EP1801520A1 - Air conditioning system - Google Patents
Air conditioning system Download PDFInfo
- 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
- Authority
- 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
Links
Images
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.
Landscapes
- 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)
Abstract
Description
- 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. As the air conditioner mentioned above, there has been known 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. In other words, 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. Further, 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. In other words, when the indoor electromagnetic valve is closed, the reheat coil operates as a part of the condenser, thereby executing the reheat dehumidification operation. When the indoor electromagnetic valve is opened, the reheat coil is bypassed, thereby executing the cooling operation accompanying no reheat dehumidification function.
- It is possible to achieve the dehumidification preventing an excessive cooling by executing such the reheat dehumidification operation, however, there is a case that a cooling capacity of the indoor heat exchanger is increased at a time when the indoor is exposed to a high dehumidifying load, and the reheating capacity is insufficient in the reheating device.
-
JP-A-7-294060 - However, since the technique described in
JP-A-7-294060 - 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.
- In order to achieve the objects mentioned above, in accordance with the present invention, there is provided 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.
- In other words, if the temperature of the refrigerant is lowered on the discharge side of the compressor, 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. In other words, it is possible to control the reheating capacity of the reheat coil on the basis of the simple structure which is not provided with the piping bypassing the outdoor heat exchanger, the regulating valve for regulating the amount of the refrigerant flowing through the bypass piping, and the like.
- Further, 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.
- In other words, since an amount of a reduced pressure of the refrigerant in the indoor expansion valve becomes smaller by enlarging the opening degree of the indoor expansion valve, an evaporating pressure in the second indoor heat exchanger corresponding to the evaporator comes to a high pressure, and an evaporating temperature becomes higher. Accordingly, a heat quantity exchanged by the second indoor heat exchanger becomes smaller, and the refrigerant circulating to the accumulator comes to the refrigerant in the wet state having the increased rate of the liquid cooling medium. As a result, the liquid refrigerant is reserved in the accumulator in the same manner as mentioned above, and the outdoor heat exchanger comes to the refrigerant lack state. Therefore, since 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. In other words, it is possible to control the reheating capacity of the reheat coil on the basis of the simple structure which is not provided with the piping bypassing the outdoor heat exchanger, the regulating valve for regulating the amount of the refrigerant flowing through the bypass piping, and the like.
- Further, there is provided 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.
- In accordance with this structure, 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. In other words, since 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.
- In accordance with the present invention, it is possible to control the reheating capacity of the reheat coil on the basis of the simple structure, and it is possible to improve the reliability by suppressing the necessary amount of the refrigerant at a time of the cooling operation.
- IN THE DRAWINGS:
- Fig. 1 is a view showing a structure of an air conditioner in accordance with the present embodiment;
- Fig. 2 is a view showing a structure of an accumulator in accordance with the present embodiment;
- Fig. 3 is a view showing an operation characteristic of the accumulator in accordance with the present embodiment;
- Fig. 4 is a view showing a cooling cycle of a reheat dehumidification operation in the case of setting a temperature of a compressor discharge gas similar to that of a cooling operation time;
- Fig. 5 is a view showing a cooling cycle of the reheat dehumidification operation in the case of setting the temperature of the compressor discharge gas lower than that of the cooling operation time; and
- Fig. 6 is a view showing a concept of a set value of the temperature of the compressor discharge gas.
- A description will be given below of an embodiment of an air conditioner to which the present invention is applied, with reference to Figs. 1 to 6.
- Fig. 1 is a view showing a structure of the air conditioner in accordance with the present embodiment. As shown in Fig. 1, an
air conditioner 1 is constituted by anoutdoor unit 2, anindoor unit 3, and a gasside connection piping 4 and a liquidside connection piping 5 which connect theoutdoor unit 2 and theindoor unit 3 annularly. - The
outdoor unit 2 is formed by connecting a four-way valve 6, anaccumulator 7, acompressor 8, an outdoor heat exchanger 9 and anoutdoor 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 thecompressor 8, and the outdoor heat exchanger 9 is provided with anoutdoor blower 13 blowing an outdoor air to the outdoor heat exchanger 9. - The
indoor unit 3 is formed by connecting a firstindoor heat exchanger 15, acheck valve 16, anindoor expansion valve 17 and a secondindoor heat exchanger 18 by a piping circulating the cooling medium. Further, there is provided apiping 19 bypassing the first heat exchanger and thecheck valve 16, and thepiping 19 is provided with an indoorelectromagnetic valve 20 opening and closing thepiping 19. Further, the secondindoor heat exchanger 18 is provided with ablower 21 blowing an indoor air to the secondindoor heat exchanger 18 and the firstindoor heat exchanger 15 in this order. Further, an indoorair temperature sensor 25 and an indoorair humidity sensor 26 are provided on an indoor air suction side of the secondindoor heat exchanger 18, and an indoor blow-offair temperature sensor 27 is provided on an indoor air blow-off side of the firstindoor heat exchanger 15. - Next, a description will be given of details of the
accumulator 7 with reference to Figs. 2 and 3. Fig. 2 is a view showing a structure of theaccumulator 7. Theaccumulator 7 is constituted by acontainer 30, and anintroduction pipe 31 and a U-shapedpipe 32 provided within thecontainer 30. The U-shapedpipe 32 is provided with anoil return hole 33 in a lower portion, and with apressure equalization hole 34 in an upper portion. - If the refrigerant and a lubricating oil are returned to an inner side of the
container 30 from the four-way valve 6 through theintroduction pipe 31 while circulating the cooling cycle, the lubricating oil dissolving in the refrigerant is temporarily reserved in a lower portion of thecontainer 30. The U-shapedpipe 32 lets out the gas refrigerant in the upper portion and sucks the lubricating oil in the lower portion from theoil return hole 33 so as to return to a suction side of thecompressor 8. Fig. 3 is a view showing an example of an operation characteristic of theaccumulator 7. As shown in Fig. 3, 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. In other words, in the case that the quality of the refrigerant in an inlet of theaccumulator 7 is low, the liquid refrigerant reserved within theaccumulator 7 is increased. On the contrary, in the case that the quality is high, the liquid refrigerant reserved in theaccumulator 7 is reduced. As mentioned above, an amount of the refrigerant reserved within theaccumulator 7 is determined in accordance with a state of the refrigerant in the inlet of theaccumulator 7. - Next, a description will be given of an operation motion at a time of the cooling operation. At a time of the cooling operation, the four-
way valve 6 is switched as shown by a solid line in Fig. 1, thereby connecting the discharge side of thecompressor 8 and the outdoor heat exchanger 9, and theaccumulator 7 and the gasside connection piping 4. Accordingly, the high-pressure gas refrigerant discharged from thecompressor 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 theoutdoor expansion valve 10 so as to form low-pressure two phases passes through the liquidside connection piping 5 and is fed to theindoor unit 3. In theindoor unit 3, the refrigerant passes through the opened indoorelectromagnetic valve 20 and the fully-openedindoor expansion valve 17, and flows into the secondindoor heat exchanger 18. The refrigerant cooling and dehumidifying the indoor air in the secondindoor heat exchanger 18 so as to be evaporated passes through the gas side connection piping 4, is again returned to theoutdoor unit 2, is sucked to thecompressor 8 from theaccumulator 7 via the four-way valve 6, and makes a circuit of the cycle. - In this case, a part of the refrigerant flows into the first
indoor heat exchanger 15, however, since the refrigerant is depressurized by theoutdoor 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. - Next, a description will be given of a motion at a time of the reheat dehumidification operation. At a time of the reheat dehumidification operation, 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 thecompressor 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. Theoutdoor expansion valve 10 is fully opened, the gas refrigerant is hardly depressurized and is fed to theindoor unit 3. Since the indoorelectromagnetic valve 20 is closed in theindoor unit 3, the refrigerant flows into the firstindoor heat exchanger 15. The refrigerant circulating the firstindoor heat exchanger 15 is heat exchanged with the indoor air cooled in the secondindoor heat exchanger 18 so as to be cooled. In other words, the firstindoor heat exchanger 15 is operated as a reheat coil heating the indoor air. The refrigerant condensed or excessively cooled by the firstindoor heat exchanger 15 is depressurized by theindoor expansion valve 17, and flows into the secondindoor heat exchanger 18. The refrigerant circulating in the secondindoor heat exchanger 18 is heat exchanged with the indoor air so as to be heated. In other words, the secondindoor heat exchanger 18 is operated as a cooling coil cooling and dehumidifying the indoor air. The refrigerant heated by the indoor air in the secondindoor heat exchanger 18 is evaporated so as to be returned to theoutdoor unit 2 via the gasside connection piping 4. In theoutdoor unit 2, the refrigerant is returned to the suction side piping of thecompressor 8 from the four-way valve 6 via theaccumulator 7, and makes a circuit of the cycle. - In this case, a description will be given of details of an operation state at a time of the reheat dehumidification operation by using a Mollier diagram in Figs. 4 and 5. 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. In this case, 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. In this case, the temperature detected by the compressor discharge gas temperature sensor 11 is controlled by the opening degree of theindoor 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. - In this case, Tdo denotes a target temperature of discharge gas at a normal time, Tc denotes a condensing temperature, Pd denotes a discharge gas pressure, and SHa denotes a normal superheat degree of discharge gas.
- In this case, the normal superheat degree of discharge gas SHa is normally set to about 25 to 40°C. Further, in the target temperature of discharge gas at the normal time Tdo, an upper limit Tdomax and a lower limit Tdomin are set as the following expression for securing a reliability of the compressor.
- Since the opening degree of the
indoor expansion valve 17 is controlled in such a manner that the quality of theaccumulator 7 comes to about 0.95, the liquid refrigerant is not reserved within theaccumulator 7 and theaccumulator 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 firstindoor 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. - On the contrary, 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. As shown in Fig. 6, the target discharge gas set temperature is shown by the following expression.
- In this case, Tdor denotes a target temperature of discharge gas at a reheat dehumidification operation, Tc denotes a condensing temperature, Pd denotes a discharge gas pressure, and SHb denotes a superheat degree of discharge gas at a reheat dehumidification operation time.
-
- In this case, 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. Further, ΔPL in Figs. 4 and 5 indicates a pressure loss in the liquid side connection piping 5 in a simulation manner.
- Since the refrigerant in the wet state is returned to the
accumulator 7 by controlling the temperature of the discharge gas low as mentioned above, the liquid refrigerant is reserved within theaccumulator 7 on the basis of the characteristic of theaccumulator 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. - Further, it is possible to change the 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-offair temperature sensor 27. In accordance with 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. - Further, it is possible to change the control target value of the discharge gas temperature on the basis of a detected value of the indoor
air humidity sensor 26. For example, in the case that the room temperature is close to a set temperature, and the indoor humidity is widely higher than a set humidity or a comfortable humidity, 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. In accordance with this control method, it is possible to execute the indoor temperature and humidity control to a comfortable humidity range. - In Fig. 1 showing the structure of the air conditioner in accordance with the present embodiment, the
check valve 16 installed within theindoor unit 3 is provided for the purpose of preventing the refrigerant from flowing into the firstindoor 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 indoorelectromagnetic valve 20 by fully opening theindoor expansion valve 17 at a time of the heating operation, and achieving the depressurizing effect by theoutdoor expansion valve 10. In this case, it is possible to omit a circulation preventing means such as thecheck valve 16 or the like.
Claims (3)
- An air conditioner (1) in which a cooling cycle is formed by arranging an outdoor unit (2) provided with an accumulator (7), a compressor (8), a four-way valve (6) and an outdoor heat exchanger (9), and an indoor unit (3) provided with a first indoor heat exchanger (15), a check valve (16), an indoor expansion valve (17), a second indoor heat exchanger (18) and an indoor electromagnetic valve (20) formed in a piping (19) bypassing the first indoor heat exchanger (15) and the check valve (16), in a piping circulating a refrigerant,
characterized in that said air conditioner further comprises a control means for lowering a temperature of the refrigerant on a discharge side of the compressor (8) at a set temperature, on the basis of a signal generated by closing of the indoor electromagnetic valve (20), at a time of a reheat dehumidification operation. - An air conditioner (1) in which a cooling cycle is formed by arranging an outdoor unit (2) provided with an accumulator (7), a compressor (8), a four-way valve (6) and an outdoor heat exchanger (9), and an indoor unit (3) provided with a first indoor heat exchanger (15), a check valve (16), an indoor expansion valve (17), a second indoor heat exchanger (18) and an indoor electromagnetic valve (20) formed in a piping (19) bypassing the first indoor heat exchanger (15) and the check valve (16), in a piping circulating a refrigerant,
characterized in that said air conditioner further comprises a control means for enlarging an opening degree of the indoor expansion valve (17) on the basis of a signal generated by closing of the indoor electromagnetic valve (20), at a time of a reheat dehumidification operation. - An air conditioner (1) in which a cooling cycle is formed by arranging an outdoor unit (2) provided with an accumulator (7), a compressor (8), a four-way valve (6), an outdoor heat exchanger (9) and an outdoor expansion valve (10), and an indoor unit (3) provided with a first indoor heat exchanger (15), a check valve (16), an indoor expansion valve (17), a second indoor heat exchanger (18) and an indoor electromagnetic valve (20) formed in a piping (19) bypassing the first indoor heat exchanger (15) and the check valve (16), in a piping circulating a refrigerant,
characterized in that said air conditioner further comprises a control means for controlling an opening degree of the indoor expansion valve (17) on the basis of a signal generated by closing of the indoor electromagnetic valve (20), at a time of a reheat dehumidification operation, and controlling an opening degree of the outdoor expansion valve (10) on the basis of a signal generated by opening of the indoor electromagnetic valve (17), at a time of a cooling operation.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005371785A JP4730738B2 (en) | 2005-12-26 | 2005-12-26 | Air conditioner |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1801520A1 true EP1801520A1 (en) | 2007-06-27 |
EP1801520B1 EP1801520B1 (en) | 2009-11-11 |
Family
ID=37846368
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06256498A Expired - Fee Related EP1801520B1 (en) | 2005-12-26 | 2006-12-21 | Air conditioning system |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1801520B1 (en) |
JP (1) | JP4730738B2 (en) |
CN (1) | CN1991276B (en) |
DE (1) | DE602006010312D1 (en) |
ES (1) | ES2335302T3 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2881685A4 (en) * | 2012-07-31 | 2016-03-23 | Daikin Ind Ltd | Refrigeration device for container |
WO2016025498A3 (en) * | 2014-08-11 | 2016-05-19 | Wong Lee Wa | Water-cooled split air conditioning system |
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 (en) * | 2020-03-13 | 2021-09-15 | Air Supplies Holland B.V. | Climate control unit and system comprising the same |
Families Citing this family (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011048724A1 (en) * | 2009-10-22 | 2011-04-28 | ダイキン工業株式会社 | Flow path switching valve, and air conditioner provided therewith |
CN102645056A (en) * | 2011-02-16 | 2012-08-22 | 广东美芝制冷设备有限公司 | Refrigerating device for flammable refrigerant |
JP6000053B2 (en) * | 2012-10-15 | 2016-09-28 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー(ホンコン)リミテッド | Air conditioner |
CN102927715B (en) * | 2012-10-31 | 2015-07-01 | 青岛海信日立空调系统有限公司 | Multiple-on-line heat pump air-conditioning system and method for controlling multiple-on-line heat pump air-conditioning system |
CN103017410B (en) * | 2013-01-22 | 2016-09-21 | 北京丰联奥睿科技有限公司 | A kind of heating-refrigerating heat-pipe heat-pump type combined cycle system |
CN105987430A (en) * | 2015-02-05 | 2016-10-05 | 佛山市禾才科技服务有限公司 | Household air conditioner and anti-condensation method thereof |
CN105115181B (en) * | 2015-07-21 | 2018-06-26 | 上海海立电器有限公司 | A kind of air-conditioning system |
CN106885403B (en) * | 2015-12-16 | 2018-11-02 | 上海海立电器有限公司 | The air-conditioning system of sensible heat latent heat separation control |
CN106885387A (en) * | 2015-12-16 | 2017-06-23 | 上海日立电器有限公司 | A kind of air-conditioning system |
CN106885388B (en) * | 2015-12-16 | 2018-07-27 | 上海海立电器有限公司 | A kind of air-conditioning system |
CN106885402B (en) * | 2015-12-16 | 2019-01-29 | 上海海立电器有限公司 | The air-conditioning system of sensible heat latent heat separation control |
CN112771320B (en) * | 2018-09-25 | 2022-08-02 | 东芝开利株式会社 | Air conditioner |
CN109855184B (en) * | 2019-01-23 | 2020-12-25 | 青岛海尔空调器有限总公司 | Air conditioner and dehumidification control method thereof |
CN110207330B (en) * | 2019-06-04 | 2021-05-04 | 广东美的暖通设备有限公司 | Air conditioner and control method and device thereof |
CN112797657A (en) * | 2019-10-28 | 2021-05-14 | 广东美的制冷设备有限公司 | Air conditioner and control method thereof |
CN114761107A (en) * | 2019-12-12 | 2022-07-15 | 三菱电机株式会社 | Dehumidifying device |
CN114046612B (en) * | 2021-11-02 | 2023-05-26 | 南京天加环境科技有限公司 | Air conditioner/floor heating/floor cooling multi-system with double evaporating temperatures |
JP7112787B1 (en) * | 2021-12-02 | 2022-08-04 | 株式会社Fhアライアンス | air conditioning ventilation system |
CN114263991B (en) * | 2021-12-03 | 2024-01-30 | 雅凯热能技术(江苏)有限公司 | Fresh air dehumidification system |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH07294060A (en) * | 1994-04-28 | 1995-11-10 | Sanyo Electric Co Ltd | Air conditioner |
JP2000274879A (en) * | 1999-03-25 | 2000-10-06 | Mitsubishi Electric Corp | Air conditioner |
JP2003262429A (en) * | 2002-03-06 | 2003-09-19 | Mitsubishi Electric Corp | Air conditioner and method of operating it |
JP2004293941A (en) * | 2003-03-27 | 2004-10-21 | Mitsubishi Electric Corp | Air conditioner and operation control method for air conditioner |
JP2005283058A (en) * | 2004-03-31 | 2005-10-13 | Hitachi Ltd | Reheating dehumidifying type air conditioner |
JP2006194525A (en) * | 2005-01-14 | 2006-07-27 | Hitachi Ltd | Multi-chamber type air conditioner |
JP2006200869A (en) * | 2005-01-24 | 2006-08-03 | Hitachi Ltd | Air conditioner |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB8721986D0 (en) * | 1987-09-18 | 1987-10-28 | Ici Plc | Pyridine derivative |
JPH01106865U (en) * | 1988-01-12 | 1989-07-19 | ||
JPH0618074A (en) * | 1992-07-01 | 1994-01-25 | Fujitsu General Ltd | Controlling method for air conditioner |
JP2002107000A (en) * | 2000-09-29 | 2002-04-10 | Fujitsu General Ltd | Air conditioner |
JP4258117B2 (en) * | 2000-09-29 | 2009-04-30 | 三菱電機株式会社 | Air conditioner |
JP2005133976A (en) * | 2003-10-28 | 2005-05-26 | Hitachi Ltd | Air-conditioner |
-
2005
- 2005-12-26 JP JP2005371785A patent/JP4730738B2/en not_active Expired - Fee Related
-
2006
- 2006-12-21 EP EP06256498A patent/EP1801520B1/en not_active Expired - Fee Related
- 2006-12-21 DE DE602006010312T patent/DE602006010312D1/en active Active
- 2006-12-21 ES ES06256498T patent/ES2335302T3/en active Active
- 2006-12-26 CN CN2006101725028A patent/CN1991276B/en not_active Expired - Fee Related
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH07294060A (en) * | 1994-04-28 | 1995-11-10 | Sanyo Electric Co Ltd | Air conditioner |
JP2000274879A (en) * | 1999-03-25 | 2000-10-06 | Mitsubishi Electric Corp | Air conditioner |
JP2003262429A (en) * | 2002-03-06 | 2003-09-19 | Mitsubishi Electric Corp | Air conditioner and method of operating it |
JP2004293941A (en) * | 2003-03-27 | 2004-10-21 | Mitsubishi Electric Corp | Air conditioner and operation control method for air conditioner |
JP2005283058A (en) * | 2004-03-31 | 2005-10-13 | Hitachi Ltd | Reheating dehumidifying type air conditioner |
JP2006194525A (en) * | 2005-01-14 | 2006-07-27 | Hitachi Ltd | Multi-chamber type air conditioner |
JP2006200869A (en) * | 2005-01-24 | 2006-08-03 | Hitachi Ltd | Air conditioner |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2881685A4 (en) * | 2012-07-31 | 2016-03-23 | Daikin Ind Ltd | Refrigeration device for container |
US9718612B2 (en) | 2012-07-31 | 2017-08-01 | Daikin Industries, Ltd. | Refrigeration device for container |
WO2016025498A3 (en) * | 2014-08-11 | 2016-05-19 | Wong Lee Wa | Water-cooled split air conditioning system |
US9933170B2 (en) | 2014-08-11 | 2018-04-03 | Lee Wa Wong | Water-cooled split air conditioning system |
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 |
US10345003B2 (en) * | 2016-05-02 | 2019-07-09 | Lee Wa Wong | Split-type air conditioning and heat pump system with energy efficient arrangement |
EP3879209A1 (en) * | 2020-03-13 | 2021-09-15 | Air Supplies Holland B.V. | Climate control unit and system comprising the same |
NL2025130B1 (en) * | 2020-03-13 | 2021-10-19 | Air Supplies Holland B V | Climate control unit and system comprising the same |
US11959680B2 (en) | 2020-03-13 | 2024-04-16 | Air Supplies Holland B.V. | Climate control unit for controlling air temperature and humidity and system comprising the same |
Also Published As
Publication number | Publication date |
---|---|
ES2335302T3 (en) | 2010-03-24 |
DE602006010312D1 (en) | 2009-12-24 |
EP1801520B1 (en) | 2009-11-11 |
JP2007170769A (en) | 2007-07-05 |
CN1991276A (en) | 2007-07-04 |
CN1991276B (en) | 2010-09-08 |
JP4730738B2 (en) | 2011-07-20 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1801520B1 (en) | Air conditioning system | |
JP3925545B2 (en) | Refrigeration equipment | |
JP4931848B2 (en) | Heat pump type outdoor unit for hot water supply | |
AU2004267299B2 (en) | Refrigeration system | |
KR101479458B1 (en) | Refrigeration device | |
US10955160B2 (en) | Air conditioner including a plurality of utilization units connected in parallel to a heat source unit | |
WO2018185841A1 (en) | Refrigeration cycle device | |
JP4668021B2 (en) | Air conditioner | |
WO2021085529A1 (en) | Refrigerant system | |
EP3657097B1 (en) | Freezer | |
JP4462436B2 (en) | Refrigeration equipment | |
JP2007232265A (en) | Refrigeration unit | |
JP4599190B2 (en) | Flow rate adjusting device and air conditioner | |
JP5213372B2 (en) | Air conditioner | |
CN110709648B (en) | Air conditioner | |
GB2533042A (en) | Air conditioner | |
JP3334222B2 (en) | Air conditioner | |
KR20060070885A (en) | Air conditioner | |
JP6404539B2 (en) | Air conditioner | |
JP4176677B2 (en) | Air conditioner | |
KR100696712B1 (en) | System and method for protecting compressor of multi air-conditioner | |
KR20080084482A (en) | Controlling method for air conditioner | |
KR20070031653A (en) | Process for preventing rising of pressure in multi type air conditioner | |
JP3059886B2 (en) | Refrigeration equipment | |
JP3945523B2 (en) | Refrigeration equipment |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20070110 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA HR MK YU |
|
AKX | Designation fees paid |
Designated state(s): DE ES FR GB |
|
17Q | First examination report despatched |
Effective date: 20080520 |
|
R17C | First examination report despatched (corrected) |
Effective date: 20080609 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE ES FR GB |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REF | Corresponds to: |
Ref document number: 602006010312 Country of ref document: DE Date of ref document: 20091224 Kind code of ref document: P |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2335302 Country of ref document: ES Kind code of ref document: T3 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20100812 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 10 |
|
REG | Reference to a national code |
Ref legal event code: R082 Country of ref document: DE Ref country code: DE Ref legal event code: R082 Ref document number: 602006010312 Country of ref document: DE Representative=s name: MERH-IP MATIAS ERNY REICHL HOFFMANN PATENTANWA, DE Ref country code: DE Ref document number: 602006010312 Representative=s name: PATENTANWAELTE STREHL, SCHUEBEL-HOPF & PARTNER, DE Ref country code: DE Ref legal event code: R082 Ref document number: 602006010312 Country of ref document: DE Representative=s name: STREHL SCHUEBEL-HOPF & PARTNER MBB PATENTANWAE, DE Ref country code: DE Ref legal event code: R081 Ref document number: 602006010312 Country of ref document: DE Owner name: JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECH, HK Free format text: FORMER OWNER: HITACHI APPLIANCES, INC., TOKYO, JP Ref country code: DE Ref legal event code: R081 Ref document number: 602006010312 Country of ref document: DE Owner name: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, INC, JP Free format text: FORMER OWNER: HITACHI APPLIANCES, INC., TOKYO, JP |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: PC2A Owner name: JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECHNOLO Effective date: 20160914 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 11 |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E Free format text: REGISTERED BETWEEN 20161027 AND 20161102 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: CA Effective date: 20161104 Ref country code: FR Ref legal event code: TP Owner name: JOHNSON CONTROLS-HITACHI AIR CONDITIONINGTECHN, CN Effective date: 20161104 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 12 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: PC2A Owner name: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, INC. Effective date: 20171121 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 602006010312 Country of ref document: DE Representative=s name: MERH-IP MATIAS ERNY REICHL HOFFMANN PATENTANWA, DE Ref country code: DE Ref legal event code: R082 Ref document number: 602006010312 Country of ref document: DE Ref country code: DE Ref legal event code: R081 Ref document number: 602006010312 Country of ref document: DE Owner name: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, INC, JP Free format text: FORMER OWNER: JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECHNOLOGY (HONG KONG) LTD., HONG KONG, HK |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E Free format text: REGISTERED BETWEEN 20180111 AND 20180117 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: TP Owner name: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, INC, JP Effective date: 20180206 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 602006010312 Country of ref document: DE |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20201123 Year of fee payment: 15 Ref country code: FR Payment date: 20201120 Year of fee payment: 15 Ref country code: DE Payment date: 20201119 Year of fee payment: 15 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: ES Payment date: 20210107 Year of fee payment: 15 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 602006010312 Country of ref document: DE |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20211221 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20211221 Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20220701 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20211231 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FD2A Effective date: 20230217 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20211222 |