EP1431677B1 - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
EP1431677B1
EP1431677B1 EP02768028A EP02768028A EP1431677B1 EP 1431677 B1 EP1431677 B1 EP 1431677B1 EP 02768028 A EP02768028 A EP 02768028A EP 02768028 A EP02768028 A EP 02768028A EP 1431677 B1 EP1431677 B1 EP 1431677B1
Authority
EP
European Patent Office
Prior art keywords
temperature
room
heat exchanger
value
target
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02768028A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1431677A1 (en
EP1431677A4 (en
Inventor
Junichi Kanaoka Factory Sakai Plant SHIMODA
Makoto Momosaki
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
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Daikin Industries Ltd
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Filing date
Publication date
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Publication of EP1431677A1 publication Critical patent/EP1431677A1/en
Publication of EP1431677A4 publication Critical patent/EP1431677A4/en
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Publication of EP1431677B1 publication Critical patent/EP1431677B1/en
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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
    • F24F11/80—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
    • 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
    • F24F11/84—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 valves
    • 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
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • 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
    • 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
    • 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
    • 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
    • F24F2110/20—Humidity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid 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
    • 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
    • F25B2313/0314—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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B2700/02—Humidity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air

Definitions

  • This invention relates to the control of an air conditioning system.
  • the capacity of the compressor is increased to enhance air-conditioning capacity.
  • the capacity of the compressor is decreased to lower air-conditioning capacity.
  • the compressor is deactivated to stop the cooling of the room air. In this manner, the above-described air conditioning system uses the difference between the room temperature and the set temperature as a control parameter to control the capacity of the compressor so that the room temperature reaches the set temperature.
  • the room air is sent to an indoor heat exchanger and cooled therein.
  • the indoor heat exchanger produces dew condensation on its surface to reduce the amount of moisture in the air.
  • the relative humidity of the room air also changes accordingly. In this manner, the cooling operation of the air conditioning system changes not only the room temperature but also the relative humidity.
  • An air-conditioning system having the features in the preamble of claim 1 or 2 is known from US-A-5,305,822 .
  • both the temperature and relative humidity of the room air cannot be concurrently controlled in a suitable manner. Therefore, the user has to select either one of the cooling operation in which emphasis is placed on temperature control and the dry operation in which emphasis is placed on humidity control.
  • the present invention has been made in view of the foregoing points, and an object thereof is to improve the comfort of people in a room during cooling operation of an air conditioning system by suitably controlling both the room temperature and relative humidity.
  • a first solution provided by the present invention is directed to an air conditioning system that operates on a refrigeration cycle by circulating refrigerant in a refrigerant circuit ( 20 ) and conducts at least cooling operation in which the refrigerant evaporates in an indoor heat exchanger ( 37 ) of the refrigerant circuit ( 20 ).
  • the system further includes: heat exchanger temperature detecting means ( 76 ) for detecting the temperature of the indoor heat exchanger ( 37 ) as an evaporation temperature of the refrigerant during cooling operation, room temperature detecting means ( 75 ) for detecting the dry-bulb temperature of a room air being sent to the indoor heat exchanger ( 37 ); room humidity detecting means ( 78 ) for detecting the relative humidity of the room air being sent to the indoor heat exchanger ( 37 ); setting means ( 81 ) for setting a target control value for the evaporation temperature of the refrigerant during cooling operation at specified time intervals, based on a detected value of the heat exchanger temperature detecting means ( 76 ), a detected value of the room temperature detecting means ( 75 ) and a user-input set temperature, within a range up to an upper limit determined according to a detected value of the room humidity detecting means ( 78 ); and capacity control means ( 82 ) for controlling the capacity of a compressor ( 30 ) of the refriger
  • a second solution provided by the present invention is directed to an air conditioning system for operating on a refrigeration cycle by circulating refrigerant in a refrigerant circuit ( 20 ) and conducts at least cooling operation in which the refrigerant evaporates in an indoor heat exchanger ( 37 ) of the refrigerant circuit ( 20 ).
  • the system further includes: room temperature detecting means ( 75 ) for detecting the dry-bulb temperature of a room air being sent to the indoor heat exchanger ( 37 ); room humidity detecting means ( 78 ) for detecting the relative humidity of the room air being sent to the indoor heat exchanger ( 37 ); setting means ( 81 ) for setting a target control value for the evaporation temperature of the refrigerant during cooling operation so that a detected value of the room temperature detecting means ( 75 ) reaches a set temperature, and for limiting the target control value to within a range up to an upper limit determined according to a detected value of the room humidity detecting means ( 78 ); and capacity control means ( 82 ) for controlling the capacity of a compressor ( 30 ) of the refrigerant circuit ( 20 ) so that the detected value of the heat exchanger temperature detecting means ( 76 ) reaches the target control value set by the setting means ( 81 ).
  • a third solution provided by the present invention is, in the first or second solution, that the setting means ( 81 ) drops the upper limit of the target control value for the evaporation temperature of the refrigerant in a stepwise manner as the detected value of the room humidity detecting means ( 78 ) increases.
  • a fourth solution provided by the present invention is, in the first or second solution, that the setting means ( 81) stores the minimum and maximum values in a target range for the room relative humidity, and that when the detected value of the room humidity detecting means ( 78 ) is equal to or larger than the minimum value in the target range, the setting means ( 81 ) takes for the upper limit of the target control value a value lower than the wet-bulb temperature of an air whose dry-bulb temperature is a detected value of the indoor heat exchanger ( 37 ) and whose relative humidity is the minimum value in the target range.
  • a fifth solution provided by the present invention is, in the fourth solution, that when the detected value of the room humidity detecting means ( 78 ) exceeds the maximum value in the target range for the room relative humidity, the setting means ( 81 ) drops the upper limit of the target control value below that of the target control value when the detected value of the room humidity detecting means ( 78 ) falls within the target range.
  • a sixth solution provided by the present invention is, in the first or second solution, that the setting means (81) sets the target control value within the range down to 0°C.
  • a seventh solution provided by the present invention is, in the sixth solution, that only when the room is brought into high humidity conditions that the detected value of the room humidity detecting means ( 78 ) exceeds a predetermined reference value, the setting means ( 81 ) sets the target control value within the range down to a predetermined lower limit which is higher than 0°C.
  • refrigerant circulates in the refrigerant circuit ( 20 ) of the air conditioning system to complete a refrigeration cycle.
  • refrigerant circulates while changing its phase so that compression, condensation, expansion and evaporation of the refrigerant sequentially take place.
  • the air conditioning system is provided with heat exchanger temperature detecting means ( 76 ), room temperature detecting means ( 75 ), room humidity detecting means ( 78 ), setting means ( 81 ) and capacity control means ( 82 ).
  • the air conditioning system conducts at least cooling operation. More specifically, the air conditioning system may conduct cooling operation alone, or may selectively conduct cooling operation and heating operation.
  • refrigerant and room air exchange heat with each other at the indoor heat exchanger ( 37 ).
  • the refrigerant in the indoor heat exchanger ( 37 ) absorbs heat from the room air to evaporate.
  • the heat exchanger temperature detecting means ( 76 ) detects the temperature of part of the indoor heat exchanger ( 37 ) in which refrigerant is changing its phase. During cooling operation, since the indoor heat exchanger ( 37 ) serves as an evaporator, the detected value of the heat exchanger temperature detecting means ( 76 ) corresponds to the evaporation temperature of the refrigerant.
  • the room temperature detecting means ( 75 ) detects the temperature of the room air being sent to the indoor heat exchanger ( 37 ).
  • the room humidity detecting means ( 78 ) detects the relative humidity of the room air being sent to the indoor heat exchanger ( 37 ). In other words, for the room air before exchanging heat with the refrigerant at the indoor heat exchanger ( 37 ), its temperature is detected by the room temperature detecting means ( 75 ) while its relative humidity is detected by the room humidity detecting means ( 78 ).
  • Input to the setting means ( 81 ) are a detected value of the heat exchanger temperature detecting means ( 76 ), a detected value of the room temperature detecting means ( 75 ) and a detected value of the room humidity detecting means ( 78 ).
  • a set temperature set by a user of the air conditioning system is also input to the setting means ( 81 ).
  • This setting means ( 81 ) carries out, for example, a calculation using the detected values of the heat exchanger temperature detecting means ( 76 ) and room temperature detecting means ( 75 ) to set a target control value for the evaporation temperature of refrigerant during cooling operation. This target control value is set so that the room air reaches the set temperature.
  • the setting means ( 81 ) re-sets the target control value after each elapse of a predetermined time period. In other words, the setting means ( 81 ) updates the target control value at specified time intervals.
  • the setting means ( 81 ) sets the target control value within a range up to the upper limit determined according to the detected value of the room humidity detecting means ( 78 ). For example, even when the value obtained, for example, by the calculation using the detected value of the heat exchanger temperature detecting means ( 76 ), exceeds the upper limit, the setting means ( 81 ) sets the target control value at a value equal to or smaller than the upper limit.
  • Input to the capacity control means ( 82 ) are the detected value of the heat exchanger temperature detecting means ( 76 ) and the target control value set by the setting means ( 81 ).
  • the capacity control means ( 82 ) controls the capacity of the compressor ( 30 ) so that the detected value of the heat exchanger temperature detecting means ( 76 ) reaches the target control value. More specifically, during cooling operation, the capacity control means ( 82 ) controls the capacity of the compressor ( 30 ) so that the evaporation temperature of refrigerant in the indoor heat exchanger ( 37 ) matches the target control value.
  • refrigerant circulates in the refrigerant circuit ( 20 ) of the air conditioning system to complete a refrigeration cycle.
  • refrigerant circuit ( 20 ) refrigerant circulates while changing its phase so that compression, condensation, expansion and evaporation of the refrigerant sequentially take place.
  • the air conditioning system is provided with room temperature detecting means ( 75 ), room humidity detecting means ( 78 ), setting means ( 81 ) and capacity control means ( 82 ).
  • the air conditioning system conducts at least cooling operation. More specifically, the air conditioning system may conduct cooling operation alone, or may selectively conduct cooling operation and heating operation.
  • refrigerant and room air exchange heat with each other at the indoor heat exchanger ( 37 ).
  • the refrigerant in the indoor heat exchanger ( 37 ) absorbs heat from the room air to evaporate.
  • the room temperature detecting means ( 75 ) detects the temperature of the room air being sent to the indoor heat exchanger ( 37 ).
  • the room humidity detecting means ( 78 ) detects the relative humidity of the room air being sent to the indoor heat exchanger ( 37 ). In other words, for the room air before exchanging heat with the refrigerant at the indoor heat exchanger ( 37 ), its temperature is detected by the room temperature detecting means ( 75 ) while its relative humidity is detected by the room humidity detecting means ( 78 ).
  • Input to the setting means ( 81 ) are a detected value of the room temperature detecting means ( 75 ) and a detected value of the room humidity detecting means ( 78 ).
  • a set temperature set by a user of the air conditioning system is also input to the setting means ( 81 ).
  • This setting means ( 81 ) sets a target control value for the evaporation temperature of refrigerant during cooling operation so that the detected value of the room temperature detecting means ( 75 ) reaches the set temperature.
  • the target control value for the evaporation temperature of refrigerant during cooling operation is limited to within a range up to an upper limit determined according to a detected value of the room humidity detecting means ( 78 ). For example, even when the value derived based on the detected value of the room temperature detecting means ( 75 ) and the set temperature exceeds the upper limit, the setting means ( 81 ) sets the target control value at a value equal to or smaller than the upper limit.
  • the capacity control means ( 82 ) controls the capacity of the compressor ( 30 ) so that the evaporation temperature of refrigerant in the indoor heat exchanger ( 37 ) matches the target control value.
  • the setting means ( 81 ) changes the upper limit of the target control value for the evaporation temperature of the refrigerant according to the detected value of the room humidity detecting means ( 78 ).
  • the upper limit of the target control value for the evaporation temperature of the refrigerant becomes lower in a stepwise manner as the detected value of the room humidity detecting means ( 78 ) increases.
  • the setting means ( 81 ) compares the input detected value of the room humidity detecting means ( 78 ) with the minimum value in a target range for the room relative humidity.
  • the setting means ( 81 ) derives the wet-bulb temperature of an air whose dry-bulb temperature is a detected value of the room temperature detecting means ( 75 ) and whose relative humidity is the minimum value in the target range, and sets the target control value while taking for the upper limit a value lower than the wet-bulb temperature.
  • the target control value set by the setting means ( 81 ) is always lower than the wet-bulb temperature of the room air at that time. Therefore, in this case, when the room air is cooled at the indoor heat exchanger ( 37 ), moisture in the room air concurrently condenses to provide dehumidification of the room.
  • the setting means ( 81 ) compares the input detected value of the room humidity detecting means ( 78 ) with the maximum value in the target range for the room relative humidity. When the detected value of the room humidity detecting means ( 78 ) is higher than the maximum value in the target range, the setting means ( 81 ) takes, for the upper limit of the target control value, a lower value than that of the target control value when the detected value of the room humidity detecting means ( 78 ) is anywhere from the minimum value to the maximum value in the target range.
  • the setting means ( 81 ) of this solution lowers the upper limit of the target control value to set the target control value relatively low, thereby ensuring the amount of moisture to be removed from the room air.
  • the setting means ( 81 ) sets the target control value while taking 0°C for the lower limit.
  • the target control value set by the setting means ( 81 ) always has any value not lower than 0°C and does not fall below 0°C. Therefore, the temperature of the indoor heat exchanger ( 37 ) may temporarily fall below 0°C but is never held below 0°C for hours, i.e., is fundamentally held at 0°C or more.
  • the setting means ( 81 ) sets the target control value while taking a value higher than 0°C for the lower limit. At this time, when a low value is set as the target control value, the temperature of the indoor heat exchanger ( 37 ) is decreased accordingly. Therefore, if a low target control value is set under the above high humidity conditions, this may cause an adverse effect such that the amount of moisture condensed in the indoor heat exchanger ( 37 ) may be increased too much for drainage of produced water to catch up with. To avoid this, the setting means ( 81 ) sets the target control value relatively high only under the above high humidity conditions, thereby preventing the amount of moisture condensed in the indoor heat exchanger ( 37 ) from being excessive.
  • the setting means ( 81 ) of this invention determines the upper limit of the target control value according to the detected value of the room relative humidity detecting means ( 78 ) while considering the detected value of the room temperature detecting means ( 75 ) and so on.
  • the setting means ( 81 ) sets the target control value by considering not only the temperature of the room air but also the relative humidity thereof. Therefore, the air conditioning system of this invention can concurrently control both the room temperature and relative humidity in a suitable manner without forcing the user to select the operation centred on temperature control or the operation centred on humidity control unlike the conventional technique. Therefore, according to this invention, the room temperature and relative humidity can be adjusted in a comfort region thereby improving the comfort of people in the room.
  • the indoor heat exchanger ( 37 ) is fundamentally maintained at 0°C or higher. Therefore, according to this solution, the indoor heat exchanger ( 37 ) can be avoided from moisture freezing thereby preventing any adverse effect resulting from freezing.
  • the setting means ( 81 ) takes a value higher than 0°C for the lower limit of the target control value when the room is under high humidity conditions that the amount of moisture condensed in the indoor heat exchanger ( 37 ) is expected to be excessive. Therefore, according to this solution, the amount of drain produced in the indoor heat exchanger ( 37 ) is prevented from being excessive, thereby avoiding any problem resulting from production of excessive drain.
  • An air conditioner ( 10 ) as an air conditioning system according to the present invention is structured to selectively conduct cooling operation and heating operation.
  • the air conditioner ( 10 ) includes a refrigerant circuit ( 20 ) and a controller ( 80 ).
  • the refrigerant circuit ( 20 ) is constituted by an outdoor circuit ( 21 ), an indoor circuit ( 22 ), a liquid-side connection pipe ( 23 ), and a gas-side connection pipe ( 24 ).
  • the outdoor circuit ( 21 ) is disposed in an outdoor unit ( 11 ).
  • the outdoor unit ( 11 ) is provided with an outdoor fan ( 12 ).
  • the indoor circuit ( 22 ) is disposed in an indoor unit ( 13 ).
  • the indoor unit ( 13 ) is provided with an indoor fan ( 14 ).
  • a compressor ( 30 ), a four-way selector valve ( 33 ), an outdoor heat exchanger ( 34 ), a receiver ( 35 ), and a motor-operated expansion valve ( 36 ) are disposed. Furthermore, in the outdoor circuit ( 21 ), a bridge circuit ( 40 ), a subcooling circuit ( 50 ), a liquid-side shut-off valve ( 25 ), and a gas-side shut-off valve ( 26 ) are also disposed. Moreover, the outdoor circuit ( 21 ) is connected to a gas communication pipe ( 61 ) and a pressure equalising pipe ( 63 ).
  • a discharge port ( 32 ) of the compressor ( 30 ) is connected to a first port of the four-way selector valve ( 33 ).
  • a second port of the four-way selector valve ( 33 ) is connected to one end of the outdoor heat exchanger ( 34 ).
  • the other end of the outdoor heat exchanger ( 34 ) is connected to the bridge circuit ( 40 ).
  • the bridge circuit ( 40 ) is connected to the receiver ( 35 ), the motor-operated expansion valve ( 36 ), and the liquid-side shut-off valve ( 25 ). Description on this point will be described below.
  • An intake port ( 31 ) of the compressor ( 30 ) is connected to a third port of the four-way selector valve ( 33 ).
  • a fourth port of the four-way selector valve ( 33 ) is connected to the gas-side shut-off valve ( 26 ).
  • the bridge circuit ( 40 ) is configured by connecting a first line ( 41 ), a second line ( 42 ), a third line ( 43 ), and a fourth line ( 44 ) in the form of a bridge.
  • an outlet end of the first line ( 41 ) is connected to an outlet end of the second line ( 42 )
  • an inlet end of the second line ( 42 ) is connected to an outlet end of the third line ( 43 )
  • an inlet end of the third line ( 43 ) is connected to an inlet end of the fourth line ( 44 )
  • an outlet end of the fourth line ( 44 ) is connected to an inlet end of the first line ( 41 ).
  • Check valves are provided one each in the first to fourth lines ( 41-44 ).
  • the first line ( 41 ) is provided with the check valve ( CV-1 ) for allowing only refrigerant flow from its inlet end toward its outlet end.
  • the second line ( 42 ) is provided with the check valve ( CV-2 ) for allowing only refrigerant flow from its inlet end toward its outlet end.
  • the third line ( 43 ) is provided with the check valve ( CV-3 ) for allowing only refrigerant flow from its inlet end toward its outlet end.
  • the fourth line ( 44 ) is provided with the check valve ( CV-4 ) for allowing only refrigerant flow from its inlet end toward its outlet end.
  • the other end of the outdoor heat exchanger ( 34 ) is connected, in the bridge circuit ( 40 ), to the inlet end of the first line ( 41 ) and the outlet end of the fourth line ( 44 ).
  • the outlet ends of the first line ( 41 ) and the second line ( 42 ) both in the bridge circuit ( 40 ) are connected to an upper end part of the receiver ( 35 ) formed in the shape of a cylindrical container.
  • a lower end part of the receiver ( 35 ) is connected via the motor-operated expansion valve ( 36 ) to the inlet ends of the third line ( 43 ) and the fourth line ( 44 ) both in the bridge circuit ( 40 ).
  • the inlet end of the second line ( 42 ) and the outlet end of the third line ( 43 ) both in the bridge circuit ( 40 ) are connected to the liquid-side shut-off valve ( 25 ).
  • an indoor heat exchanger ( 37 ) is provided in the indoor circuit ( 22 ).
  • One end of the indoor circuit ( 22 ) is connected to the liquid-side shut-off valve ( 25 ) through the liquid-side connection pipe ( 23 ).
  • the other end of the indoor circuit ( 22 ) is connected to the gas-side shut-off valve ( 26 ) through the gas-side connection pipe ( 24 ).
  • the liquid-side connection pipe ( 23 ) and the gas-side connection pipe ( 24 ) are disposed across the outdoor unit (11) and the indoor unit (13).
  • the subcooling circuit ( 50 ) is connected at one end thereof to the line between the lower end of the receiver ( 35 ) and the motor-operated expansion valve ( 36 ), and connected at the other end to the inlet port ( 31 ) of the compressor ( 30 ).
  • a first solenoid valve ( 51 ), a thermostatic expansion valve ( 52 ) and a subcooling heat exchanger ( 54 ) are disposed in the order of one end to the other of the circuit.
  • the subcooling heat exchanger ( 54 ) is arranged to conduct heat exchange between the refrigerant flowing from the receiver ( 35 ) toward the motor-operated expansion valve ( 36 ) and the refrigerant flowing through the subcooling circuit ( 50 ).
  • a temperature-sensing bulb ( 53 ) of the thermostatic expansion valve ( 52 ) is attached to the subcooling circuit ( 50 ) downstream of the subcooling heat exchanger ( 54 ).
  • the gas communication pipe ( 61 ) is connected at one end to the upper end part of the receiver ( 35 ), and connected at the other end to the line between the motor-operated expansion valve ( 36 ) and the bridge circuit ( 40 ). Furthermore, the gas communication line ( 61 ) is provided on its way with a second solenoid valve ( 62 ).
  • the pressure equalising pipe ( 63 ) is connected at one end to the gas communication pipe ( 61 ) between the second solenoid valve ( 62 ) and the receiver ( 35 ), and connected at the other end to the outdoor circuit ( 21 ) between the discharge port ( 32 ) and the four-way selector valve ( 33 ) of the compressor ( 30 ). Furthermore, the pressure equalising pipe ( 63 ) is provided with a pressure equalising check valve ( 53 ) for allowing only refrigerant flow from its one end toward the other end.
  • the compressor ( 30 ) is of hermetic, high-pressure dome type. More specifically, this compressor ( 30 ) is formed by containing a scroll type compression mechanism and a motor for driving the compression mechanism in a cylindrical housing. The refrigerant taken in through the inlet port ( 31 ) is introduced directly into the compression mechanism. The refrigerant compressed in the compression mechanism is first discharged to the inside of the housing and then let out through the discharge port ( 32 ). The compression mechanism and the motor are not shown in the figure.
  • the motor for the compressor ( 30 ) is supplied with electric power through an unshown inverter.
  • the RPM of the motor is also changed and the compressor capacity is in turn changed.
  • the compressor ( 30 ) is structured to be variable in capacity.
  • the outdoor heat exchanger ( 34 ) is formed of a cross fin coil type fin-and-tube heat exchanger. This outdoor heat exchanger ( 34 ) is composed of two parts connected in series with each other. The outdoor heat exchanger ( 34 ) is supplied with an outdoor air by the outdoor fan ( 12 ). Furthermore, the outdoor heat exchanger ( 34 ) conducts heat exchange between the refrigerant circulating in the refrigerant circuit ( 20 ) and the outdoor air.
  • the indoor heat exchanger ( 37 ) is formed of a cross fin coil type fin-and-tube heat exchanger. This indoor heat exchanger ( 37 ) is supplied with a room air by the indoor fan ( 14 ). Furthermore, the indoor heat exchanger ( 37 ) conducts heat exchange between the refrigerant in the refrigerant circuit ( 20 ) and the room air.
  • the four-way selector valve ( 33 ) changes between a position in which communication is provided between the first and second ports and between the third and fourth ports (a position shown in the solid lines in Figure 1 ) and a position in which communication is provided between the first and fourth ports and between the second and third ports (a position shown in the broken lines in Figure 1 ).
  • This changeover operation of the four-way selector valve ( 33 ) inverts the circulating direction of refrigerant in the refrigerant circuit ( 20 ).
  • the air conditioner ( 10 ) is provided with various kinds of sensors. The detected values of these sensors are input into the controller ( 80 ) for use in operation control over the air conditioner ( 10 ).
  • the line connected to the intake port ( 31 ) of the compressor ( 30 ) is provided with a low-pressure sensor ( 71 ) for detecting the pressure of an intake refrigerant of the compressor ( 30 ), and an intake pipe temperature sensor ( 77 ) for detecting the temperature of the intake refrigerant.
  • the line connected to the discharge port (32) of the compressor ( 30 ) is provided with a discharge pipe temperature sensor ( 74 ) for detecting the temperature of a discharge refrigerant of the compressor ( 30 ).
  • the outdoor unit ( 11 ) is provided with an outdoor air temperature sensor ( 72 ) for detecting the temperature of the outdoor air.
  • the outdoor heat exchanger ( 34 ) is provided with an outdoor heat exchanger temperature sensor ( 73 ) for detecting the temperature of its heat transfer pipe.
  • the indoor unit ( 13 ) is provided with an room temperature sensor ( 75 ) for detecting the temperature of the room air being sent to the indoor heat exchanger (37), and a relative humidity sensor ( 78 ) for detecting the temperature of the room air being sent to the indoor heat exchanger ( 37 ).
  • the room temperature sensor ( 75 ) has the function of outputting the detected value as a detected room temperature, and thus constitutes a room temperature detecting means.
  • the relative humidity sensor ( 78 ) has the function of outputting the detected value as a detected room humidity, and thus constitutes a room humidity detecting means.
  • the indoor heat exchanger ( 37 ) is provided with an indoor heat exchanger temperature sensor ( 76 ) for detecting the temperature of its heat transfer pipe.
  • This indoor heat exchanger temperature sensor ( 76 ) is attached to part of the heat transfer pipe of the indoor heat exchanger ( 37 ) at the inside of which refrigerant falls into a gas-liquid two-phase condition during operation.
  • the indoor heat exchanger temperature sensor ( 76 ) constitutes a heat exchanger temperature detecting means for detecting the temperature of the indoor heat exchanger ( 37 ) as the evaporation temperature or the condensation temperature of the refrigerant and outputting the detected value as a detected heat exchanger temperature.
  • the controller ( 80 ) includes a target value setting section ( 81 ) that is a setting means.
  • the target value setting section ( 81 ) inputs the detected room temperature from the room temperature sensor ( 75 ), the detected heat exchanger temperature from the indoor heat exchanger temperature sensor ( 76 ), and a set temperature from an unshown remote controller.
  • the set temperature is input thereto through the user's operation of the remote controller.
  • the detected room humidity from the relative humidity sensor ( 78 ) is also input to the target value setting section ( 81 ).
  • the target value setting section ( 81 ) is configured to set a target control value, based on the detected room temperature, the detected heat exchanger temperature and the set temperature, within a range up to the upper limit determined according to the detected room humidity.
  • the controller ( 80 ) also includes a capacity control section ( 82 ) that is a capacity control means.
  • the capacity control section ( 82 ) inputs the detected heat exchanger temperature from the indoor heat exchanger temperature sensor ( 76 ), and the target control value set by the target value setting section ( 81 ).
  • the capacity control section ( 82 ) changes the power supply frequency output from the inverter so that the detected heat exchanger temperature can reach the target control value.
  • the capacity control section ( 82 ) is configured to control the capacity of the compressor ( 30 ) to match the detected heat exchanger temperature with the target control value.
  • This air conditioner (10) selectively conducts a cooling operation under refrigerating action and a heating operation under heat-pumping action.
  • the four-way selector valve (33) is changed to the position shown in the solid lines in Figure 1 , the motor-operated expansion valve (36) is adjusted to a predetermined opening, the first solenoid valve ( 51 ) is made open, and the second solenoid valve ( 62 ) is made closed.
  • the outdoor fan ( 12 ) and the indoor fan ( 14 ) are operated. Under these conditions, the refrigerant circulates in the refrigerant circuit ( 20 ) so that the system operates on a refrigeration cycle in which the outdoor heat exchanger ( 34 ) serves as a condenser and the indoor heat exchanger ( 37 ) serves as an evaporator.
  • the refrigerant discharged from the discharge port ( 32 ) of the compressor ( 30 ) is sent through the four-way selector valve ( 33 ) to the outdoor heat exchanger ( 34 ).
  • the outdoor heat exchanger ( 34 ) the refrigerant condenses by releasing heat to the outdoor air.
  • the condensed refrigerant flows through the first line ( 41 ) of the bridge circuit ( 40 ) into the receiver ( 35 ).
  • Part of the high-pressure liquid refrigerant having flowed out of the receiver ( 35 ) is diverted to the subcooling circuit ( 50 ), while the rest flows into the subcooling heat exchanger ( 54 ).
  • the refrigerant flowing into the subcooling circuit ( 50 ) is reduced in pressure by the thermostatic expansion valve ( 52 ) to turn into a low-pressure refrigerant, and then flows into the subcooling heat exchanger ( 54 ).
  • the subcooling heat exchanger ( 54 ) heat is exchanged between the high-pressure liquid refrigerant from the receiver ( 35 ) and the low-pressure refrigerant reduced in pressure by the thermostatic expansion valve ( 52 ).
  • the low-pressure refrigerant absorbs heat from the high-pressure liquid refrigerant to evaporate so that the high-pressure liquid refrigerant is cooled.
  • the low-pressure refrigerant evaporated in the subcooling heat exchanger ( 54 ) flows through the subcooling circuit ( 50 ) and is then taken into the compressor ( 30 ).
  • the high-pressure liquid refrigerant cooled in the subcooling heat exchanger ( 54 ) is sent to the motor-operated expansion valve ( 36 ).
  • the sent high-pressure liquid refrigerant is reduced in pressure.
  • the refrigerant reduced in pressure by the motor-operated expansion valve ( 36 ) is sent from the third line ( 43 ) of the bridge circuit ( 40 ) through the liquid-side connection pipe ( 23 ) to the indoor heat exchanger ( 37 ).
  • the indoor heat exchanger ( 37 ) the refrigerant absorbs heat from the room air to evaporate.
  • the indoor heat exchanger ( 37 ) the room air taken into the indoor unit ( 13 ) releases heat to the refrigerant. This heat release causes the room temperature to drop.
  • moisture of the room air condenses in the indoor heat exchanger ( 37 ).
  • the indoor heat exchanger ( 37 ) the room air is cooled and concurrently reduced in humidity.
  • a conditioned air obtained through the cooling and moisture reduction of the room air is fed from the indoor unit ( 13 ) to the room for use in cooling.
  • the refrigerant evaporated in the indoor heat exchanger ( 37 ) flows through the gas-side connection pipe ( 24 ) and the four-way selector valve ( 33 ), and is taken into the compressor ( 30 ) through the intake port ( 31 ).
  • the compressor ( 30 ) compresses the intake refrigerant and discharges the compressed refrigerant through the discharge port ( 32 ) again.
  • the refrigerant circuit ( 20 ) the refrigerant circulates in the above manner to perform the refrigerating action.
  • the four-way selector valve ( 33 ) is changed to the position shown in the broken lines in Figure 1 , the motor-operated expansion valve ( 36 ) is adjusted to a predetermined opening, and the first solenoid valve ( 51 ) and the second solenoid valve ( 62 ) are closed.
  • the outdoor fan ( 12 ) and the indoor fan ( 14 ) are operated. Under these conditions, the refrigerant circulates in the refrigerant circuit ( 20 ) so that the system operates on a refrigeration cycle in which the indoor heat exchanger ( 37 ) serves as a condenser and the outdoor heat exchanger ( 34 ) serves as an evaporator.
  • the refrigerant discharged from the discharge port ( 32 ) of the compressor ( 30 ) is sent through the four-way selector valve ( 33 ) and the gas-side connection pipe ( 24 ) to the indoor heat exchanger ( 37 ).
  • the indoor heat exchanger ( 37 ) the refrigerant releases heat to the room air to condense.
  • the refrigerant applies heat to the room air taken into the indoor unit ( 13 ). This heat application raises the temperature of the room air to produce a warm conditioned air.
  • the conditioned air thus produced is fed from the indoor unit ( 13 ) to the room for use in heating.
  • the refrigerant condensed in the indoor heat exchanger ( 37 ) flows through the liquid-side connection pipe ( 23 ) and the second line ( 42 ) of the bridge circuit ( 40 ) into the receiver ( 35 ).
  • the refrigerant having flowed out of the receiver ( 35 ) is reduced in pressure by the motor-operated expansion valve ( 36 ), and then sent through the fourth line ( 44 ) of the bridge circuit ( 40 ) to the outdoor heat exchanger ( 34 ).
  • the refrigerant evaporates by absorbing heat from the outdoor air.
  • the refrigerant evaporated in the outdoor heat exchanger ( 34 ) passes through the four-way selector valve ( 33 ) and is then taken into the compressor ( 30 ) through the intake port ( 31 ).
  • the compressor ( 30 ) compresses the intake refrigerant and discharges the compressed refrigerant through the discharge port ( 32 ) again.
  • the refrigerant circulates in the above manner to perform the heat-pumping action.
  • the target value setting section ( 81 ) inputs the detected room temperature from the room temperature sensor ( 75 ), the detected heat exchanger temperature from the indoor heat exchanger temperature sensor ( 76 ), and the set temperature from the remote controller.
  • the target value setting section ( 81 ) carries out calculations shown in the below Equations ⁇ 1> and ⁇ 2> at specified time intervals (for example, every 60 seconds).
  • TcS TcSo + KT ⁇ 1 - KT ⁇ 2
  • Equation ⁇ 3> the term (KT1) for a capacity increase due to a temperature difference between the room temperature and the set temperature is calculated from the below Equation ⁇ 3>.
  • the correction term (KT2) derived by learning is determined based on the map shown in Figure 2 .
  • This correction term (KT2) corresponds to a second correction value.
  • the abscissa axis e1 is calculated from different equations for cooling operation and heating operation. Specifically, the abscissa axis e1 is calculated according to the below equations:
  • KT2 a correction term by learning based on the map of Figure 2 .
  • KT2 -2.0 holds.
  • KT2 -1.0 holds.
  • KT2 0 holds.
  • the correction term (KT2) by learning is determined from the map of Figure 2 in this manner.
  • the target value setting section ( 81 ) acts as described above to set the target evaporation temperature (TeS) as a target control value during cooling operation and set the target condensation temperature (TcS) as a target control value during heating operation. It should be noted that in the target value setting section ( 81 ), possible values of the target evaporation temperature (TeS) as a target control value during cooling operation are limited to a predetermined range.
  • the target value setting section ( 81 ) the range in which the target evaporation temperature (TeS) can be set is changed depending upon the detected room humidity provided from the relative humidity sensor ( 78 ). Furthermore, the target value setting section ( 81 ) stores a value of "40%" as the minimum value in the target range for the room relative humidity and a value of "60%" as the maximum value in the target range.
  • the limits of the target evaporation temperature (TeS) in the target value setting section ( 81 ) will be described taking as an example the condition that the dry-bulb temperature of the room air (i.e., detected room temperature) is 27°C.
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) in the range from a first lower limit to a first upper limit inclusive.
  • the first lower limit is fixed at "0°C”
  • the first upper limit is fixed at "19°C”.
  • the target value setting section ( 81 ) selects the calculated value as the target evaporation temperature (TeS).
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) only at 0°C.
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) only at 19°C.
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) within the range of the first lower limit to a second upper limit inclusive.
  • the second upper limit is fixed at "16°C".
  • the target value setting section ( 81 ) selects the calculated value as the target evaporation temperature (TeS).
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) only at 0°C.
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) only at 16°C.
  • the target value setting section (81) sets the target evaporation temperature (TeS) within the range of the first lower limit to a third upper limit inclusive.
  • the third upper limit is fixed at "13°C".
  • the target value setting section ( 81 ) selects the calculated value as the target evaporation temperature (TeS).
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) only at 0°C.
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) only at 13°C.
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) within the range of a second lower limit to the third upper limit inclusive.
  • the second lower limit is fixed at "12°C".
  • the target value setting section ( 81 ) selects the calculated value as the target evaporation temperature (TeS).
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) only at 12°C.
  • the target value setting section ( 81 ) sets the target evaporation temperature (TeS) only at 13°C.
  • the first upper limit is determined to restrict the lower-side pressure of the refrigeration cycle to a predetermined value or less by considering the operation limit of the compressor ( 30 ). In other words, the first upper limit is determined regardless of the dry-bulb temperature and the wet-bulb temperature of the room air, and held constant even when these values vary. Therefore, when the detected room humidity is below 40%, the target evaporation temperature (TeS) may be set higher than the wet-bulb temperature of the room air to produce no dew condensation at the indoor heat exchanger ( 37 ). In such a case, however, it is desirable to conduct no room dehumidification because the detected room humidity has already fallen below the target range.
  • TeS target evaporation temperature
  • the target evaporation temperature (TeS) can be set relatively high. Thereby, the compressor ( 30 ) is operated at a capacity as small as possible to reduce power consumption of the motor for the compressor ( 30 ).
  • the second upper limit is determined to be always lower than the wet-bulb temperature of the air having a dry-bulb temperature equal to a detected room temperature and having a relative humidity of 40%. For example, when the detected room temperature is 27°C, the wet-bulb temperature of the air having a dry-bulb temperature of 27°C and a relative humidity of 40% is 17.5 °C. Therefore, the second upper limit is given as 16°C. The second upper limit varies depending upon the detected room temperature.
  • the target evaporation temperature (TeS) is always set lower than the wet-bulb temperature of the room air to condense moisture thereof in the indoor heat exchanger ( 37 ), resulting in dehumidify the room air.
  • the third upper limit is determined to be always lower than the second upper limit.
  • the second upper limit is 16°C. Therefore, the second upper limit is given as 13°C.
  • This third upper limit varies, like the second upper limit, depending upon the detected room temperature.
  • the target evaporation temperature (TeS) is always set lower than the second upper limit to increase the amount of moisture to be condensed in the indoor heat exchanger ( 37 ), resulting in increasing the amount of moisture to be removed from the room air.
  • the first lower limit is determined taking it into consideration to maintain the detected heat exchanger temperature at the freezing point of water or higher.
  • the setting of the first lower limit aims at preventing ice accretion on the indoor heat exchanger ( 37 ) and thereby avoiding the occurrence of problems such as increased resistance to air flow due to freezing.
  • the second lower limit is determined taking it into consideration to suppress the amount of drain to be produced. More specifically, in high humidity conditions where the detected room humidity exceeds 80% which is a reference value, when the refrigerant evaporation temperature in the indoor heat exchanger ( 37 ) excessively drops, the amount of moisture condensed may be too increased for the discharge of drain to catch up with, or may cause the production of dew condensation at the casing surface of the indoor unit ( 13 ). Therefore, in such high humidity conditions, the target evaporation temperature (TeS) is set relatively high in order to prevent dew condensation on the indoor unit (13) and thereby ensure reliability.
  • TeS target evaporation temperature
  • the target evaporation temperature (TeS) is limited to the first upper limit or lower in the target value setting section ( 81 ).
  • the target evaporation temperature (TeS) is limited to the second upper limit, which is lower than the first upper limit, or lower.
  • the target evaporation temperature (TeS) is limited to the third upper limit, which is lower than the second upper limit, or lower.
  • the capacity control section ( 82 ) inputs the detected heat exchanger temperature from the indoor heat exchanger temperature sensor ( 76 ), and the target control value set by the target value setting section ( 81 ). Then, the capacity control section ( 82 ) controls the capacity of the compressor ( 30 ) by changing the power supply frequency output from the inverter so that the detected heat exchanger temperature can match the target control value.
  • the capacity control section ( 82 ) increases the power supply frequency output of the inverter.
  • the capacity control section ( 82 ) decreases the power supply frequency output of the inverter.
  • the capacity control section ( 82 ) increases the power supply frequency output of the inverter.
  • the capacity control section ( 82 ) decreases the power supply frequency output of the inverter.
  • the target evaporation temperature (TeS) When the detected heat exchanger temperature (Te) is lower than the target evaporation temperature (TeS) (e1 has a negative value) and the detected room temperature (Tr) is higher than the set temperature (TrS) ( ⁇ TrS has a positive value), the target evaporation temperature (TeS) may be set too high even though it is necessary to cool the air much more. In such a case, the correction term (KT2) by learning is set at a negative value so that the target evaporation temperature (TeS) can be set relatively low.
  • the target evaporation temperature (TeS) may be set too low even though it is unnecessary to cool the air so much.
  • the correction term (KT2) by learning is set at a positive value so that the target evaporation temperature (TeS) can be set relatively high.
  • the detected heat exchanger temperature (Te) is higher than the target evaporation temperature (TeS) (e1 has a positive value) and the detected room temperature (Tr) is higher than the set temperature (TrS) ( ⁇ TrS has a positive value), it is necessary to cool the air much more and the target evaporation temperature (TeS) may be set relatively low.
  • the detected heat exchanger temperature (Te) is lower than the target evaporation temperature (TeS) (e1 has a negative value) and the detected room temperature (Tr) is lower than the set temperature (TrS) ( ⁇ TrS has a negative value)
  • it is unnecessary to cool the air much and the target evaporation temperature (TeS) may be set relatively high.
  • the correction term (KT2) by learning is set zero to maintain the target evaporation temperature (TeS) at the current value.
  • the target value setting section ( 81 ) of the present embodiment determines the upper limit of the target evaporation temperature (TeS), which is being set, according to the detected value of the relative humidity sensor ( 78 ) while considering the detected room temperature (Tr) and so on.
  • the target value setting section ( 81 ) sets the target control value by considering not only the temperature of the room air but also the relative humidity thereof Therefore, the air conditioner ( 10 ) of this embodiment can concurrently control both the room temperature and relative humidity in a suitable manner without forcing the user to select the operation centred on temperature control or the operation centred on humidity control unlike the conventional techniques. Therefore, according to this embodiment, the room temperature and relative humidity can be adjusted in a comfort region thereby improving the comfort of people in the room.
  • the indoor heat exchanger ( 37 ) since the target value setting section ( 81 ) takes 0°C for the first lower limit, the indoor heat exchanger ( 37 ) is fundamentally maintained at 0°C or higher. Therefore, according to this embodiment, the indoor heat exchanger ( 37 ) can be avoided from moisture freezing thereby preventing any adverse effect resulting from freezing.
  • the target value setting section ( 81 ) takes the second lower limit higher than 0°C for the lower limit of the target evaporation temperature (TeS) when the room is under high humidity conditions that the amount of moisture condensed in the indoor heat exchanger ( 37 ) is expected to be excessive. Therefore, according to this embodiment, the target evaporation temperature (TeS) can be set relatively high to prevent excessive drop of the refrigerant evaporation temperature during cooling operation and thereby avoid any adverse effect of excessive drain and dew condensation on the casing of the indoor unit ( 13 ).
  • the present invention is useful for air conditioning systems that conduct cooling operation.
EP02768028A 2001-09-28 2002-09-24 Air conditioner Expired - Lifetime EP1431677B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2001298725 2001-09-28
JP2001298725 2001-09-28
PCT/JP2002/009788 WO2003029728A1 (en) 2001-09-28 2002-09-24 Air conditioner

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EP1431677A1 EP1431677A1 (en) 2004-06-23
EP1431677A4 EP1431677A4 (en) 2010-02-24
EP1431677B1 true EP1431677B1 (en) 2011-06-29

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AT (1) ATE514908T1 (ja)
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JP3668786B2 (ja) 2003-12-04 2005-07-06 ダイキン工業株式会社 空気調和装置
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AU2002332260B2 (en) 2005-03-10
ATE514908T1 (de) 2011-07-15
WO2003029728A1 (en) 2003-04-10
EP1431677A1 (en) 2004-06-23
TW571060B (en) 2004-01-11
JP3835453B2 (ja) 2006-10-18
EP1431677A4 (en) 2010-02-24
JPWO2003029728A1 (ja) 2005-01-20
ES2366535T3 (es) 2011-10-21

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