US20120060530A1 - Air conditioner - Google Patents

Air conditioner Download PDF

Info

Publication number
US20120060530A1
US20120060530A1 US13/321,874 US201013321874A US2012060530A1 US 20120060530 A1 US20120060530 A1 US 20120060530A1 US 201013321874 A US201013321874 A US 201013321874A US 2012060530 A1 US2012060530 A1 US 2012060530A1
Authority
US
United States
Prior art keywords
compressor
heat exchanger
control unit
temperature
operating frequency
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.)
Abandoned
Application number
US13/321,874
Other languages
English (en)
Inventor
Junichi Shimoda
Hidehiko Kinoshita
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
Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KINOSHITA, HIDEHIKO, SHIMODA, JUNICHI
Publication of US20120060530A1 publication Critical patent/US20120060530A1/en
Abandoned legal-status Critical Current

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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/77—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by controlling the speed of ventilators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/85—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using variable-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/029—Control issues
    • F25B2313/0294—Control issues related to the outdoor fan, e.g. controlling speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to an air conditioner.
  • the air conditioners are normally configured to execute a control of inhibiting degradation in heating performance due to frost attachment onto the outdoor heat exchangers thereof immediately before the start of a defrosting operation.
  • Patent Literature 1 Japanese Laid-open Patent Application Publication No. JP-A-S62-069070 describes a control of preventing reduction in the rotation speed of an outdoor fan due to increase in ventilation resistance.
  • a control unit is herein configured to increase voltage to be inputted into a fan motor for keeping the rotation speed of the outdoor fan constant, and thereby inhibits reduction in the evaporation temperature of a refrigerant. The control inhibits increase in the amount of frost attaching onto the outdoor heat exchanger and prevents degradation in heating performance.
  • An air conditioner is of a type using a vapor compression refrigeration cycle for circulating a refrigerant sequentially through a compressor, an indoor heat exchanger, a decompressor and an outdoor heat exchanger during execution of a heating operation.
  • the air conditioner includes an outdoor fan and a control unit.
  • the outdoor fan is configured to blow the outdoor heat exchanger.
  • the control unit includes a determining part configured to determine whether or not the amount of frost attaching onto the outdoor heat exchanger is increased during execution of the heating operation.
  • the control unit is configured to control an operating frequency of the compressor and a rotation speed of the outdoor fan. Further, the control unit is configured to: reduce the rotation speed of the outdoor fan when the determining part determines that the amount of frost attaching onto the outdoor heat exchanger is increased; and execute a frost attaching condition operation control for increasing the operating frequency of the compressor either simultaneously with reducing the rotation speed of the outdoor fan or when a predetermined performance degradation is subsequently caused after reducing the rotation speed of the outdoor fan.
  • noise of the outdoor fan is reduced in response to reduction in the rotation speed of the outdoor fan even when noise is easily produced due to frost attachment onto the outdoor heat exchanger during execution of the heating operation. Therefore, increase in noise of the entire air conditioner is inhibited. Further, degradation in heating performance is inhibited by increasing the operating frequency of the compressor. It should be noted that noise of the compressor is increased in accordance with increase in the operating frequency of the compressor. However, noise of the outdoor fan is herein reduced. Consequently, noise increase is inhibited for the entire air conditioner.
  • An air conditioner according to a second aspect of the present invention relates to the air conditioner according to the first aspect of the present invention.
  • the control unit is configured to reduce the rotation speed of the outdoor fan in accordance with an increase amount of the operating frequency of the compressor during execution of the frost attaching condition operation control.
  • noise is increased in accordance with the increase amount of the operating frequency of the compressor.
  • the rotation speed of the outdoor fan is reduced to the extent that the increase amount of the noise is cancelled out. Therefore, noise is kept roughly constant in the entire air conditioner.
  • An air conditioner relates to the air conditioner according to one of the first and second aspects of the present invention.
  • the air conditioner further includes a first temperature sensor and a second temperature sensor.
  • the first temperature sensor is configured to detect an outdoor temperature
  • the second temperature sensor is configured to detect a temperature of the outdoor heat exchanger.
  • the control unit is configured to: monitor a difference between a value detected by the first temperature sensor and a value detected by the second temperature sensor; and determine that the amount of frost attaching onto the outdoor heat exchanger is increased when the difference is increased.
  • the air conditioner of the third aspect of the present invention it is estimated that the evaporation temperature of the refrigerant is reduced due to frost attachment when the difference between the outdoor temperature and the temperature of the outdoor heat exchanger is increased. This is because the difference between the outdoor temperature and the evaporation temperature of the refrigerant is roughly constant in a frost-free condition of the outdoor heat exchanger during execution of the heating operation. Therefore, it is easily determined whether or not the amount of frost attaching onto the outdoor heat exchanger is increased through the monitoring of the difference between the outdoor temperature and the temperature of the outdoor heat exchanger.
  • An air conditioner according to a fourth aspect of the present invention relates to the air conditioner according to the third aspect of the present invention.
  • the air conditioner further includes a third temperature sensor.
  • the third temperature sensor is configured to detect a temperature of the indoor heat exchanger.
  • the control unit is configured to: monitor the temperature of the indoor heat exchanger through the third temperature sensor; and increase the operating frequency of the compressor in accordance with a reduction amount of the temperature of the indoor heat exchanger during execution of the frost attaching condition operation control.
  • degradation in heating performance is expressed as reduction in the condensation temperature during execution of the heating operation. Therefore, degradation in heating performance is inhibited by increasing the operating frequency of the compressor in accordance with the reduction amount of the temperature of the indoor heat exchanger.
  • An air conditioner according to a fifth aspect of the present invention relates to the air conditioner according to the fourth aspect of the present invention.
  • the control unit includes change amounts preliminarily set for changing the operating frequency of the compressor in stages.
  • the change amounts correspond to the stages on a one-to-one basis.
  • the operating frequency of the compressor is herein configured to be increased by corresponding one of the change amounts required for upgrading a present stage of the operating frequency of the compressor to a stage immediately higher than the present stage every time the temperature of the indoor heat exchanger is reduced by a predetermined amount.
  • multiple stages are set for the operating frequency of the compressor in order to increase or reduce the operating frequency of the compressor in stages in accordance with a load during execution of the normal operation. Further, the stages are designed to be applied to the operating frequency during execution of the frost attaching condition operation control. Therefore, the control design can be easily created.
  • An air conditioner according to a sixth aspect of the present invention relates to the air conditioner according to the third aspect of the present invention.
  • the air conditioner further includes a pressure sensor.
  • the pressure sensor is disposed on a discharge side of the compressor.
  • the pressure sensor is configured to detect a higher side pressure.
  • the control unit is configured to: monitor the higher side pressure through the pressure sensor; and increase the operating frequency of the compressor in accordance with a reduction amount of the higher side pressure during execution of the frost attaching condition operation control.
  • degradation in heating performance is expressed as reduction in the higher side pressure during execution of the heating operation. Therefore, degradation in heating performance is inhibited by increasing the operating frequency of the compressor in accordance with the reduction amount of the higher side pressure.
  • An air conditioner according to a seventh aspect of the present invention relates to the air conditioner according to the sixth aspect of the present invention.
  • the control unit includes change amount preliminarily set for changing the operating frequency of the compressor in stages.
  • the change amounts correspond to the stages of the operating frequency of the compressor on a one-to-one basis.
  • the operating frequency of the compressor is configured to be increased by corresponding one of the change amounts required for upgrading a present stage of the operating frequency of the compressor to a stage immediately higher than the present stage every time the higher side pressure is reduced by a predetermined amount.
  • multiple stages are set for the operating frequency of the compressor in order to increase or reduce the operating frequency of the compressor in stages in accordance with load during execution of the normal operation. Further, the stages are designed to be applied to the operating frequency of the compressor during execution of the frost attaching condition operation control. Therefore, the control design can be easily created.
  • An air conditioner according to an eighth aspect of the present invention relates to the air conditioner according to one of the first to seventh aspects of the present invention.
  • the control unit is configured to: count an elapsed time after activation of the compressor; and execute a defrosting operation control for resolving frost attachment onto the outdoor heat exchanger when the elapsed time reaches a predetermined period of time during execution of the frost attaching condition operation condition while an evaporation temperature of the refrigerant reaches a predetermined temperature.
  • the frost attaching condition operation control is executed until immediately before the start of the defrosting operation. This makes a user or users less likely to feel that heating is insufficient.
  • noise of the outdoor fan is reduced even when noise is easily produced due to frost attachment onto the outdoor heat exchanger during execution of the heating operation. Therefore, noise increase is inhibited for the entire air conditioner. Further, degradation in heating performance due to frost attachment is inhibited by increasing the operating frequency of the compressor.
  • noise is increased in accordance with the increase amount of the operating frequency of the compressor.
  • the rotation speed of the outdoor fan is reduced to the extent that the increase amount of the noise is cancelled out. Therefore, noise is kept roughly constant in the entire air conditioner.
  • the air conditioner of the third aspect of the present invention it is easily determined whether or not the amount of frost attaching onto the outdoor heat exchanger is increased through the monitoring of the difference between the outdoor temperature and the temperature of the outdoor heat exchanger.
  • degradation in heating performance is expressed as reduction in the condensation temperature during execution of the heating operation. Therefore, degradation in heating performance is inhibited by increasing the operating frequency of the compressor in accordance with the reduction amount of the temperature of the indoor heat exchanger.
  • multiple stages are set for the operating frequency of the compressor in order to increase or reduce the operating frequency of the compressor in stages in accordance with load during execution of the normal operation. Further, the stages are designed to be applied to the operating frequency during execution of the frost attaching condition operation control. Therefore, the control design can be easily created.
  • degradation in heating performance is expressed as reduction in the higher side pressure during execution of the heating operation. Therefore, degradation in heating performance is inhibited by increasing the operating frequency of the compressor in accordance with the reduction amount of the higher side pressure.
  • multiple stages are set for the operating frequency of the compressor in order to increase or reduce the operating frequency of the compressor in stages in accordance with load during execution of the normal operation. Further, the stages are designed to be applied to the operating frequency of the compressor during execution of the frost attaching condition operation control. Therefore, the control design can be easily created.
  • the frost attaching condition operation control is executed until immediately before the start of the defrosting operation. This makes a user or users less likely to feel that heating is insufficient.
  • FIG. 1 is a configuration diagram of an air conditioner according to a first exemplary embodiment of the present invention.
  • FIG. 2 includes charts representing relations among outdoor fan input, outdoor fan rotation speed and outdoor fan blowing sound in executing a normal control under a frost attaching condition.
  • FIG. 3 is an operational flowchart from start of a heating operation control to start of a defrosting operation control.
  • FIG. 4 is a chart representing relations among elapsed time after start of a heating operation, indoor heat exchanger temperature and compressor operating frequency.
  • FIG. 5 is an operational flowchart from start of a heating operation control to start of a defrosting operation control in an air conditioner according to a first modification of the present invention.
  • FIG. 6 is an operational flowchart from start of a heating operation control to start of a defrosting operation control in an air conditioner according to a second modification of the present invention.
  • FIG. 7 is a chart representing relations among elapsed time after start of a heating operation, indoor heat exchanger temperature and compressor operating frequency in an air conditioner according to a second exemplary embodiment.
  • FIG. 8 is a chart representing relations among elapsed time after start of a heating operation, higher side pressure and compressor operating frequency in an air conditioner according to a modification of the second exemplary embodiment.
  • FIG. 1 is a configuration diagram of an air conditioner according to a first exemplary embodiment of the present invention.
  • the air conditioner 1 includes an outdoor unit 2 and an indoor unit 3 . It should be noted that a plurality of the indoor units 3 may be herein provided.
  • the air conditioner 1 includes a refrigerant circuit 10 filled with a refrigerant.
  • the refrigerant circuit 10 includes an outdoor circuit accommodated in the outdoor unit 2 and an indoor circuit accommodated in the indoor unit 3 .
  • the outdoor circuit and the indoor circuit are connected through a gas-side communicating pipe 17 a and a liquid-side communicating pipe 17 b.
  • a compressor 11 , a four-way switching valve 12 , an outdoor heat exchanger 13 and an expansion valve 14 are connected to the outdoor circuit in the outdoor unit 2 .
  • a liquid-side closing valve 19 is disposed in one end of the outdoor circuit, and the liquid-side communicating pipe 17 b is connected thereto.
  • a gas-side closing valve 18 is disposed on the other end of the outdoor circuit, and the gas-side communicating pipe 17 a is connected thereto.
  • the discharge side of the compressor 11 is connected to a first port P 1 of the four-way switching valve 12 .
  • the suction side of the compressor 11 is connected to a third port P 3 of the four-way switching valve 12 via an accumulator 20 .
  • the accumulator 20 is configured to separate the liquid refrigerant and the gas refrigerant.
  • the outdoor heat exchanger 13 is a cross-fin type fin-and-tube heat exchanger.
  • An outdoor fan 23 is disposed in the vicinity of the outdoor heat exchanger 13 in order to supply outdoor air to the outdoor heat exchanger 13 .
  • One end of the outdoor heat exchanger 13 is connected to a fourth port P 4 of the four-way switching valve 12 .
  • the other end of the outdoor heat exchanger 13 is connected to the expansion valve 14 functioning as a decompression unit.
  • the expansion valve 14 is an electronic expansion valve of an opening degree variable type and is connected to the liquid-side closing valve 19 . Further, a second port P 2 of the four-way switching valve 12 is connected to the gas-side closing valve 18 .
  • the four-way switching valve 12 is configured to switch between a first state (a state depicted with a solid line in FIG. 1 ) and a second state (a state depicted with a dotted line in FIG. 1 ).
  • a first state a state depicted with a solid line in FIG. 1
  • a second state a state depicted with a dotted line in FIG. 1 .
  • the first port P 1 and the fourth port P 4 are communicated while the second port P 2 and the third port P 3 are communicated.
  • the second state the first port P 1 and the second port P 2 are communicated while the third port P 3 and the fourth port P 4 are communicated.
  • the indoor circuit is provided with an indoor heat exchanger 15 .
  • the indoor heat exchanger 15 is a cross-fin type fin-and-tube heat exchanger.
  • An indoor fan 33 is disposed in the vicinity of the indoor heat exchanger 15 in order to supply indoor air to the indoor heat exchanger 15 .
  • the air conditioner 1 includes an outdoor temperature sensor 101 formed by a thermistor, an outdoor heat exchanger temperature sensor 102 and an indoor heat exchanger temperature sensor 103 .
  • the outdoor temperature sensor 101 is configured to detect the temperature of the surrounding of the outdoor unit 2 .
  • the outdoor heat exchanger temperature sensor 102 is attached to the outdoor heat exchanger 13 and is configured to detect the temperature of the refrigerant flowing through a predetermined region of the outdoor heat exchanger 13 .
  • a control unit 4 is configured to control the operation of the air conditioner 1 based on the values measured by the aforementioned temperature sensors.
  • the operation of the air conditioner 1 can be switched into either the cooling operation or the heating operation through the four-way switching valve 12 .
  • the four-way switching valve 12 is set to be in the first state (depicted with the solid line in FIG. 1 ).
  • a vapor compression refrigeration cycle is executed in the refrigerant circuit 10 .
  • the outdoor heat exchanger 13 is configured to function as a condenser whereas the indoor heat exchanger 15 is configured to function as an evaporator.
  • High-pressure refrigerant discharged from the compressor 11 exchanges heat with the outdoor air in the outdoor heat exchanger 13 and is thereby condensed. After passing through the outdoor heat exchanger 13 , the refrigerant is decompressed in passing through the expansion valve 14 . Subsequently, the decompressed refrigerant exchanges heat with the indoor air in the indoor heat exchanger 15 and is thereby evaporated. After passing through the indoor heat exchanger 15 , the refrigerant is inhaled into the compressor 11 and is therein compressed.
  • the four-way switching valve 12 is set to be in the second state (depicted with the dotted line in FIG. 1 ).
  • a vapor compression refrigeration cycle is executed in the refrigerant circuit 10 .
  • the outdoor heat exchanger 13 is configured to function as an evaporator whereas the indoor heat exchanger 15 is configured to function as a condenser.
  • High-pressure refrigerant discharged from the compressor 11 exchanges heat with the indoor air in the indoor heat exchanger 15 and is thereby condensed.
  • the condensed refrigerant is decompressed in passing through the expansion valve 14 .
  • the decompressed refrigerant exchanges heat with the outdoor air in the outdoor heat exchanger 13 and is thereby evaporated.
  • the refrigerant is inhaled into the compressor 11 and is therein compressed.
  • the outdoor fan 23 includes a motor 23 a .
  • the motor 23 a is a long-life brushless DC motor and is configured to execute a duty control.
  • the motor 23 a is configured to control an on-time ratio in a power input cycle (i.e., a duty cycle) in order to change the rotation speed of the outdoor fan 23 .
  • a duty cycle a power input cycle
  • the rotation speed of the outdoor fan 23 is reduced when ventilation resistance increases due to frost attachment onto the outdoor heat exchanger 13 .
  • power supply to be inputted into the motor 23 a of the outdoor fan 23 is increased in proportion to increase in the duty cycle.
  • the rotation speed of the outdoor fan 23 is accordingly increased.
  • FIG. 2 includes charts representing “relations among outdoor fan input, outdoor fan rotation speed and outdoor fan blowing sound in executing a normal control under a frost attaching condition”.
  • the horizontal axes from bottom to top, represent elapsed time after start of a heating operation, whereas the vertical axes represent outdoor fan input, outdoor fan rotation speed and outdoor fan blowing sound.
  • frost starts attaching onto the outdoor heat exchanger 13 and ventilation resistance accordingly starts increasing.
  • the outdoor fan input is increased for preventing reduction in the rotation speed due to ventilation resistance and thereby for keeping the rotation speed of the outdoor fan 23 constant. Therefore, blowing sound is acutely increased.
  • FIG. 3 is an operational flowchart from start of a heating operation control to start of a defrosting operation control.
  • the control unit 4 starts counting an elapsed time TD after the start of the heating operation in Step S 1 .
  • the processing then proceeds to Step S 2 .
  • the control unit 4 keeps a standby state for a predetermined period of time (TD 0 ) until the rotation speed of the compressor 11 reaches a target rotation speed.
  • the processing then proceeds to Step S 3 and the control unit 4 sets the value of a variable X to be “a”.
  • a value, herein substituted in the variable X is obtained by adding a predetermined value to the difference between an outdoor temperature To and an outdoor heat exchanger temperature Te.
  • Step S 4 the control unit 4 detects the outdoor temperature To through the outdoor temperature sensor 101 . The processing then proceeds to Step S 5 . In Step S 5 , the control unit 4 detects the outdoor heat exchanger temperature Te through the outdoor heat exchanger temperature sensor 102 . The processing then proceeds to Step S 6 . In Step S 6 , the control unit 4 determines whether or not the difference between the outdoor temperature To and the outdoor heat exchanger temperature Te is greater than or equal to X.
  • Step S 7 when the control unit 4 determines the result in Step S 6 as “Yes”.
  • the processing returns to Step S 4 when the control unit 4 determines the result in Step S 6 as “No”.
  • Step S 7 the control unit 4 sets the value of the variable X to be a value obtained by adding a predetermined amount “s” to “To ⁇ Te” in Step S 6 (i.e., To ⁇ Te+s).
  • the processing then proceeds to Step S 8 .
  • the difference between the outdoor temperature To and the outdoor heat exchanger temperature Te is greater than “a”, the evaporation temperature of the refrigerant is lowered. Therefore, it is determined that frost attaches onto the outdoor heat exchanger 13 .
  • the control unit 4 resets the value of the variable X every time the difference between the outdoor temperature To and the outdoor heat exchanger temperature Te is reduced by the predetermined amount “s”.
  • Step S 8 the control unit 4 determines whether or not the elapsed time TD after start of the heating operation reaches a predetermined period of time TD 1 .
  • the processing then proceeds to Step S 9 when the control unit 4 determines the result in Step S 8 as “Yes”.
  • the processing returns to Step S 4 when the control unit 4 determines the result in Step S 8 as “No”.
  • the control unit 4 herein determines whether or not “TD>TD 1 ” is true.
  • the operation efficiency is set as a ratio of a net heating operation time to a total heating operation time, where the total heating operation time is set as the sum of the net heating operation time and a defrosting operation time.
  • Step S 9 the control unit 4 increases the operating frequency of the compressor 11 by a predetermined amount.
  • the control unit 4 executes Step S 9 for preventing degradation in heating performance until the heating operation control is switched into the defrosting operation control after the predetermined period of time TD 1 is elapsed for reliably achieving a predetermined level of operation efficiency.
  • the control unit 4 includes change amounts preliminarily set for changing the operating frequency of the compressor 11 in stages. The change amounts herein correspond to the stages on a one-to-one basis.
  • the control unit 4 is configured to increase the operating frequency by corresponding one of the change amounts required for upgrading the present stage of the operating frequency of the compressor 11 to a stage immediately higher than the present stage.
  • Step S 10 the control unit 4 reduces the rotation speed of the outdoor fan 23 by a predetermined amount.
  • the control unit 4 executes Step S 10 for cancelling out noise increased in response to increase in the operating frequency of the compressor 11 by reducing the rotation sound of the outdoor fan 23 . Therefore, noise is increased in response to increase in the operating frequency of the compressor 11 , whereas noise is reduced in response to reduction in the rotation speed of the outdoor fan 23 . Consequently, noise is kept roughly constant in the air conditioner 1 .
  • Step S 11 the control unit 4 determines whether or not the outdoor heat exchanger temperature Te is less than or equal to a predetermined calculated value. The processing then proceeds to Step S 12 when the control unit 4 determines the result in Step S 11 as “Yes”. In Step S 12 , the control unit 4 starts executing the defrosting operation control. By contrast, the processing returns to Step S 4 when the control unit 4 determines the result in Step S 11 as “No”.
  • the predetermined calculated value is a value calculated based on the outdoor temperature To (i.e., ⁇ To ⁇ + ⁇ ). The calculated value is set in consideration of not only lowering in the outdoor temperature To but also the other factors (e.g., humidity) as the reasons for frost attachment onto the outdoor heat exchanger 13 .
  • the control unit 4 increases the operating frequency of the compressor 11 and reduces the rotation speed of the outdoor fan 23 every time the difference between the outdoor temperature To and the outdoor heat exchanger temperature Te exceeds the predetermined amount “s”.
  • FIG. 4 is a chart representing the relation among elapsed time after start of the heating operation, indoor heat exchanger temperature and compressor operating frequency. It should be noted that FIG. 4 simply represents how the rotation speed of the outdoor fan 23 is reduced with a dotted line on a conceptual basis. Therefore, vertical plots of the dotted line are not exactly matched with the frequency values of the right side scale in the chart.
  • FIG. 4 represents that reduction in an indoor heat exchanger temperature Ti starts before the predetermined period of time TD 1 is elapsed after start of the heating operation.
  • the reason is that the amount of frost attaching onto the outdoor heat exchanger 13 is increased and the evaporation temperature of the refrigerant is lowered.
  • the condensation temperature of the refrigerant is increased when the control unit 4 upgrades the present stage of the operating frequency of the compressor 11 to a stage immediately higher than the present stage. This is expressed as increase in the indoor heat exchanger temperature Ti.
  • the control unit 4 does not increase the operating frequency of the compressor 11 , the indoor heat exchanger temperature Ti is reduced along the slope depicted with a dashed two-dotted line in FIG. 4 . Accordingly, heating performance is also degraded.
  • the control unit 4 downgrades the rotation speed of the outdoor fan 23 from the present level to a level immediately lower than the present level in order to cancel out a partial amount of noise increased in response to increase in the operating frequency of the compressor 11 . Such actions are repeated until start of the defrosting operation control. It should be noted that the control, which is executed until start of the defrosting operation control after the heating operation is started and the predetermined period of time TD 1 is further elapsed, will be hereinafter referred to as “a frost attaching condition operation control” for easy explanation.
  • a determining part 43 of the control unit 4 determines that the amount of frost attaching onto the outdoor heat exchanger 13 is increased when the difference between the outdoor temperature To and the outdoor heat exchanger temperature Te is increased. Accordingly, the frost attaching condition operation control is executed for increasing the operating frequency of the compressor 11 in accordance with the reduction amount of temperature of the indoor heat exchanger 15 and for reducing the rotation speed of the outdoor fan 23 .
  • the control unit 4 includes the change amounts preliminarily set for changing the operating frequency of the compressor 11 in stages, and the change amounts correspond to the stages on a one-to-one basis.
  • the control unit 4 is configured to increase the operating frequency of the compressor 11 by corresponding one of the change amounts required for upgrading the present stage of the operating frequency of the compressor 11 to a stage immediately higher than the present stage every time the temperature of the indoor heat exchanger 15 is reduced by a predetermined amount. Further, the control unit 4 is configured to reduce the rotation speed of the outdoor fan 23 in accordance with the change amount. Consequently, degradation in heating performance, caused due to frost attachment onto the outdoor heat exchanger, is inhibited in executing the heating operation. Further, noise of the compressor 11 is increased in response to increase in the operating frequency of the compressor 11 . However, noise of the outdoor fan 23 is reduced in accordance with reduction in the rotation speed of the outdoor fan 23 . Therefore, noise increase is inhibited for the entire air conditioner 1 .
  • the control unit 4 is configured to count the elapsed time TD immediately after activation of the compressor 11 and execute the defrosting operation control for resolving a frost attachment condition of the outdoor heat exchanger 13 when the elapsed time TD reaches the predetermined period of time TD 1 during execution of the frost attaching condition operation control and the evaporation temperature of the refrigerant (i.e., the outdoor heat exchanger temperature Te) becomes less than or equal to a predetermined temperature. Consequently, the frost attaching condition operation control is configured to be executed until immediately before start of the defrosting operation. This makes a user or users less likely to feel that heating is insufficient.
  • control unit 4 is configured to monitor the difference between the outdoor temperature To and the outdoor heat exchanger temperature Te, and simultaneously, control the compressor 11 and the outdoor fan 23 in executing the frost attaching condition operation control.
  • control unit 4 may be configured to monitor the indoor heat exchanger temperature Ti, and simultaneously, control the compressor 11 and the outdoor fan 23 .
  • FIG. 5 is an operational flowchart from start of the heating operation control to start of the defrosting operation control in an air conditioner according to a first modification of the present invention.
  • the control unit 4 starts counting the elapsed time TD after start of the heating operation in Step S 31 .
  • the processing then proceeds to Step S 32 .
  • Step S 32 the control unit 4 keeps a standby state for a predetermined period of time (TD 0 ) until the rotation speed of the compressor 11 reaches a target rotation speed.
  • the processing then proceeds to Step S 33 and the control unit 4 sets the value of a variable Y to be “b”.
  • a value, herein substituted into the variable Y is obtained by adding a predetermined amount “t” to the indoor heat exchanger temperature Ti.
  • the indoor heat exchanger temperature Ti is constant when the outdoor heat exchanger 13 is in a frost-free condition. Therefore, the value “b” of a temperature slightly lower than the condensation temperature of the refrigerant is set as the initial value of the variable Y.
  • Step S 34 the control unit 4 detects the indoor heat exchanger temperature Ti through the indoor heat exchanger temperature sensor 103 . The processing then proceeds to Step S 35 .
  • Step S 35 the control unit 4 determines whether or not the indoor heat exchanger temperature Ti becomes less than or equal to Y.
  • Step S 36 the control unit 4 determines the result in Step S 35 as “Yes”.
  • Step S 34 the control unit 4 determines the result in Step S 35 as “No”.
  • Step S 36 the control unit 4 sets the variable Y to be a value obtained by adding a predetermined amount “t” to the indoor heat exchanger temperature Ti (i.e., Ti+t).
  • the processing then proceeds to Step S 37 .
  • the indoor heat exchanger temperature Ti becomes less than or equal to “b”, it is determined that the condensation temperature is lowered due to increase in the amount of frost attaching onto the outdoor heat exchanger 13 .
  • the control unit 4 subsequently resets the variable Y every time the indoor heat exchanger temperature Ti is reduced by a predetermined amount “t”.
  • Step S 37 the control unit 4 determines whether or not the elapsed time TD after start of the heating operation reaches the predetermined period of time TD 1 .
  • the processing then proceeds to Step S 38 when the control unit 4 determines the result in Step S 37 as “Yes”.
  • the processing returns to Step S 34 when the control unit 4 determines the result in Step S 37 as “No”.
  • Step S 38 the control unit 4 increases the operating frequency of the compressor 11 by a predetermined amount.
  • Step S 39 the control unit 4 reduces the rotation speed of the outdoor fan 23 by a predetermined amount.
  • Step S 40 the control unit 4 detects the outdoor temperature To through the outdoor temperature sensor 101 .
  • Step S 41 the control unit 4 detects the outdoor heat exchanger temperature Te through the outdoor heat exchanger temperature sensor 102 .
  • Step S 42 the control unit 4 determines whether or not the outdoor heat exchanger temperature Te becomes less than or equal to a calculated value (i.e., ⁇ To ⁇ + ⁇ ).
  • the control unit 4 starts executing the defrosting operation control when determining the result in Step S 42 as “Yes”.
  • the processing returns to Step S 34 when the control unit 4 determines the result in Step S 42 as “No”.
  • control unit 4 can monitor the indoor heat exchanger temperature Ti, and simultaneously, control the compressor 11 and the outdoor fan 23 . Therefore, it is herein possible to achieve an advantageous effect equivalent to that achieved in the aforementioned exemplary embodiment.
  • control unit 4 is configured to monitor the indoor heat exchanger temperature Ti, and simultaneously, control the compressor 11 and the outdoor fan 23 .
  • the control unit 4 may be configured to monitor a higher side pressure Ph instead of the indoor heat exchanger temperature Ti, and simultaneously, control the compressor 11 and the outdoor fan 23 .
  • FIG. 6 is an operational flowchart from start of the heating operation control to start of the defrosting operation control in an air conditioner according to a second modification of the present invention.
  • the control unit 4 starts counting the elapsed time TD after start of the heating operation in Step S 51 .
  • the processing then proceeds to Step S 52 .
  • Step S 52 the control unit 4 keeps a standby state for a predetermined period of time (TD 0 ) until the rotation speed of the compressor 11 reaches a target rotation speed.
  • the processing then proceeds to Step S 53 and the control unit 4 sets the value of a variable Z to be “c”.
  • a value, herein substituted into the variable Z is obtained by adding a predetermined amount “p” to the higher side pressure Ph.
  • the higher side pressure Ph is constant when the outdoor heat exchanger 13 is in a frost-free condition. Therefore, the value “c” of a pressure slightly lower than the condensation pressure of the refrigerant is set as the initial value of the variable Z.
  • Step S 54 the control unit 4 detects the higher side pressure Ph through a discharge side pressure sensor 111 . The processing then proceeds to Step S 55 .
  • Step S 55 the control unit 4 determines whether or not the higher side pressure Ph is less than or equal to Z.
  • Step S 56 the control unit 4 determines the result in Step S 55 as “Yes”.
  • Step S 54 the control unit 4 determines the result in Step S 55 as “No”.
  • Step S 56 the control unit 4 sets the value of the variable Z to be a value obtained by adding a predetermined amount “p” to the higher side pressure Ph (i.e., Ph+p).
  • the processing then proceeds to Step S 57 .
  • the higher side pressure Ph becomes less than or equal to “c”
  • the condensation pressure is reduced due to increase in the amount of frost attaching onto the outdoor heat exchanger 13 .
  • the control unit 4 subsequently resets the variable Z every time the higher side pressure Ph is reduced by the predetermined amount “p”.
  • Step S 57 the control unit 4 determines whether or not the elapsed time TD after start of the heating operation reaches the predetermined period of time TD 1 .
  • the processing then proceeds to Step S 58 when the control unit 4 determines the result in Step S 57 as “Yes”.
  • the processing returns to Step S 54 when the control unit 4 determines the result in Step S 57 as “No”.
  • Step S 58 the control unit 4 increases the operating frequency of the compressor 11 by a predetermined amount.
  • Step S 59 the control unit 4 reduces the rotation speed of the outdoor fan 23 by a predetermined amount.
  • Step S 60 the control unit 4 detects the outdoor temperature To through the outdoor temperature sensor 101 .
  • Step S 61 the control unit 4 detects the outdoor heat exchanger temperature Te through the outdoor heat exchanger temperature sensor 102 .
  • Step S 62 the control unit 4 determines whether or not the outdoor heat exchanger temperature Te becomes less than or equal to a calculated value (i.e., ⁇ To ⁇ + ⁇ ).
  • the control unit 4 starts executing the defrosting operation control when determining the result in Step S 62 as “Yes”.
  • the processing returns to Step S 54 when the control unit 4 determines the result in Step S 62 as “No”.
  • control unit 4 can monitor the higher side pressure Ph, and simultaneously, control the compressor 11 and the outdoor fan 23 . Therefore, it is herein possible to achieve an advantageous effect equivalent to that achieved in the aforementioned exemplary embodiment and the first modification thereof.
  • the operating frequency of the compressor 11 is increased, and subsequently, the rotation speed of the outdoor fan 23 is reduced.
  • the operation order is not limited to the above.
  • the rotation speed of the outdoor fan 23 may be reduced, and thereafter, the operating frequency of the compressor 11 may be reduced.
  • noise is reduced in response to reduction in the rotation speed of the outdoor fan 23 . Therefore, noise is still acceptable by the reduction amount.
  • the operating frequency of the compressor 11 is increased by the amount corresponding to the acceptable range of noise increase while monitoring is executed for the indoor heat exchanger temperature Ti, the higher side pressure Ph or the difference between the outdoor temperature To and the outdoor heat exchanger temperature Te. With the control, noise is kept constant in the entire air conditioner 1 . The following will be explained with reference to FIGS. 7 and 8 .
  • FIG. 7 is a chart representing the relation among elapsed time after start of the heating operation, indoor heat exchanger temperature and compressor operating frequency in an air conditioner according to a second exemplary embodiment.
  • the rotation speed of the outdoor fan 23 is reduced to a predetermined rotation speed when it is determined that frost attaches onto the outdoor heat exchanger 13 and the elapsed time TD reaches the predetermined period of time TD 1 after start of the heating operation.
  • the indoor heat exchanger temperature Ti is monitored, and simultaneously, the operating frequency of the compressor 11 is increased by the amount corresponding to the acceptable range of noise increase when the indoor heat exchanger temperature Ti is reduced by ⁇ T.
  • ⁇ T is preferably equal to “3K”.
  • the control unit 4 includes the change amounts preliminarily set for changing the operating frequency of the compressor 11 in stages.
  • the change amounts correspond to the stages on a one-to-one basis.
  • the control unit 4 is configured to increase the operating frequency of the compressor 11 by corresponding one of the change amounts required for upgrading the present stage of the operating frequency of the compressor 11 to a stage immediately higher than the present stage.
  • FIG. 8 is a chart representing the relation among elapsed time after start of the heating operation, higher side pressure and compressor operating frequency in an air conditioner according to a modification of the second exemplary embodiment.
  • the rotation speed of the outdoor fan 23 is reduced to a predetermined rotation speed when it is determined that frost attaches onto the outdoor heat exchanger 13 and the elapsed time TD after start of the heating operation reaches the predetermined period of time TD 1 .
  • ⁇ P is preferably equal to 0.2 MPa.
  • the frost attaching condition operation control inhibits degradation in heating performance in a period of time when the heating performance is normally degraded due to frost attachment. Therefore, the present invention is useful for the general air conditioners using the vapor compression refrigeration cycle.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Signal Processing (AREA)
  • Thermal Sciences (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Fluid Mechanics (AREA)
  • Air Conditioning Control Device (AREA)
US13/321,874 2009-05-29 2010-05-28 Air conditioner Abandoned US20120060530A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2009-130114 2009-05-29
JP2009130114 2009-05-29
PCT/JP2010/003612 WO2010137344A1 (ja) 2009-05-29 2010-05-28 空気調和装置

Publications (1)

Publication Number Publication Date
US20120060530A1 true US20120060530A1 (en) 2012-03-15

Family

ID=43222470

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/321,874 Abandoned US20120060530A1 (en) 2009-05-29 2010-05-28 Air conditioner

Country Status (8)

Country Link
US (1) US20120060530A1 (de)
EP (1) EP2436999B1 (de)
JP (1) JP4711020B2 (de)
KR (1) KR101347520B1 (de)
CN (1) CN102449408B (de)
AU (1) AU2010253331B2 (de)
ES (1) ES2672818T3 (de)
WO (1) WO2010137344A1 (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140150479A1 (en) * 2012-11-30 2014-06-05 Yi Qu Secondary Defrost for Heat Pumps
US20170321939A1 (en) * 2014-12-26 2017-11-09 Daikin Industries, Ltd. Air conditioner
US9829237B2 (en) 2012-03-05 2017-11-28 Hanon Systems Heat pump system for vehicle and method of controlling the same
US10197317B2 (en) 2013-07-11 2019-02-05 Fujitsu General Limited Air conditioner with outdoor unit compressor driven at controllable activation rotational speed
US10731905B2 (en) * 2016-06-21 2020-08-04 Mitsubishi Electric Corporation Defrosting determination device, defrosting control device, and air conditioner
CN114061024A (zh) * 2020-07-30 2022-02-18 广东美的暖通设备有限公司 空调系统化霜的控制方法、控制装置、控制器及空调系统
US11371761B2 (en) * 2020-04-13 2022-06-28 Haier Us Appliance Solutions, Inc. Method of operating an air conditioner unit based on airflow
CN114857757A (zh) * 2022-03-31 2022-08-05 青岛海尔空调器有限总公司 用于控制空调器的方法及装置、空调器、存储介质
CN114992824A (zh) * 2022-06-28 2022-09-02 宁波奥克斯电气股份有限公司 一种空调器的控制方法、控制装置和空调器
US20230106953A1 (en) * 2021-10-06 2023-04-06 LGL France S.A.S. Proper deicing end detection and defrost cycle optimization
US20230243543A1 (en) * 2022-01-31 2023-08-03 Mitsubishi Electric Us, Inc. System and method for controlling the operation of a fan in an air conditioning system
US11808466B2 (en) 2022-01-04 2023-11-07 Haier Us Appliance Solutions, Inc. Air conditioner with variable speed compressor and variable speed fan

Families Citing this family (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101481698B1 (ko) * 2012-03-05 2015-01-13 한라비스테온공조 주식회사 차량용 히트 펌프 시스템 및 그 제어방법
FR3001029B1 (fr) * 2013-01-16 2017-09-01 Armor Geothermie Systeme de regulation dans une installation de climatisation a detente directe
DE102013218429A1 (de) * 2013-09-13 2015-04-02 Robert Bosch Gmbh Verfahren zum Enteisen einer Wärmepumpe
KR101983697B1 (ko) * 2013-09-23 2019-06-04 한온시스템 주식회사 차량용 히트 펌프 시스템의 전동 압축기 제어 방법
CN103940038B (zh) * 2014-04-03 2016-09-28 广东美的集团芜湖制冷设备有限公司 空调器的化霜控制方法
JP6397050B2 (ja) * 2014-11-26 2018-09-26 日立ジョンソンコントロールズ空調株式会社 空気調和機
WO2016132473A1 (ja) * 2015-02-18 2016-08-25 三菱電機株式会社 空気調和装置
JP6569899B2 (ja) * 2015-07-01 2019-09-04 三菱重工サーマルシステムズ株式会社 空気調和システム、制御方法及びプログラム
CN104964400B (zh) * 2015-07-21 2018-01-02 芜湖美智空调设备有限公司 空调器及其控制方法
CN105222436A (zh) * 2015-09-21 2016-01-06 珠海格力电器股份有限公司 空调系统及空调系统的控制方法
CN107238183A (zh) * 2017-06-26 2017-10-10 广东美的暖通设备有限公司 室外风机控制方法、装置和计算机可读存储介质
CN108224703A (zh) * 2017-12-25 2018-06-29 青岛海尔空调电子有限公司 空调的控制方法
CN108731208A (zh) * 2018-04-20 2018-11-02 四川长虹空调有限公司 变频热泵空调结霜过程控制方法
CN109028465B (zh) * 2018-05-24 2021-04-20 青岛海尔空调器有限总公司 空调器除霜控制方法
CN108692423B (zh) * 2018-05-24 2021-01-29 青岛海尔空调器有限总公司 空调器除霜控制方法
CN108775741B (zh) * 2018-05-24 2020-09-25 青岛海尔空调器有限总公司 空调器除霜控制方法
CN109028464B (zh) * 2018-05-24 2020-11-03 青岛海尔空调器有限总公司 空调器除霜控制方法
CN108592294B (zh) * 2018-05-24 2020-09-25 青岛海尔空调器有限总公司 空调器除霜控制方法
CN108775675A (zh) * 2018-05-24 2018-11-09 青岛海尔空调器有限总公司 空调器除霜控制方法
CN109373539B (zh) * 2018-11-07 2020-01-31 珠海格力电器股份有限公司 空调及其控制方法和装置
CN110470022B (zh) * 2019-08-04 2021-12-21 重庆海尔空调器有限公司 用于空调除霜的控制方法及装置、空调
CN112728740A (zh) * 2020-12-07 2021-04-30 珠海格力电器股份有限公司 空调、内机、高负载降频噪音的控制方法、控制器及介质
CN112628941B (zh) * 2020-12-11 2022-02-18 珠海格力电器股份有限公司 一种空调化霜控制方法、装置、存储介质及空调
CN112797570B (zh) * 2020-12-30 2022-08-23 宁波奥克斯电气股份有限公司 除霜控制方法、除霜装置及多联空调系统
CN115930366A (zh) * 2022-12-30 2023-04-07 珠海格力电器股份有限公司 空气调节器除霜控制方法、装置、空气调节器及存储介质

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4873649A (en) * 1988-06-10 1989-10-10 Honeywell Inc. Method for operating variable speed heat pumps and air conditioners
US4989414A (en) * 1988-10-26 1991-02-05 Hitachi, Ltd Capacity-controllable air conditioner
JPH0413037A (ja) * 1990-04-27 1992-01-17 Fujitsu General Ltd 空気調和機の制御方法
JPH109728A (ja) * 1996-06-20 1998-01-16 Mitsubishi Heavy Ind Ltd 冷凍装置
JPH10205935A (ja) * 1997-01-18 1998-08-04 Matsushita Electric Ind Co Ltd 除霜制御装置およびそれを用いた空気調和機
US5931009A (en) * 1997-06-27 1999-08-03 Samsung Electronics Co., Ltd. Defrosting apparatus of air conditioner and method thereof
US6178760B1 (en) * 1998-09-25 2001-01-30 Denso Corporation Electric vehicle air conditioner system and method for effecting defrosting operation before battery charging operation
US20080168781A1 (en) * 2005-02-10 2008-07-17 Yuuichi Yakumaru Refrigerating Machine
US20080276638A1 (en) * 2004-05-12 2008-11-13 Electro Industries, Inc. Heat pump with forced air heating regulated by withdrawal of heat to a radiant heating system
JP2009058222A (ja) * 2006-03-31 2009-03-19 Daikin Ind Ltd 室外機
US20090105884A1 (en) * 2006-05-19 2009-04-23 Shinichi Kaga Cooling Storage Cabinet and Method of Operating the Same
US20090235677A1 (en) * 2006-05-15 2009-09-24 Shinya Yanagida Cooling Storage Cabinet and Method of Operating Thereof
US20100235013A1 (en) * 2007-09-06 2010-09-16 Yoshiyasu Suzuki Inside temperature control device for cold storage

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07111288B2 (ja) 1985-09-20 1995-11-29 株式会社日立製作所 空気調和機
JPH0493540A (ja) * 1990-08-10 1992-03-26 Matsushita Electric Ind Co Ltd 空気調和機
US5797273A (en) * 1997-02-14 1998-08-25 Carrier Corporation Control of defrost in heat pump
JP4078447B2 (ja) * 2003-01-15 2008-04-23 株式会社日立製作所 空気調和機及び空気調和機の室外機
JP4254532B2 (ja) * 2003-12-26 2009-04-15 ダイキン工業株式会社 ヒートポンプ式給湯装置
CN100370200C (zh) * 2005-02-04 2008-02-20 松下电器产业株式会社 空调装置
JP4270274B2 (ja) * 2006-03-31 2009-05-27 ダイキン工業株式会社 室外機
JP2007285614A (ja) * 2006-04-18 2007-11-01 Matsushita Electric Ind Co Ltd 空気調和装置

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4873649A (en) * 1988-06-10 1989-10-10 Honeywell Inc. Method for operating variable speed heat pumps and air conditioners
US4989414A (en) * 1988-10-26 1991-02-05 Hitachi, Ltd Capacity-controllable air conditioner
JPH0413037A (ja) * 1990-04-27 1992-01-17 Fujitsu General Ltd 空気調和機の制御方法
JPH109728A (ja) * 1996-06-20 1998-01-16 Mitsubishi Heavy Ind Ltd 冷凍装置
JPH10205935A (ja) * 1997-01-18 1998-08-04 Matsushita Electric Ind Co Ltd 除霜制御装置およびそれを用いた空気調和機
US5931009A (en) * 1997-06-27 1999-08-03 Samsung Electronics Co., Ltd. Defrosting apparatus of air conditioner and method thereof
US6178760B1 (en) * 1998-09-25 2001-01-30 Denso Corporation Electric vehicle air conditioner system and method for effecting defrosting operation before battery charging operation
US20080276638A1 (en) * 2004-05-12 2008-11-13 Electro Industries, Inc. Heat pump with forced air heating regulated by withdrawal of heat to a radiant heating system
US20080168781A1 (en) * 2005-02-10 2008-07-17 Yuuichi Yakumaru Refrigerating Machine
JP2009058222A (ja) * 2006-03-31 2009-03-19 Daikin Ind Ltd 室外機
US20090235677A1 (en) * 2006-05-15 2009-09-24 Shinya Yanagida Cooling Storage Cabinet and Method of Operating Thereof
US20090105884A1 (en) * 2006-05-19 2009-04-23 Shinichi Kaga Cooling Storage Cabinet and Method of Operating the Same
US20100235013A1 (en) * 2007-09-06 2010-09-16 Yoshiyasu Suzuki Inside temperature control device for cold storage

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9829237B2 (en) 2012-03-05 2017-11-28 Hanon Systems Heat pump system for vehicle and method of controlling the same
US20140150479A1 (en) * 2012-11-30 2014-06-05 Yi Qu Secondary Defrost for Heat Pumps
US10041721B2 (en) * 2012-11-30 2018-08-07 Lennox Industries Inc. Heat pump comprising primary defrost operation and secondary defrost operation and method of operating heat pump
US10197317B2 (en) 2013-07-11 2019-02-05 Fujitsu General Limited Air conditioner with outdoor unit compressor driven at controllable activation rotational speed
US20170321939A1 (en) * 2014-12-26 2017-11-09 Daikin Industries, Ltd. Air conditioner
US10544958B2 (en) * 2014-12-26 2020-01-28 Daikin Industries, Ltd. Air conditioner with defrost control
US10731905B2 (en) * 2016-06-21 2020-08-04 Mitsubishi Electric Corporation Defrosting determination device, defrosting control device, and air conditioner
US11371761B2 (en) * 2020-04-13 2022-06-28 Haier Us Appliance Solutions, Inc. Method of operating an air conditioner unit based on airflow
CN114061024A (zh) * 2020-07-30 2022-02-18 广东美的暖通设备有限公司 空调系统化霜的控制方法、控制装置、控制器及空调系统
US20230106953A1 (en) * 2021-10-06 2023-04-06 LGL France S.A.S. Proper deicing end detection and defrost cycle optimization
US11808466B2 (en) 2022-01-04 2023-11-07 Haier Us Appliance Solutions, Inc. Air conditioner with variable speed compressor and variable speed fan
US20230243543A1 (en) * 2022-01-31 2023-08-03 Mitsubishi Electric Us, Inc. System and method for controlling the operation of a fan in an air conditioning system
US11815280B2 (en) * 2022-01-31 2023-11-14 Mitsubishi Electric Us, Inc. System and method for controlling the operation of a fan in an air conditioning system
CN114857757A (zh) * 2022-03-31 2022-08-05 青岛海尔空调器有限总公司 用于控制空调器的方法及装置、空调器、存储介质
CN114992824A (zh) * 2022-06-28 2022-09-02 宁波奥克斯电气股份有限公司 一种空调器的控制方法、控制装置和空调器

Also Published As

Publication number Publication date
KR20120016151A (ko) 2012-02-22
JP4711020B2 (ja) 2011-06-29
WO2010137344A1 (ja) 2010-12-02
AU2010253331A1 (en) 2012-01-19
EP2436999A4 (de) 2013-11-27
EP2436999A1 (de) 2012-04-04
CN102449408A (zh) 2012-05-09
ES2672818T3 (es) 2018-06-18
KR101347520B1 (ko) 2014-01-02
EP2436999B1 (de) 2018-05-09
AU2010253331B2 (en) 2013-04-11
CN102449408B (zh) 2014-07-30
JP2011007485A (ja) 2011-01-13

Similar Documents

Publication Publication Date Title
US20120060530A1 (en) Air conditioner
JP3290306B2 (ja) 空気調和機
US11686490B2 (en) HVAC functionality restoration systems and methods
US10168066B2 (en) Air conditioner with outdoor fan control in accordance with suction pressure and suction superheating degree of a compressor
US8572995B2 (en) Refrigeration system
US20100241287A1 (en) Air conditioning control device, air conditioning apparatus, and air conditioning control method
US20100218527A1 (en) Operation controller for compressor and air conditioner having the same
EP2320169A1 (de) Klimaanlage und verfahren zur bestimmung der darin enthaltenen kältemittelmenge
KR101739407B1 (ko) 공기조화기의 제어방법
US20210404691A1 (en) Air conditioner system
CN111033152B (zh) 制冷机
JP6141217B2 (ja) 圧縮機劣化診断装置及び圧縮機劣化診断方法
US20150153085A1 (en) Refrigerating device
KR101151321B1 (ko) 멀티형 공기조화기 및 그 운전방법
KR20090081909A (ko) 공기조화기 및 그 제어 방법
JP5125695B2 (ja) 空調システム
JP6650567B2 (ja) 空気調和機
JP2011149611A (ja) 空気調和機
KR100565995B1 (ko) 실내기 설치 위치에 따른 멀티형 에어컨의 운전 방법
AU2013200092B2 (en) Air conditioning apparatus and air conditioning apparatus refrigerant quantity determination method
KR100964369B1 (ko) 공기조화기의 제어방법
JP2008202868A (ja) 空気調和機
EP4286767A1 (de) Kältekreislaufvorrichtung
CN116971972A (zh) 压缩机容量控制方法和控制装置、存储介质、空调器
CN112856712A (zh) 膨胀阀控制方法及装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: DAIKIN INDUSTRIES, LTD., JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SHIMODA, JUNICHI;KINOSHITA, HIDEHIKO;REEL/FRAME:027270/0243

Effective date: 20101008

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION