CN100451464C - Second-refrigerant pump driving type air conditioner - Google Patents
Second-refrigerant pump driving type air conditioner Download PDFInfo
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- CN100451464C CN100451464C CNB2006100549739A CN200610054973A CN100451464C CN 100451464 C CN100451464 C CN 100451464C CN B2006100549739 A CNB2006100549739 A CN B2006100549739A CN 200610054973 A CN200610054973 A CN 200610054973A CN 100451464 C CN100451464 C CN 100451464C
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- producing medium
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- 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
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- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
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- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/025—Motor control arrangements
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- 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
- F24F2140/10—Pressure
- F24F2140/12—Heat-exchange fluid pressure
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0315—Temperature sensors near the outdoor heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
- F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities
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- 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
- F25B2600/02—Compressor control
- F25B2600/021—Inverters therefor
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- 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
- F25B2600/02—Compressor control
- F25B2600/022—Compressor control for multi-stage operation
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- 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
- F25B2600/05—Refrigerant levels
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- 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
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- 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
- F25B2700/04—Refrigerant level
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
A second-refrigerant pump driving type air conditioner, including an indoor unit having an indoor heat exchanger that circulates a refrigerant containing no oil, a first circulator including a compressor that compresses and discharges a refrigerant containing oil, a first outdoor heat exchanger, a second outdoor heat exchanger, and an outdoor expander, and a second circulator including an intermediate heat exchanger connected to the indoor heat exchanger that circulates the refrigerant containing no oil and heat-exchanges the refrigerant of the first outdoor heat exchanger, a receiver, and a pump. A restriction of a length and a diameter of a connection pipe for connecting an outdoor unit and the indoor unit is decreased, and an oil shortage of the compressor is prevented.
Description
Technical field
The present invention relates to a kind of second refrigerant pump driving type air conditioner, more particularly, the present invention relates to a kind of second such refrigerant pump driving type air conditioner, this air-conditioner can be finished heating operation, reduced the length of the tube connector that is used to connect outdoor unit and indoor unit and the restriction of diameter, and prevented the compressor oil starvation.
Background technology
Usually, air-conditioner has and is used to heat or the indoor unit of cooling chamber inner room and be used for compression back cold-producing medium is provided to the outdoor unit of indoor unit.
As shown in Figure 1, this air-conditioner comprises a plurality of indoor units 10 and a plurality of outdoor unit 20, and wherein this outdoor unit 20 is used for providing cold-producing medium according to the driving condition of each indoor unit 10.
Each indoor unit 10 comprises indoor heat converter 11 and indoor expander 13.This indoor heat converter 11 is used to make this cold-producing medium and room air to carry out heat exchange, and indoor expander 13 is arranged on the inlet of indoor heat converter 11, is used to make this cold-producing medium decompression and expansion.
Each outdoor unit 20 comprises compressor 21 and is connected to the outdoor heat converter 27 of this compressor 21 that wherein this outdoor heat converter 27 is used to make this cold-producing medium and outdoor air to carry out heat exchange.Be used for the public reservoir 23 that gas refrigerant is drawn into each compressor 21 is installed in compressor 21 inlets, and the cross valve 25 that is used to switch coolant channel is installed in compressor 21 outlets.Outdoor expander 29 is installed in a side of this outdoor heat converter 27 along refrigerant flow direction.In addition, the bypass 31 with check-valves 33 is formed on a side of this outdoor expander 29.Each outdoor unit 20 has service valve 35, and the tube connector 37 that is used to scatter or compiles cold-producing medium is arranged between each outdoor unit 20 and each indoor unit 10.
When air-conditioner was operated, corresponding with the load capacity of driven indoor unit 10 in a plurality of indoor units 10, this outdoor unit 20 was driven selectively.Each cross valve 25 of driven this outdoor unit 20 switches coolant channel according to the drive pattern of indoor unit 10.When indoor unit 10 was operated with refrigerating mode, the cross valve 25 of driven outdoor unit 20 switched coolant channel, thereby can be through outdoor heat converter 27 from the cold-producing medium of compressor 21 discharges.Through those cold-producing mediums of outdoor heat converter 27 indoor expander 13, thereby be depressurized and expand by driven indoor unit 10.Decompression and the cold-producing medium that expands carry out heat exchange by indoor heat converter 11 and room air, carry out cooling down operation whereby.Then, cold-producing medium is inhaled into compressor 21 by the cross valve 25 and the reservoir 23 of outdoor unit 20, thereby is compressed repeatedly, discharges and circulate.
Oil is filled in the compressor 21 with cold-producing medium, so that cooling and lubricate compressors 21.Therefore, oil content is dispersed in the indoor unit 10 that comprises this indoor heat converter 11, and is dispersed in and is used for indoor unit 10 and outdoor unit 20 tube connectors connected to one another.
In traditional air-conditioner, the pressure that surpasses to a certain degree must remain in the tube connector, so that the oil that is retained in indoor heat converter 11 and the tube connector can successfully regather in the compressor 21.Therefore, the increase of tube connector diameter surpasses a certain value and is restricted, and tube connector length must remain less than a certain value simultaneously.Therefore, between outdoor unit 20 and indoor unit 10, has distance limit.
In addition, the oil that the oil that is trapped in indoor heat converter 11 and each tube connector is regathered regathers drive cycle ground and carries out (for example 6 to 8 hours).Regather when driving when carrying out oil, produce noise, cooling operation simultaneously stops, thereby causes user's inconvenience.
Summary of the invention
Therefore, the purpose of this invention is to provide a kind of second refrigerant pump driving type air conditioner, this air-conditioner can reduce the length of the tube connector that is used to connect outdoor unit and indoor unit and the restriction of diameter, and stops the oil shortage of compressor.
For realizing these and other advantage here according to the object of the invention of specializing and briefly describing, a kind of second refrigerant pump driving type air conditioner is provided, wherein this air-conditioner includes the indoor unit of indoor heat converter, and wherein this indoor heat converter makes not that the cold-producing medium and the room air of oil-containing carry out heat exchange; First circulator, this first circulator comprise compression and discharging refrigerating agent containing oil compressor, be connected to compressor first side make first outdoor heat converter from the cold-producing medium of this compressor discharge and the cold-producing medium heat exchange of oil-containing not, be connected to compressor second side make from second outdoor heat converter of the cold-producing medium of compressor discharge and outdoor air heat exchange and be connected to first outdoor heat converter and second outdoor heat converter so that from the cold-producing medium decompression of compressor discharge and the outdoor expander of expansion; Second circulator, this second circulator comprise be connected to indoor heat converter first side so that not the intermediate heat exchanger of the cold-producing medium of oil-containing and cold-producing medium heat exchange in first outdoor heat converter, be connected to indoor heat converter second side and receive from the receiver of the cold-producing medium of indoor heat converter discharging, and the cold-producing medium that suction is received by receiver is so that make the pump of cold-producing medium circulation; Controller, the revolutions per minute of this controller control pump (rpm) is introduced into gas refrigeration dosage in the pump with minimizing.
From the detailed description of the invention below in conjunction with accompanying drawing, above-mentioned and other purpose of the present invention, feature, form and advantage will become more obvious.
Description of drawings
The accompanying drawing that comprises provides the further understanding to invention, incorporates and form the part of specification simultaneously into.These accompanying drawings show inventive embodiment, and are used for explaining inventive principle with written description.In the accompanying drawings:
Fig. 1 is the topology view that shows according to the air-conditioner of conventional art;
Fig. 2 is the topology view that illustrates according to second refrigerant pump driving type air conditioner of first embodiment of the invention;
Fig. 3 is the control block diagram of Fig. 2;
Fig. 4 illustrates the topology view of second refrigerant pump driving type air conditioner in accordance with another embodiment of the present invention;
Fig. 5 is the control block diagram of Fig. 4;
Fig. 6 is the view of cold-producing medium stream when being illustrated in cooling down operation among Fig. 4;
Fig. 7 illustrates the view of second a refrigerant pump driving type air conditioner part in accordance with another embodiment of the present invention; And
Fig. 8 illustrates the view of second a refrigerant pump driving type air conditioner part in accordance with another embodiment of the present invention.
The specific embodiment
Below will be in detail with reference to the preferred embodiments of the present invention, the example of these preferred embodiments shown in the drawings.
Hereinafter, second refrigerant pump driving type air conditioner according to the preferred embodiment of the invention will be described with reference to the accompanying drawings.
Fig. 2 is the topology view that illustrates according to second refrigerant pump driving type air conditioner of first embodiment of the invention, and Fig. 3 is the control block diagram of Fig. 2.
Referring to Fig. 2 and 3, this second refrigerant pump driving type air conditioner comprises: have the indoor unit 100 of indoor heat converter 111, wherein this indoor heat converter 111 is used to make the not cold-producing medium and the room air heat exchange of oil-containing; First circulator 150, this first circulator 150 comprises compressor 151, being connected to compressor 151 1 sides is used to make from compressor 151 cold-producing medium of discharging and first outdoor heat converter 171 that passes the cold-producing medium heat exchange of indoor unit 100, be connected to compressor 151 opposite sides be used to make wherein cold-producing medium and second outdoor heat converter 181 of outdoor air heat exchange, be connected to the outside expander 190 that first outdoor heat converter 171 and second outdoor heat converter 181 are used to make cold-producing medium decompression and expansion, and be used to make first pipe 193 by the circulation of compressor 151 refrigerant compressed; And second circulator 200, this second circulator 200 comprise be connected to indoor heat converter 111 1 sides be used to make wherein the cold-producing medium and the intermediate heat exchanger 211 of the cold-producing medium heat exchange of first outdoor heat converter 171, be connected to indoor heat converter 111 another sides and receive therein temporarily cold-producing medium receiver 221, be connected to receiver 221 1 sides and be used for liquid refrigerant in the receiver is aspirated and thereby the pump 231 of this cold-producing medium that circulates and be used to make second pipe 239 by the cold-producing medium circulation of pump 231 suctions.Preferably, this first circulator 150 and second circulator 200 are designed to be arranged in the outdoor unit in the outdoor chamber.This first circulator 150 is designed to make the oil and the cold-producing medium that all are contained in the compressor 151 to circulate along first pipe 193, so that cooling and lubricate compressors 151.Second circulator 200 is designed so that the cold-producing medium of oil-containing can be along 239 circulations of second pipe.
Each indoor unit 100 comprises and is used to make the indoor heat converter 111 of cold-producing medium and room air heat exchange and be arranged in the control valve 113 that indoor heat converter 111 1 sides are used to control refrigerant flow.The tube connector 115 that is used to connect each indoor unit 100 is arranged in the both sides of each indoor unit 100.
The 3rd hygrosensor 121 that is used to survey refrigerant temperature is installed in the mid portion of each indoor heat converter 111.In addition, the 4th hygrosensor 123 that is used to detect the oral-lateral refrigerant temperature correspondingly is installed in the outlet of indoor heat converter 111.
This first circulator 150 comprises: the compressor 151 that is used for compressed refrigerant, being connected to compressor 151 inlets is used to make cold-producing medium wherein and has passed first outdoor heat converter 171 of the cold-producing medium heat exchange of indoor unit 100, be connected to second outdoor heat converter 181 that compressor 151 outlets are used to make compressed cold-producing medium and outdoor air heat exchange, be arranged in the outside expander 190 that is used to make cold-producing medium decompression and expansion between first outdoor heat converter 171 and second outdoor heat converter 181, and first pipe 193 that is used to make the cold-producing medium circulation.
Be used to provide the reservoir 153 of gas refrigerant to be connected to the inlet of compressor 151, and second pressure detector 155 that is used to survey inlet pressure is arranged between reservoir 153 and the compressor 151.In addition, according to the flow direction of cold-producing medium when the cooling down operation, second hygrosensor 175 that is used to survey first hygrosensor 173 of the first outdoor heat converter inlet temperature and is used to survey the first outdoor heat converter outlet temperature is separately positioned on the entrance and exit of first outdoor heat converter 171.
This second circulator 200 comprises: be used to make the cold-producing medium heat exchange of the cold-producing medium that passed indoor heat converter 111 and first outdoor heat converter 171 intermediate heat exchanger 211, be used for interim reception and passed the receiver 221 of the cold-producing medium of intermediate heat exchanger 211, be used for second pipe 239 that the cold-producing medium in the receiver 221 is drawn into the pump 231 of driven indoor unit 100 and is used to make the cold-producing medium circulation.
The 5th hygrosensor 213 and first pressure detector 215 that are used to survey intermediate heat exchanger 211 outlet temperatures and outlet pressure are installed in intermediate heat exchanger 211 outlets respectively.The cold-producing medium water level detector 223 that is used to survey liquid refrigerant water level in receiver 221 is arranged in the receiver 221.Be used to stop the check-valves 237 of back flow of refrigerant to be arranged on the outlet of pump 231.
When selecting the cooling down operation of indoor unit 100, controller 300 control compressors 151 are so that this compressor 151 drives with the load capacity of driven indoor unit 100 is corresponding.Shown in dotted arrow among Fig. 2, thereby the cold-producing medium that compresses first circulator 150 of discharging by compressor 151 circulates along first pipe 193.Simultaneously, controller 300 driving pumps 231, shown in solid arrow among Fig. 2, the cold-producing medium of second circulator 200 by pump 231 suction is along 239 circulations of second pipe.Circulating refrigerant in indoor unit 100 with the room air heat exchange, thereby carry out cooling down operation.
The cold-producing medium that discharges by compressor 151 compressions is introduced in first outdoor heat converter 171, is condensed with the outdoor air heat exchange then.Condensating refrigerant is introduced into first outdoor heat converter 171 then by 190 decompressions of outside expander and expansion.Then, in first outdoor heat converter 171, cold-producing medium carries out heat exchange with the cold-producing medium that passes indoor unit 100, is drawn into compressor 151 by reservoir 153 then, thereby is compressed repeatedly and discharge.
When pump 231 was driven, the liquid refrigerant in receiver 221 was discharged into indoor unit 100 via pump 231 and check-valves 237.When pump 231 was driven, current probe 331 was surveyed the variation of the input current that is input to pump 231, and cold-producing medium water level detector 223 is surveyed the water level of liquid refrigerant in receiver 221 simultaneously.The 5th hygrosensor 213 and first pressure detector 215 are surveyed the outlet temperature and the outlet pressure of intermediate heat exchanger 211 respectively.This first supercooling degree calculator 321 converts the outlet pressure that detects to temperature, calculates then in inversion temperature with by the difference between the temperature of the 5th hygrosensor 213 detections, i.e. the outlet supercooling degree of intermediate heat exchanger 211.
When the input current variable quantity of surveying by current probe 331 that is input to pump 231 reached certain hour above a certain value, controller 300 reduced the revolutions per minute of pump 231, has stoped gas refrigerant to be introduced in the pump 231 like this.When the liquid refrigerant water level of surveying by cold-producing medium water level detector 223 reduced to predetermined water level (lower limit), the revolutions per minute (frequency) of controller 300 control pumps 231 did not increase, and has stoped gas refrigerant to be introduced in the pump 231 like this.When the outlet supercooling degree of the intermediate heat exchanger 211 that calculates by the first supercooling degree calculator 321 increased, controller 300 increased the revolutions per minute of pump 231.On the contrary, when the outlet supercooling degree of the intermediate heat exchanger 211 that calculates by the first supercooling degree calculator 321 reduced, controller 300 reduced the revolutions per minute of pump 231.
The cold-producing medium that flows to indoor unit 100 is introduced into indoor heat converter 111 via control valve 113, then with the room air heat exchange, thereby carries out cooling down operation.Here, the 3rd hygrosensor 121 and the 4th hygrosensor 123 are surveyed the temperature and indoor heat converter 111 outlet temperatures of indoor heat converter 111 mid portions respectively.According to the detecting temperature of indoor heat converter 111 mid portions and outlet, second crosses the mistake that adds temperature calculator 313 calculating indoor heat converters 111 adds temperature.Cross after crossing the calculating add the indoor heat converter 111 that temperature calculator 313 surveys by second when adding temperature and increasing, the open degree of controller 300 control control valves 113 is to increase.On the contrary, when the mistake of calculating added the temperature reduction, the open degree of controller 300 control control valves 113 was to reduce.
The cold-producing medium of carrying out cooling down operation in indoor unit 100 is introduced into intermediate heat exchanger 211, and carries out heat exchange with first outdoor heat converter 171, thereby is condensed.Condensed refrigerant is introduced into receiver 221, and the liquid refrigerant in receiver 221 aspirates by pump 231, thereby is discharged into indoor unit 100.These steps are carried out repeatedly.
When the condenser heat of the intermediate heat exchanger 211 along with indoor unit 100 load increases increased, the supercooling degree of intermediate heat exchanger 211 outlets reduced.When the condenser heat of middle heat exchanger 211 increased, the inlet pressure of the evaporating pressure of first circulator 150 and compressor 151 also increased.Here, controller 300 is at first controlled compressor 151 revolutions per minutes before control pump 231 revolutions per minutes, thereby stops pump 231 revolutions per minutes owing to second circulator 200 to reduce the cooling capacity reduction that causes.
On the contrary, when the outlet supercooling degree of the intermediate heat exchanger 211 along with indoor unit 100 load reductions increases, controller 300 revolutions per minute of control pump 231 at first before control compressor 151 revolutions per minutes.
When changing the compression volume of compressor 151 for the security control of first circulator 150, controller 300 revolutions per minute of control pump 231 at first before control compressor 151 volume change is in order to avoid gas refrigerant is introduced in the pump 231.
For example, being used between compressor 151 is equilibrated under the situation of the oil equalizing operation of oil in a plurality of compressors 151 that are provided with in first circulator 150, just when compressor 151 will alternately be driven, controller 300 is at first according to will be by each compression volume of the compressor 151 of driven and the revolutions per minute of control pump 231, and driven compressor 151 is wanted in operation then.
When compressor 151 comprise at least one frequency-changeable compressor (inverter compressor) and constant velocity type compressor, when the revolutions per minute of frequency-changeable compressor reduces to and is used to drive the low-limit frequency of constant velocity type compressor simultaneously, controller 300 at first according to the revolutions per minute of frequency-changeable compressor low-limit frequency control pump 231, drives the constant velocity type compressor then.
Fig. 4 illustrates the topology view of second refrigerant pump driving type air conditioner in accordance with another embodiment of the present invention.Fig. 5 is the control block diagram of Fig. 4, and Fig. 6 is the view of flow of refrigerant when showing in Fig. 4 cooling down operation, and Fig. 7 and Fig. 8 illustrate the view of the second refrigerant pump driving type air conditioner major part in accordance with another embodiment of the present invention.Identical reference number is used to represent parts same with the above-mentioned embodiment, omits simultaneously its detailed description.
Referring to Figure 4 and 5, second refrigerant pump driving type air conditioner comprises: each all has a plurality of indoor units 100 of indoor heat converter 111; First circulator 150, this first circulator 150 comprises a plurality of compressors 151, being connected to compressor 151 1 sides is used to make cold-producing medium therein and has passed first outdoor heat converter 171 of the cold-producing medium heat exchange of indoor unit 100, be connected to compressor 151 opposite sides be used to make therein cold-producing medium and second outdoor heat converter 181 of outdoor air heat exchange, be arranged in the first outside expander 191 that is used to make cold-producing medium decompression and expansion between first outdoor heat converter 171 and second outdoor heat converter 181, and be used to make first pipe 193 by the circulation of compressor 151 refrigerant compressed; And second circulator 200, this second circulator 200 comprise be connected to indoor heat converter 111 1 sides be used to make therein the cold-producing medium and the intermediate heat exchanger 211 of the cold-producing medium heat exchange of first outdoor heat converter 171, be connected to indoor heat converter 111 another sides and receive therein temporarily cold-producing medium receiver 221, be used for the cold-producing medium in the receiver is aspirated and thereby the pump 231 of this cold-producing medium that circulates and be used to make second pipe 239 by the cold-producing medium circulation of these pump 231 suctions.
Preferably, this first circulator 150 and second circulator 200 are configured to be arranged in the outdoor unit in the outdoor chamber.Oil and cold-producing medium that this first circulator 150 is configured to all be contained in the compressor 151 can be along 193 circulations of first pipe, so that cooling and lubricate compressors 151.Second circulator 200 is configured to, and the cold-producing medium of oil-containing can circulate along second pipe 239.
Each indoor unit 100 comprises and is used to make the indoor heat converter 111 of cold-producing medium and room air heat exchange and be arranged in the control valve 113 that indoor heat converter 111 1 sides are used to control refrigerant flow.The tube connector 115 that is used to connect each indoor unit 100 is arranged in the both sides of each indoor unit 100.The 3rd hygrosensor 121 that is used to survey refrigerant temperature is installed in the mid portion of each indoor heat converter 111.In addition, the 8th hygrosensor 125 that is used to survey indoor heat converter 111 outlet refrigerant temperatures correspondingly is installed in the outlet of indoor heat converter 111.The 4th hygrosensor 123 that is used to survey each indoor heat converter 111 outlet temperature correspondingly is installed in the inlet of each indoor heat converter 111.
Be used to survey the 7th hygrosensor 217 of intermediate heat exchanger 211 outlet temperatures and outlet pressure and the 3rd pressure detector 219 and be installed in intermediate heat exchanger 211 outlets respectively along the flow direction of cold-producing medium when the heating operation.In addition, be used to survey the 5th hygrosensor 213 of intermediate heat exchanger 211 outlet temperatures and outlet pressure and first pressure detector 215 and be installed in intermediate heat exchanger 211 inlets respectively along the flow direction of the cold-producing medium when the cooling down operation.
The cold-producing medium water level detector 223 that is used to survey liquid refrigerant water level in receiver 221 is arranged in the receiver 221.The 4th pressure detector 232 that is used for detection pressure is arranged on the outlet of pump 231.Be used to stop the check-valves 237 of back flow of refrigerant to be arranged between the pump 231 and second cross valve 235.
The 9th hygrosensor 261 that is used to survey refrigerant temperature is arranged in the outlet of subcooler 250 along the flow direction of cold-producing medium when the heating operation.In addition, be used to survey the tenth hygrosensor 263 of refrigerant temperature and refrigerant pressure and the inlet that the 6th pressure detector 265 is installed in subcooler 250 respectively.As shown in Figure 7, first bypass 255 is arranged on a side of this subcooler 250, and wherein this first bypass 255 is used to make by second cross valve 235 and walks around to the abundant overcooled cold-producing medium of this subcooler 250.One end of first bypass 255 branches off between the 6th pressure detector 265 and the tenth hygrosensor 263, and the other end of first bypass 255 is combined between subcooler 250 and the 9th hygrosensor 261.First valve 256 and second valve 257 that are used for opening and closing selectively each passage are separately positioned on these subcooler 250 upper ends and first bypass, 255 upper ends.
When selecting the heating operation of indoor unit 100, controller 300 is according to the load capacity control compressor 151 and first cross valve 161 of driven indoor unit 100, thereby the cold-producing medium of first circulator 150 is along 193 circulations of the pipe of first shown in Fig. 4 dotted arrow.Simultaneously, controller 300 control pumps 231 and second cross valve 235, thus the cold-producing medium of second circulator 200 can be along 239 circulations of second pipe, to carry out heating operation in indoor unit 100 shown in Fig. 4 solid arrow.
The cold-producing medium that is discharged by compressor 151 compressions is introduced in first outdoor heat converter 171 via first cross valve 161, with the cold-producing medium heat exchange of passing through this indoor heat converter 111, is condensed then then.Condensed refrigerant flows along the second outside expander 177 and second bypass 178, is depressurized via the first outside expander 191 then, thereby is introduced in second outdoor heat converter 181.Then, in second outdoor heat converter 181, cold-producing medium and outdoor air carry out heat exchange, are pumped in the compressor 151 via reservoir 153 then, thereby are compressed repeatedly and discharge.
According to the end value by second hygrosensor 175 and the one 173 detection, second crosses the mistake that adds temperature calculator 323 calculating first outdoor heat converter 171 adds temperature.The 3rd adds temperature calculator 315 excessively converts the pressure that detect by second pressure detector 155 to saturation temperature, calculate then in this inversion temperature with by the difference between the temperature of the 6th hygrosensor 157 detections, i.e. the heating degree of going into to make a slip of the tongue of compressor 151.When the outlet supercooling degree of first outdoor heat converter 171 surpasses a certain value, and the heating degree of going into to make a slip of the tongue of compressor 151 is when surpassing a certain value, and controller 300 is controlled the open degree of the first outside expander 191 with increase.Therefore, the circulating mass of refrigerant of first circulator 150 increases.
When pump 231 was driven, the liquid refrigerant in receiver 221 flowed to intermediate heat exchanger 211 via pump 231, check-valves 237 and second cross valve 235.Then, liquid refrigerant is by 171 heat exchanges of first outdoor heat converter.Here, current probe 331 is surveyed the input current that is input to pump 231 and is changed, and cold-producing medium water level detector 223 is surveyed the water level of liquid refrigerant in receiver 221 simultaneously.The 4th pressure detector 232 is surveyed the outlet pressure of pump 231, and the 7th hygrosensor 217 and the 3rd pressure detector 219 are surveyed the outlet temperature and the outlet pressure of intermediate heat exchanger 211 respectively.The 4th adds temperature calculator 317 excessively converts the outlet pressures that detect to saturation temperature, calculates then in this inversion temperature with by the difference between the temperature of the 7th hygrosensor 217 detections, i.e. the heating degree that goes out to make a slip of the tongue of intermediate heat exchanger 211.
The revolutions per minute of controller 300 control pumps 231 is so that the outlet pressure of the pump that detects 231 can be greater than the outlet pressure of intermediate heat exchanger 211.When the input current variable quantity of surveying by current probe 331 that is input to pump 231 reached certain hour above a certain value, controller 300 reduced the revolutions per minute of pump 231, has stoped gas refrigerant to be introduced in the pump 231 like this.When the liquid refrigerant water level of surveying by cold-producing medium water level detector 223 reduced to predetermined water level (lower limit), the revolutions per minute (frequency) of controller 300 control pumps 231 did not increase, and has stoped gas refrigerant to be introduced in the pump 231 like this.When increasing by the 4th heating degree that goes out to make a slip of the tongue of crossing the intermediate heat exchanger 211 that adds 317 calculating of temperature calculator, controller 300 increases the revolutions per minute of pumps 231.On the contrary, when reducing by the 4th heating degree that goes out to make a slip of the tongue of crossing the intermediate heat exchanger 211 that adds 317 calculating of temperature calculator, controller 300 reduces the revolutions per minute of pumps 231.
Passed through the driven indoor unit 100 of refrigerant flow direction of the cold-producing medium heat exchange of the intermediate heat exchanger 211 and first outdoor heat converter 171, and in indoor heat converter 111 and room air heat exchange, thereby heating operation carried out.Then, cold-producing medium is introduced into subcooler 250 via the control valve 113 and second cross valve 235.Here, the 3rd hygrosensor 121 and the 8th hygrosensor 125 are surveyed the temperature and indoor heat converter 111 outlet temperatures of indoor heat converter 111 mid portions respectively.According to the temperature that is detected of indoor heat converter 111 mid portions and outlet, the 3rd supercooling degree calculator 325 calculates the supercooling degree of indoor heat converter 111.As shown in Figure 8, when the 5th pressure sensor 127 of the outlet pressure that is provided for surveying indoor heat converter 111, controller 300 is converted into saturation temperature to the pressure of surveying by the 5th pressure detector 127.Then, controller 300 calculates the difference between the outlet temperature of this inversion temperature and the indoor heat converter 111 surveyed by the 8th hygrosensor 125, i.e. indoor heat converter 111 outlet supercooling degree, thereby control control valve 113.
When the calculating supercooling degree of the indoor heat converter of surveying by the 3rd supercooling degree calculator 325 111 increased, the open degree of controller 300 control control valves 113 was to increase.On the contrary, when the supercooling degree that calculates reduced, the open degree of controller 300 control control valves 113 was to reduce.When the degree of supercooling of the indoor heat converter 111 of the static indoor unit 100 that calculates by the 3rd supercooling degree calculator 325 greater than preset value, controller 300 can regather operation by opening corresponding control valve 113 execution liquid refrigerants, and this operation is used for the liquid refrigerant in 111 condensations of respective chambers heat exchanger is regathered.
The cold-producing medium that has been introduced into subcooler 250 is from subcooler 250 radiation, thereby is condensed.Then, cold-producing medium is introduced into receiver 221, is discharged into indoor unit 100 by pump 231 then, and these steps repeat.Here, the tenth hygrosensor 263 and the 6th pressure detector 265 are surveyed the inlet temperature and the inlet pressure of subcooler 250 respectively.In addition, the 9th hygrosensor 261 is surveyed the outlet temperature of subcooler 250.The 4th supercooling degree calculator 327 is converted into saturation temperature to the inlet pressure of subcooler 250, and calculates the inlet supercooling degree of subcooler 250 according to the difference between the detection inlet temperature of this inversion temperature and subcooler 250.In addition, according to the difference between the detection outlet temperature of this inversion temperature and subcooler 250, the 4th supercooling degree calculator 327 calculates the outlet supercooling degree of subcooler 250.When the inlet supercooling degree of subcooler 250 during less than predetermined value, the supercooling amount of controller 300 control subcoolers 250 is so that the outlet supercooling degree of subcooler 250 can be greater than predetermined value.As shown in Figure 7, when the inlet supercooling degree of subcooler 250 during greater than predetermined value, controller 300 is controlled first valve 256 and second valve 257 respectively, so that this cold-producing medium can flow along first bypass 255.
When the evaporation capacity of the intermediate heat exchanger 211 along with indoor unit 100 load increases increases, the intermediate heat exchanger 211 heating degree reduction that goes out to make a slip of the tongue.When the evaporation capacity of middle heat exchanger 211 increased, the pressure drop of condensing of first outdoor heat converter 171 of first circulator 151 was low, and the discharge pressure of compressor 151 reduces.Here, controller 300 is at first controlled the revolutions per minute of compressor 151, then the revolutions per minute of control pump 231.
When the supercooling degree of the indoor heat converter 111 along with indoor unit 100 load reductions reduces,, controller 300 stop gas refrigerant to be introduced in the pump 231 thereby reducing the revolutions per minute of pump 231.
When changing the compression volume of compressor 151 for the security control of first circulator 150, controller 300 revolutions per minute of control pump 231 at first before control compressor 151 volume change is in order to avoid gas refrigerant is introduced in the pump 231.
For example, under the oil equalizing operation situation between a plurality of compressors 151, controller 300 is at first according to being operated then and want driven compressor 151 by the revolutions per minute of compressor 151 each compression volume control pump 231 of driven.
When comprising the revolutions per minute of at least one frequency-changeable compressor and constant velocity type compressor and frequency-changeable compressor, compressor 151 reduces to when being used to drive the low-limit frequency of constant velocity type compressor, controller 300 at first according to the revolutions per minute of frequency-changeable compressor low-limit frequency control pump 231, drives the constant velocity type compressor then.
When implementing the cooling down operation of indoor unit 100, controller 300 controls first cross valve 161, so that the cold-producing medium of discharging from compressor 151 can be introduced into second outdoor heat converter 181 and control second cross valve 235 simultaneously, so that the cold-producing medium that is sucked can be introduced into intermediate heat exchanger 211.The control that is used for cooling down operation is similar to above-mentioned control in Fig. 2 and 3.Therefore, the detailed description of control cooling down operation will be omitted, and explanation be flow through each cold-producing medium stream of first circulator 150 and second circulator 200.
Thereby the cold-producing medium that is discharged by compressor 151 compressions is introduced into second outdoor heat converter 181, thereby is condensed, and is depressurized via the second outside expander 177 then.Latent heat around this post-decompression cold-producing medium absorbs in first outdoor heat converter 171, thus evaporation is introduced into reservoir 153 via first cross valve 161 then.Then, the gas refrigerant in reservoir 153 is drawn into capable compressor 151, thereby is compressed and discharges, and these steps are carried out repeatedly.
Cold-producing medium by pump 231 suction is introduced into via second cross valve 235 in the indoor heat converter 111 of indoor unit 100 of driving, and with the room air heat exchange, thereby carry out cooling down operation.Then, the cold-producing medium that executes cooling down operation is introduced into intermediate heat exchanger 211, and carries out heat exchange by the cold-producing medium of the intermediate heat exchanger 211 and first outdoor heat converter 171, thereby has lower temperature.Cold-producing medium by intermediate heat exchanger 211 is introduced into receiver 221 via second cross valve 235 and subcooler 250, and circulates along second pipe 239 by pump 231, thereby carries out cooling down operation.
As mentioned above, in second refrigerant pump driving type air conditioner according to the present invention, the tube connector length that outdoor unit is connected to indoor unit and the restriction on the diameter have been reduced, thereby the restriction on the mounting distance between outdoor unit and the indoor unit has also been reduced.In addition, shorten the cold-producing medium peripheral passage of oil-containing, thereby stoped the oil shortage of compressor.
Because the present invention can have some forms when not breaking away from its spirit or necessary characteristic, therefore it is to be further understood that, unless otherwise mentioned, the foregoing description can't help above to describe any details restriction, but should think briefly that in the spirit and scope that the accessory claim book limits the equivalency range that therefore belongs to the interior all changes of claims scope and modification or this scope is included by additional claims.
Claims (13)
1. refrigerant pump driving type air conditioner comprises:
Indoor unit with indoor heat converter, wherein this indoor heat converter makes not that the cold-producing medium and the room air of oil-containing carry out heat exchange;
First circulator, this first circulator comprise compression and discharging refrigerating agent containing oil compressor, be connected to compressor first side make first outdoor heat converter from the cold-producing medium of this compressor discharge and the cold-producing medium heat exchange of oil-containing not, be connected to compressor second side make from second outdoor heat converter of the cold-producing medium of compressor discharge and outdoor air heat exchange and be connected to first outdoor heat converter and second outdoor heat converter so that from the cold-producing medium decompression of compressor discharge and the outdoor expander of expansion;
Second circulator, this second circulator comprise be connected to indoor heat converter first side so that not the intermediate heat exchanger of the cold-producing medium of oil-containing and cold-producing medium heat exchange in first outdoor heat converter, be connected to indoor heat converter second side and receive from the receiver of the cold-producing medium of indoor heat converter discharging, and the cold-producing medium that suction is received by receiver is so that make the pump of cold-producing medium circulation; And
Controller, the revolutions per minute of this controller control pump (rpm) is introduced into gas refrigeration dosage in the pump with minimizing.
2. according to the air-conditioner of claim 1, also comprise:
Survey first hygrosensor and second hygrosensor of first outdoor heat converter inlet cold-producing medium and outlet refrigerant temperature; And
Cross and to add the temperature calculator according to numerical computations first outdoor heat converter that provides by first hygrosensor and second hygrosensor first of the heating degree that goes out to make a slip of the tongue, wherein first outdoor heat converter is connected to the suction port of compressor, second outdoor heat converter is connected to compressor outlet, and controller is according to crossing the open degree add the outdoor expander of Numerical Control that the temperature calculator provides by first.
3. according to the air-conditioner of claim 2, also comprise:
Be arranged in the control valve of indoor heat converter one side, control refrigerant flow;
Detection is at the 3rd hygrosensor of indoor heat converter central part refrigerant temperature;
The 4th hygrosensor of heat exchanger outlet refrigerant temperature in the detecting chamber; And
Heat exchanger outlet is crossed and is added second of temperature and cross and add the temperature calculator in the counting chamber, and its middle controller adds the Numerical Control control valve open degree that the temperature calculator provides according to crossing by second.
4. according to the air-conditioner of claim 3, also comprise:
Survey the 5th hygrosensor of intermediate heat exchanger outlet refrigerant temperature;
Survey first pressure detector of intermediate heat exchanger outlet refrigerant pressure; And
According to the first supercooling degree calculator of the numerical computations intermediate heat exchanger outlet supercooling degree that is provided by the 5th hygrosensor and first pressure detector, its middle controller is according to the refrigerant amount of the Numerical Control that is provided by the first supercooling degree calculator by the pump discharging.
5. according to the air-conditioner of claim 1, also comprise:
Survey first hygrosensor and second hygrosensor of first outdoor heat converter inlet cold-producing medium and outlet refrigerant temperature;
Supercooling degree calculator, it is according to the outlet supercooling degree of numerical computations first outdoor heat converter that is provided by first hygrosensor and second hygrosensor;
Survey the 3rd hygrosensor and the pressure detector of suction port of compressor refrigerant temperature and pressure; And
Cross the mistake that adds temperature according to the numerical computations suction port of compressor that provides by the 3rd hygrosensor and pressure detector and add the temperature calculator, wherein first outdoor heat converter is connected to compressor outlet, second outdoor heat converter is connected to the suction port of compressor, and cross when adding temperature greater than predetermined value greater than predetermined value and suction port of compressor when first outdoor heat converter outlet supercooling degree, controller increases outside expander open degree.
6. according to the air-conditioner of claim 1, also comprise:
Survey the pressure detector of intermediate heat exchanger outlet refrigerant pressure;
Survey the hygrosensor of intermediate heat exchanger outlet refrigerant temperature; And
Calculate intermediate heat exchanger go out the to make a slip of the tongue mistake of heating degree according to the pressure and temperature of intermediate heat exchanger outlet cold-producing medium and add the temperature calculator, wherein first outdoor heat converter is connected to compressor outlet, second outdoor heat converter is connected to the suction port of compressor, and the revolutions per minute of controller control pump, so that the mistake that the heating degree that goes out to make a slip of the tongue of intermediate heat exchanger is arranged to expect adds temperature.
7. according to the air-conditioner of claim 1, also comprise:
Be arranged in the control valve of indoor heat converter one side, control refrigerant flow; And
The 3rd supercooling degree calculator of heat exchanger outlet supercooling degree in the counting chamber, wherein first outdoor heat converter is connected to compressor outlet, second outdoor heat converter is connected to the suction port of compressor, and controller control control valve, so that the supercooling degree that the supercooling degree of indoor heat converter is arranged to expect.
8. according to the air-conditioner of claim 1, also comprise and be connected to indoor heat converter one side, the cold-producing medium by indoor heat converter is carried out overcooled subcooler, wherein first outdoor heat converter is connected to the outlet of compressor, second outdoor heat converter is connected to the inlet of compressor, and controller is controlled this subcooler is introduced into the gas refrigerant in the pump with minimizing amount.
9. air-conditioner according to Claim 8 also comprises:
Survey the 6th pressure detector of subcooler inlet refrigerant pressure;
Survey the 9th hygrosensor of the temperature of subcooler outlet cold-producing medium;
Survey the tenth hygrosensor of the temperature of subcooler inlet cold-producing medium; And
Supercooling degree calculator, it is according to the outlet supercooling degree of the numerical computations subcooler that is provided by the 6th pressure detector and the 9th and the tenth hygrosensor.
10. according to the air-conditioner of claim 9, also comprise: first bypass, this first bypass have first side that is connected to the subcooler inlet and are connected to second side of this subcooler outlet;
Be arranged in first valve of subcooler inlet, this subcooler inlet of opening and closing; And
Second valve of opening and closing first bypass, wherein when the inlet supercooling degree of subcooler during greater than predetermined value, controller is controlled first valve and second valve, so that cold-producing medium is walked around subcooler.
11., also comprise according to each described air-conditioner among the claim 1-10:
Be connected to first cross valve of compressor outlet, be used to switch the coolant channel of first cycling element; With
Be connected to second cross valve of pump discharge, be used to switch the coolant channel of second cycling element, its middle controller is controlled first cross valve and second cross valve, makes each coolant channel to be switched according to the drive pattern of indoor unit.
12. according to each described air-conditioner among the claim 1-10, wherein compressor constructions is a plurality of, and the revolutions per minute that controller comes control pump according to the capacity of wanting driven compressor when the oil equalizing operation of compressor, driven compressor is wanted in operation then.
13. according to each described air-conditioner among the claim 1-10, wherein compressor is provided with at least one frequency-changeable compressor and constant velocity type compressor, and controller control frequency-changeable compressor with have be used to drive the low-limit frequency of constant velocity type compressor before, according to the revolutions per minute of the low-limit frequency control pump of frequency-changeable compressor, control frequency-changeable compressor then to have low-limit frequency.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020050016281A KR100748519B1 (en) | 2005-02-26 | 2005-02-26 | Secondary refrigerant pump driven air conditioner |
| KR1020050016282 | 2005-02-26 | ||
| KR1020050016281 | 2005-02-26 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1825008A CN1825008A (en) | 2006-08-30 |
| CN100451464C true CN100451464C (en) | 2009-01-14 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2006100549739A Expired - Fee Related CN100451464C (en) | 2005-02-26 | 2006-02-27 | Second-refrigerant pump driving type air conditioner |
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| Country | Link |
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| KR (1) | KR100748519B1 (en) |
| CN (1) | CN100451464C (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2341296B1 (en) * | 2008-10-29 | 2018-08-08 | Mitsubishi Electric Corporation | Air conditioner |
| JP5178841B2 (en) | 2008-10-29 | 2013-04-10 | 三菱電機株式会社 | Air conditioner |
| CN201589348U (en) * | 2010-02-04 | 2010-09-22 | 珠海格力电器股份有限公司 | Household air conditioner using secondary refrigerant and air conditioner outdoor unit |
| WO2011099063A1 (en) * | 2010-02-10 | 2011-08-18 | 三菱電機株式会社 | Air-conditioning device |
| KR101201635B1 (en) * | 2010-09-27 | 2012-11-20 | 엘지전자 주식회사 | An air conditioner |
| CN102853583A (en) * | 2012-10-12 | 2013-01-02 | 天津商业大学 | Heat pump system |
| CN104110740B (en) * | 2014-07-25 | 2017-01-11 | 珠海格力电器股份有限公司 | Air conditioning system and control method thereof |
| CN105402818B (en) * | 2015-12-22 | 2018-02-06 | 广东美的暖通设备有限公司 | Multiple on-line system and its purging method |
| CN107869865B (en) * | 2016-09-27 | 2020-09-01 | 维谛公司 | Method for controlling superheat level during pump mode of operation and refrigeration system |
| CN110462309B (en) * | 2017-03-27 | 2022-03-01 | 大金工业株式会社 | Heat exchanger and refrigerating apparatus |
| KR102165354B1 (en) * | 2018-07-20 | 2020-10-13 | 엘지전자 주식회사 | An air conditioning system and a method for controlling the same |
| KR20210094213A (en) * | 2020-01-21 | 2021-07-29 | 엘지전자 주식회사 | An air conditioning apparatus |
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|---|---|---|---|---|
| EP0887599A1 (en) * | 1996-12-27 | 1998-12-30 | Daikin Industries, Limited | Refrigeration apparatus and method of manufacturing same |
| JP2004177067A (en) * | 2002-11-29 | 2004-06-24 | Hitachi Home & Life Solutions Inc | Heat pump type air conditioner |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR0164745B1 (en) * | 1994-08-30 | 1999-03-20 | 김광호 | Detachable Air Conditioner |
| KR20000073046A (en) | 1999-05-04 | 2000-12-05 | 구자홍 | Drive controlling apparatus and the same method for air conditioner |
| KR100395919B1 (en) | 2000-06-07 | 2003-08-27 | 삼성전자주식회사 | Control system of degree of superheat of air conditioner and control method thereof |
-
2005
- 2005-02-26 KR KR1020050016281A patent/KR100748519B1/en not_active IP Right Cessation
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- 2006-02-27 CN CNB2006100549739A patent/CN100451464C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0887599A1 (en) * | 1996-12-27 | 1998-12-30 | Daikin Industries, Limited | Refrigeration apparatus and method of manufacturing same |
| CN1216607A (en) * | 1996-12-27 | 1999-05-12 | 大金工业株式会社 | Refrigeration apparatus and method of manufacturing same |
| KR100360966B1 (en) * | 1996-12-27 | 2003-04-21 | 다이킨 고교 가부시키가이샤 | Refrigeration apparatus and manufacturing method thereof |
| JP2004177067A (en) * | 2002-11-29 | 2004-06-24 | Hitachi Home & Life Solutions Inc | Heat pump type air conditioner |
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|---|---|
| KR100748519B1 (en) | 2007-08-13 |
| CN1825008A (en) | 2006-08-30 |
| KR20060094802A (en) | 2006-08-30 |
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