantity judging operation. Since a highly precise refrigerant quantity judging operation can be performed, the present invention is useful as a refrigerant circuit of an air conditioner, an air conditioner provided therewith, and other air conditioners.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
EP06834561.0A 2005-12-16 2006-12-13 Conditionneur d'air Active EP1965150B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005363739A JP2007163106A (ja) 2005-12-16 2005-12-16 空気調和装置
PCT/JP2006/324806 WO2007069624A1 (fr) 2005-12-16 2006-12-13 Conditionneur d'air

Publications (3)

Publication Number Publication Date
EP1965150A1 true EP1965150A1 (fr) 2008-09-03
EP1965150A4 EP1965150A4 (fr) 2014-07-02
EP1965150B1 EP1965150B1 (fr) 2017-07-26

Family

ID=38162931

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06834561.0A Active EP1965150B1 (fr) 2005-12-16 2006-12-13 Conditionneur d'air

Country Status (8)

Country Link
US (1) US20090314017A1 (fr)
EP (1) EP1965150B1 (fr)
JP (1) JP2007163106A (fr)
KR (1) KR20080071601A (fr)
CN (1) CN101331366B (fr)
AU (1) AU2006324541B2 (fr)
ES (1) ES2636912T3 (fr)
WO (1) WO2007069624A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1965159A1 (fr) * 2005-12-16 2008-09-03 Daikin Industries, Ltd. Conditionneur d'air
EP2088391A2 (fr) * 2008-02-05 2009-08-12 LG Electronics Inc. Appareil de climatisation d'air et procédé pour déterminer la quantité de réfrigérant de l'appareil de climatisation d'air
EP2103889A2 (fr) * 2008-03-21 2009-09-23 Lg Electronics Inc. Climatiseur et procédé de chargement de réfrigérant de climatiseur
EP2196746A3 (fr) * 2008-12-11 2015-01-28 Fujitsu General Limited Appareil de réfrigération
EP3026371A1 (fr) * 2014-11-21 2016-06-01 Mitsubishi Electric Corporation Appareil de circuit de refrigeration
WO2018140756A1 (fr) 2017-01-27 2018-08-02 Emerson Climate Technologies, Inc. Système de détection de faible charge pour systèmes de refroidissement

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5124404B2 (ja) * 2008-09-12 2013-01-23 日立アプライアンス株式会社 空気調和装置
JP5183609B2 (ja) 2009-10-23 2013-04-17 三菱電機株式会社 冷凍空調装置
JP2011102674A (ja) * 2009-11-11 2011-05-26 Mitsubishi Electric Corp 空気調和機
JP5464615B2 (ja) * 2010-02-04 2014-04-09 株式会社前川製作所 ヒートポンプ装置及びヒートポンプ装置の運転方法
US9222711B2 (en) * 2010-03-12 2015-12-29 Mitsubishi Electric Corporation Refrigerating and air-conditioning apparatus
JP4888583B2 (ja) * 2010-05-31 2012-02-29 ダイキン工業株式会社 冷凍装置
AU2010363489B2 (en) * 2010-11-04 2015-05-07 Mitsubishi Electric Corporation Air conditioner
JP5831830B2 (ja) * 2011-08-11 2015-12-09 Ｋｙｂ株式会社 鉄道車両用制振装置
US9759465B2 (en) * 2011-12-27 2017-09-12 Carrier Corporation Air conditioner self-charging and charge monitoring system
JP5288020B1 (ja) * 2012-03-30 2013-09-11 ダイキン工業株式会社 冷凍装置
JP6111665B2 (ja) * 2012-12-28 2017-04-12 ダイキン工業株式会社 冷凍装置
JP2014185786A (ja) * 2013-03-22 2014-10-02 Mitsubishi Electric Corp 冷凍サイクル用圧縮機の駆動制御装置
JP6191447B2 (ja) * 2013-12-25 2017-09-06 株式会社富士通ゼネラル 空気調和装置
CN103912958B (zh) * 2014-04-10 2017-12-01 安徽美芝精密制造有限公司 空调系统的控制方法、控制装置和空调系统
US10119738B2 (en) 2014-09-26 2018-11-06 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
US10641268B2 (en) * 2015-08-11 2020-05-05 Emerson Climate Technologies, Inc. Multiple compressor configuration with oil-balancing system
JP2017180894A (ja) * 2016-03-29 2017-10-05 株式会社富士通ゼネラル 空気調和機
AU2016420272B2 (en) * 2016-08-16 2019-07-04 Mitsubishi Electric Corporation Air-conditioning apparatus
JP6859461B2 (ja) * 2018-02-16 2021-04-14 東芝キヤリア株式会社 冷凍サイクル装置
US11592215B2 (en) 2018-08-29 2023-02-28 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
JP7282157B2 (ja) * 2019-03-19 2023-05-26 三菱電機株式会社 室外機及びそれを備える冷凍サイクル装置
CN110553440B (zh) * 2019-09-04 2021-07-27 广东美的暖通设备有限公司 多联机系统、防液击控制方法、装置及可读存储介质

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004028503A (ja) * 2002-06-27 2004-01-29 Mitsubishi Heavy Ind Ltd 車両輸送用冷凍装置
US20040194485A1 (en) * 2003-04-04 2004-10-07 Dudley Kevin F. Compressor protection from liquid hazards

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63101755U (fr) * 1986-12-23 1988-07-02
JPH0618103A (ja) * 1992-06-30 1994-01-25 Toshiba Corp 空気調和機
KR19990039709A (ko) * 1997-11-13 1999-06-05 최진호 냉동시스템 설계방법
JP2001263885A (ja) * 2000-03-24 2001-09-26 Japan Climate Systems Corp 車両空調用不足冷媒量検出装置
JP2002350014A (ja) * 2001-05-22 2002-12-04 Daikin Ind Ltd 冷凍装置
JP2005043008A (ja) * 2003-07-24 2005-02-17 Denso Corp 冷凍サイクル装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004028503A (ja) * 2002-06-27 2004-01-29 Mitsubishi Heavy Ind Ltd 車両輸送用冷凍装置
US20040194485A1 (en) * 2003-04-04 2004-10-07 Dudley Kevin F. Compressor protection from liquid hazards

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2007069624A1 *

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1965159A1 (fr) * 2005-12-16 2008-09-03 Daikin Industries, Ltd. Conditionneur d'air
EP1965159A4 (fr) * 2005-12-16 2015-11-25 Daikin Ind Ltd Conditionneur d'air
EP2088391A2 (fr) * 2008-02-05 2009-08-12 LG Electronics Inc. Appareil de climatisation d'air et procédé pour déterminer la quantité de réfrigérant de l'appareil de climatisation d'air
EP2088391A3 (fr) * 2008-02-05 2011-08-24 LG Electronics Inc. Appareil de climatisation d'air et procédé pour déterminer la quantité de réfrigérant de l'appareil de climatisation d'air
EP2103889A2 (fr) * 2008-03-21 2009-09-23 Lg Electronics Inc. Climatiseur et procédé de chargement de réfrigérant de climatiseur
EP2103889A3 (fr) * 2008-03-21 2011-04-13 LG Electronics Inc. Climatiseur et procédé de chargement de réfrigérant de climatiseur
US9027357B2 (en) 2008-03-21 2015-05-12 Lg Electronics Inc. Method for determining if refrigerant charge is sufficient and charging refrigerant
EP2196746A3 (fr) * 2008-12-11 2015-01-28 Fujitsu General Limited Appareil de réfrigération
EP3026371A1 (fr) * 2014-11-21 2016-06-01 Mitsubishi Electric Corporation Appareil de circuit de refrigeration
WO2018140756A1 (fr) 2017-01-27 2018-08-02 Emerson Climate Technologies, Inc. Système de détection de faible charge pour systèmes de refroidissement
EP3574271A4 (fr) * 2017-01-27 2020-09-09 Emerson Climate Technologies, Inc. Système de détection de faible charge pour systèmes de refroidissement
US11085679B2 (en) 2017-01-27 2021-08-10 Emerson Climate Technologies, Inc. Low charge detection system for cooling systems

Also Published As

Publication number Publication date
US20090314017A1 (en) 2009-12-24
JP2007163106A (ja) 2007-06-28
AU2006324541B2 (en) 2009-11-12
WO2007069624A1 (fr) 2007-06-21
AU2006324541A1 (en) 2007-06-21
CN101331366A (zh) 2008-12-24
EP1965150A4 (fr) 2014-07-02
CN101331366B (zh) 2010-09-22
KR20080071601A (ko) 2008-08-04
EP1965150B1 (fr) 2017-07-26
ES2636912T3 (es) 2017-10-10

Similar Documents

Publication Publication Date Title
EP1965150B1 (fr) Conditionneur d'air
EP2535670B1 (fr) Climatiseur
EP1970652B1 (fr) Conditionneur d'air
AU2007244357B2 (en) Air conditioner
EP1970655B1 (fr) Conditionneur d'air
KR101207004B1 (ko) 공기 조화 장치
JP4479565B2 (ja) 異常検知システム
US9739513B2 (en) Air conditioning apparatus
JP5971371B1 (ja) 冷凍装置
US20090260376A1 (en) Air conditioner
JP4826117B2 (ja) 冷媒漏洩検知システム
EP1965159B1 (fr) Conditionneur d'air
JP2006275303A (ja) 異常検知システム
KR20060029565A (ko) 멀티 에어컨 시스템 및 멀티 에어컨 시스템의 배관연결탐색방법
JP2002188874A (ja) 冷凍装置
EP4166865A1 (fr) Système d'évaluation de dispositif de circuit de réfrigérant
JP2015152290A (ja) 空気調和装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20080701

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20140604

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 13/00 20060101ALI20140528BHEP

Ipc: F25B 49/00 20060101ALI20140528BHEP

Ipc: F25B 45/00 20060101ALI20140528BHEP

Ipc: F25B 1/00 20060101AFI20140528BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20170315

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 912705

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170815

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602006053157

Country of ref document: DE

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2636912

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20171010

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20170726

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 912705

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170726

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171026

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171126

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171027

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602006053157

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20180430

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171213

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20171231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171213

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171231

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171231

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20061213

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170726

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170726

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230525

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20231102

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20231110

Year of fee payment: 18

Ref country code: FR

Payment date: 20231108

Year of fee payment: 18

Ref country code: DE

Payment date: 20231031

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20240110

Year of fee payment: 18