EP2320169A1 - Climatiseur et procédé pour déterminer la quantité d agent frigorigène dans celui-ci - Google Patents

Climatiseur et procédé pour déterminer la quantité d agent frigorigène dans celui-ci Download PDF

Info

Publication number
EP2320169A1
EP2320169A1 EP09769901A EP09769901A EP2320169A1 EP 2320169 A1 EP2320169 A1 EP 2320169A1 EP 09769901 A EP09769901 A EP 09769901A EP 09769901 A EP09769901 A EP 09769901A EP 2320169 A1 EP2320169 A1 EP 2320169A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
degree
supercooling
heat exchanger
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
EP09769901A
Other languages
German (de)
English (en)
Other versions
EP2320169B1 (fr
EP2320169A4 (fr
Inventor
Takahiro Yamaguchi
Takuro Yamada
Masahiro Yamada
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 EP2320169A1 publication Critical patent/EP2320169A1/fr
Publication of EP2320169A4 publication Critical patent/EP2320169A4/fr
Application granted granted Critical
Publication of EP2320169B1 publication Critical patent/EP2320169B1/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
    • F25B49/005—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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0312—Pressure 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
    • F25B2313/0313—Pressure 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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/19—Refrigerant outlet condenser temperature
    • 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
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor

Definitions

  • the present invention relates to the function of determining the adequacy of the quantity of refrigerant with which the inside of a refrigerant circuit of an air conditioning apparatus is charged and particularly relates to the function of determining the adequacy of the quantity of refrigerant with which the inside of a refrigerant circuit of an air conditioning apparatus where a heat source unit and a utilization unit are interconnected via refrigerant connection pipes is charged.
  • control is performed such that the degree of superheat and the evaporation pressure in the evaporator become constant in a cooling operation state, and the degree of supercooling in the condenser is measured. Then, in the refrigerant quantity determination operation, whether or not the refrigerant is leaking is determined on the basis of the difference between the degree of supercooling that has been measured at that time and the degree of supercooling that was measured the first time or before then.
  • An air conditioning apparatus pertaining to a first aspect of the invention comprises a refrigerant circuit, mode switching means, detecting means, degree of supercooling correcting means, and refrigerant quantity adequacy determining means.
  • the refrigerant circuit includes a heat source unit, a utilization unit, an expansion mechanism, and a liquid refrigerant connection pipe and a gas refrigerant connection pipe.
  • the heat source unit has a compressor, a heat source-side heat exchanger, and cooling heat source adjusting means. The operating capacity of the compressor can be adjusted.
  • the cooling heat source adjusting means can adjust the cooling action of a cooling heat source with respect to the heat source-side heat exchanger.
  • the utilization unit has a utilization-side heat exchanger.
  • the liquid refrigerant connection pipe and the gas refrigerant connection pipe interconnect the heat source unit and the utilization unit. Further, the refrigerant circuit is capable of performing at least cooling operation where the heat source-side heat exchanger is caused to function as a condenser of refrigerant compressed in the compressor and where the utilization-side heat exchanger is caused to function as an evaporator of the refrigerant condensed in the heat source-side heat exchanger.
  • the mode switching means switches an operating state of the refrigerant circuit from a normal operation mode, where control of each device of the heat source unit and the utilization unit is performed according to the operating load of the utilization unit, to a refrigerant quantity determination operation mode, where the cooling operation is performed and the utilization-side expansion mechanism is controlled such that the degree of superheat of the refrigerant in the outlet of the utilization-side heat exchanger becomes a positive value.
  • the detecting means detects, as a first detected value, the degree of supercooling of the refrigerant in the outlet of the heat source-side heat exchanger or an operating state quantity that fluctuates in response to fluctuations in the degree of supercooling in the refrigerant quantity determination operation mode.
  • the degree of supercooling correcting means corrects the degree of supercooling value or the operating state quantity by at least one of outside air temperature, condensation temperature, and a value obtained by numericizing the cooling action, to thereby derive a first degree of supercooling corrected value.
  • the refrigerant quantity adequacy determining means performs, as a refrigerant quantity adequacy determination, a determination of the adequacy of the quantity of the refrigerant with which the inside of the refrigerant circuit is charged on the basis of the first degree of supercooling corrected value in the refrigerant quantity determination operation mode.
  • the air conditioning apparatus of this aspect of the invention is a separate type air conditioning apparatus where the refrigerant circuit is configured as a result of the heat source unit and the utilization unit being interconnected via the refrigerant connection pipes and which is capable of performing at least cooling operation.
  • the reason "at least” is used here is because the air conditioning apparatus to which the present invention can be applied include air conditioning apparatus that can also perform another operation such as heating operation other than cooling operation.
  • this air conditioning apparatus is configured such that it can switch between and operate in normal operation such as cooling operation (hereinafter called "normal operation mode") and a refrigerant quantity determination operation mode where the utilization unit is forcibly caused to perform the cooling operation; this air conditioning apparatus detects the degree of supercooling of the refrigerant in the outlet of the heat source-side heat exchanger or the operating state quantity that fluctuates in response to fluctuations in the degree of supercooling and determines the adequacy of the quantity of the refrigerant with which the inside of the refrigerant circuit is charged on the basis of the first degree of supercooling corrected value derived by correcting the detected degree of supercooling or operating state quantity by at least one of outside air temperature, condensation temperature, and a value obtained by numericizing the cooling action.
  • normal operation mode cooling operation
  • refrigerant quantity determination operation mode where the utilization unit is forcibly caused to perform the cooling operation
  • the first degree of supercooling corrected value includes, for example, a relative degree of supercooling value obtained by dividing the degree of supercooling by a function of outside air temperature and condensation temperature, and this relative degree of supercooling value is corrected by the outside air temperature and the condensation temperature, so even in cases where the outside air temperature conditions differ (in cases where the adequacy of the quantity of the refrigerant is performed periodically, the potential for the outside air temperatures to differ between the first time and the second time, and there is the fear that the first detected value will fluctuate depending on changes in the outside air temperature) and even in cases where the condensation temperature conditions differ (in cases where the condensation temperatures differ because of influences resulting from disturbances such as dirt in the outdoor heat exchanger, the installation situation of the outdoor unit, and wind and rain), the relative degree of supercooling can be kept at a fairly constant value when the quantity of the refrigerant inside the refrigerant circuit virtually does not change.
  • this first degree of supercooling corrected value as an index for performing the refrigerant quantity adequacy determination, the determination of the adequacy of the quantity of the refrigerant inside the refrigerant circuit can be performed virtually without being affected by the aforementioned disturbances, and the adequacy of the quantity of the refrigerant inside the refrigerant circuit can be determined with virtually no errors.
  • An air conditioning apparatus pertaining to a second aspect of the invention is the air conditioning apparatus pertaining to the first aspect of the invention, wherein the degree of supercooling correcting means derives the first degree of supercooling corrected value by correcting the degree of supercooling or the operating state quantity that has been detected by a function or a map associated with at least one of outside air temperature, condensation temperature, and a value obtained by numericizing the cooling action.
  • An air conditioning apparatus pertaining to a third aspect of the invention is the air conditioning apparatus pertaining to the first aspect of the invention, wherein the degree of supercooling correcting means derives, as the first degree of supercooling corrected value, a value obtained by dividing the degree of supercooling or the operating state quantity by a function including as a variable at least one of outside air temperature, condensation temperature, and a value obtained by numericizing the cooling action.
  • An air conditioning apparatus pertaining to a fourth aspect of the invention is the air conditioning apparatus pertaining to any of the first to third aspects of the invention, wherein the refrigerant quantity adequacy determining means periodically performs the refrigerant quantity adequacy determination.
  • the adequacy of the quantity of the refrigerant with which the inside of the refrigerant circuit is charged can be precisely determined by periodically (e.g., once every year) performing the operation resulting from the refrigerant quantity determination operation mode, and if there is a change in the quantity of the refrigerant, it can be quickly discovered.
  • An air conditioning apparatus pertaining to a fifth aspect of the invention is the air conditioning apparatus pertaining to any of the first to fourth aspects of the invention, wherein the compressor is driven by a motor controlled by an inverter and is operated such that its speed resulting from the motor always becomes a predetermined speed in the refrigerant quantity determination operation mode.
  • the operating capacity of the compressor can be controlled with high precision.
  • An air conditioning apparatus pertaining to a sixth aspect of the invention is the air conditioning apparatus pertaining to any of the first to fifth aspects of the invention, wherein the heat source-side heat exchanger is an air-cooled heat exchanger whose cooling heat source is an air heat source.
  • the invention of this aspect is applied to an air conditioning apparatus of a system that cools the heat source-side heat exchanger by blowing air. Consequently, the first degree of supercooling corrected value is employed as a refrigerant quantity adequacy determination index also with respect to an air conditioning apparatus that employs as the heat source-side heat exchanger an air-cooled heat exchanger whose cooling heat source is an air heat source, so the adequacy of the quantity of the refrigerant can be precisely determined without being much affected by disturbances such as dirt in the heat source-side heat exchanger, the installation situation of the heat source unit, and wind and rain.
  • An air conditioning apparatus pertaining to a seventh aspect of the invention is the air conditioning apparatus pertaining to the sixth aspect of the invention, wherein the cooling heat source adjusting means is a blower fan that can vary the volume of air it blows towards the heat source-side heat exchanger.
  • the detecting means detects, as a second detected value, the degree of supercooling of the refrigerant in the outlet of the heat source-side heat exchanger or an operating state quantity that fluctuates in response to fluctuations in the degree of supercooling in a state where the air volume of the blower fan has been maximized in the refrigerant quantity determination operation mode.
  • the degree of supercooling correcting means corrects the second detected value by at least one of outside air temperature, condensation temperature, and a value obtained by numericizing the cooling action, to thereby derive a second degree of supercooling corrected value.
  • the refrigerant quantity adequacy determining means performs the refrigerant quantity adequacy determination on the basis of the second degree of supercooling corrected value.
  • the invention of this aspect is applied to an air conditioning apparatus that cools the heat source-side heat exchanger by blowing air with a blower fan that can vary the volume of air it blows.
  • the detecting means detects the degree of supercooling of the refrigerant in the outlet of the heat source-side heat exchanger or the operating state quantity that fluctuates in response to fluctuations in the degree of supercooling in a state where the air volume of the blower fan has been maximized in the refrigerant quantity determination operation mode, and the refrigerant quantity adequacy determining means determines the adequacy of the quantity of the refrigerant with which the inside of the refrigerant circuit is charged.
  • the adequacy of the quantity of the refrigerant can be precisely determined without being much affected by disturbances such as dirt in the heat source-side heat exchanger, the installation situation of the heat source unit, and wind and rain.
  • An air conditioning apparatus pertaining to an eighth aspect of the invention is the air conditioning apparatus pertaining to the sixth aspect of the invention, wherein the cooling heat source adjusting means is a water spraying device that sprays water towards the heat source-side heat exchanger.
  • the detecting means detects, as a third detected value, the degree of supercooling of the refrigerant in the outlet of the heat source-side heat exchanger or an operating state quantity that fluctuates in response to fluctuations in the degree of supercooling in a state where water has been sprayed from the water spraying device in the refrigerant quantity determination operation mode.
  • the degree of supercooling correcting means corrects the third detected value by at least one of condensation temperature and a value obtained by numericizing the cooling action, to thereby derive a third degree of supercooling corrected value.
  • the refrigerant quantity adequacy determining means performs the refrigerant quantity adequacy determination on the basis of the third degree of supercooling corrected value.
  • the invention of this aspect is applied to an air conditioning apparatus that performs heat exchange utilizing cooling action resulting from the sensible heat of water and cooling action resulting from the latent heat of water by causing the water spraying device to spray water towards the heat source-side heat exchanger employing an air-cooled heat exchanger with an air heat source.
  • the refrigerant quantity adequacy determination is performed by maximizing the effect of the cooling heat source by spraying water on the heat source-side heat exchanger employing an air-cooled heat exchanger with an air heat source, so the adequacy of the quantity of the refrigerant can be precisely determined without being much affected by disturbances such as dirt in the heat source-side heat exchanger, the installation situation of the heat source unit, and wind and rain.
  • An air conditioning apparatus pertaining to a ninth aspect of the invention is the air conditioning apparatus pertaining to the sixth aspect of the invention, wherein the cooling heat source adjusting means is a blower fan that can vary the volume of air it blows towards the heat source-side heat exchanger and a water spraying device that sprays water towards the heat source-side heat exchanger.
  • the detecting means detects, as a third detected value, the degree of supercooling of the refrigerant in the outlet of the heat source-side heat exchanger or an operating state quantity that fluctuates in response to fluctuations in the degree of supercooling in a state where the air volume of the blower fan has been maximized and where water has been sprayed from the water spraying device in the refrigerant quantity determination operation mode.
  • the degree of supercooling correcting means corrects the third detected value by at least one of condensation temperature and a value obtained by numericizing the cooling action, to thereby derive a third degree of supercooling corrected value.
  • the refrigerant quantity adequacy determining means performs the refrigerant quantity adequacy determination on the basis of the third degree of supercooling corrected value.
  • the invention of this aspect is applied to an air conditioning apparatus employing a heat source-side heat exchanger using, as the cooling heat source, a combination of cooling action resulting from the blowing of air utilizing the blower fan and cooling action resulting from the spraying of water utilizing the water spraying device.
  • the refrigerant quantity adequacy determination is performed by maximizing the effect of the cooling heat source by spraying water in addition to blowing air at maximum air volume on the heat source-side heat exchanger employing an air-cooled heat exchanger with an air heat source, so the adequacy of the quantity of the refrigerant can be precisely determined without being much affected by disturbances such as dirt in the heat source-side heat exchanger, the installation situation of the heat source unit, and wind and rain.
  • An air conditioning apparatus refrigerant quantity determination method pertaining to a tenth aspect of the invention is a refrigerant quantity determination method of determining, in an air conditioning apparatus having a refrigerant circuit that includes a heat source unit having a compressor whose operating capacity can be adjusted, a heat source-side heat exchanger, and cooling heat source adjusting means that can adjust the cooling action of a cooling heat source with respect to the heat source-side heat exchanger, a utilization unit having a utilization-side heat exchanger, an expansion mechanism, and a liquid refrigerant connection pipe and a gas refrigerant connection pipe that interconnect the heat source unit and the utilization unit, with the refrigerant circuit being capable of performing at least cooling operation where the heat source-side heat exchanger is caused to function as a condenser of refrigerant compressed in the compressor and where the utilization-side heat exchanger is caused to function as an evaporator of the refrigerant condensed in the heat source-side heat exchanger, the adequacy of the quantity of the ref
  • the refrigerant circuit is switched from a normal operation mode, where control of each device of the heat source unit and the utilization unit is performed according to the operating load of the utilization unit, to a refrigerant quantity determination operation mode, where the cooling operation is performed and the utilization-side expansion mechanism is controlled such that the degree of superheat of the refrigerant in the outlet of the utilization-side heat exchanger becomes a positive value.
  • the degree of supercooling of the refrigerant in the outlet of the heat source-side heat exchanger or an operating state quantity that fluctuates in response to fluctuations in the degree of supercooling in the refrigerant quantity determination operation mode is detected as a first detected value.
  • the first detected value is corrected by at least one of outside air temperature, condensation temperature, and a value obtained by numericizing the cooling action, to thereby derive a first degree of supercooling corrected value.
  • the refrigerant quantity adequacy determining step a determination of the adequacy of the quantity of the refrigerant with which the inside of the refrigerant circuit is charged on the basis of the first degree of supercooling corrected value in the refrigerant quantity determination operation mode is performed.
  • the air conditioning apparatus in which this aspect of the invention is employed, it is a method that is performed in a separate type air conditioning apparatus where the refrigerant circuit is configured as a result of the heat source unit and the utilization unit being interconnected via the refrigerant connection pipes and which is capable of performing at least cooling operation.
  • the reason "at least” is used here is because the air conditioning apparatus to which the present invention can be applied include air conditioning apparatus that can also perform another operation such as heating operation other than cooling operation.
  • this air conditioning apparatus is configured such that it can switch between and operate in normal operation such as cooling operation (hereinafter called a "normal operation mode") and a refrigerant quantity determination operation mode where the utilization unit is forcibly caused to perform the cooling operation; this air conditioning apparatus detects the degree of supercooling of the refrigerant in the outlet of the heat source-side heat exchanger or the operating state quantity that fluctuates in response to fluctuations in the degree of supercooling and determines the adequacy of the quantity of the refrigerant with which the inside of the refrigerant circuit is charged on the basis of the first degree of supercooling corrected value derived by correcting the detected degree of supercooling or operating state quantity by at least one of outside air temperature, condensation temperature, and a value obtained by numericizing the cooling action.
  • normal operation mode cooling operation
  • refrigerant quantity determination operation mode where the utilization unit is forcibly caused to perform the cooling operation
  • the first degree of supercooling corrected value includes, for example, a relative degree of supercooling value obtained by dividing the degree of supercooling by a function of outside air temperature and condensation temperature, and this relative degree of supercooling value is corrected by the outside air temperature and the condensation temperature, so even in cases where the outside air temperature conditions differ (in cases where the adequacy of the quantity of the refrigerant is performed periodically, the potential for the outside air temperatures to differ between the first time and the second time, and there is the fear that the first detected value will fluctuate depending on changes in the outside air temperature) and even in cases where the condensation temperature conditions differ (in cases where the condensation temperatures differ because of influences resulting from disturbances such as dirt in the outdoor heat exchanger, the installation situation of the outdoor unit, and wind and rain), the relative degree of supercooling can be kept at a fairly constant value when the quantity of the refrigerant inside the refrigerant circuit virtually does not change.
  • this first degree of supercooling corrected value as an index for performing the refrigerant quantity adequacy determination, the determination of the adequacy of the quantity of the refrigerant inside the refrigerant circuit can be performed virtually without being affected by the aforementioned disturbances, and the adequacy of the quantity of the refrigerant inside the refrigerant circuit can be determined with virtually no errors.
  • the determination of the adequacy of the quantity of the refrigerant inside the refrigerant circuit can be performed virtually without being affected by the aforementioned disturbances, and the adequacy of the quantity of the refrigerant inside the refrigerant circuit can be determined with virtually no errors.
  • the adequacy of the quantity of the refrigerant with which the inside of the refrigerant circuit is charged can be precisely determined by periodically (e.g., once every year) performing the operation resulting from the refrigerant quantity determination operation mode, and if there is a change in the quantity of the refrigerant, it can be quickly discovered.
  • the operating capacity of the compressor can be controlled with high precision.
  • the first degree of supercooling corrected value is employed as a refrigerant quantity adequacy determination index also with respect to an air conditioning apparatus that employs as the heat source-side heat exchanger an air-cooled heat exchanger whose cooling heat source is an air heat source, so the adequacy of the quantity of the refrigerant can be precisely determined without being much affected by disturbances such as dirt in the heat source-side heat exchanger, the installation situation of the heat source unit, and wind and rain.
  • the adequacy of the quantity of the refrigerant can be precisely determined without being much affected by disturbances such as dirt in the heat source-side heat exchanger, the installation situation of the heat source unit, and wind and rain.
  • the refrigerant quantity adequacy determination is performed by maximizing the effect of the cooling heat source by spraying water on the heat source-side heat exchanger employing an air-cooled heat exchanger with an air heat source, so the adequacy of the quantity of the refrigerant can be precisely determined without being much affected by disturbances such as dirt in the heat source-side heat exchanger, the installation situation of the heat source unit, and wind and rain.
  • the refrigerant quantity adequacy determination is performed by maximizing the effect of the cooling heat source by spraying water in addition to blowing air at maximum air volume on the heat source-side heat exchanger employing an air-cooled heat exchanger with an air heat source, so the adequacy of the quantity of the refrigerant can be precisely determined without being much affected by disturbances such as dirt in the heat source-side heat exchanger, the installation situation of the heat source unit, and wind and rain.
  • the determination of the adequacy of the quantity of the refrigerant inside the refrigerant circuit can be performed virtually without being affected by the aforementioned disturbances, and the adequacy of the quantity of the refrigerant inside the refrigerant circuit can be determined with virtually no errors.
  • FIG. 1 is a general refrigerant circuit diagram of an air conditioning apparatus 1 of one embodiment pertaining to the present invention.
  • the air conditioning apparatus 1 is an apparatus used to heat and cool the inside of a building or the like by performing vapor compression refrigeration cycle operation.
  • the air conditioning apparatus 1 is mainly equipped with one outdoor unit 2, an indoor unit 4, and a liquid refrigerant connection pipe 6 and a gas refrigerant connection pipe 7 that interconnect the outdoor unit 2 and the indoor unit 4. That is, a vapor compression refrigerant circuit 10 of the air conditioning apparatus 1 of the present embodiment is configured as a result of the outdoor unit 2, the indoor unit 4, and the liquid refrigerant connection pipe 6 and the gas refrigerant connection pipe 7 being connected.
  • the indoor unit 4 is installed by being embedded in or hung from a ceiling inside a room in a building or the like or by being mounted on a wall surface inside a room.
  • the indoor unit 4 is connected to the outdoor unit 2 via the liquid refrigerant connection pipe 6 and the gas refrigerant connection pipe 7 and configures part of the refrigerant circuit 10.
  • the indoor unit 4 mainly has an indoor-side refrigerant circuit 11 that configures part of the refrigerant circuit 10.
  • This indoor-side refrigerant circuit 11 mainly has an indoor heat exchanger 41 serving as a utilization-side heat exchanger.
  • the indoor heat exchanger 41 is a cross-fin type fin-and-tube heat exchanger configured by heat transfer tubes and numerous fins and is a heat exchanger that functions as an evaporator of the refrigerant during cooling operation to cool the room air and functions as a condenser of the refrigerant during heating operation to heat the room air.
  • the indoor heat exchanger 41 is a cross-fin type fin-and-tube heat exchanger, but the indoor heat exchanger 41 is not limited to this and may also be another type of heat exchanger.
  • the indoor unit 4 has an indoor fan 42 serving as a blower fan for sucking the room air into the inside of the unit, allowing heat to be exchanged with the refrigerant in the indoor heat exchanger 41, and thereafter supplying the air to the inside of the room as supply air.
  • the indoor fan 42 is a fan that can vary the volume of air it supplies to the indoor heat exchanger 41 and, in the present embodiment, is a centrifugal, fan or a multiblade fan driven by a motor 42m comprising a DC fan motor or the like.
  • an indoor temperature sensor 43 that detects the temperature of the room air (that is, the indoor temperature) flowing into the inside of the unit is disposed on a room air suction opening side of the indoor unit 4.
  • the indoor temperature sensor 43 comprises a thermistor.
  • the indoor unit 4 has an indoor-side controller 44 that controls the operation of each part configuring the indoor unit 4.
  • the indoor-side controller 44 has a microcomputer and a memory disposed in order to perform control of the indoor unit 4 and is configured such that it can exchange control signals and the like with a remote controller (not shown) for individually operating the indoor unit 4 and such that it can exchange control signals and the like with the outdoor unit 2 via a transmission line 8a.
  • the outdoor unit 2 is installed outdoors of a building or the like, is connected to the indoor unit 4 via the liquid refrigerant connection pipe 6 and the gas refrigerant connection pipe 7, and configures the refrigerant circuit 10 together with the indoor unit 4.
  • the outdoor unit 2 mainly has an outdoor-side refrigerant circuit 12 that configures part of the refrigerant circuit 10.
  • This outdoor-side refrigerant circuit 12 mainly has a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23 serving as a heat source-side heat exchanger, an outdoor expansion valve 33 serving as an expansion mechanism, an accumulator 24, a liquid-side stop valve 25, and a gas-side stop valve 26.
  • the compressor 21 is a compressor whose operating capacity can be varied and, in the present embodiment, is a positive displacement compressor driven by a motor 21m whose speed is controlled by an inverter.
  • the compressor 21 comprises only one compressor, but the compressor 21 is not limited to this, and two or more compressors may also be connected in parallel depending on the connection number of the indoor units and the like.
  • the four-way switching valve 22 is a valve for switching the direction of the flow of the refrigerant such that, during the cooling operation, the four-way switching valve 22 can interconnect the discharge side of the compressor 21 and the gas side of the outdoor heat exchanger 23 and also interconnect the suction side of the compressor 21 (specifically, the accumulator 24) and the gas refrigerant connection pipe 7 side to cause the outdoor heat exchanger 23 to function as a condenser of the refrigerant compressed by the compressor 21 and to cause the indoor heat exchanger 41 to function as an evaporator of the refrigerant condensed in the outdoor heat exchanger 23 (a cooling operation state: see the solid lines of the four-way switching valve 22 in FIG.
  • the four-way switching valve 22 can interconnect the discharge side of the compressor 21 and the gas refrigerant connection pipe 7 side and also interconnect the suction side of the compressor 21 and the gas side of the outdoor heat exchanger 23 to cause the indoor heat exchanger 41 to function as a condenser of the refrigerant compressed by the compressor 21 1 and to cause the outdoor heat exchanger 23 to function as an evaporator of the refrigerant condensed in the indoor heat exchanger 41 (a heating operation state: see the broken lines of the four-way switching valve 22 in FIG. 1 ).
  • the outdoor heat exchanger 23 is a cross-fin type fin-and-tube heat exchanger configured by heat transfer tubes and numerous fins and is a heat exchanger that functions as a condenser of the refrigerant during the cooling operation and functions as an evaporator of the refrigerant during the heating operation.
  • the gas side of the outdoor heat exchanger 23 is connected to the four-way switching valve 22, and the liquid side of the outdoor heat exchanger 23 is connected to the liquid refrigerant connection pipe 6.
  • the outdoor heat exchanger 23 is a cross-fin type fin-and-tube heat exchanger, but the outdoor heat exchanger 23 is not limited to this and may also be another type of heat exchanger.
  • the outdoor expansion valve 33 is a motor-driven expansion valve placed on the downstream side of the outdoor heat exchanger 23 in the flow direction of the refrigerant in the refrigerant circuit 10 when performing the cooling operation (in the present embodiment, the outdoor expansion valve 33 is connected to the liquid side of the outdoor heat exchanger 23) in order to adjust, for example, the pressure and the flow rate of the refrigerant flowing through the inside of the outdoor-side refrigerant circuit 12; the outdoor expansion valve 33 can also shut off passage of the refrigerant.
  • the outdoor unit 2 has an outdoor fan 27 serving as a blower fan for sucking outdoor air into the inside of the unit, allowing heat to be exchanged with the refrigerant in the outdoor heat exchanger 23, and thereafter expelling the air to the outdoors.
  • This outdoor fan 27 is a fan that can vary the volume of the air it supplies to the outdoor heat exchanger 23 and, in the present embodiment, is a propeller fan driven by a motor 27m comprising a DC fan motor or the like.
  • the accumulator 24 is connected between the four-way switching valve 22 and the compressor 21 and is a container that can accumulate surplus refrigerant generated inside the refrigerant circuit 10 depending on, for example, fluctuations in the operating load of the indoor unit 4.
  • the liquid-side stop valve 25 and the gas-side stop valve 26 are valves disposed in openings to which external devices and pipes (specifically, the liquid refrigerant connection pipe 6 and the gas refrigerant connection pipe 7) connect.
  • the liquid-side stop valve 25 is connected to the outdoor heat exchanger 23.
  • the gas-side stop valve 26 is connected to the four-way switching valve 22.
  • an evaporation pressure sensor 28 that detects the pressure of the gas refrigerant that has flowed in from the indoor heat exchanger 41
  • a condensation pressure sensor 29 that detects the condensation pressure of the refrigerant condensed by the outdoor heat exchanger 23
  • a suction temperature sensor 30 that detects the suction temperature of the compressor 21
  • a liquid-side temperature sensor 31 that detects the temperature of the refrigerant in a liquid state or in a gas-liquid two-phase state on the liquid side of the outdoor heat exchanger 23 are disposed in the outdoor unit 2.
  • An outdoor temperature sensor 32 that detects the temperature of the outdoor air (that is, the outdoor temperature) flowing into the inside of the unit is disposed on an outdoor air suction opening side of the outdoor unit 2.
  • the suction temperature sensor 30, the liquid-side temperature sensor 31, and the outdoor temperature sensor 32 comprise thermistors.
  • the outdoor unit 2 is equipped with an outdoor-side controller 34 that controls the operation of each part configuring the outdoor unit 2.
  • the outdoor-side controller 34 has a microcomputer and a memory disposed in order to perform control of the outdoor unit 2 and an inverter circuit that controls the motor 21m, and the outdoor-side controller 34 is configured such that it can exchange control signals and the like with the indoor-side controller 44 of the indoor unit 4. That is, a controller 8 that performs operation control of the entire air conditioning apparatus 1 is configured by the indoor-side controller 44, the outdoor-side controller 34, and the transmission line 8a that interconnects the controllers 34 and 44.
  • the refrigerant circuit 10 of the air conditioning apparatus 1 is configured as a result of the indoor-side refrigerant circuit 11, the outdoor-side refrigerant circuit 12, and the refrigerant connection pipes 6 and 7 being connected. Additionally, the air conditioning apparatus 1 of the present embodiment uses the four-way switching valve 22 to switch between the cooling operation and the heating operation and performs operation, and the air conditioning apparatus 1 performs control of each device of the outdoor unit 2 and the indoor unit 4 according to the operating load of the indoor unit 4.
  • operation modes of the air conditioning apparatus 1 of the present embodiment there are a normal operation mode, where control of each device of the outdoor unit 2 and the indoor unit 4 is performed according to the operating load of the indoor unit 4, and a refrigerant quantity determination operation mode, where the degree of supercooling of the refrigerant in the outlet of the outdoor heat exchanger 23 functioning as a condenser is detected while the indoor unit 4 is run in the cooling operation and the adequacy of the quantity of refrigerant with which the inside of the refrigerant circuit 10 is charged is judged.
  • the normal operation mode there are the cooling operation and the heating operation
  • refrigerant quantity determination operation mode there is refrigerant leak detection operation.
  • the four-way switching valve 22 is in the state indicated by the solid lines in FIG 1 , that is, a state where the discharge side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23 and where the suction side of the compressor 21 is connected to the gas side of the indoor heat exchanger 41.
  • the liquid-side stop valve 25 and the gas-side stop valve 26 are placed in an open state.
  • the opening degree of the outdoor expansion valve 33 is adjusted such that the degree of supercooling of the refrigerant in the outlet of the outdoor heat exchanger 23 becomes a predetermined value.
  • the degree of supercooling of the refrigerant in the outlet of the outdoor heat exchanger 23 is detected by converting the refrigerant pressure (the condensation pressure) value on the outlet side of the outdoor heat exchanger 23 detected by the condensation pressure sensor 29 into the saturation temperature value of the refrigerant and subtracting the refrigerant temperature value detected by the liquid-side temperature sensor 31 from this saturation temperature value of the refrigerant.
  • the outdoor expansion valve 33 controls the flow rate of the refrigerant flowing through the inside of the outdoor heat exchanger 23 such that the degree of supercooling in the outlet of the outdoor heat exchanger 23 becomes the predetermined value, so the high-pressure liquid refrigerant that has been condensed in the outdoor heat exchanger 23 reaches a state where it has the predetermined degree of supercooling.
  • the low-pressure refrigerant in the gas-liquid two-phase state that has been sent to the indoor unit 4 is sent to the indoor heat exchanger 41 and undergoes heat exchange with the inside air, is evaporated, and becomes low-pressure gas refrigerant in the indoor heat exchanger 41. Then, refrigerant with a flow rate corresponding to the required operating load in the air-conditioned space where the indoor unit 4 is installed flows in the indoor heat exchanger 41.
  • This low-pressure gas refrigerant is sent to the outdoor unit 2 via the gas refrigerant connection pipe 7 and flows into the accumulator 24 via the gas-side stop valve 26 and the four-way switching valve 22. Then, the low-pressure gas refrigerant that has flowed into the accumulator 24 is again sucked into the compressor 21.
  • surplus refrigerant accumulates in the accumulator 24 depending on the operating load of the indoor unit 4, such as, for example, when the operating load of the indoor unit 4 is small or when the indoor unit 4 is stopped.
  • the state of distribution of the refrigerant in the refrigerant circuit 10 when it is performing the cooling operation in the normal operation mode is such that, as shown in FIG. 2 , the refrigerant takes each of the states of a liquid state (the filled-in hatching portions in FIG. 2 ), a gas-liquid two-phase state (the grid-like hatching portions in FIG. 2 ), and a gas state (the diagonal line hatching portion in FIG 2 ).
  • the portion from near the outlet of the outdoor heat exchanger 23 to the outdoor expansion valve 33 is filled with the refrigerant in the liquid state.
  • FIG. 2 is a schematic diagram showing states of the refrigerant flowing through the inside of the refrigerant circuit 10 in the cooling operation.
  • the four-way switching valve 22 is in the state indicated by the broken lines in FIG. 1 , that is, a state where the discharge side of the compressor 21 is connected to the gas side of the indoor heat exchanger 41 and where the suction side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23.
  • the opening degree of the outdoor expansion valve 33 is adjusted in order to reduce the pressure of the refrigerant flowing into the outdoor heat exchanger 23 to a pressure that can allow the refrigerant to evaporate in the outdoor heat exchanger 23 (that is, the evaporation pressure).
  • the liquid-side stop valve 25 and the gas-side stop valve 26 are placed in an open state.
  • the high-pressure gas refrigerant that has been sent to the indoor unit 4 undergoes heat exchange with the inside air, is condensed, and becomes high-pressure liquid refrigerant in the indoor heat exchanger 41, and the high-pressure liquid refrigerant is thereafter sent to the outdoor unit 2 via the liquid refrigerant connection pipe 6.
  • refrigerant with a flow rate corresponding to the required operating load in the air-conditioned space where the indoor unit 4 is installed flows in the indoor heat exchanger 41.
  • This high-pressure liquid refrigerant has its pressure reduced by the outdoor expansion valve 33 via the liquid-side stop valve 25, becomes low-pressure refrigerant in a gas-liquid two-phase state, and flows into the outdoor heat exchanger 23. Then, the low-pressure refrigerant in the gas-liquid two-phase state that has flowed into the outdoor heat exchanger 23 undergoes heat exchange with the outside air supplied by the outdoor fan 27, is evaporated, becomes low-pressure gas refrigerant, and flows into the accumulator 24 via the four-way switching valve 22. Then, the low-pressure gas refrigerant that has flowed into the accumulator 24 is again sucked into the compressor 21.
  • the surplus refrigerant when a quantity of surplus refrigerant is generated inside the refrigerant circuit 10 depending on the operating load of the indoor unit 4, such as, for example, when the operating load of one of the indoor units 4 is small or when the indoor unit 4 is stopped, the surplus refrigerant accumulates in the accumulator 24 like during the cooling operation.
  • the refrigerant leak detection operation is performed, and within that, the way of operation differs between operation that is first performed after the air conditioning apparatus 1 has been installed (hereinafter called “initial setup operation”) and operation from the second time on (hereinafter called “determination operation”). For this reason, the refrigerant quantity determination operation mode will be divided between the initial setup operation and the determination operation and described below.
  • step S1 Running of Indoor Unit in Cooling Operation (Outdoor Fan Air Volume at Maximum)-
  • step S1 when a command to start the initial setup operation is issued, in the refrigerant circuit 10, the four-way switching valve 22 of the outdoor unit 2 is placed in the state indicated by the solid lines in FIG. 1 , the compressor 21 and the outdoor fan 27 are started, and the cooling operation is forcibly performed in regard to all of the indoor units 4 (see FIG. 2 ). At this time, the speed of the motor 27m becomes a maximum such that the air volume of the outdoor fan 27 becomes a maximum.
  • step S1 the air volume of the outdoor fan 27 is maximized in the cooling operation, so the heat transfer coefficient in the air side of the efficiency of heat exchange performed by the outdoor heat exchanger 23 can be maximized, and the influence of disturbances can be reduced.
  • the "disturbances" here are, for example, dirt in the outdoor heat exchanger 23, the installation situation of the outdoor unit 2, and wind and rain. Additionally, when the air volume of this outdoor fan 27 reaches a maximum, the initial setup operation moves to the next step S2.
  • step S2 reading of the indoor temperature detected by the indoor temperature sensor 43 and the outdoor temperature detected by the outdoor temperature sensor 32 is performed.
  • the initial setup operation moves to the next step S3.
  • step S3 whether or not the indoor temperature and the outdoor temperature that have been detected are within predetermined temperature ranges suitable for the refrigerant quantity determination operation mode that are set beforehand is determined. In step S3, when the indoor temperature and the outdoor temperature are within the predetermined temperature ranges, the initial setup operation moves to the next step S4, and when the indoor temperature and the outdoor temperature are not within the predetermined temperature ranges, the cooling operation of step S1 is continued.
  • Step S4 Determination of Whether or Not Relative Degree of Supercooling is Equal to or Greater than Predetermined Vale-
  • a relative degree of supercooling value is derived to determine whether or not the relative degree of supercooling value is equal to or greater than a predetermined value.
  • the "relative degree of supercooling value” here is a value obtained by dividing the degree of supercooling value in the outlet of the outdoor heat exchanger 23 by the difference between the condensation temperature value and the outdoor temperature. The “relative degree of supercooling value” will be described in detail later.
  • a value obtained by converting the pressure (the condensation pressure) value on the outlet side of the outdoor heat exchanger 23 detected by the condensation pressure sensor 29 into the saturation temperature of the refrigerant is used for the condensation temperature value.
  • step S4 when it is determined that the relative degree of supercooling value is less than the predetermined value, the initial setup operation moves to the next step S5, and when it is determined that the relative degree of supercooling value is equal to or greater than the predetermined value, the initial setup operation moves to step S6.
  • step S5 the relative degree of supercooling value is less than the predetermined value, so the rotational frequency of the compressor 21 and the degree of superheat in the outlet of the indoor heat exchanger 41 are controlled such that the relative degree of supercooling value becomes equal to or greater than the predetermined value.
  • the cooling operation in step S1 is performed in a state where the rotational frequency of the compressor 21 is 40 Hz and the degree of superheat in the outlet of the indoor heat exchanger 41 is 5°C, and whether or not the relative degree of supercooling value is equal to or greater than the predetermined value is determined.
  • the rotational frequency of the compressor 21 is raised from 40 Hz to 50 Hz, for example, the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 is lowered to 5°C, and whether or not the relative degree of supercooling value is equal to or greater than the predetermined value is similarly determined.
  • control is performed such that the relative degree of supercooling value becomes equal to or greater than the predetermined value by repeating raising the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 again by 5°C at a time as described above. Then, when the relative degree of supercooling value becomes equal to or greater than the predetermined value, the initial setup operation moves to step S6.
  • Control of the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 e.g., control to raise the degree of superheat from 5°C by 5°C at a time
  • narrowing the outdoor expansion valve 33 from an open state is performed.
  • control of the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 is not limited to this and may also be performed by controlling the air volume of the indoor fan 42 or by combining control of the valve opening degree of the outdoor expansion valve 33 and control of the air volume of the indoor fan 42.
  • the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 here is detected by subtracting, from the refrigerant temperature value detected by the suction temperature sensor 30, a value obtained by converting the evaporation pressure value detected by the evaporation pressure sensor 28 into the saturation temperature value of the refrigerant.
  • the degree of superheat is controlled so as to become a positive value by step S5; thus, as shown in FIG. 4 , the state becomes one where surplus refrigerant is not accumulating in the accumulator 24, and the refrigerant that had accumulated in the accumulator 24 moves to the outdoor heat exchanger 23.
  • step S6 the relative degree of supercooling value that is equal to or greater than the predetermined value in step S4 or step S6 is stored as an initial relative degree of supercooling value, and then the initial setup operation moves to the next step S7.
  • step S7 the rotational frequency of the compressor 21, the rotational frequency of the indoor fan 42, the outdoor temperature Ta, and the indoor temperature Tb in the operating state at the time of the degree of supercooling value stored in step S6 are stored, and then the initial setup operation is ended.
  • FIG. 5 is a flowchart at the time of the determination operation.
  • the relative degree of supercooling is written as "relative SC”.
  • a case where whether or not the refrigerant inside the refrigerant circuit is leaking to the outside due to some accidental cause is detected by switching to the determination operation, which is one operation in the refrigerant quantity determination operation mode, and performing operation periodically (e.g., once a month, when a load is not required in the air-conditioned space, etc.) at the time of the cooling operation or the heating operation in the normal operation mode will be taken as an example and described.
  • step S 11 Determination of Whether or Not Normal Operation Mode has Gone On a Certain Amount of Time-
  • the four-way switching valve 22 of the outdoor unit 2 is placed in the state indicated by the solid lines in FIG. 1 , the compressor 21 and the outdoor fan 27 are started, and the cooling operation is performed forcibly in regard to all of the indoor units 4 like in step S1 of the initial setup operation described above.
  • step S13 reading of the indoor temperature and the outdoor temperature is performed like in step S2 of the initial setup operation described above. When the indoor temperature and the outdoor temperature are detected, the detection operation moves to the next step S 14.
  • step S 14 whether or not the indoor temperature and the outdoor temperature that have been detected are within the predetermined temperature ranges suitable for the refrigerant quantity determination operation mode that are set beforehand is determined like in step S3 of the initial setup operation described above.
  • step S14 when the indoor temperature and the outdoor temperature are within the predetermined temperature ranges, the determination operation moves to the next step S15, and when the indoor temperature and the outdoor temperature are not within the predetermined temperature ranges, the cooling operation of step S12 is continued.
  • step S15 the compressor 21 and the indoor fan 42 are controlled at the rotational frequency of the compressor 21 and the rotational frequency of the indoor fan 42 that were stored in step S7 of the initial setup operation described above.
  • the state of the refrigerant inside the refrigerant circuit 10 can be regarded as a state that is the same as in the initial setup operation. That is, conditions that are identical to the conditions of the cooling operation that was performed in the initial setting operation become reproduced.
  • step S16 the relative degree of supercooling is derived like in step S4 of the initial setup operation described above. Then, whether or not the difference (hereinafter called the relative degree of supercooling difference) between the initial relative degree of supercooling and the relative degree of supercooling is equal to or greater than a second predetermined value is determined. In step S16, when it is determined that the relative degree of supercooling difference is less than the second predetermined value, the determination operation is ended, and when it is determined that the relative degree of supercooling difference is equal to or greater than the second predetermined value, the determination operation moves to step S 17.
  • the relative degree of supercooling difference the difference between the initial relative degree of supercooling and the relative degree of supercooling is equal to or greater than a second predetermined value
  • step S 17 it is determined that leakage of the refrigerant is occurring, a warning indication informing that a refrigerant leak has been detected is given, and thereafter the determination operation is ended.
  • FIG. 6 is a graph showing the condensation temperature Tc and the outdoor heat exchanger outlet temperature Tl when the outdoor temperature Ta with respect to outdoor fan air volume is constant. Looking at FIG. 6 , in a condition where the outdoor temperature Ta is constant, as the outdoor fan air volume increases, the condensation temperature Tc and the outdoor heat exchanger outlet temperature Tl decrease. Additionally, the drop of that decrease is larger in the condensation temperature Tc than in the outdoor heat exchanger outlet temperature T1. That is, it will be understood that when the outdoor fan air volume becomes larger, the degree of supercooling value that is the difference between the condensation temperature Tc and the outdoor heat exchanger outlet temperature T1 becomes smaller.
  • FIG. 7 is a graph showing a distribution of degree of supercooling values with respect to outdoor fan air volume
  • the degree of supercooling value becomes smaller.
  • variations in the degree of supercooling value become larger when the outdoor fan air volume is small than when the outdoor fan air volume is large. This is thought to be because it is easier when the outdoor fan air volume is small to be affected by disturbances such as dirt in the outdoor heat exchanger, the installation situation of the outdoor unit, and wind and rain and it is more difficult when the outdoor fan air volume is large to be affected by disturbances. For this reason, by maximizing the outdoor fan air volume, variations in the detected degree of supercooling value can be suppressed and detection errors can be reduced.
  • FIG. 8 is a graph showing a distribution of relative degree of supercooling values with respect to outdoor fan air volume.
  • the relative degree of supercooling value is, as described above, a value obtained by dividing the degree of supercooling value by the difference between the condensation temperature and the outdoor temperature. Looking at FIG. 8 , it will be understood that that value stays substantially between 0.3 and 0.4 regardless how large or small the outdoor fan air volume is and that it has few variations. For this reason, by utilizing this relative degree of supercooling value as an index when determining the adequacy of the quantity of the refrigerant, the adequacy of the quantity of the refrigerant can be determined without being affected as much as possible by disturbances and detection errors can be suppressed. Consequently, utilizing the relative degree of supercooling value to determine the adequacy of the quantity of the refrigerant is extremely useful.
  • the refrigerant circuit 10 is configured as a result of the outdoor unit 2 and the indoor unit 4 being interconnected via the refrigerant connection pipes 6 and 7. Additionally, this air conditioning apparatus 1 is configured such that it can switch between and operate in the normal operation such as the cooling operation (hereinafter called the normal operation mode) and the refrigerant quantity determination operation mode where the indoor unit 4 is forcibly caused to run in the cooling operation; the adequacy of the quantity of the refrigerant with which the inside of the refrigerant circuit 10 is charged can be determined by detecting the degree of supercooling of the refrigerant in the outlet of the outdoor heat exchanger 23.
  • the normal operation mode the cooling operation
  • the refrigerant quantity determination operation mode where the indoor unit 4 is forcibly caused to run in the cooling operation
  • the adequacy of the quantity of the refrigerant with which the inside of the refrigerant circuit 10 is charged can be determined by detecting the degree of supercooling of the refrigerant in the outlet of the outdoor heat exchanger 23.
  • the relative degree of supercooling value is employed as an index in the refrigerant quantity adequacy determination, and the relative degree of supercooling value is a value obtained by dividing the degree of supercooling value by the difference between the condensation temperature value and the outdoor temperature. Additionally, the relative degree of supercooling value stays substantially between 0.3 and 0.4 regardless of how large or small the outdoor fan air volume is, and it does not vary that much.
  • this relative degree of supercooling value as an index when determining the adequacy of the quantity of the refrigerant, the adequacy of the quantity of the refrigerant can be determined without being affected as much as possible by disturbances such as dirt in the outdoor heat exchanger, the installation situation of the outdoor unit, and wind and rain, and detection errors can be suppressed. Consequently, utilizing the relative degree of supercooling value to determine the adequacy of the quantity of the refrigerant is extremely useful.
  • the degree of supercooling of the refrigerant in the outlet of the outdoor heat exchanger 23 is detected by converting the refrigerant pressure (which corresponds to the condensation pressure) value on the outlet side of the outdoor heat exchanger 23 detected by the condensation pressure sensor 29 into the saturation temperature value of the refrigerant and subtracting the refrigerant temperature value detected by the liquid-side temperature sensor 31 from this saturation temperature value of the refrigerant, but the invention is not limited to this.
  • the invention may also be configured such that the degree of supercooling of the refrigerant in the outlet of the outdoor heat exchanger 23 is detected by disposing an outdoor heat exchange sensor that can detect the temperature of the refrigerant in the outdoor heat exchanger 23, detecting the condensation temperature value as the saturation temperature value of the refrigerant, and subtracting the refrigerant temperature value detected by the liquid-side temperature sensor 31 from this saturation temperature value of the refrigerant.
  • the outdoor heat exchanger 23 employs an air-cooled heat exchanger that uses an air heat source, and its heat transfer effect is promoted by the blower fan 27, but the outdoor heat exchanger 23 is not limited to this and may also be further equipped with a water spraying device so that water spraying is performed together with the blowing by the blower fan 27 or may not have the blower fan 27 so that its heat transfer effect is promoted by just the water spraying by the water spraying device.
  • the outdoor heat exchanger 23 employs an air-cooled heat exchanger that uses an air heat source, but the outdoor heat exchanger 23 is not limited to this and may also employ a water-cooled heat exchanger that uses a water heat source.
  • the cooling operation in the refrigerant quantity determination operation mode is performed in either one of a state where the supply flow rate of the cooling water that is the water heat source is a maximum or a state where the temperature of the cooling water that is the water heat source has been set to a minimum or a combination of these states.
  • the relative degree of supercooling value is defined as a value obtained by dividing the degree of supercooling value in the outlet of the outdoor heat exchanger 23 by the difference between the condensation temperature value and the outdoor temperature, but the relative degree of supercooling value is not limited to this and may also be a value that has been corrected by an expression resulting from the degree of supercooling and at least one of the outdoor temperature, the condensation temperature, and the outdoor fan air volume.
  • the relative degree of supercooling may be not only a correction resulting from these expressions but also a correction resulting from a map held beforehand.
  • a value to which a value obtained by numericizing the cooling action resulting from the water spraying has been added becomes replaced with the outdoor fan air volume.
  • a value obtained by numericizing the cooling action resulting from the cooling water (at least one of the cooling water flow rate and the cooling water temperature) becomes replaced with the outdoor fan air volume.
  • the invention may also be configured such that a switch or the like for switching the refrigerant circuit to the refrigerant quantity determination operation mode is disposed in the air conditioning apparatus 1 and such that a serviceman or an installation manager operates the switch or the like on site to thereby periodically perform the refrigerant leak detection operation.
  • the present invention is applied to an air conditioning apparatus that can switch between heating and cooling, but the invention is not limited to this and is applicable as long as the air conditioning apparatus is a separate type air conditioning apparatus; the present invention may also be applied to pair type air conditioning apparatus and air conditioning apparatus dedicated to cooling.
  • Patent Literature 1 JP-ANo. 2006-23072

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
EP09769901.1A 2008-06-27 2009-06-24 Climatiseur et procédé pour déterminer la quantité d agent frigorigène dans celui-ci Active EP2320169B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008169595A JP2010007994A (ja) 2008-06-27 2008-06-27 空気調和装置および空気調和装置の冷媒量判定方法
PCT/JP2009/002888 WO2009157191A1 (fr) 2008-06-27 2009-06-24 Climatiseur et procédé pour déterminer la quantité d’agent frigorigène dans celui-ci

Publications (3)

Publication Number Publication Date
EP2320169A1 true EP2320169A1 (fr) 2011-05-11
EP2320169A4 EP2320169A4 (fr) 2014-11-26
EP2320169B1 EP2320169B1 (fr) 2020-10-21

Family

ID=41444264

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09769901.1A Active EP2320169B1 (fr) 2008-06-27 2009-06-24 Climatiseur et procédé pour déterminer la quantité d agent frigorigène dans celui-ci

Country Status (7)

Country Link
US (1) US20110107780A1 (fr)
EP (1) EP2320169B1 (fr)
JP (1) JP2010007994A (fr)
CN (1) CN102077041B (fr)
AU (1) AU2009263631B8 (fr)
ES (1) ES2833226T3 (fr)
WO (1) WO2009157191A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108800634A (zh) * 2018-06-29 2018-11-13 重庆美的通用制冷设备有限公司 双级离心冷水机组及其一级节流的控制方法、装置

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010007995A (ja) * 2008-06-27 2010-01-14 Daikin Ind Ltd 空気調和装置の冷媒量判定方法および空気調和装置
CN102725599B (zh) 2010-01-29 2014-11-26 大金工业株式会社 热泵系统
JP5693328B2 (ja) * 2011-03-31 2015-04-01 中野冷機株式会社 冷凍装置及び冷凍装置の冷媒漏れ検知方法
CN103712309A (zh) * 2012-10-04 2014-04-09 Tcl空调器(中山)有限公司 一种空调器冷媒流量控制方法
JP5812081B2 (ja) * 2013-11-12 2015-11-11 ダイキン工業株式会社 室内機
WO2015125509A1 (fr) * 2014-02-18 2015-08-27 東芝キヤリア株式会社 Dispositif à cycle de réfrigération
US10119738B2 (en) 2014-09-26 2018-11-06 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
JP6289727B2 (ja) * 2015-02-27 2018-03-07 三菱電機株式会社 冷凍装置
JP2017053566A (ja) * 2015-09-10 2017-03-16 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 冷凍サイクル装置
CN105928135A (zh) * 2016-04-19 2016-09-07 青岛海尔空调器有限总公司 一种判断冷媒量的方法、装置及制冷设备
WO2018080150A1 (fr) * 2016-10-25 2018-05-03 Samsung Electronics Co., Ltd. Climatiseur
US10571171B2 (en) * 2017-01-27 2020-02-25 Emerson Climate Technologies, Inc. Low charge detection system for cooling systems
CN109147977B (zh) * 2017-06-16 2020-04-21 苏州热工研究院有限公司 一种核电厂制冷机保护系统以及方法
US11592215B2 (en) 2018-08-29 2023-02-28 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
JP6732862B2 (ja) * 2018-12-06 2020-07-29 三菱電機株式会社 冷凍装置
CN114364925B (zh) * 2019-09-09 2023-10-20 大金工业株式会社 制冷剂泄漏判定系统
WO2021095238A1 (fr) * 2019-11-15 2021-05-20 三菱電機株式会社 Dispositif de climatisation
CN112728816B (zh) * 2020-12-14 2022-04-29 镇江市威胜电气有限公司 一种风门冷凝器及其生产工艺
CN114370689B (zh) * 2022-01-27 2023-06-02 宁波奥克斯电气股份有限公司 制冷剂充注量判定方法、控制方法、空调器以及存储介质

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6220041B1 (en) * 1998-07-22 2001-04-24 Mitsubishi Denki Kabushiki Kaisha Method for determining a charging amount of refrigerant for an air conditioner, a method for controlling refrigerant for an air conditioner and an air conditioner
EP1775532A1 (fr) * 2004-06-11 2007-04-18 Daikin Industries, Ltd. Climatiseur
EP1876403A1 (fr) * 2005-04-07 2008-01-09 Daikin Industries, Ltd. Systeme de jugement de la quantite de refrigerant d un systeme d air conditionne
WO2008035418A1 (fr) * 2006-09-21 2008-03-27 Mitsubishi Electric Corporation SystÈme de rÉFRIGÉration/de climatisation de l'air ayant une fonction de dÉtection de fuite de rÉFRIGÉrant, rÉFRIGÉrateur/climatiseur d'air et procÉDÉ de dÉtection d'une fuite de rÉFRIGÉrant

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030159458A1 (en) * 2002-02-25 2003-08-28 Wei Fang Dual phase condenser system
JP3719246B2 (ja) * 2003-01-10 2005-11-24 ダイキン工業株式会社 冷凍装置及び冷凍装置の冷媒量検出方法
JP2005041252A (ja) * 2003-07-22 2005-02-17 Mitsubishi Heavy Ind Ltd 車両用空調装置
JP3852472B2 (ja) 2004-06-11 2006-11-29 ダイキン工業株式会社 空気調和装置
CN100580347C (zh) * 2005-04-07 2010-01-13 大金工业株式会社 空调装置的制冷剂量判定系统
US7386985B2 (en) * 2005-12-05 2008-06-17 Carrier Corporation Detection of refrigerant charge adequacy based on multiple temperature measurements

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6220041B1 (en) * 1998-07-22 2001-04-24 Mitsubishi Denki Kabushiki Kaisha Method for determining a charging amount of refrigerant for an air conditioner, a method for controlling refrigerant for an air conditioner and an air conditioner
EP1775532A1 (fr) * 2004-06-11 2007-04-18 Daikin Industries, Ltd. Climatiseur
EP1876403A1 (fr) * 2005-04-07 2008-01-09 Daikin Industries, Ltd. Systeme de jugement de la quantite de refrigerant d un systeme d air conditionne
WO2008035418A1 (fr) * 2006-09-21 2008-03-27 Mitsubishi Electric Corporation SystÈme de rÉFRIGÉration/de climatisation de l'air ayant une fonction de dÉtection de fuite de rÉFRIGÉrant, rÉFRIGÉrateur/climatiseur d'air et procÉDÉ de dÉtection d'une fuite de rÉFRIGÉrant

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2009157191A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108800634A (zh) * 2018-06-29 2018-11-13 重庆美的通用制冷设备有限公司 双级离心冷水机组及其一级节流的控制方法、装置
CN108800634B (zh) * 2018-06-29 2020-11-24 重庆美的通用制冷设备有限公司 双级离心冷水机组及其一级节流的控制方法、装置

Also Published As

Publication number Publication date
AU2009263631A8 (en) 2013-02-28
EP2320169B1 (fr) 2020-10-21
JP2010007994A (ja) 2010-01-14
US20110107780A1 (en) 2011-05-12
CN102077041A (zh) 2011-05-25
AU2009263631B8 (en) 2013-02-28
WO2009157191A1 (fr) 2009-12-30
AU2009263631B2 (en) 2013-02-07
CN102077041B (zh) 2013-06-26
ES2833226T3 (es) 2021-06-14
EP2320169A4 (fr) 2014-11-26
AU2009263631A1 (en) 2009-12-30

Similar Documents

Publication Publication Date Title
EP2320169A1 (fr) Climatiseur et procédé pour déterminer la quantité d agent frigorigène dans celui-ci
AU2009263640B2 (en) Air conditioning apparatus refrigerant quantity determination method and air conditioning apparatus
US8919139B2 (en) Air conditioning apparatus
EP1775532B1 (fr) Climatiseur
KR101161240B1 (ko) 공기 조화 장치
US20090095000A1 (en) Air conditioner
JP4462096B2 (ja) 空気調和装置
CN112840164B (zh) 空调装置和管理装置
JP5505477B2 (ja) 空気調和装置および空気調和装置の冷媒量判定方法
JP2011099591A (ja) 冷凍装置
JP2017075760A (ja) 空気調和機
JP2010007996A (ja) 空気調和装置の試運転方法および空気調和装置
AU2013200092B2 (en) Air conditioning apparatus and air conditioning apparatus refrigerant quantity determination method
JP5245575B2 (ja) 空気調和装置の冷媒量判定方法および空気調和装置
JP5245576B2 (ja) 空気調和装置の冷媒量判定方法および空気調和装置
JP6057512B2 (ja) クランクケースヒータを備えた空気調和機
JP2010133635A (ja) 冷凍装置
JP2010096397A (ja) 空気調和装置の冷媒量判定方法
JP2010096398A (ja) 空気調和装置および空気調和装置の冷媒量判定方法

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: 20110125

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 HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA RS

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

Effective date: 20141029

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 49/00 20060101ALI20141023BHEP

Ipc: F25B 39/04 20060101ALI20141023BHEP

Ipc: F25B 1/00 20060101ALI20141023BHEP

Ipc: F25B 49/02 20060101AFI20141023BHEP

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

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20180605

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20191212

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

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

Free format text: STATUS: EXAMINATION IS IN PROGRESS

INTC Intention to grant announced (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20200512

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

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 HR HU IE IS IT LI LT LU LV MC MK MT NL NO 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: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602009062943

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1326235

Country of ref document: AT

Kind code of ref document: T

Effective date: 20201115

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1326235

Country of ref document: AT

Kind code of ref document: T

Effective date: 20201021

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20201021

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

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: 20210122

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: 20210222

Ref country code: NO

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: 20210121

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: 20201021

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: 20201021

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

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: 20201021

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: 20201021

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: 20201021

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: 20210121

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: 20201021

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: 20210221

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2833226

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20210614

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

Ref country code: HR

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: 20201021

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602009062943

Country of ref document: DE

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

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: 20201021

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: 20201021

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: 20201021

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: 20201021

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: 20201021

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

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

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: 20201021

26N No opposition filed

Effective date: 20210722

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: 20201021

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: 20201021

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20210630

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: 20210624

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

Ref country code: LI

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

Effective date: 20210630

Ref country code: IE

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

Effective date: 20210624

Ref country code: CH

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

Effective date: 20210630

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

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: 20210221

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

Ref country code: BE

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

Effective date: 20210630

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

Ref country code: IT

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

Effective date: 20210624

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: 20090624

Ref country code: CY

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: 20201021

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: FR

Payment date: 20230510

Year of fee payment: 15

Ref country code: DE

Payment date: 20230502

Year of fee payment: 15

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

Ref country code: GB

Payment date: 20230504

Year of fee payment: 15

Ref country code: ES

Payment date: 20230706

Year of fee payment: 15

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

Ref country code: MK

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: 20201021