EP1662212A2 - Air conditioning system and method for controlling the same - Google Patents
Air conditioning system and method for controlling the same Download PDFInfo
- 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- Withdrawn
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)
Abstract
Description
- 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.
- In general, the air conditioning system cools or heats a room by compressing, condensing, expanding, and evaporating refrigerant. In general, the air conditioning system is provided with a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger.
- In 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.
- Moreover, in 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.
- However, if a height difference or a distance between the indoor heat exchanger, and the outdoor heat exchanger is great significantly, since the related art air conditioning system has a poor oil recovery rate, to fail in supply of an adequate rate of oil to the compressor, which is liable to result in damage to the compressor, development of an air conditioning system that can solve such a problem has been required.
- Accordingly, 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.
- Additional advantages, objects, and features of the invention will be set forth in part in the description which follows and in part will become apparent to those having ordinary skill in the art upon examination of the following or may be learned from practice of the invention. The objectives and other advantages of the invention may be realized and attained by the structure particularly pointed out in the written description and claims hereof as well as the appended drawings.
- To achieve these objects and other advantages and in accordance with the purpose of the invention, as embodied and broadly described herein, 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. Preferably, 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.
- In the meantime, in another aspect of the present invention, 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.
- In another aspect of the present invention, an air conditioning system 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.
- It is to be understood that both the foregoing general description and the following detailed description of the present invention are exemplary and explanatory and are intended to provide further explanation of the invention as claimed.
- The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the principle of the invention. In the drawings;
- 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; and
- FIG. 5 illustrates a P-h diagram showing a state change of refrigerant in heating operation of the air conditioning system in FIG. 1.
- Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings. Wherever possible, the same reference numbers will be used throughout the drawings to refer to the same or like parts.
- FIGS. 1 and 2 illustrate diagrams each showing an air conditioning system in accordance with a preferred embodiment of the present invention.
- Referring to FIGS. 1 and 2, 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 ahybrid heat exchanger 30 for making refrigerant in the indoorheat exchange part 10 and refrigerant in the outdoorheat exchange part 20 to heat exchange with each other. - The indoor
heat exchange part 10 includes afirst heat exchanger 14 for heat exchange with the room air, apump 12 for circulating the refrigerant to thefirst heat exchanger 14, and a flow rate control device for controlling a flow rate of the refrigerant to thefirst heat exchanger 14. - The outdoor
heat exchange part 20 has a refrigerant flow path independent from the indoorheat exchange part 10, and includes afourth heat exchanger 24 for making the refrigerant to heat exchange with outdoor air, and acompressor 22 for compressing, and circulating the refrigerant to thefourth heat exchanger 24. - The outdoor
heat exchange part 20 includes anexpansion device 28 for expanding the refrigerant to drop a pressure of the refrigerant, and aflow controller 23 for controlling a flow direction of the refrigerant, additionally. - In the meantime, the outdoor
heat exchange part 20 may have many variations as far as the part can transfer heat to the refrigerant in the indoorheat exchange part 10. As an example, the part may use warm water or waste heat as a heat source. - The hybrid
heat exchange part 30 is configured such that the indoorheat exchange part 10 and the outdoorheat exchange part 20 having refrigerant flow paths independent from each other can heat exchange with each other, without mix of the refrigerant between the indoorheat exchange part 10 and the outdoorheat exchange part 20. - In order to enable the
indoor heat exchanger 10 and theoutdoor heat exchanger 20 make heat exchange with each other, the hybridheat exchange part 30 includes asecond heat exchanger 16 in a flow path of the indoorheat exchange part 10, and a third heat exchanger 26 in a flow path of the outdoorheat exchange part 20 for heat exchange with thesecond heat exchanger 16. - That is, the
second heat exchanger 16 exchanges heat with the third heat exchanger 26 so that the indoorheat exchange part 10 and the outdoorheat exchange part 20 make heat exchange. - Moreover, the
second heat exchanger 16 forms a refrigerant circulating flow path as a portion of the indoorheat exchange part 10, and the third heat exchanger 26 forms a refrigerant circulating flow path as a portion of the outdoorheat exchange part 20. - That is, the outdoor
heat exchange part 20 forms a refrigerant flow path with the third heat exchanger 26, thefourth heat exchanger 24, thecompressor 22, and theexpansion device 28, and the indoorheat exchange part 10 forms a refrigerant flow path with thefirst heat exchanger 14, thesecond heat exchanger 16, thepump 12, and a flow rate control device. - The
second heat exchanger 16 and the third heat exchanger 26 may have many variations. That is, thesecond 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 thesecond heat exchanger 16, and the third heat exchanger 26 in the outdoor heat exchange part to make thermal contact with each other. - For an example, the hybrid
heat exchange part 30 may be constructed of a stack of a plurality of plate type heat conductive fins having thesecond heat exchanger 16 and the third heat exchanger 26 placed therebetween so as to be thermally in contact with each other. - Or alternatively, 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. Or, thesecond heat exchanger 16 and the third heat exchanger 26 are configured to have a form of a double tube. - In the meantime, the indoor
heat exchange part 10 will be described in more detail. - As described before, the indoor
heat exchange part 10 has a flow path independent from the outdoorheat exchange part 20, and includes afirst heat exchanger 14, apump 12, a flow rate control device, and asecond heat exchanger 16 of the hybridheat exchange part 30. - The indoor
heat exchange part 10 has apump 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 indoorheat exchange part 10 requires no oil for operation of the compressor, and consequently, no operation for recovery of the refrigerant is required. - It is preferable that the
pump 12 includes a pumping motor (not shown) and an impeller (not shown). Moreover, it is preferable that liquid refrigerant is supplied to thepump 12, for which, though not shown, a separate refrigerant storage tank may be provided between the hybridheat exchange part 30 and thepump 12, for supplying refrigerant to thepump 12. - It is preferable that 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. Of course, a constant speed motor having a constant rotation speed may be used.
- In general, the
first heat exchanger 14 is mounted in anindoor unit 15 installed in a room which requires cooling/heating. That is, thefirst heat exchanger 14 is an indoor heat exchanger for heat exchange with room air to cool or heat the room. - There may be a plurality of
indoor units 15 installed in a room if required, and according to this, a plurality ofindoor heat exchangers 14 may be mounted thereon. - The flow rate control device includes a plurality of
temperature sensors indoor heat exchanger 14, a controller (not shown) for determining a degree of superheat or subcooling of the refrigerant in theindoor heat exchanger 14 with reference to the temperatures measured at thetemperature sensors rate control valves indoor heat exchanger 14 according to the determination of the controller. - It is preferable that the flow
rate control valve rate control valves - Moreover, though it is preferable that the flow
rate control valve indoor heat exchanger 14 into which the refrigerant flows in/out, the mounting positions of the flowrate control valve rate control valve - Mounting positions of the temperature sensors will be described with reference to FIG. 2.
- It is preferable that the
temperature sensors inlet 17a through which the refrigerant is introduced into theindoor heat exchanger 14, anoutlet 17b through which the refrigerant is discharged from theindoor heat exchanger 14, and apredetermined portion 17c between theinlet 17a, and theoutlet 17b, respectively. - That is, at least three
temperature sensors indoor heat exchanger 14 mounted on theindoor unit 15. - Of the three
temperature sensors temperature sensor 17c mounted on the predetermined portion between theinlet 17a, and theoutlet 17b is mounted on one point where refrigerant in theindoor heat exchanger 14 is in a saturated state, so that thetemperature 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 thetemperature sensors - The degrees of superheat or subcooling is a temperature difference measured between the
temperature sensor 17b at the outlet and thetemperature sensor 17c at the middle of theindoor heat exchanger 14. - The degree of superheat is a temperature difference at the time of cooling, and the degree of subcooling is a temperature difference at the time of heating.
- A method for controlling a flow rate of refrigerant with reference to the degree of superheat or subcooling in the air conditioning system will be described.
- 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.
- Referring to FIG 3, 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.
- As described, 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 theindoor heat exchanger 14. - Moreover, as described, the temperatures of the refrigerant are measured with a plurality of
temperature sensors indoor heat exchanger 14. - At first, 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.
- Then, 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. In the measuring step (S2), the temperatures of the refrigerant are measured with thetemperature sensors indoor heat exchanger 14. - That is, since the degree of superheat or the degree of subcooling is a difference of a temperature of the refrigerant at the outlet of the
indoor heat exchanger 14 and a saturation temperature of the refrigerant flowing in the indoor heat exchanger, the controller can calculate the degree of superheat or the degree of subcooling with the temperatures measured at thetemperature sensors - Then, 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. In 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.
- Then, 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). - In the adjusting step (S4), the flow rate of the refrigerant is adjusted by controlling the flow
rate control valve heat exchange part 10. - In more detail, if the degree of superheat measured is higher than the preset degree of superheat at the time of room cooling, opening of the flow
rate control valves rate control valves - If the degree of superheat measured is the same with the preset degree of superheat at the time of room cooling, the flow rate of the refrigerant flowing in the
indoor heat exchanger 14 is maintained (S4b). - In the meantime, if the degree of subcooling measured is higher than the preset degree of subcooling at the time of room heating, opening of the flow
rate control valves rate control valves - If the degree of superheat measured is the same with the preset degree of superheat at the time of room cooling, the flow rate of the refrigerant flowing in the
indoor heat exchanger 14 is maintained (S4b). - The operation of the air conditioning system will be described.
- 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 indoorheat 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.
- At the time of cooling or heating, the hybrid
heat exchange part 30 exchanges heat between the outdoorheat exchange part 20 and the indoorheat exchange part 10. - The cooling operation will be described with reference to FIGS. 1 and 2.
- The refrigerant in the outdoor
heat exchange part 20 is compressed at thecompressor 22, and forwarded to the flow controller 23 (A-B section). Theflow controller 23 changes over the refrigerant to a side of thefourth heat exchanger 24. In this instance, the refrigerant introduced to thefourth 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). After cooling down the third heat exchanger 26 of the hybridheat exchange part 30, the low temperature and low pressure refrigerant is introduced into thecompressor 22 through the flow controller 23 (D-A section). In the outdoorheat exchange part 20, thecompressor 22 serves as a driving source if the refrigerant flow. - Then, the refrigerant in the indoor
heat exchange part 10 is cooled down as thesecond heat exchanger 16 and the third heat exchanger 26 in the hybridheat 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). In this instance, the refrigerant is neither in a two phase state, nor at a saturated temperature. The pumped refrigerant is introduced to thefirst heat exchanger 14 through the flowrate control valves first heat exchanger 14, and discharged from thefirst 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). In this step, thetemperature sensor 17c between opposite ends of thefirst heat exchanger 14 measures a saturation temperature of the refrigerant, and thetemperature sensor 17b at the outlet of the first heat exchanger 14 (corresponding to 'd' point) measures a superheated temperature of the refrigerant. - According to this, 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 - That is, if it is determined that the measured degree of superheat is higher than the preset degree of superheat, opening of the flow
rate control valves first heat exchanger 14 is made greater, to increase a flow rate of the refrigerant. - Opposite to this, if it is determined that the measured degree of superheat is lower than the preset degree of superheat, opening of the flow
rate control valves first heat exchanger 14 is made smaller, to decrease a flow rate of the refrigerant. - In this instance, of the flow
rate control valves first heat exchanger 14, though it is preferable that opening of the flowrate control valve 13a at an inlet end of thefirst heat exchanger 14 is made greater or smaller, and opening of the flowrate control valve 13b at an outlet end of thefirst heat exchanger 14 is opened to the maximum, the way of opening of the flowrate control valves - According to this, the flow rate of the refrigerant to the
first heat exchanger 14 can be controlled to the optimum. - After making heat exchange at the
first heat exchanger 14, the refrigerant is discharged from thefirst heat exchanger 14 to thesecond heat exchanger 16 of the hybridheat exchange part 30, and cooled therein again, to circulate therefrom. - Next, heating operation will be described with reference to FIGS. 1, 2, and 5.
- After compressed at the
compressor 22 in the outdoorheat exchange part 20, the refrigerant is forwarded to the flow controller 23 (A-B). Theflow controller 23 changes over the refrigerant to a side of the third heat exchanger 26 of the hybridheat exchange part 30. In this instance, the refrigerant introduced into the hybridheat 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 thefourth 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 outdoorheat exchange part 20 is opposite to the cooling operation. - Then, 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 thesecond heat exchanger 16 of the hybridheat 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 thepump 12. The refrigerant introduced into thefirst heat exchanger 14 heat exchanges with room air to heat the room, while the refrigerant itself is condensed (c-a). - In this instance, as the refrigerant in the
first heat exchanger 14 heat exchanges with the room air, the refrigerant reaches to a saturation temperature at which the refrigerant is involved in no temperature change, but a phase change (d-e). In such a step, thetemperature sensor 17c between the refrigerant inlet/outlet of thefirst heat exchanger 14 measures the saturation temperature of the refrigerant ('e' point), and thetemperature sensor 17b at the outlet of thefirst heat exchanger 14 measures a superheated temperature of the refrigerant ('a' point). - According to this, 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 - That is, if it is determined that the measured degree of superheat is higher than the preset degree of superheat, opening of the flow
rate control valves 13a on the refrigerant inlet of thefirst heat exchanger 14 is made greater, to increase the flow rate of the refrigerant to thefirst heat exchanger 14. - Opposite to this, if it is determined that the measured degree of superheat is lower than the preset degree of superheat, 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 thefirst 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 thesecond heat exchanger 16 of the hybridheat exchange part 30. - As has been described, 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.
- According to this, 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.
- Moreover, 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.
- Furthermore, since the outdoor heat exchange part is connected to the indoor heat exchange part through the hybrid heat exchange part, 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.
- Since 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.
- It will be apparent to those skilled in the art that various modifications and variations can be made in the present invention without departing from the scope of the inventions. Thus, it is intended that the present invention covers the modifications and variations of this invention provided they come within the scope of the appended claims and their equivalents.
Claims (10)
- An air conditioning system comprising: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; anda 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 system as claimed in claim 1, wherein the flow rate control device includes;
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 system as claimed in claim 2, wherein the flow rate control valve is mounted on a refrigerant inlet end of the indoor heat exchanger.
- The system as claimed in claim 2, wherein the flow rate control valve is mounted on a refrigerant outlet end of the indoor heat exchanger.
- The system as claimed in claim 2, wherein 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 system as claimed in claim 5, wherein 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 comprising 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; andcontrolling 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 method as claimed in claim 7, wherein 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 method as claimed in claim 7, wherein 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 method as claimed in claim 7, wherein 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.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020040096315A KR100758902B1 (en) | 2004-11-23 | 2004-11-23 | multi type air conditioning system and controlling method of the system |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1662212A2 true EP1662212A2 (en) | 2006-05-31 |
EP1662212A3 EP1662212A3 (en) | 2006-09-06 |
Family
ID=35840122
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05025039A Withdrawn EP1662212A3 (en) | 2004-11-23 | 2005-11-16 | Air conditioning system and method for controlling the same |
Country Status (4)
Country | Link |
---|---|
US (1) | US20060107683A1 (en) |
EP (1) | EP1662212A3 (en) |
KR (1) | KR100758902B1 (en) |
CN (1) | CN1779391A (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009009164A1 (en) * | 2007-07-11 | 2009-01-15 | Liebert Corporation | Method and apparatus for equalizing a pumped refrigerant system |
WO2010010557A1 (en) * | 2008-07-23 | 2010-01-28 | Joual Sarhan | Dividing unit of the air-conditioner |
EP2435883A1 (en) * | 2009-05-28 | 2012-04-04 | American Power Conversion Corporation | Systems and methods for controlling load dynamics in a pumped refrigerant cooling system |
EP2667106A1 (en) * | 2012-05-22 | 2013-11-27 | Compagnie Industrielle D'Applications Thermiques | Kit and method for implementing a temperature control system for a building |
FR2995389A1 (en) * | 2012-09-13 | 2014-03-14 | Alstom Transport Sa | AIR CONDITIONING DEVICE, IN PARTICULAR FOR A RAILWAY VEHICLE |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5125124B2 (en) * | 2007-01-31 | 2013-01-23 | ダイキン工業株式会社 | Refrigeration equipment |
US10775054B2 (en) * | 2009-03-13 | 2020-09-15 | Treau, Inc. | Modular air conditioning system |
CN102422093B (en) | 2009-05-12 | 2014-03-19 | 三菱电机株式会社 | Air conditioner |
US8452459B2 (en) * | 2009-08-31 | 2013-05-28 | Fisher-Rosemount Systems, Inc. | Heat exchange network heat recovery optimization in a process plant |
EP2505938B1 (en) * | 2009-11-25 | 2019-04-10 | Mitsubishi Electric Corporation | Air conditioning device |
WO2012032580A1 (en) * | 2010-09-10 | 2012-03-15 | 三菱電機株式会社 | Air-conditioning device |
KR101294082B1 (en) * | 2011-11-24 | 2013-08-08 | 현대자동차주식회사 | Heat exchanger for lpi vehicle |
US9915453B2 (en) * | 2012-02-07 | 2018-03-13 | Systecon, Inc. | Indirect evaporative cooling system with supplemental chiller that can be bypassed |
CN102607146B (en) * | 2012-04-06 | 2014-09-10 | 谭仲禧 | Central air-conditioning system and control method thereof |
CN102620494B (en) * | 2012-05-08 | 2014-03-12 | 程有凯 | Control technology for superheat degree of automatic cascade refrigeration thermostatic expansion valve |
CN104791941B (en) * | 2014-01-21 | 2017-11-10 | 广东美的暖通设备有限公司 | Air-conditioning system and its control method, the outdoor unit of air-conditioning system |
WO2016187600A1 (en) | 2015-05-20 | 2016-11-24 | Other Lab, Llc | Near-isothermal compressor/expander |
US10739024B2 (en) | 2017-01-11 | 2020-08-11 | Semco Llc | Air conditioning system and method with chiller and water |
JP6834562B2 (en) * | 2017-02-13 | 2021-02-24 | 株式会社富士通ゼネラル | Air conditioner |
CN107477780A (en) * | 2017-08-14 | 2017-12-15 | 珠海格力电器股份有限公司 | Method for adjusting evaporation temperature of indoor unit of air conditioner and air conditioner |
US11054194B2 (en) | 2017-10-10 | 2021-07-06 | Other Lab, Llc | Conformable heat exchanger system and method |
CN108375241A (en) * | 2018-03-23 | 2018-08-07 | 中国工程物理研究院流体物理研究所 | A kind of accurate temperature controlling cooling system required suitable for high insulation resistance |
US11253958B2 (en) | 2019-01-29 | 2022-02-22 | Treau, Inc. | Polymer film heat exchanger sealing system and method |
US11498163B2 (en) | 2019-09-13 | 2022-11-15 | Treau, Inc. | Window installation system and method for split-architecture air conditioning unit |
KR20210096785A (en) * | 2020-01-29 | 2021-08-06 | 엘지전자 주식회사 | An air conditioning apparatus and a method controlling the same |
Citations (9)
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 (en) * | 1987-03-20 | 1988-09-21 | Hitachi, Ltd. | Multiple room type air conditioning system and control method therefor |
DE4315924A1 (en) * | 1993-05-12 | 1994-11-17 | Forschungszentrum Fuer Kaeltet | Coolant for refrigerating machines or heat pumps |
EP0675331A2 (en) * | 1994-03-30 | 1995-10-04 | Kabushiki Kaisha Toshiba | Air conditioning system with built-in intermediate heat exchanger with two different types of refrigerants circulated |
EP0887599A1 (en) * | 1996-12-27 | 1998-12-30 | Daikin Industries, Limited | Refrigeration apparatus and method of manufacturing same |
JPH1123079A (en) * | 1997-06-27 | 1999-01-26 | Mitsubishi Heavy Ind Ltd | Refrigerator |
JPH11201560A (en) * | 1998-01-08 | 1999-07-30 | Denso Corp | Supercritical refrigerating cycle |
Family Cites Families (21)
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 (en) * | 1989-06-08 | 1991-01-18 | Matsushita Refrig Co Ltd | Multi-room air-conditioning equipment |
JP2725709B2 (en) * | 1989-06-28 | 1998-03-11 | 松下冷機株式会社 | Multi-room air conditioner |
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 (en) * | 1994-05-31 | 1995-12-12 | Toshiba Corp | Multi-room air conditioner |
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 (en) | 2000-01-13 | 2008-03-19 | 三菱電機株式会社 | Air conditioner and multi-type air conditioner |
KR100851005B1 (en) * | 2002-03-06 | 2008-08-12 | 엘지전자 주식회사 | Refrigerant flow amount control apparatus for multi air conditioner |
JP3966044B2 (en) * | 2002-04-02 | 2007-08-29 | 株式会社デンソー | Air conditioner |
JP3709482B2 (en) * | 2004-03-31 | 2005-10-26 | ダイキン工業株式会社 | Air conditioning system |
JP3781046B2 (en) * | 2004-07-01 | 2006-05-31 | ダイキン工業株式会社 | Air conditioner |
CA2575974C (en) * | 2004-08-11 | 2010-09-28 | Lawrence Kates | Method and apparatus for monitoring refrigerant-cycle systems |
JP4670329B2 (en) * | 2004-11-29 | 2011-04-13 | 三菱電機株式会社 | Refrigeration air conditioner, operation control method of refrigeration air conditioner, refrigerant amount control method of refrigeration air conditioner |
JP2008533429A (en) * | 2005-03-18 | 2008-08-21 | キャリア・コマーシャル・リフリージレーション・インコーポレーテッド | Defroster for bottle cooler and method thereof |
EP2000751B1 (en) * | 2006-03-27 | 2019-09-18 | Mitsubishi Electric Corporation | Refrigeration air conditioning device |
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 |
-
2004
- 2004-11-23 KR KR1020040096315A patent/KR100758902B1/en not_active IP Right Cessation
-
2005
- 2005-11-16 EP EP05025039A patent/EP1662212A3/en not_active Withdrawn
- 2005-11-22 US US11/283,694 patent/US20060107683A1/en not_active Abandoned
- 2005-11-23 CN CNA2005101248842A patent/CN1779391A/en active Pending
Patent Citations (9)
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 (en) * | 1987-03-20 | 1988-09-21 | Hitachi, Ltd. | Multiple room type air conditioning system and control method therefor |
DE4315924A1 (en) * | 1993-05-12 | 1994-11-17 | Forschungszentrum Fuer Kaeltet | Coolant for refrigerating machines or heat pumps |
EP0675331A2 (en) * | 1994-03-30 | 1995-10-04 | Kabushiki Kaisha Toshiba | Air conditioning system with built-in intermediate heat exchanger with two different types of refrigerants circulated |
EP0887599A1 (en) * | 1996-12-27 | 1998-12-30 | Daikin Industries, Limited | Refrigeration apparatus and method of manufacturing same |
JPH1123079A (en) * | 1997-06-27 | 1999-01-26 | Mitsubishi Heavy Ind Ltd | Refrigerator |
JPH11201560A (en) * | 1998-01-08 | 1999-07-30 | Denso Corp | Supercritical refrigerating cycle |
Non-Patent Citations (2)
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)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009009164A1 (en) * | 2007-07-11 | 2009-01-15 | Liebert Corporation | Method and apparatus for equalizing a pumped refrigerant system |
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 (en) * | 2008-07-23 | 2010-01-28 | Joual Sarhan | Dividing unit of the air-conditioner |
EP2435883A1 (en) * | 2009-05-28 | 2012-04-04 | American Power Conversion Corporation | Systems and methods for controlling load dynamics in a pumped refrigerant cooling system |
EP2435883B1 (en) * | 2009-05-28 | 2016-08-31 | Schneider Electric IT Corporation | Systems and methods for controlling load dynamics in a pumped refrigerant cooling system |
EP2667106A1 (en) * | 2012-05-22 | 2013-11-27 | Compagnie Industrielle D'Applications Thermiques | Kit and method for implementing a temperature control system for a building |
FR2991029A1 (en) * | 2012-05-22 | 2013-11-29 | Ciat Sa | KIT AND METHOD FOR OPERATING A TEMPERATURE REGULATION INSTALLATION FOR A BUILDING |
FR2995389A1 (en) * | 2012-09-13 | 2014-03-14 | Alstom Transport Sa | AIR CONDITIONING DEVICE, IN PARTICULAR FOR A RAILWAY VEHICLE |
EP2708436A1 (en) * | 2012-09-13 | 2014-03-19 | ALSTOM Transport SA | Air-conditioning device, in particular for a railway vehicle |
Also Published As
Publication number | Publication date |
---|---|
US20060107683A1 (en) | 2006-05-25 |
KR20060057226A (en) | 2006-05-26 |
EP1662212A3 (en) | 2006-09-06 |
CN1779391A (en) | 2006-05-31 |
KR100758902B1 (en) | 2007-09-14 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1662212A2 (en) | Air conditioning system and method for controlling the same | |
JP5642207B2 (en) | Refrigeration cycle apparatus and refrigeration cycle control method | |
JP4999529B2 (en) | Heat source machine and refrigeration air conditioner | |
WO2011108068A1 (en) | Air-conditioning hot-water-supplying system | |
US10036580B2 (en) | Multi-stage system for cooling a refrigerant | |
JP5419437B2 (en) | Air conditioning combined water heater | |
CN103733002A (en) | Air conditioner | |
US20100243202A1 (en) | Hot water circulation system associated with heat pump | |
JP4058696B2 (en) | Heat pump hot water supply system | |
JP2014102050A (en) | Refrigeration device | |
WO2005059448A2 (en) | Transcritical vapor compression optimization through maximization of heating capacity | |
KR101166385B1 (en) | A air conditioning system by water source and control method thereof | |
JP5881339B2 (en) | Air conditioner | |
JP5627564B2 (en) | Refrigeration cycle system | |
JP2004020070A5 (en) | ||
US11619425B2 (en) | Heat pump and method for controlling compressor based on operation of boiler | |
KR101321545B1 (en) | Air conditioner | |
KR101227477B1 (en) | Air conditioner having volume variableness type condenser and method of control thereof | |
US20100043465A1 (en) | Heat pump system and method of controlling the same | |
JPWO2019026234A1 (en) | Refrigeration cycle device | |
JP3661014B2 (en) | Refrigeration equipment | |
US20230080007A1 (en) | Free cooling system for hvac system | |
JP2009281595A (en) | Refrigerating device | |
CA2991825C (en) | Multi-stage system for cooling a refrigerant | |
JP2008111584A (en) | Air conditioner |
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 |