EP1662212A2 - Conditionneur d'air et procédé de commande de celui-ci - Google Patents

Conditionneur d'air et procédé de commande de celui-ci Download PDF

Info

Publication number
EP1662212A2
EP1662212A2 EP05025039A EP05025039A EP1662212A2 EP 1662212 A2 EP1662212 A2 EP 1662212A2 EP 05025039 A EP05025039 A EP 05025039A EP 05025039 A EP05025039 A EP 05025039A EP 1662212 A2 EP1662212 A2 EP 1662212A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
heat exchange
flow rate
indoor heat
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.)
Withdrawn
Application number
EP05025039A
Other languages
German (de)
English (en)
Other versions
EP1662212A3 (fr
Inventor
Chi Woo Song
Bong Soo Park
Ju Won Kim
Se Dong Chang
Baik Young Chung
Sai Kee Oh
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
Publication of EP1662212A2 publication Critical patent/EP1662212A2/fr
Publication of EP1662212A3 publication Critical patent/EP1662212A3/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/85—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using variable-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • 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
    • F24F3/06—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 arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the present invention relates to air conditioning systems, and more particularly, to an air conditioning system which can control a refrigerant flow rate to a heat exchanger exchanging heat with room air to be optimum; and a method for controlling the same.
  • the air conditioning system cools or heats a room by compressing, condensing, expanding, and evaporating refrigerant.
  • the air conditioning system is provided with a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger.
  • the air conditioning systems there are a cooling system in which a refrigerating cycle is operated only in one direction, to supply only cold air to the room, and a heating/cooling system in which the refrigerating cycle is operated in two directions selectively, to supply cold air or warm air to the room.
  • the air conditioning systems depending on a number of indoor units connected thereto, there are single air conditioning systems in each of which one indoor unit is connected to one outdoor unit, and multiple air conditioning systems in each of which a plurality of indoor units are connected to one outdoor unit.
  • the air conditioning system uses the compressor as a driving source for making the refrigerant to flow, and oil for lubricating the compressor.
  • the present invention is directed to an air conditioning system and a method for controlling the same that substantially obviates one or more problems due to limitations and disadvantages of the related art.
  • An object of the present invention is to provide a an air conditioning system and a method for controlling the same, which is applicable even to a case a height difference or a distance between an indoor heat exchanger, and an outdoor heat exchanger is great significantly.
  • Another object of the present invention is to provide an air conditioning system and a method for controlling the same, which enables a fine control of a room temperature.
  • an air conditioning system includes an outdoor heat exchange part including a compressor for compressing refrigerant, an outdoor heat exchanger for making the refrigerant to heat exchange with outdoor air, and an expansion device for expanding the refrigerant, an indoor heat exchange part including a pump for making refrigerant in a flow path independent from the outdoor heat exchange part to flow, a indoor heat exchanger for making the refrigerant heat exchange with room air, and a flow rate control device for controlling a flow rate of the refrigerant, and a hybrid heat exchange part for making the outdoor heat exchange part and - the indoor heat exchange part, which are independent from each other, to heat exchange with - each other.
  • the flow rate control device may include a temperature sensor for measuring temperatures of refrigerant flowing in the indoor heat exchanger, a controller for determining a degree of superheat or subcooling of the refrigerant with the temperatures measured at the temperature sensor, and a flow rate control valve for controlling a refrigerant flow rate to the indoor heat exchanger according to the determination of the controller.
  • the flow rate control valve may be mounted on a refrigerant inlet end of the indoor heat exchanger.
  • the flow rate control valve may be mounted on a refrigerant outlet end of the indoor heat exchanger.
  • the temperature sensors are mounted on the refrigerant inlet end, the refrigerant outlet end, and a predetermined portion between the refrigerant inlet end and the refrigerant outlet end of the indoor heat exchanger.
  • the predetermined portion between the refrigerant inlet end and the refrigerant outlet end of the indoor heat exchanger is a section in which the refrigerant flowing in the indoor heat exchanger is in a saturated state.
  • a method for controlling an air conditioning system includes the steps of setting an ideal degree of superheat, and an ideal degree of subcooling at a controller, comparing the degree of superheat or subcooling set thus with a degree of superheat or subcooling measured thus, and controlling a flow rate of refrigerant flowing in an indoor heat exchanger according to a result of the step of comparing the degree of superheat or subcooling set thus with a degree of superheat or subcooling measured thus.
  • the degree of superheat or subcooling is a difference between a temperature of the refrigerant at the refrigerant outlet of the indoor heat exchanger and a saturation temperature of the refrigerant flowing in the indoor heat exchanger.
  • the step of controlling a flow rate of refrigerant flowing in an indoor heat exchanger includes the steps of increasing the flow rate of the refrigerant flowing in the indoor heat exchanger if the degree of superheat measured is higher than the degree of superheat set, and decreasing the flow rate of the refrigerant flowing in the indoor heat exchanger if the degree of superheat measured is lower than the degree of superheat set.
  • the step of controlling a flow rate of refrigerant flowing in an indoor heat exchanger includes the steps of increasing the flow rate of the refrigerant flowing in the indoor heat exchanger if the degree of subcooling measured is higher than the degree of subcooling set, and decreasing the flow rate of the refrigerant flowing in the indoor heat exchanger if the degree of subcooling measured is lower than the degree of subcooling set.
  • an air conditioning system in another aspect of the present invention, includes at least one first heat exchanger for heat exchange with room air, a second heat exchanger for transferring heat from the first heat exchanger to an outside of a refrigerant flow path having the first heat exchanger mounted therein, a pump for circulating the refrigerant to the first heat exchanger and the second heat exchanger, a third heat exchanger in a flow path independent both from the first heat exchanger and the second heat exchanger for heat exchange with the second heat exchanger, a fourth heat exchanger for transferring heat from the third heat exchanger to outdoor air, a compressor for compressing the refrigerant and circulating the refrigerant to the third heat exchanger and the fourth heat exchanger, a plurality of temperature sensors for measuring temperatures of the refrigerant flowing in the first heat exchanger, at least one flow rate control valve for controlling a flow rate of the refrigerant flowing in the first heat exchanger according to temperatures measured at the temperature sensors.
  • the temperature sensors are provided at a refrigerant inlet end and a refrigerant outlet end of the first heat exchanger, and at a predetermined portion between the refrigerant inlet end and the refrigerant outlet end, respectively.
  • the temperature sensor provided at a predetermined portion between the refrigerant inlet end and the refrigerant outlet end measures a saturation temperature of the refrigerant flowing in the first heat exchanger.
  • the flow rate control valves are provided to a refrigerant inlet end and a refrigerant outlet end of the indoor heat exchanger. At the time of controlling a refrigerant flow rate, an opening of the flow rate control valve at the refrigerant inlet end of the first heat exchanger is adjusted, and an opening of the flow rate control valve at the refrigerant outlet end is opened to the maximum.
  • FIG. 1 illustrates a diagram of an air conditioning system in accordance with a preferred embodiment of the present invention, schematically;
  • FIG 2 illustrates a diagram of an indoor heat exchange part in the air conditioning system in FIG. 1, schematically;
  • FIG. 3 illustrates a flow chart showing the steps of a method for controlling an air conditioning system in accordance with a preferred embodiment of the present invention
  • FIG. 4 illustrates a P-h diagram showing a state change of refrigerant in cooling operation of the air conditioning system in FIG 1;
  • FIG. 5 illustrates a P-h diagram showing a state change of refrigerant in heating operation of the air conditioning system in FIG. 1.
  • FIGS. 1 and 2 illustrate diagrams each showing an air conditioning system in accordance with a preferred embodiment of the present invention.
  • the air conditioning system includes an indoor heat exchange part 10 for heat exchange with room air, an outdoor heat exchange-part 20 for heat exchange with outdoor air, and a hybrid heat exchanger 30 for making refrigerant in the indoor heat exchange part 10 and refrigerant in the outdoor heat exchange part 20 to heat exchange with each other.
  • the indoor heat exchange part 10 includes a first heat exchanger 14 for heat exchange with the room air, a pump 12 for circulating the refrigerant to the first heat exchanger 14, and a flow rate control device for controlling a flow rate of the refrigerant to the first heat exchanger 14.
  • the outdoor heat exchange part 20 has a refrigerant flow path independent from the indoor heat exchange part 10, and includes a fourth heat exchanger 24 for making the refrigerant to heat exchange with outdoor air, and a compressor 22 for compressing, and circulating the refrigerant to the fourth heat exchanger 24.
  • the outdoor heat exchange part 20 includes an expansion device 28 for expanding the refrigerant to drop a pressure of the refrigerant, and a flow controller 23 for controlling a flow direction of the refrigerant, additionally.
  • the outdoor heat exchange part 20 may have many variations as far as the part can transfer heat to the refrigerant in the indoor heat exchange part 10.
  • the part may use warm water or waste heat as a heat source.
  • the hybrid heat exchange part 30 is configured such that the indoor heat exchange part 10 and the outdoor heat exchange part 20 having refrigerant flow paths independent from each other can heat exchange with each other, without mix of the refrigerant between the indoor heat exchange part 10 and the outdoor heat exchange part 20.
  • the hybrid heat exchange part 30 includes a second heat exchanger 16 in a flow path of the indoor heat exchange part 10, and a third heat exchanger 26 in a flow path of the outdoor heat exchange part 20 for heat exchange with the second heat exchanger 16.
  • the second heat exchanger 16 exchanges heat with the third heat exchanger 26 so that the indoor heat exchange part 10 and the outdoor heat exchange part 20 make heat exchange.
  • the second heat exchanger 16 forms a refrigerant circulating flow path as a portion of the indoor heat exchange part 10
  • the third heat exchanger 26 forms a refrigerant circulating flow path as a portion of the outdoor heat exchange part 20.
  • the outdoor heat exchange part 20 forms a refrigerant flow path with the third heat exchanger 26, the fourth heat exchanger 24, the compressor 22, and the expansion device 28, and the indoor heat exchange part 10 forms a refrigerant flow path with the first heat exchanger 14, the second heat exchanger 16, the pump 12, and a flow rate control device.
  • the second heat exchanger 16 and the third heat exchanger 26 may have many variations. That is, the second heat exchanger 16 and the third heat exchanger 26 may be constructed of heat dissipation plates, or refrigerant tubes.
  • the hybrid heat exchange part 30 is configured to enable the second heat exchanger 16, and the third heat exchanger 26 in the outdoor heat exchange part to make thermal contact with each other.
  • the hybrid heat exchange part 30 may be constructed of a stack of a plurality of plate type heat conductive fins having the second heat exchanger 16 and the third heat exchanger 26 placed therebetween so as to be thermally in contact with each other.
  • the hybrid heat exchange part 30 may has a structure in which the second heat exchanger and the third heat exchanger heat exchange with each other through a heat conductive fluid.
  • the second heat exchanger 16 and the third heat exchanger 26 are configured to have a form of a double tube.
  • the indoor heat exchange part 10 has a flow path independent from the outdoor heat exchange part 20, and includes a first heat exchanger 14, a pump 12, a flow rate control device, and a second heat exchanger 16 of the hybrid heat exchange part 30.
  • the indoor heat exchange part 10 has a pump 12 instead of a compressor as a driving source for making the refrigerant to flow, and has no separate expansion device for expanding the refrigerant. Owing to this, the indoor heat exchange part 10 requires no oil for operation of the compressor, and consequently, no operation for recovery of the refrigerant is required.
  • the pump 12 includes a pumping motor (not shown) and an impeller (not shown). Moreover, it is preferable that liquid refrigerant is supplied to the pump 12, for which, though not shown, a separate refrigerant storage tank may be provided between the hybrid heat exchange part 30 and the pump 12, for supplying refrigerant to the pump 12.
  • an inverter motor is employed as the pumping motor for controlling a rotation speed of the motor, to control a flow rate of the refrigerant.
  • a constant speed motor having a constant rotation speed may be used.
  • the first heat exchanger 14 is mounted in an indoor unit 15 installed in a room which requires cooling/heating. That is, the first heat exchanger 14 is an indoor heat exchanger for heat exchange with room air to cool or heat the room.
  • the flow rate control device includes a plurality of temperature sensors 17a, 17b, and 17c for measuring temperatures of the refrigerant flowing through the indoor heat exchanger 14, a controller (not shown) for determining a degree of superheat or subcooling of the refrigerant in the indoor heat exchanger 14 with reference to the temperatures measured at the temperature sensors 17a, 17b, and 17c, and flow rate control valves 13a, and 13b for controlling a flow rate of the refrigerant to the indoor heat exchanger 14 according to the determination of the controller.
  • the flow rate control valve 13a, and 13b are solenoid valves each for controlling an opening of a flow passage with an electromagnetic force.
  • the flow rate control valves 13a, and 13b there can be a variety of the flow rate control valves 13a, and 13b as far as the valve can control the opening of the flow passage.
  • the flow rate control valve 13a, and 13b are mounted on opposite ends of the indoor heat exchanger 14 into which the refrigerant flows in/out, the mounting positions of the flow rate control valve 13a, and 13b are not limited to this, but the flow rate control valve 13a, and 13b may be mounted only one of the opposite ends.
  • the temperature sensors 17a, 17b, and 17c are mounted on an inlet 17a through which the refrigerant is introduced into the indoor heat exchanger 14, an outlet 17b through which the refrigerant is discharged from the indoor heat exchanger 14, and a predetermined portion 17c between the inlet 17a, and the outlet 17b, respectively.
  • At least three temperature sensors 17a, 17b, and 17c are mounted on every indoor heat exchanger 14 mounted on the indoor unit 15.
  • the temperature sensor 17c mounted on the predetermined portion between the inlet 17a, and the outlet 17b is mounted on one point where refrigerant in the indoor heat exchanger 14 is in a saturated state, so that the temperature sensor 17c can measure a temperature at a saturated state of the refrigerant.
  • the temperature at a saturated state is a temperature when there is no temperature change even if a phase of the refrigerant changes following heat exchange of the refrigerant.
  • the controller has an ideal degree of superheat and an ideal degree of subcooling preset thereto at a pressure of the refrigerant, and an actual degree of superheat and an actual degree of subcooling are calculated with temperatures measured at respective portions of the indoor heat exchanger 14 with the temperature sensors 17a, 17b, and 17c.
  • the degrees of superheat or subcooling is a temperature difference measured between the temperature sensor 17b at the outlet and the temperature sensor 17c at the middle of the indoor heat exchanger 14.
  • the degree of superheat is a temperature difference at the time of cooling
  • the degree of subcooling is a temperature difference at the time of heating.
  • FIG 3 illustrates a flow chart showing the steps of a method for controlling an air conditioning system in accordance with a preferred embodiment of the present invention.
  • the method for controlling an air conditioning system includes the steps of setting an ideal degree of subcooling and an ideal degree of superheat at a controller (S1), measuring the degree of subcooling or superheat of the refrigerant flowing in an indoor heat exchanger (S2), comparing the degree of subcooling or superheat set thus to the degree of subcooling or superheat measured (S3), and controlling a flow rate of the refrigerant flowing in the indoor heat exchanger according to a result in the step S3 in which the degree of subcooling or superheat set thus is compared to the degree of subcooling or superheat measured.
  • the degree of superheat or the degree of subcooling is a difference between a temperature of the refrigerant at the outlet of the indoor heat exchanger 14, and a temperature of the refrigerant at a saturation state of the refrigerant flowing in the indoor heat exchanger 14.
  • the temperatures of the refrigerant are measured with a plurality of temperature sensors 17a, 17b, and 17c mounted on the indoor heat exchanger 14.
  • a setting step (S1) is performed, in which an ideal degree of superheat and an ideal degree of subcooling at the time of operation of the indoor heat exchanger are set at the controller.
  • the ideal degree of superheat and the ideal degree of subcooling vary with a pressure of the refrigerant and an environmental temperature.
  • a measuring step (S2) is performed, in which an actual degree of superheat or an actual degree of subcooling of the refrigerant flowing in the indoor heat exchanger 14 is measured.
  • the temperatures of the refrigerant are measured with the temperature sensors 17a, 17b, and 17c mounted on the indoor heat exchanger 14.
  • the controller can calculate the degree of superheat or the degree of subcooling with the temperatures measured at the temperature sensors 17a, 17b, and 17c.
  • a determination step (S3) is performed, in which a measured degree of superheat or subcooling is compared to a preset degree of superheat or subcooling.
  • the determination step (S3) it is determined whether the measured degree of superheat or subcooling converges to the preset degree of superheat or subcooling, or not; or if not, which one has how much difference.
  • an adjusting step (S4) is performed, in which a flow rate of the refrigerant flowing in the indoor heat exchanger 14 is adjusted according to a result of determination in the determination step (S3).
  • the flow rate of the refrigerant is adjusted by controlling the flow rate control valve 13a, and 13b at opposite ends of the indoor heat exchange part 10.
  • opening of the flow rate control valves 13a, and 13b are adjusted, to increase a flow rate of the refrigerant flowing in the indoor heat exchanger 14 (S4a), and if the degree of superheat measured is lower than the preset degree of superheat at the time of room cooling, opening of the flow rate control valves 13a, and 13b are adjusted, to decrease a flow rate of the refrigerant flowing in the indoor heat exchanger 14 (S4c).
  • opening of the flow rate control valves 13a, and 13b are adjusted, to increase a flow rate of the refrigerant flowing in the indoor heat exchanger 14 (S4a), and if the degree of subcooling measured is lower than the preset degree of subcooling at the time of room cooling, opening of the flow rate control valves 13a, and 13b are adjusted, to decrease a flow rate of the refrigerant flowing in the indoor heat exchanger 14 (S4c).
  • FIGS. 4 and 5 illustrate graphs showing variations of a pressure 'P' and enthalpy 'h' of refrigerant at the outdoor heat exchange part 20 and the indoor heat exchange part 10 at the time of room cooling and room heating of the air conditioning system, respectively.
  • the air conditioning system cools or heats the room depending on an operation.
  • the hybrid heat exchange part 30 exchanges heat between the outdoor heat exchange part 20 and the indoor heat exchange part 10.
  • the refrigerant in the outdoor heat exchange part 20 is compressed at the compressor 22, and forwarded to the flow controller 23 (A-B section).
  • the flow controller 23 changes over the refrigerant to a side of the fourth heat exchanger 24.
  • the refrigerant introduced to the fourth heat exchanger 24 is condensed as the refrigerant heat exchanges with outdoor air (B-C section).
  • the condensed refrigerant changes to a refrigerant of a low temperature and low pressure as the refrigerant passes through the expansion device 28 (C-D section).
  • the low temperature and low pressure refrigerant is introduced into the compressor 22 through the flow controller 23 (D-A section).
  • the compressor 22 serves as a driving source if the refrigerant flow.
  • the refrigerant in the indoor heat exchange part 10 is cooled down as the second heat exchanger 16 and the third heat exchanger 26 in the hybrid heat exchange part 30 exchange heat (e-a section).
  • the refrigerant cooled down thus is pumped to a side of the first heat exchanger by the pump 12 (a-b section).
  • the refrigerant is neither in a two phase state, nor at a saturated temperature.
  • the pumped refrigerant is introduced to the first heat exchanger 14 through the flow rate control valves 13a, and 13b at an inlet of the first heat exchanger 14, and discharged from the first heat exchanger 14 after heat exchanger with room air (b-c-d section).
  • the refrigerant in the indoor heat exchange part 10 reaches to a saturation temperature at which the refrigerant is involved no temperature change, but a phase change as the refrigerant heat exchanges with room air (c point).
  • the temperature sensor 17c between opposite ends of the first heat exchanger 14 measures a saturation temperature of the refrigerant
  • the temperature sensor 17b at the outlet of the first heat exchanger 14 (corresponding to 'd' point) measures a superheated temperature of the refrigerant.
  • the controller determines a difference between the saturation temperature and the superheated temperature, to derive the degree of superheat, compares the derived degree of superheat to the preset degree of superheat of the refrigerant, and adjusts opening of the flow rate control valves 13a, and 13b.
  • opening of the flow rate control valves 13a, and 13b on the first heat exchanger 14 is made greater, to increase a flow rate of the refrigerant.
  • opening of the flow rate control valves 13a, and 13b on the first heat exchanger 14 is made smaller, to decrease a flow rate of the refrigerant.
  • opening of the flow rate control valve 13a at an inlet end of the first heat exchanger 14 is made greater or smaller, and opening of the flow rate control valve 13b at an outlet end of the first heat exchanger 14 is opened to the maximum, the way of opening of the flow rate control valves 13a, and 13b is not limited to this one.
  • the flow rate of the refrigerant to the first heat exchanger 14 can be controlled to the optimum.
  • the refrigerant is discharged from the first heat exchanger 14 to the second heat exchanger 16 of the hybrid heat exchange part 30, and cooled therein again, to circulate therefrom.
  • the refrigerant After compressed at the compressor 22 in the outdoor heat exchange part 20, the refrigerant is forwarded to the flow controller 23 (A-B).
  • the flow controller 23 changes over the refrigerant to a side of the third heat exchanger 26 of the hybrid heat exchange part 30.
  • the refrigerant introduced into the hybrid heat exchange part 30 discharges heat, and condensed at the third heat exchanger 26 (B-C).
  • the condensed refrigerant is changed to refrigerant of a low pressure and a low temperature as the refrigerant passes through the expansion device 28 (C-D), introduced into the fourth heat exchanger 24, heat exchanges with outdoor air, and is introduced into the compressor through the flow controller 23 (D-A).
  • a circulation direction of the refrigerant in the outdoor heat exchange part 20 is opposite to the cooling operation.
  • the refrigerant at the indoor heat exchange part 10 has a pressure boosted by pumping of the pump 12 (a-b).
  • the pumped refrigerant is heated as the refrigerant heat exchanges at the second heat exchanger 16 of the hybrid heat exchange part 30 with the third heat exchanger 26 of the outdoor heat exchange part 20 (b-c).
  • the refrigerant heated thus is forwarded to a side of the first heat exchanger 14 by the pump 12.
  • the refrigerant introduced into the first heat exchanger 14 heat exchanges with room air to heat the room, while the refrigerant itself is condensed (c-a).
  • the temperature sensor 17c between the refrigerant inlet/outlet of the first heat exchanger 14 measures the saturation temperature of the refrigerant ('e' point), and the temperature sensor 17b at the outlet of the first heat exchanger 14 measures a superheated temperature of the refrigerant ('a' point).
  • the controller derives the degree of superheat as a difference between the saturation temperature and the superheated temperature, compares the derived degree of superheat to the preset degree of superheat of the refrigerant, and adjusts opening of the flow rate control valves 13a, and 13b.
  • opening of the flow rate control valves 13a on the refrigerant inlet of the first heat exchanger 14 is made greater, to increase the flow rate of the refrigerant to the first heat exchanger 14.
  • opening of the flow rate control valves 13a is made smaller, to decrease a flow rate of the refrigerant. According to this, the flow rate to the first heat exchanger 14 is adjusted.
  • the refrigerant having room air heat exchanged therewith at the first heat exchanger 14 makes circulation in which the refrigerant is introduced into, and heated again at the second heat exchanger 16 of the hybrid heat exchange part 30.
  • the air conditioning system and the method for controlling the same of the present invention have the following advantages.
  • the supply of refrigerant to the indoor heat exchange part by using a pump as a driving source that requires no oil permits to dispense with an oil recovery operation at the indoor heat exchange part.
  • the air conditioning system can be installed on a multistory building without limitation of a height of the building as far as a capacity of the pump permits. Moreover, even if a refrigerant pipe is long, the air conditioning system is applicable even to a system with a refrigerant pipe line longer than the related art as far as the capacity of the pump permits.
  • the compressor and the expansion device of the outdoor heat exchange part may be placed outside of a room mounted on the outdoor unit. Therefore, even if the compressor and the expansion device generate noise, the noise can not reach to the user.
  • a length of the refrigerant pipeline of the outdoor heat exchange part can be shortened significantly regardless of a height of the building. According to this, a refrigerant recovery ratio can be improved significantly, to prevent the compressor suffering from damage caused by a poor refrigerant recovery ratio.
  • the saturation temperature of the refrigerant can be measured at the first heat exchanger in the indoor heat exchange part, control of the refrigerant flow rate to the first heat exchanger can be optimized.
  • the optimum control of the refrigerant flow rate from the first heat exchanger permits fine control of the room temperature.
  • the no provision of the compressor and the expansion device to the indoor heat exchange part to be installed in a room permits simple structure of the indoor heat exchange part, which enables to reduce price of the indoor unit.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP05025039A 2004-11-23 2005-11-16 Conditionneur d'air et procédé de commande de celui-ci Withdrawn EP1662212A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020040096315A KR100758902B1 (ko) 2004-11-23 2004-11-23 멀티 공기조화 시스템 및 그 제어방법

Publications (2)

Publication Number Publication Date
EP1662212A2 true EP1662212A2 (fr) 2006-05-31
EP1662212A3 EP1662212A3 (fr) 2006-09-06

Family

ID=35840122

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05025039A Withdrawn EP1662212A3 (fr) 2004-11-23 2005-11-16 Conditionneur d'air et procédé de commande de celui-ci

Country Status (4)

Country Link
US (1) US20060107683A1 (fr)
EP (1) EP1662212A3 (fr)
KR (1) KR100758902B1 (fr)
CN (1) CN1779391A (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009009164A1 (fr) * 2007-07-11 2009-01-15 Liebert Corporation Procédé et appareil permettant d'égaliser un système de frigorigène pompé
WO2010010557A1 (fr) * 2008-07-23 2010-01-28 Joual Sarhan Unité de division de conditionneur d'air
EP2435883A1 (fr) * 2009-05-28 2012-04-04 American Power Conversion Corporation Systèmes et procédés de commande de la dynamique de charge dans un système de refroidissement par fluide frigorigène pompé
EP2667106A1 (fr) * 2012-05-22 2013-11-27 Compagnie Industrielle D'Applications Thermiques Kit et méthode de mise en oeuvre d'une installation de régulation de température pour un bâtiment
FR2995389A1 (fr) * 2012-09-13 2014-03-14 Alstom Transport Sa Dispositif de climatisation d'air, notamment pour un vehicule ferroviaire

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5125124B2 (ja) * 2007-01-31 2013-01-23 ダイキン工業株式会社 冷凍装置
US10775054B2 (en) 2009-03-13 2020-09-15 Treau, Inc. Modular air conditioning system
EP2431675B1 (fr) 2009-05-12 2019-09-11 Mitsubishi Electric Corporation Ventilateur
US8452459B2 (en) * 2009-08-31 2013-05-28 Fisher-Rosemount Systems, Inc. Heat exchange network heat recovery optimization in a process plant
JP5328933B2 (ja) * 2009-11-25 2013-10-30 三菱電機株式会社 空気調和装置
WO2012032580A1 (fr) * 2010-09-10 2012-03-15 三菱電機株式会社 Dispositif de climatisation
KR101294082B1 (ko) * 2011-11-24 2013-08-08 현대자동차주식회사 Ｌｐｉ차량용 열교환기
US9915453B2 (en) * 2012-02-07 2018-03-13 Systecon, Inc. Indirect evaporative cooling system with supplemental chiller that can be bypassed
CN102607146B (zh) * 2012-04-06 2014-09-10 谭仲禧 一种中央空调系统及其控制方法
CN102620494B (zh) * 2012-05-08 2014-03-12 程有凯 自动复叠制冷热力膨胀阀过热度的控制方法
CN104791941B (zh) * 2014-01-21 2017-11-10 广东美的暖通设备有限公司 空调系统及其控制方法、空调系统的室外机
WO2016187598A1 (fr) 2015-05-20 2016-11-24 Other Lab, Llc Système d'échangeur de chaleur à membrane et procédé
US10739024B2 (en) 2017-01-11 2020-08-11 Semco Llc Air conditioning system and method with chiller and water
JP6834562B2 (ja) * 2017-02-13 2021-02-24 株式会社富士通ゼネラル 空気調和装置
CN107477780A (zh) * 2017-08-14 2017-12-15 珠海格力电器股份有限公司 用于调节空调室内机的蒸发温度的方法及空调
US11054194B2 (en) 2017-10-10 2021-07-06 Other Lab, Llc Conformable heat exchanger system and method
CN108375241A (zh) * 2018-03-23 2018-08-07 中国工程物理研究院流体物理研究所 一种适用于高绝缘强度要求的精确控温冷却系统
WO2020160028A1 (fr) 2019-01-29 2020-08-06 Treau, Inc. Système et procédé d'accouplement d'échangeurs de chaleur à feuilles minces
US11498163B2 (en) 2019-09-13 2022-11-15 Treau, Inc. Window installation system and method for split-architecture air conditioning unit
KR20210096785A (ko) * 2020-01-29 2021-08-06 엘지전자 주식회사 공기조화장치 및 그 제어방법

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2779171A (en) * 1954-01-04 1957-01-29 Rca Corp Room temperature conditioner
US4067203A (en) * 1976-09-07 1978-01-10 Emerson Electric Co. Control system for maximizing the efficiency of an evaporator coil
US4644756A (en) * 1983-12-21 1987-02-24 Daikin Industries, Ltd. Multi-room type air conditioner
EP0282782A2 (fr) * 1987-03-20 1988-09-21 Hitachi, Ltd. Système de conditionnement d'air pour plusieurs chambres et procédé pour sa commande
DE4315924A1 (de) * 1993-05-12 1994-11-17 Forschungszentrum Fuer Kaeltet Kälteträger für Kältemaschinen oder Wärmepumpen
EP0675331A2 (fr) * 1994-03-30 1995-10-04 Kabushiki Kaisha Toshiba Système de conditionnement d'air avec un échangeur de chaleur intermédiaire intégré dans lequel deux sortes différentes de réfrigérants sont mises en circulation
EP0887599A1 (fr) * 1996-12-27 1998-12-30 Daikin Industries, Limited Appareil de refrigeration et son procede de fabrication
JPH1123079A (ja) * 1997-06-27 1999-01-26 Mitsubishi Heavy Ind Ltd 冷凍装置
JPH11201560A (ja) * 1998-01-08 1999-07-30 Denso Corp 超臨界冷凍サイクル

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3478534A (en) * 1967-08-11 1969-11-18 Controls Co Of America Thermistor controlled refrigeration expansion valve
US4149389A (en) * 1978-03-06 1979-04-17 The Trane Company Heat pump system selectively operable in a cascade mode and method of operation
US4576011A (en) * 1982-11-01 1986-03-18 Electric Power Research Institute Air conditioning system and method of operation
JPH0311250A (ja) * 1989-06-08 1991-01-18 Matsushita Refrig Co Ltd 多室冷暖房装置
JP2725709B2 (ja) * 1989-06-28 1998-03-11 松下冷機株式会社 多室式空気調和機
GB2241091B (en) * 1990-02-14 1994-01-19 Toshiba Kk Air conditioning apparatus connecting one outdoor unit with several indoor units through several refrigerant tubes and signal conductors
JPH07324836A (ja) * 1994-05-31 1995-12-12 Toshiba Corp 多室空気調和機
US5551248A (en) * 1995-02-03 1996-09-03 Heatcraft Inc. Control apparatus for space cooling system
US5761921A (en) * 1996-03-14 1998-06-09 Kabushiki Kaisha Toshiba Air conditioning equipment
US6505475B1 (en) * 1999-08-20 2003-01-14 Hudson Technologies Inc. Method and apparatus for measuring and improving efficiency in refrigeration systems
JP4063465B2 (ja) 2000-01-13 2008-03-19 三菱電機株式会社 空気調和機及びマルチタイプの空気調和機
KR100851005B1 (ko) * 2002-03-06 2008-08-12 엘지전자 주식회사 멀티형 공기조화기의 냉매유량 제어장치
JP3966044B2 (ja) * 2002-04-02 2007-08-29 株式会社デンソー 空調装置
JP3709482B2 (ja) * 2004-03-31 2005-10-26 ダイキン工業株式会社 空気調和システム
JP3781046B2 (ja) * 2004-07-01 2006-05-31 ダイキン工業株式会社 空気調和装置
WO2006023075A2 (fr) * 2004-08-11 2006-03-02 Lawrence Kates Procede et dispositif pour le controle de systemes de cycle de refrigeration
JP4670329B2 (ja) * 2004-11-29 2011-04-13 三菱電機株式会社 冷凍空調装置、冷凍空調装置の運転制御方法、冷凍空調装置の冷媒量制御方法
CN101142454A (zh) * 2005-03-18 2008-03-12 开利商业冷藏公司 瓶冷却器除霜器和方法
EP2000751B1 (fr) * 2006-03-27 2019-09-18 Mitsubishi Electric Corporation Dispositif de climatisation frigorifique
US7874499B2 (en) * 2006-11-22 2011-01-25 Store-N-Stuff Llc System and method to control sensible and latent heat in a storage unit
US20090031735A1 (en) * 2007-08-01 2009-02-05 Liebert Corporation System and method of controlling fluid flow through a fluid cooled heat exchanger

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2779171A (en) * 1954-01-04 1957-01-29 Rca Corp Room temperature conditioner
US4067203A (en) * 1976-09-07 1978-01-10 Emerson Electric Co. Control system for maximizing the efficiency of an evaporator coil
US4644756A (en) * 1983-12-21 1987-02-24 Daikin Industries, Ltd. Multi-room type air conditioner
EP0282782A2 (fr) * 1987-03-20 1988-09-21 Hitachi, Ltd. Système de conditionnement d'air pour plusieurs chambres et procédé pour sa commande
DE4315924A1 (de) * 1993-05-12 1994-11-17 Forschungszentrum Fuer Kaeltet Kälteträger für Kältemaschinen oder Wärmepumpen
EP0675331A2 (fr) * 1994-03-30 1995-10-04 Kabushiki Kaisha Toshiba Système de conditionnement d'air avec un échangeur de chaleur intermédiaire intégré dans lequel deux sortes différentes de réfrigérants sont mises en circulation
EP0887599A1 (fr) * 1996-12-27 1998-12-30 Daikin Industries, Limited Appareil de refrigeration et son procede de fabrication
JPH1123079A (ja) * 1997-06-27 1999-01-26 Mitsubishi Heavy Ind Ltd 冷凍装置
JPH11201560A (ja) * 1998-01-08 1999-07-30 Denso Corp 超臨界冷凍サイクル

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1999, no. 04, 30 April 1999 (1999-04-30) & JP 11 023079 A (MITSUBISHI HEAVY IND LTD), 26 January 1999 (1999-01-26) *
PATENT ABSTRACTS OF JAPAN vol. 1999, no. 12, 29 October 1999 (1999-10-29) & JP 11 201560 A (DENSO CORP), 30 July 1999 (1999-07-30) *

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009009164A1 (fr) * 2007-07-11 2009-01-15 Liebert Corporation Procédé et appareil permettant d'égaliser un système de frigorigène pompé
US7900468B2 (en) 2007-07-11 2011-03-08 Liebert Corporation Method and apparatus for equalizing a pumped refrigerant system
US8484984B2 (en) 2007-07-11 2013-07-16 Liebert Corporation Method and apparatus for equalizing a pumped refrigerant system
WO2010010557A1 (fr) * 2008-07-23 2010-01-28 Joual Sarhan Unité de division de conditionneur d'air
EP2435883A1 (fr) * 2009-05-28 2012-04-04 American Power Conversion Corporation Systèmes et procédés de commande de la dynamique de charge dans un système de refroidissement par fluide frigorigène pompé
EP2435883B1 (fr) * 2009-05-28 2016-08-31 Schneider Electric IT Corporation Système et procédé de réglage des charges dynamiques dans un système de refroidissement avec frigorigène pompé
EP2667106A1 (fr) * 2012-05-22 2013-11-27 Compagnie Industrielle D'Applications Thermiques Kit et méthode de mise en oeuvre d'une installation de régulation de température pour un bâtiment
FR2991029A1 (fr) * 2012-05-22 2013-11-29 Ciat Sa Kit et methode de mise en oeuvre d'une installation de regulation de temperature pour un batiment
FR2995389A1 (fr) * 2012-09-13 2014-03-14 Alstom Transport Sa Dispositif de climatisation d'air, notamment pour un vehicule ferroviaire
EP2708436A1 (fr) * 2012-09-13 2014-03-19 ALSTOM Transport SA Dispositif de climatisation d'air, notamment pour un véhicule ferroviaire

Also Published As

Publication number Publication date
EP1662212A3 (fr) 2006-09-06
KR100758902B1 (ko) 2007-09-14
KR20060057226A (ko) 2006-05-26
CN1779391A (zh) 2006-05-31
US20060107683A1 (en) 2006-05-25

Similar Documents

Publication Publication Date Title
EP1662212A2 (fr) Conditionneur d'air et procédé de commande de celui-ci
JP5642207B2 (ja) 冷凍サイクル装置及び冷凍サイクル制御方法
JP4999529B2 (ja) 熱源機および冷凍空調装置
WO2011108068A1 (fr) Système de climatisation et de fourniture d'eau chaude
US10036580B2 (en) Multi-stage system for cooling a refrigerant
JP5419437B2 (ja) 空調複合給湯装置
CN103733002A (zh) 空气调节装置
US20100243202A1 (en) Hot water circulation system associated with heat pump
JP4058696B2 (ja) ヒートポンプ給湯システム
JP2014102050A (ja) 冷凍装置
EP1709373A2 (fr) Optimisation de la compression de vapeur transcritique par maximisation de la capacite de chauffage
JP2000161721A (ja) 空気調和装置
KR101166385B1 (ko) 수열원 공기 조화 시스템 및 그 제어방법
JP5881339B2 (ja) 空気調和機
US20210239370A1 (en) Heat pump and method of operating heat pump
JP5627564B2 (ja) 冷凍サイクルシステム
JP2004020070A5 (fr)
US20230080007A1 (en) Free cooling system for hvac system
KR101321545B1 (ko) 공기조화기
KR101227477B1 (ko) 용량 가변형 응축기가 구비된 공기조화기 및 그 제어방법
US20100043465A1 (en) Heat pump system and method of controlling the same
JPWO2019026234A1 (ja) 冷凍サイクル装置
JP3661014B2 (ja) 冷凍装置
JP2009281595A (ja) 冷凍装置
CA2991825C (fr) Systeme multietage destine au refroidissement d'un refrigerant

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: 20051214

AK Designated contracting states

Kind code of ref document: A2

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

RIN1 Information on inventor provided before grant (corrected)

Inventor name: OH, SAI KEE

Inventor name: CHUNG, BAIK YOUNG

Inventor name: CHANG, SE DONG

Inventor name: KIM, JU WON

Inventor name: PARK, BONG SOO

Inventor name: SONG, CHI WOO

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

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 FR GB

17Q First examination report despatched

Effective date: 20070416

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20070828