EP1801520A1 - Système de conditionnement d'air - Google Patents

Système de conditionnement d'air Download PDF

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Publication number
EP1801520A1
EP1801520A1 EP06256498A EP06256498A EP1801520A1 EP 1801520 A1 EP1801520 A1 EP 1801520A1 EP 06256498 A EP06256498 A EP 06256498A EP 06256498 A EP06256498 A EP 06256498A EP 1801520 A1 EP1801520 A1 EP 1801520A1
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EP
European Patent Office
Prior art keywords
indoor
heat exchanger
refrigerant
valve
outdoor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06256498A
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German (de)
English (en)
Other versions
EP1801520B1 (fr
Inventor
Atsuhiko Yokozeki
Kenji Matsumura
Susumu Nakayama
Naoki Sugimoto
Yoshiharu Tsukada
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Hitachi Appliances Inc
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Hitachi Appliances Inc
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Publication date
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Publication of EP1801520A1 publication Critical patent/EP1801520A1/fr
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Publication of EP1801520B1 publication Critical patent/EP1801520B1/fr
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Classifications

    • 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
    • F24F11/50—Control or safety arrangements characterised by user interfaces or communication
    • F24F11/52—Indication arrangements, e.g. displays
    • 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
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • 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
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F2003/144—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0232—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses
    • F25B2313/02321—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses during cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • F25B2313/02343—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements during dehumidification
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/02—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
    • F25B2700/21—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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to an air conditioner, and more particularly to an air conditioner provided with a reheat dehumidification function.
  • An air conditioner forms a refrigerating cycle by connecting an outdoor unit provided with a compressor, an outdoor heat exchanger and the like, and an indoor unit provided with an indoor expansion valve, an indoor heat exchanger and the like by a piping so as to circulate a refrigerant.
  • an air conditioner provided with a so-called reheat dehumidification function of reheating an air cooled and dehumidified by the indoor heat exchanger to a temperature near a room temperature so as to blow in the room under a cooling operation mode.
  • the reheat dehumidification function is achieved by installing a reheat coil within the indoor unit on an upstream side of the indoor expansion valve.
  • each of the outdoor heat exchanger and the reheat coil is operated as a condenser, whereby the air cooled and dehumidified by the indoor heat exchanger is reheated to the temperature near the room temperature on the basis of a heat exchange by the reheat coil.
  • a reheat dehumidification operation and a cooling operation accompanying no reheat and dehumidification are switched by setting a piping bypassing the reheat coil and an indoor electromagnetic valve opening and closing the piping.
  • the reheat coil operates as a part of the condenser, thereby executing the reheat dehumidification operation.
  • the indoor electromagnetic valve is opened, the reheat coil is bypassed, thereby executing the cooling operation accompanying no reheat dehumidification function.
  • JP-A-7-294060 describes a structure provided with a piping bypassing the outdoor heat exchanger, and a regulating valve regulating an amount of a refrigerant flowing through the bypass piping.
  • a piping bypassing the outdoor heat exchanger and a regulating valve regulating an amount of a refrigerant flowing through the bypass piping.
  • An object of the present invention is to control a reheating capacity of the reheat coil on the basis of a simple structure.
  • Another object of the present invention is to improve a reliability by suppressing a necessary amount of a refrigerant at a time of a cooling operation.
  • an air conditioner in which a cooling cycle is formed by arranging an outdoor unit provided with an accumulator, a compressor, a four-way valve and an outdoor heat exchanger, and an indoor unit provided with a first indoor heat exchanger, a check valve, an indoor expansion valve, a second indoor heat exchanger and an indoor electromagnetic valve formed in a piping bypassing the first indoor heat exchanger and the check valve, in a piping circulating a cooling medium, comprising a control means for lowering a temperature of the refrigerant on a discharge side of the compressor at a set temperature, on the basis of a signal generated by closing of the indoor electromagnetic valve, at a time of a reheat dehumidification operation.
  • the refrigerant in a wet state having an increased rate of liquid refrigerant is circulated to the accumulator as is apparent from a Mollier diagram. Accordingly, since the liquid refrigerant is reserved in the accumulator, and the amount of the refrigerant circulating in the outdoor heat exchanger is reduced, the outdoor heat exchanger comes to a refrigerant lack state. Therefore, since the refrigerant in the outlet of the outdoor heat exchanger comes to a two-phase state, and an enthalpy difference in the first indoor heat exchanger corresponding to the reheat coil is increased, it is possible to improve the reheating capacity of the reheating device.
  • the objects mentioned above can be achieved by providing a control means for enlarging an opening degree of the indoor expansion valve, in place of the provision of the control means for lowering the temperature of the refrigerant on the discharge side of the compressor at the set temperature.
  • the refrigerant in the outlet of the outdoor heat exchanger comes to the two-phase state, and the enthalpy difference in the first indoor heat exchanger corresponding to the reheat coil is increased, it is possible to improve the reheating capacity of the reheating device.
  • an air conditioner in which a cooling cycle is formed by arranging an outdoor unit provided with an accumulator, a compressor, a four-way valve, an outdoor heat exchanger and an outdoor expansion valve, and an indoor unit provided with a first indoor heat exchanger, a check valve, an indoor expansion valve, a second indoor heat exchanger and an indoor electromagnetic valve formed in a piping bypassing the first indoor heat exchanger and the check valve, in a piping circulating a cooling medium, comprising a control means for controlling an opening degree of the indoor expansion valve on the basis of a signal generated by closing of the indoor electromagnetic valve, at a time of a reheat dehumidification operation, and controlling an opening degree of the outdoor expansion valve on the basis of a signal generated by opening of the indoor electromagnetic valve, at a time of a cooling operation.
  • the indoor electromagnetic valve when the indoor electromagnetic valve is open, the first indoor heat exchanger is bypassed, and the cooling operation accompanying no reheat and dehumidification is executed, however, a part of the refrigerant is circulated to the first indoor heat exchanger side. Accordingly, a part of the refrigerant under the low-pressure two-phase state is circulated to the first indoor heat exchanger by controlling the opening degree of the outdoor expansion valve provided on an upstream side of the first indoor heat exchanger so as to reduce the pressure of the cooling medium.
  • the first indoor heat exchanger serves as the evaporator in place of the reheat coil by employing the structure mentioned above, the reservation of the liquid refrigerant is not generated. Accordingly, it is possible to suppress the necessary amount of the refrigerant at a time of the cooling operation, and it is possible to improve the reliability.
  • Fig. 1 is a view showing a structure of the air conditioner in accordance with the present embodiment.
  • an air conditioner 1 is constituted by an outdoor unit 2, an indoor unit 3, and a gas side connection piping 4 and a liquid side connection piping 5 which connect the outdoor unit 2 and the indoor unit 3 annularly.
  • the outdoor unit 2 is formed by connecting a four-way valve 6, an accumulator 7, a compressor 8, an outdoor heat exchanger 9 and an outdoor expansion valve 10 by a piping circulating a cooling medium. Further, a compressor discharge gas temperature sensor 11 and a high-pressure pressure sensor 12 are provided on a discharge side of the compressor 8, and the outdoor heat exchanger 9 is provided with an outdoor blower 13 blowing an outdoor air to the outdoor heat exchanger 9.
  • the indoor unit 3 is formed by connecting a first indoor heat exchanger 15, a check valve 16, an indoor expansion valve 17 and a second indoor heat exchanger 18 by a piping circulating the cooling medium. Further, there is provided a piping 19 bypassing the first heat exchanger and the check valve 16, and the piping 19 is provided with an indoor electromagnetic valve 20 opening and closing the piping 19. Further, the second indoor heat exchanger 18 is provided with a blower 21 blowing an indoor air to the second indoor heat exchanger 18 and the first indoor heat exchanger 15 in this order. Further, an indoor air temperature sensor 25 and an indoor air humidity sensor 26 are provided on an indoor air suction side of the second indoor heat exchanger 18, and an indoor blow-off air temperature sensor 27 is provided on an indoor air blow-off side of the first indoor heat exchanger 15.
  • Fig. 2 is a view showing a structure of the accumulator 7.
  • the accumulator 7 is constituted by a container 30, and an introduction pipe 31 and a U-shaped pipe 32 provided within the container 30.
  • the U-shaped pipe 32 is provided with an oil return hole 33 in a lower portion, and with a pressure equalization hole 34 in an upper portion.
  • Fig. 3 is a view showing an example of an operation characteristic of the accumulator 7. As shown in Fig.
  • a quality (dry degree) of the refrigerant returning to the suction side of the compressor is changed by a circulating amount of the refrigerant and a height HL of a liquid surface.
  • the liquid refrigerant reserved within the accumulator 7 is increased.
  • the quality is high, the liquid refrigerant reserved in the accumulator 7 is reduced.
  • an amount of the refrigerant reserved within the accumulator 7 is determined in accordance with a state of the refrigerant in the inlet of the accumulator 7.
  • the four-way valve 6 is switched as shown by a solid line in Fig. 1, thereby connecting the discharge side of the compressor 8 and the outdoor heat exchanger 9, and the accumulator 7 and the gas side connection piping 4. Accordingly, the high-pressure gas refrigerant discharged from the compressor 8 is heat exchanged with the outdoor air in the outdoor heat exchanger 9 after passing through the four-way valve 6 so as to be condensed.
  • the refrigerant depressurized by the outdoor expansion valve 10 so as to form low-pressure two phases passes through the liquid side connection piping 5 and is fed to the indoor unit 3.
  • the refrigerant passes through the opened indoor electromagnetic valve 20 and the fully-opened indoor expansion valve 17, and flows into the second indoor heat exchanger 18.
  • the refrigerant cooling and dehumidifying the indoor air in the second indoor heat exchanger 18 so as to be evaporated passes through the gas side connection piping 4, is again returned to the outdoor unit 2, is sucked to the compressor 8 from the accumulator 7 via the four-way valve 6, and makes a circuit of the cycle.
  • the first indoor heat exchanger 15 a part of the refrigerant flows into the first indoor heat exchanger 15, however, since the refrigerant is depressurized by the outdoor expansion valve 10 so as to be in a low pressure state, the first indoor heat exchanger is operated as the evaporator. Accordingly, since the refrigerant is gasified, and the reservation of the liquid refrigerant is not generated, it is possible to reduce a sealing amount of the cooling medium. As a result, since a liquid return or the like is not generated at a time of starting the compressor, it is possible to improve a reliability.
  • the four-way valve 6 is switched in the same direction as that of the cooling operation time. Accordingly, the high-pressure gas refrigerant discharged from the compressor 8 passes through the four-way valve 6 and is heat exchanged with the outdoor air in the outdoor heat exchanger 9 so as to be condensed, in the same manner as that of the cooling operation.
  • the outdoor expansion valve 10 is fully opened, the gas refrigerant is hardly depressurized and is fed to the indoor unit 3. Since the indoor electromagnetic valve 20 is closed in the indoor unit 3, the refrigerant flows into the first indoor heat exchanger 15.
  • the refrigerant circulating the first indoor heat exchanger 15 is heat exchanged with the indoor air cooled in the second indoor heat exchanger 18 so as to be cooled.
  • the first indoor heat exchanger 15 is operated as a reheat coil heating the indoor air.
  • the refrigerant condensed or excessively cooled by the first indoor heat exchanger 15 is depressurized by the indoor expansion valve 17, and flows into the second indoor heat exchanger 18.
  • the refrigerant circulating in the second indoor heat exchanger 18 is heat exchanged with the indoor air so as to be heated.
  • the second indoor heat exchanger 18 is operated as a cooling coil cooling and dehumidifying the indoor air.
  • the refrigerant heated by the indoor air in the second indoor heat exchanger 18 is evaporated so as to be returned to the outdoor unit 2 via the gas side connection piping 4.
  • the refrigerant is returned to the suction side piping of the compressor 8 from the four-way valve 6 via the accumulator 7, and makes a circuit of the cycle.
  • Fig. 4 is a view showing a cooling cycle of the reheat dehumidification operation in the case of setting the compressor discharge gas temperature in the same as that of the cooling operation time.
  • the opening degree of the indoor expansion valve 17 is controlled in such a manner that the quality of the accumulator comes to about 0.95.
  • the compressor discharge gas temperature at this time is controlled as shown in Fig. 6.
  • the temperature detected by the compressor discharge gas temperature sensor 11 is controlled by the opening degree of the indoor expansion valve 17 in such a manner as to come to a temperature higher at a constant temperature with respect to a condensing temperature of the discharge gas pressure detected by the high-pressure pressure sensor 12, and a target temperature of discharge gas is shown by the following formula.
  • Tdo Tc Pd + SHa
  • Tdo denotes a target temperature of discharge gas at a normal time
  • Tc denotes a condensing temperature
  • Pd denotes a discharge gas pressure
  • SHa denotes a normal superheat degree of discharge gas.
  • the normal superheat degree of discharge gas SHa is normally set to about 25 to 40°C.
  • an upper limit Tdomax and a lower limit Tdomin are set as the following expression for securing a reliability of the compressor.
  • the opening degree of the indoor expansion valve 17 is controlled in such a manner that the quality of the accumulator 7 comes to about 0.95, the liquid refrigerant is not reserved within the accumulator 7 and the accumulator 7 is operated, as shown in Fig. 3. Accordingly, a necessary amount of refrigerant is supplied to the outdoor heat exchanger 9 serving as the condenser. Therefore, a completely condensed liquid refrigerant state is established in an outlet of the outdoor heat exchanger 9. Accordingly, an enthalpy difference in the first indoor heat exchanger 15 corresponding to the reheat coil becomes smaller as shown in the Mollier diagram in Fig. 4, and the reheating capacity becomes smaller.
  • the cooling cycle of the reheat dehumidification operation shown in the Mollier diagram in Fig. 5 corresponds to an operation state in the case of setting the discharge gas temperature lower than the normal temperature of discharge gas.
  • Tdor denotes a target temperature of discharge gas at a reheat dehumidification operation
  • Tc denotes a condensing temperature
  • Pd denotes a discharge gas pressure
  • SHb denotes a superheat degree of discharge gas at a reheat dehumidification operation time.
  • an upper limit Tdomax and a lower limit Tdomin are set as shown by the following expression, for securing a reliability of the compressor.
  • the superheat degree of discharge gas at the reheat dehumidification operation time SHb is set lower than the normal superheat degree of discharge gas SHa, for example, about 15 to 25°C.
  • ⁇ PL in Figs. 4 and 5 indicates a pressure loss in the liquid side connection piping 5 in a simulation manner.
  • the liquid refrigerant is reserved within the accumulator 7 on the basis of the characteristic of the accumulator 7 shown in Fig. 3. Accordingly, since the outdoor heat exchanger 9 comes to a refrigerant lack state, the refrigerant on the outlet side of the outdoor heat exchanger 9 comes to the two-phase state, the enthalpy difference in the reheat coil is increased and the reheating amount is increased, as shown in Fig. 5. Accordingly, it is possible to achieve a high dehumidifying capacity as well as the cooling capacity is suppressed, whereby it is possible to achieve a low humidity which does not lower the room temperature excessively, even at a high dehumidifying load time.
  • control target value of the discharge gas temperature on the basis of the detection values of the indoor air temperature sensor 25 and the indoor blow-off air temperature sensor 27.
  • this control method for example, it is possible to uniformly control the air temperature difference between the suction and the blow-off, it is possible to control a necessary cooling amount, and it is possible to achieve a room temperature and humidity control having a higher accuracy.
  • the control target value of the discharge gas temperature on the basis of a detected value of the indoor air humidity sensor 26.
  • the discharge gas temperature is controlled low in such a manner that the air temperature difference between the suction and the blow-off becomes small.
  • this control method it is possible to execute the indoor temperature and humidity control to a comfortable humidity range.
  • the check valve 16 installed within the indoor unit 3 is provided for the purpose of preventing the refrigerant from flowing into the first indoor heat exchanger 15 at a time of the heating operation so as to suppress the capacity reduction, however, it can be replaced by a hydraulic resisting means such as an electromagnetic valve, a capillary or the like. Further, it is possible to reduce a circulation resistance of the indoor electromagnetic valve 20 by fully opening the indoor expansion valve 17 at a time of the heating operation, and achieving the depressurizing effect by the outdoor expansion valve 10. In this case, it is possible to omit a circulation preventing means such as the check valve 16 or the like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Human Computer Interaction (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP06256498A 2005-12-26 2006-12-21 Système de conditionnement d'air Not-in-force EP1801520B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2005371785A JP4730738B2 (ja) 2005-12-26 2005-12-26 空気調和機

Publications (2)

Publication Number Publication Date
EP1801520A1 true EP1801520A1 (fr) 2007-06-27
EP1801520B1 EP1801520B1 (fr) 2009-11-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP06256498A Not-in-force EP1801520B1 (fr) 2005-12-26 2006-12-21 Système de conditionnement d'air

Country Status (5)

Country Link
EP (1) EP1801520B1 (fr)
JP (1) JP4730738B2 (fr)
CN (1) CN1991276B (fr)
DE (1) DE602006010312D1 (fr)
ES (1) ES2335302T3 (fr)

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EP2881685A4 (fr) * 2012-07-31 2016-03-23 Daikin Ind Ltd Dispositif de réfrigération pour conteneur
WO2016025498A3 (fr) * 2014-08-11 2016-05-19 Wong Lee Wa Système de conditionnement d'air à deux blocs refroidi à l'eau
GB2537105A (en) * 2015-03-30 2016-10-12 Mcgowan Gregory Air conditioning system
US20170314813A1 (en) * 2016-05-02 2017-11-02 Lee Wa Wong Split-Type Air Conditioning and Heat Pump System with Energy Efficient Arrangement
EP3879209A1 (fr) * 2020-03-13 2021-09-15 Air Supplies Holland B.V. Unité de commande de climatiseur et système le comprenant

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JP4730738B2 (ja) 2011-07-20
EP1801520B1 (fr) 2009-11-11
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CN1991276B (zh) 2010-09-08
ES2335302T3 (es) 2010-03-24
CN1991276A (zh) 2007-07-04

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