CN102466361A - Air conditioner - Google Patents
Air conditioner Download PDFInfo
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- CN102466361A CN102466361A CN2011100710859A CN201110071085A CN102466361A CN 102466361 A CN102466361 A CN 102466361A CN 2011100710859 A CN2011100710859 A CN 2011100710859A CN 201110071085 A CN201110071085 A CN 201110071085A CN 102466361 A CN102466361 A CN 102466361A
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- Prior art keywords
- compressor
- expansion valve
- air regulator
- heat exchanger
- cold
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
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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
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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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
- F25B49/022—Compressor control 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0401—Refrigeration circuit bypassing means for the compressor
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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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
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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
- 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
- F25B2400/13—Economisers
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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
- F25B2400/23—Separators
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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)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Disclosed is an air conditioner including a plurality of compressors compressing a refrigerant, a first heat exchanger for condensing the refrigerant compressed in the compressor, a first expansion valve for expanding the condensed refrigerant, a second expansion valve for expanding the refrigerant emerging from the first expansion valve, a second heat exchanger for evaporating the refrigerant emerging from the second expansion valve. The refrigerant from the first expansion valve is guided such that a portion of the refrigerant is introduced into one of the compressors after bypassing the second expansion valve and second heat exchanger, and a remaining portion of the refrigerant is introduced into another one of the compressors after passing through the second expansion valve and second heat exchanger, to minimize electric power consumption and to enhance heating performance.
Description
Technical field
The present invention relates to a kind of air regulator, particularly have the air regulator of a plurality of compressors.
Background technology
In general, air regulator is in order to build more comfortable indoor environment to the user, to utilize the kind of refrigeration cycle of the cold-producing medium that is made up of compressor, condenser, expansion mechanism and evaporimeter, to the indoor machine that carries out cooling and warming or purify air.
Recently, a plurality of compressors are located on the off-premises station, optionally drive single or a plurality of compressors according to load, and a plurality of compressors comprise first compressor and second compressor that cold-producing medium suction passage and cold-producing medium discharge stream are connected in parallel.
When the load of first compressor and second compressor hour, only drive any in first compressor and second compressor, when load is big, drive first compressor and second compressor simultaneously.
When driving first compressor and second compressor simultaneously; In first compressor compressed cold-producing medium and in second compressor compressed cold-producing medium and be drawn into first compressor and second compressor successively through being distributed to first compressor and second compressor after indoor heat converter, expansion mechanism and the outdoor heat converter with the state of low-temp low-pressure.
According to the air regulator of prior art, owing to the cold-producing medium that makes low-temp low-pressure is drawn into first compressor and second compressor is compressed, the problem that circulating mass of refrigerant is many therefore the power consumption height appears.
Summary of the invention
The present invention is suggested in order to address the above problem, and its purpose is to provide a kind of can reduce power consumption with most preferably corresponding to heating load, can increase the air regulator of heating capacity.
The air regulator according to the present invention that is used to reach above-mentioned purpose comprises: first compressor; Second compressor makes the respectively parallel connection and being connected with above-mentioned first compressor of refrigerant suction pipe and refrigerant discharge leader; First heat exchanger makes the cold-producing medium evaporation when refrigeration, when heating, make condensation of refrigerant; Second heat exchanger makes condensation of refrigerant when refrigeration, when heating, make the cold-producing medium evaporation; First expansion valve is located between above-mentioned first heat exchanger and second heat exchanger; Second expansion valve is located between above-mentioned first expansion valve and second heat exchanger; Bypass mechanism; Be connected between the branch point and above-mentioned second compressor of above-mentioned refrigerant suction pipe, so that passed through that a part in the cold-producing medium of above-mentioned first expansion valve is walked around above-mentioned second expansion valve and above-mentioned second heat exchanger is directed between the branch point and above-mentioned second compressor of above-mentioned refrigerant suction pipe; And check valve, be located between the tie point of branch point and above-mentioned bypass mechanism of above-mentioned refrigerant suction pipe, be used to block the cold-producing medium that has passed through above-mentioned bypass mechanism and flow to the branch point of above-mentioned refrigerant suction pipe.
The running capacity of above-mentioned second compressor is less than the running capacity of above-mentioned first compressor.
Above-mentioned first compressor is a compressor with variable volume, and above-mentioned second compressor is a constant speed compressor.
Above-mentioned air regulator has the second compressor single driving operation mode and first compressor-second compressor drives operation mode simultaneously; Under the above-mentioned second compressor single driving operation mode; Above-mentioned second compressor is able to drive; And make the cold-producing medium that has passed through above-mentioned first expansion valve through flowing to above-mentioned second compressor after above-mentioned second expansion valve and above-mentioned second heat exchanger; Drive simultaneously under the operation mode at above-mentioned first compressor-second compressor; Above-mentioned first compressor and second compressor are able to drive; And make a part in the cold-producing medium that has passed through above-mentioned first expansion valve walk around above-mentioned second expansion valve and above-mentioned second heat exchanger flow to above-mentioned second compressor, and make remainder in the cold-producing medium that has passed through above-mentioned first expansion valve through flowing to above-mentioned first compressor after above-mentioned second expansion valve and above-mentioned second heat exchanger.
The above-mentioned second compressor single driving operation mode optionally implemented by above-mentioned air regulator and above-mentioned first compressor-second compressor drives operation mode simultaneously.
Above-mentioned air regulator also has the first compressor single driving operation mode; Under this first compressor single driving operation mode; Above-mentioned first compressor is able to drive, and makes the cold-producing medium that has passed through above-mentioned first expansion valve through flowing to above-mentioned first compressor after above-mentioned second expansion valve and above-mentioned second heat exchanger.
Above-mentioned air regulator is optionally implemented the above-mentioned second compressor single driving operation mode, above-mentioned first compressor-second compressor drives the operation mode and the first compressor single driving operation mode simultaneously.
Above-mentioned bypass mechanism comprises: inner heat exchanger, and it comprises second stream that first stream that cold-producing medium flows and the cold-producing medium that makes cold-producing medium with above-mentioned first stream carry out heat exchange are passed through between above-mentioned first expansion valve and second expansion valve; First bypass flow path, one of which end are connected between first stream and first expansion valve of above-mentioned inner heat exchanger, and the other end is connected above-mentioned second stream; And second bypass flow path, the one of which end is connected above-mentioned second stream, and the other end is connected the suction line of above-mentioned second compressor.
Above-mentioned bypass mechanism also comprises the 3rd expansion valve that is located on above-mentioned first bypass flow path.
The capacity of above-mentioned the 3rd expansion valve is less than the capacity of above-mentioned first expansion valve and second expansion valve.
When above-mentioned air regulator is in when heating part load condition, above-mentioned second compressor is able to drive, and above-mentioned first compressor stops, and above-mentioned the 3rd expansion valve cuts out; When above-mentioned air regulator is in when heating the full load state, above-mentioned first compressor and second compressor are able to drive, and above-mentioned the 3rd expansion valve is open.
Above-mentioned bypass mechanism comprises: gas-liquid separator, and it is located between above-mentioned first expansion valve and second expansion valve; And gas-liquid separator connection stream, the one of which end is connected above-mentioned gas-liquid separator, and the other end is connected the suction line of above-mentioned second compressor, so that the gaseous refrigerant of above-mentioned gas-liquid separator flow to the suction line of above-mentioned second compressor.
Above-mentioned bypass mechanism comprises that also being located at above-mentioned gas-liquid separator connects the 3rd expansion valve on the stream.
The capacity of above-mentioned the 3rd expansion valve is less than the capacity of above-mentioned first expansion valve and second expansion valve.
When above-mentioned air regulator is in when heating part load condition, above-mentioned second compressor is able to drive, and above-mentioned first compressor stops, and above-mentioned the 3rd expansion valve cuts out; When above-mentioned air regulator is in when heating the full load state, above-mentioned first compressor and second compressor are able to drive, and above-mentioned the 3rd expansion valve is open.
Description of drawings
A plurality of characteristic of the present invention and advantage can be through the detailed description of the embodiment of the invention of following and following accompanying drawings, and this will be best understood, in the above-mentioned accompanying drawing:
Fig. 1 is the loop structure figure of air regulator one embodiment of the present invention;
The loop structure figure of flow of refrigerant when Fig. 2 is the first compressor single driving of expression air regulator one embodiment of the present invention;
The loop structure figure of flow of refrigerant when Fig. 3 is the second compressor single driving of expression air regulator one embodiment of the present invention;
Fig. 4 is the loop structure figure of the flow of refrigerant of first compressor and second compressor of expression air regulator one embodiment of the present invention when driving simultaneously;
Fig. 5 is based on the P-h line chart of a plurality of driven compressor patterns of air regulator one embodiment of the present invention;
Fig. 6 is the loop structure figure of another embodiment of air regulator of the present invention;
The loop structure figure of flow of refrigerant when Fig. 7 is the first compressor single driving of expression another embodiment of air regulator of the present invention;
The loop structure figure of flow of refrigerant when Fig. 8 is the second compressor single driving of expression another embodiment of air regulator of the present invention;
Fig. 9 is the loop structure figure of the flow of refrigerant of first compressor and second compressor of expression another embodiment of air regulator of the present invention when driving simultaneously;
Figure 10 is based on the P-h line chart of a plurality of driven compressor patterns of another embodiment of air regulator of the present invention.
The specific embodiment
Below, can realize particularly that through reference the accompanying drawing of a plurality of embodiment of the present invention of above-mentioned purpose describes.
Fig. 1 is the loop structure figure of air regulator one embodiment of the present invention; The loop structure figure of flow of refrigerant when Fig. 2 is the first compressor single driving of expression air regulator one embodiment of the present invention; The loop structure figure of flow of refrigerant when Fig. 3 is the second compressor single driving of expression air regulator one embodiment of the present invention; Fig. 4 is the loop structure figure of the flow of refrigerant of first compressor and second compressor of expression air regulator one embodiment of the present invention when driving simultaneously, and Fig. 5 is based on the P-h line chart of a plurality of driven compressor patterns of air regulator one embodiment of the present invention.
Air regulator according to present embodiment comprises: a plurality of compressors 2,8, its compressed refrigerant; First heat exchanger 10, it makes compressed condensation of refrigerant in compressor 2,8; First expansion valve 40, it expands the cold-producing medium that in first heat exchanger 10, is condensed; Second expansion valve 42, it is configured such that the cold-producing medium that has passed through first expansion valve 40 expands; Second heat exchanger 14, it makes the cold-producing medium evaporation of having passed through second expansion valve 42; And variable refrigerant stream 46, its guiding has been passed through the cold-producing medium of first expansion valve 40 and has perhaps been walked around second expansion valve 42 and second heat exchanger 14 through second expansion valve 42 and second heat exchanger 14.
Part in the cold-producing medium of variable refrigerant stream 46 guiding having passed through first expansion valve 40 walks around second expansion valve 42 and second heat exchanger 14 flow into a compressor 8 in a plurality of compressors; And guide the remainder in the cold-producing medium that has passed through first expansion valve 40 to flow into another compressor 2 in a plurality of compressors 2,8 afterwards through second expansion valve 42 and second heat exchanger 14, perhaps guide the whole cold-producing mediums that passed through first expansion valve 40 to flow at least one compressor 8 in a plurality of compressors 2,8 through second expansion valve 42 and second heat exchanger 14.
The whole cold-producing medium of variable refrigerant stream 46 guiding having passed through first expansion valve 40 is through only flowing into a compressor 8 in a plurality of compressors 2,8 after second expansion valve 42 and second heat exchanger 14; And guide the whole cold-producing mediums that passed through first expansion valve 40 only to flow into another compressor 2 in a plurality of compressors 2,8 afterwards through second expansion valve 42 and second heat exchanger 14, and whole cold-producing mediums that first expansion valve 40 has been passed through in guiding are through disperseing to flow into a plurality of compressors 2,8 after second expansion valve 42 and second heat exchanger 14.
With regard to a plurality of compressor 2, with regard to 8, can be provided with more than two or three, below to comprise first compressor 2 and to make refrigerant suction pipe 4 and refrigerant discharge leader 6 parallel connections and the situation of second compressor 8 that is connected with first compressor 2 is that example describes.
When the capacity of first compressor 2 and second compressor 8 not simultaneously; Size according to load; Only drive the little compressor of capacity 8, perhaps only drive compressor 2 capacious, perhaps drive compressor 2 capacious and the little compressor 8 of capacity simultaneously; Preferably, first compressor 2 is different with the capacity of second compressor 8.
Air regulator has a plurality of sub-load operation modes and full load operation pattern, so that corresponding to the multiple running requirements condition of outdoor temperature or indoor desired temperature etc.
The load of air regulator has can be through first's load of the compressor single driving reply that capacity is littler in first compressor 2 and second compressor 8.The load of air regulator has the second portion load that can not pass through the compressor single driving reply that capacity is littler in first compressor 2 and second compressor 8 but can pass through the compressor single driving reply that capacity is bigger in first compressor 2 and second compressor 8.The load of air regulator has and can all drive reply but the full load that can not tackle through the bigger compressor single driving of capacity in first compressor 2 and second compressor 8 through first compressor 2 and second compressor 8.
If the payload of air regulator is below first's load; Then can implement only to drive first's load running of the compressor that capacity is littler in first compressor 2 and second compressor 8; If payload is loaded greater than first's load and smaller or equal to second portion; Then can implement only to drive the second portion load running of the compressor that capacity is bigger in first compressor 2 and second compressor 8; If payload is loaded greater than second portion, then can implement to drive simultaneously the full load operation of first compressor 2 and second compressor 8.
As shown in Figure 2, first's load running pattern is single driving second compressor 8 and makes the cold-producing medium that has passed through first expansion valve 40 through flowing to the second compressor single driving operation mode of second compressor 8 after second expansion valve 42 and second heat exchanger 12.
As shown in Figure 3, second portion load running pattern is single driving first compressor 2 and makes the cold-producing medium that has passed through first expansion valve 40 through flowing to the first compressor single driving operation mode of first compressor 2 after second expansion valve 42 and second heat exchanger 12.
As shown in Figure 4; The full load operation pattern is for driving first compressor 2 and second compressor 8 and make a part in the cold-producing medium that has passed through first expansion valve 40 walk around second expansion valve 42 and second heat exchanger 12 flow to second compressor 8 simultaneously, and makes the remainder in the cold-producing medium that has passed through first expansion valve 40 drive operation mode simultaneously through first compressor-second compressor that flow to first compressor 2 after second expansion valve 42 and second heat exchanger 12.
When air regulator comprises cooling and warming transfer valve 14, optionally implement to freeze and heat.When refrigeration, cooling and warming transfer valve 14 makes the cold-producing medium that compressed flow of refrigerant is evaporated in first heat exchanger 10 in second heat exchanger 12 at least one compressor in first compressor 2 and second compressor 8 be directed to the compressor in the driving.When heating, cooling and warming transfer valve 14 makes the cold-producing medium that compressed flow of refrigerant is evaporated in second heat exchanger 12 in first heat exchanger 10 at least one compressor in first compressor 2 and second compressor 8 be directed to the compressor in the driving.
Cooling and warming transfer valve 14 is connected with first compressor 2 and second compressor 8 respectively by refrigerant suction pipe 4 and refrigerant discharge leader 6; Connect stream 16 by cooling and warming transfer valve-first heat exchanger and be connected, and be connected with second heat exchanger 12 by cooling and warming transfer valve-second heat exchanger connection stream 18 with first heat exchanger 10.
Refrigerant discharge leader 6 has the point 32 that the cold-producing medium from first compressor 2 and 8 discharges of second compressor is converged.Refrigerant discharge leader 6 comprises the shared pipe of the discharge that is connected with cooling and warming transfer valve 14 34 and converges to the discharge pipe 36,38 of discharging shared pipe 34, discharge pipe 36,38 comprise with compressed cold-producing medium in first compressor 2 be directed to first compressor of discharging shared pipe 34 discharge pipe 36 and will be in second compressor 8 compressed cold-producing medium be directed to the discharge pipe 38 of second compressor of discharging shared pipe 34.Discharge side check-valves 37 to first of first compressor 2 being provided with blocking-up compressed flow of refrigerant in second compressor 8 on the first compressor discharge pipe 36, discharge side check-valves 39 to second of second compressor 8 being provided with blocking-up compressed flow of refrigerant in first compressor 2 on the second compressor discharge pipe 38.
Make the indoor expansion valve 11 of the cold-producing medium expansion that flow to first heat exchanger 10 when on indoor set I, being provided with refrigeration, indoor expansion valve 11 is made up of electric expansion valves such as the LEV that can regulate its aperture, EEV.Indoor expansion valve 11 expands the cold-producing medium through second expansion valve 42 and first expansion valve 40 when refrigeration, when heating, all is opened, and the cold-producing medium that flows at first heat exchanger 10 is passed through.
Inner heat exchanger 53 is located between first expansion valve 40 and second expansion valve 42, so that the flow of refrigerant of having passed through first expansion valve 40 is to second expansion valve 42, the flow of refrigerant of having passed through second expansion valve 42 is to first expansion valve 40.
Bypass mechanism 50 also comprises the 3rd expansion valve 56 that is located on first bypass flow path 54.The 3rd expansion valve 56 is made up of electric expansion valves such as the LEV that can regulate its aperture, EEV.The capacity of the 3rd expansion valve 56 is less than the capacity of first expansion valve 40 and second expansion valve 42.If the capacity of the 3rd expansion valve 56 its Capacity Ratio first expansion valves 40 and second expansion valve 42 is big or identical; Liquid refrigerant flow into the possibility of second compressor 8 can be big, is difficult to critically to be adjusted in the pressure and the temperature of the cold-producing medium that first bypass flow path 54 flows.On the contrary; If the 3rd expansion valve 56 its capacity are less than the capacity of first expansion valve 40 and second expansion valve 42; The possibility that liquid refrigerant flow into second compressor 8 can be minimized, and can critically regulate the pressure and the temperature of the cold-producing medium that flow to first bypass flow path 54.The 3rd expansion valve 56 can reduce the pressure of the cold-producing medium that flow to first bypass flow path 54 with the pressure that the condensation that is lower than first heat exchanger 10 presses and be higher than the evaporation of second heat exchanger 12 to press.The 3rd expansion valve 56 is when being in the cooling operation state; Can irrespectively be closed with load; When being in when heating the full load state; Can be so that cold-producing medium be open through the setting aperture that bypass mechanism 50 flow into second compressor 8, when being in when heating part load condition, close and block refrigerant through bypass mechanism 50.
Check valve 60 is located between the tie point 58 of branch point 22 and bypass mechanism 50 of refrigerant suction pipe 4.The check-valves that check valve 60 makes the cold-producing medium that has passed through bypass mechanism 50 not flow to first compressor 2 by the flow of refrigerant that makes the branch point 22 that has passed through refrigerant suction pipe 4 to second compressor 8 time constitutes.
Air regulator is according to heating the size of load, carry out by different way first compressor 2 and second compressor 9 driving, stop and the control of the 3rd expansion valve 56.
Air regulator heats operation mode when being in, and when loading to first's load or second portion load, second compressor 8 drives, and first compressor 2 stops, and the 3rd expansion valve 56 cuts out.
Air regulator heats operation mode when being in, and when loading to full load, first compressor 2 and second compressor 8 drive, and the 3rd expansion valve 56 is open.
Air regulator any in first compressor 2 and second compressor 8 is compressor with variable volume, and when another was constant speed compressor, reply was more diversely loaded.
When first compressor 2 is a compressor with variable volume; When second compressor 8 is constant speed compressor; As stated; Air regulator is according to first's load, second portion load and full load; Do not implement the second compressor single driving operation mode, the first driven compressor operation mode and first compressor-second compressor and drive an operation mode in the operation mode simultaneously,, optionally implement the second compressor single driving operation mode and first compressor-second compressor drives operation mode simultaneously according to first load and full load.
Promptly; If air regulator is through corresponding with the sub-load below the first load and only drive second compressor 8; Just can tackle load; And through with surpass first's load and reach load below the full load corresponding and when only driving second compressor 8 first compressor 2 corresponding and can the change capacity with the residue load, then make the minimized while of power consumption tackle the following sub-load of first's load effectively and reach the load of loading greater than first.
For example; When first compressor 2 is the 5HP compressor with variable volume; When second compressor 8 is the 2HP constant speed compressor; When being in, drive (being the running of the second compressor single driving) second compressor 8, be in the time greater than 2HP and corresponding load (for example 3H, 4H, 5H, 6H, 7H) below the 7HP with sub-load corresponding below the 2HP; First compressor 2 and ability change capacity (be first compressor-second compressor simultaneously drive running) corresponding with residue load (1H, 2H, 3H, 4H, 5H) when driving (2H) second compressor 8, first compressor 2 and second compressor 8 can be tackled the load up to 7H effectively.
On the contrary; When first compressor 2 is a constant speed compressor; When second compressor 8 is compressor with variable volume; According to first's load, second portion load and full load, optionally implement the second compressor single driving operation mode, the first compressor single driving operation mode and first compressor-second compressor and drive operation mode simultaneously.
For example; When first compressor 2 is the 5HP constant speed compressor; When second compressor 8 is the 2HP compressor with variable volume; When being in sub-load corresponding below the 2HP, second compressor 8 is corresponding with load and driven (being the running of the second compressor single driving), is in above the following corresponding sub-load of 2HP and 5HP the time; First compressor 2 is irrespectively driven (promptly with load; First compressor single driving running), be in when surpassing load (for example 6H, 7H) corresponding below the 7HP with 5HP, when first compressor 2 is driven (5HP) second compressor 8 and residue load 1H, 2H is corresponding and ability change capacity (be first compressor-second compressor and drive running simultaneously); First compressor 2 and second compressor 8 can be tackled load corresponding with 0～2H and the load corresponding with 5H～7H effectively, and can tackle and surpass corresponding load below 2HP and the 5HP.
Preferably; When first compressor 2 is a compressor with variable volume; When second compressor 8 was constant speed compressor, air regulator drove operation mode simultaneously according to the second compressor single driving operation mode and first compressor-second compressor, can tackle whole loads more effectively; Thereby first compressor 2 is by constituting than second compressor, 8 compressor with variable volume capacious, and second compressor 8 is by constituting than the little constant speed compressor of first compressor, 2 capacity.
Air regulator can change the volume ratio of first compressor 2 and second compressor 8 through regulating the operating frequency of first compressor 2, through the variation of volume ratio, and according to operating condition, can control the middle pressure that makes efficient reach the best.
Preferably; When first compressor 2 by constituting than second compressor, 8 compressor with variable volume capacious; And second compressor 8 is when constituting than the little constant speed compressor of first compressor, 2 capacity, and air regulator is through single driving second compressor 8, with corresponding load setting being sub-load; And through driving first compressor 2 and second compressor 8 simultaneously, the load setting that ability is corresponding be a full load.Preferably, air regulator is when loading when heating sub-load, and second compressor 8 drives; First compressor 2 stops, and the 3rd expansion valve 56 cuts out, preferably; When load when heating full load, first compressor 2 and 8 drivings of second compressor, 56 openings of the 3rd expansion valve.
Below, with the as above effect of the present invention of formation of explanation at length.
When being in, air regulator heats operation mode; And when second compressor 8 is in the single driving running; Shown in the A of Fig. 2 and Fig. 5; The cold-producing medium that in second compressor 8, is compressed (a) in first heat exchanger 10, be condensed (b); And be inflated (c) afterwards at least one in first expansion valve 40 and second expansion valve 42 through first expansion valve 40, inner heat exchanger 53 and second expansion valve 42 time, in second heat exchanger 12, be evaporated (d), through being recovered to second compressor 2 after the check valve 60 again.When cold-producing medium circulates second compressor 8, first heat exchanger 10, first expansion valve 40, second expansion valve 42, second heat exchanger 12, check valve 60 and second compressor 8 first heat exchanger 10 is heated.
Air regulator since the capacity of second compressor 8 less than the capacity of first compressor 2, therefore when single driving second compressor 8, shown in the A and B of Fig. 5, during compared with single driving first compressor 2, work done during compression is few, condensation is forced down, height is pressed in evaporation.
When being in, air regulator heats running; And when first compressor 2 is in the single driving running; Shown in the B of Fig. 3 and Fig. 5, the cold-producing medium that in first compressor 2, is compressed (e) is condensed (f) in first heat exchanger 10, and is inflated (g) afterwards at least one in first expansion valve 40 and second expansion valve 42 through first expansion valve 40, inner heat exchanger 53 and second expansion valve 42 time; In second heat exchanger 12, be evaporated (h), be recovered to first compressor 2 again.When cold-producing medium circulates first compressor 2, first heat exchanger 10, first expansion valve 40, second expansion valve 42 and second heat exchanger 12 first heat exchanger 10 is heated.
When being in, air regulator heats running; And when driving first compressor 2 and second compressor 8 simultaneously; Shown in the C of Fig. 4 and Fig. 5, D; The cold-producing medium that in first compressor 2, is compressed the cold-producing medium of (i) and in second compressor 8, is compressed (j) will converge, and the cold-producing medium that is converged is condensed in first heat exchanger 10 (k) and through first expansion valve 40.
A part of having passed through the cold-producing medium of first expansion valve 40 flow to first bypass flow path 54, and in the 3rd expansion valve 56, is inflated (l) afterwards, and second stream 52 (m) through inner heat exchanger 53 flow to second bypass flow path 55.The cold-producing medium that flow to second bypass flow path 55 can not be drawn into first compressor 2 by check valve 60, and is drawn into second compressor 8, in second compressor 8, is compressed (j) thus.
On the other hand; Carry out after the heat exchange with the cold-producing medium of second stream 52 through inner heat exchanger 53 in the time of first stream 51 of the remainder that has passed through not flow in the cold-producing medium of first expansion valve 40 first bypass flow path 54 through inner heat exchanger 53; In second expansion valve 42, be inflated (n) and in second heat exchanger 12, be evaporated (o) afterwards, and be drawn into first compressor 2 and be compressed (i).
Air regulator makes cold-producing medium circulate first compressor 2, first heat exchanger 10, first expansion valve 40, inner heat exchanger 53, second expansion valve 42, second heat exchanger 12 and first compressor 2 (C of Fig. 5) as described above, and second compressor 8 that circulates, first heat exchanger 10, first expansion valve 40, the 3rd expansion valve 56, inner heat exchanger 53 and second compressor 8 and first heat exchanger 10 heated (D of Fig. 5).
Air regulator makes the cold-producing medium that has passed through first expansion valve 40, inner heat exchanger 53, second expansion valve 42 and second heat exchanger 12 successively flow into first compressor 2 when driving first compressor 2 and second compressor 8 simultaneously, and makes the cold-producing medium that has passed through first expansion valve 40, the 3rd expansion valve 56 and inner heat exchanger 53 flow into second compressor 8.Air regulator is higher than the pressure of the cold-producing medium that flow into first compressor 2 through the pressure that makes the cold-producing medium that flow into second compressor 8; When comparing with the situation of the cold-producing medium of a compressor compresses low-temp low-pressure; Can consume power consumption less; And, therefore can increase the flow of the cold-producing medium of circulating air adjuster, thereby can raise the efficiency because the density of cold-producing medium is high.
Fig. 6 is the loop structure figure of another embodiment of air regulator of the present invention; The loop structure figure of flow of refrigerant when Fig. 7 is the first compressor single driving of expression another embodiment of air regulator of the present invention; The loop structure figure of flow of refrigerant when Fig. 8 is the second compressor single driving of expression another embodiment of air regulator of the present invention; Fig. 9 is the loop structure figure of the flow of refrigerant of first compressor and second compressor of expression another embodiment of air regulator of the present invention when driving simultaneously, and Figure 10 is based on the P-h line chart according to a plurality of driven compressor patterns of another embodiment of air regulator of the present invention.
To shown in Figure 9, in the air regulator of present embodiment, bypass mechanism 50 comprises the gas-liquid separator 57 that is located between first expansion valve 40 and second expansion valve 42 like Fig. 6.Bypass mechanism 50 comprises that gas-liquid separator connects stream 64; The end that this gas-liquid separator connects stream 64 is connected gas-liquid separator 57; The other end is connected the suction line 28 of second compressor, so that the gaseous refrigerant of gas-liquid separator 62 flow to the suction line 28 of second compressor.Other structures except bypass mechanism and effect are identical or similar with above-mentioned one embodiment of the invention, therefore use same reference numerals and omit the detailed description to it.
Gas-liquid separator 62 is separated in liquid refrigerant and the gaseous refrigerant in the cold-producing medium that is inflated in first expansion valve 40.Gas-liquid separator 62 is connected with first expansion valve 40 by the first expansion valve tube connector, and is connected with second expansion valve 42 by the second expansion valve tube connector.
The capacity of the 3rd expansion valve 66 also can be less than the capacity of first expansion valve 40 and second expansion valve 42.If the 3rd expansion valve 66 its capacity are perhaps identical with it greater than the capacity of first expansion valve 40 and second expansion valve 42; The possibility that liquid refrigerant flows into to second compressor 8 can be big, is difficult to critically to be adjusted in the pressure and the temperature of the gaseous refrigerant that gas-liquid separator 62 flows.On the contrary; If the 3rd expansion valve 66 its capacity are less than the capacity of first expansion valve 40 and second expansion valve 42; Liquid refrigerant can be minimized to the possibility that second compressor 8 flows into, and can critically regulate the pressure and the temperature of the gaseous refrigerant that flow to first bypass flow path 54.
When being in, air regulator heats operation mode; And when second compressor 8 is in the single driving operation mode; Shown in the A of Fig. 7 and Figure 10; Make the cold-producing medium that in second compressor 8, is compressed (a) in first heat exchanger 10, be condensed (b); And be inflated (c) at least one in first expansion valve 40 and second expansion valve 42 through first expansion valve 40, gas-liquid separator 62 and second expansion valve 42 time and in second heat exchanger 12, be evaporated (d) afterwards, through being recovered to second compressor 2 after the check valve 60 again.When cold-producing medium circulates second compressor 8, first heat exchanger 10, first expansion valve 40, gas-liquid separator 62, second expansion valve 42, second heat exchanger 12, check valve 60 and second compressor 8 first heat exchanger 10 is heated.
Air regulator since the capacity of second compressor 8 less than the capacity of first compressor 2, therefore when single driving second compressor 8, shown in the A and B of Figure 10, during compared with single driving first compressor 2, work done during compression is few, condensation is forced down, height is pressed in evaporation.
When being in, air regulator heats operation mode; And when first compressor 2 is in the single driving operation mode; Shown in the B of Fig. 8 and Figure 10; Make the cold-producing medium that in first compressor 2, is compressed (e) in first heat exchanger 10, be condensed (f); And be inflated (g) afterwards at least one in first expansion valve 40 and second expansion valve 42 through first expansion valve 40, gas-liquid separator 62 and second expansion valve 42 time, and in second heat exchanger 12, be evaporated (h), be recovered to first compressor 2 again.When cold-producing medium circulates first compressor 2, first heat exchanger 10, first expansion valve 40, gas-liquid separator 62, second expansion valve 42 and second heat exchanger 12 first heat exchanger 10 is heated.
Heat running when air regulator is in, and when driving first compressor 2 and second compressor 8 simultaneously, shown in the C of Fig. 9 and Figure 10, D, the cold-producing medium that in first compressor 2, is compressed the cold-producing medium of (p) and in second compressor 8, is compressed (q) converges.The cold-producing medium that is converged is condensed (r) in first heat exchanger 10 and through being inflated (s) for the first time in first expansion valve 40.Make the cold-producing medium that in first expansion valve 40, is inflated for the first time flow into gas-liquid separator 62, separate gaseous refrigerant and liquid refrigerant (t) thus.The gaseous refrigerant of gas-liquid separator 62 flow to after the suction line 28 of second compressor through the 3rd expansion valve 66, is drawn into second compressor 8 and is compressed (q).And the liquid refrigerant of gas-liquid separator 62 is inflated for the second time (u) and in second heat exchanger 12, is evaporated afterwards and (v), then, is drawn into first compressor 2 and is compressed (p) in second expansion valve 42.
As stated; Air regulator makes cold-producing medium circulate first compressor 2, first heat exchanger 10, first expansion valve 40, gas-liquid separator 62, second expansion valve 42, second heat exchanger 12 and first compressor 2 (E of Figure 10), and second compressor 8 that circulates, first heat exchanger 10, first expansion valve 40, gas-liquid separator 62, the 3rd expansion valve 66 and second compressor 8 (F of Figure 10) and can heat first heat exchanger 10.
Air regulator makes the cold-producing medium that has passed through first expansion valve 40, gas-liquid separator 62, second expansion valve 42 and second heat exchanger 12 flow into first compressor 2 when can drive first compressor 2 and second compressor 8 simultaneously, and makes the cold-producing medium that has passed through first expansion valve 40, gas-liquid separator 62 and the 3rd expansion valve 56 flow into second compressor 8.Air regulator is higher than the pressure of the cold-producing medium that flow into first compressor 2 through the pressure that makes the cold-producing medium that flow into second compressor 8; Compare with the cold-producing medium of a compressor compresses low-temp low-pressure time; Consume power consumption less; And, therefore can increase the flow of the cold-producing medium of circulating air adjuster, thereby can raise the efficiency because the density of cold-producing medium is high.
On the other hand, as above-mentioned one embodiment of the invention, when first compressor 2 of air regulator by constituting than second compressor, 8 compressor with variable volume capacious; And second compressor 8 is when constituting than the little constant speed compressor of first compressor, 2 capacity, and through single driving second compressor 8, the load setting that will tackle is a sub-load; And through driving first compressor 2 and second compressor 8 simultaneously, the load setting that will tackle is a full load, when load when heating sub-load; Second compressor 8 drives; First compressor 2 stops, and the 3rd expansion valve 56 cuts out, when load when heating full load; First compressor 2 and second compressor 8 drive, and the 3rd expansion valve 56 is open.
Air regulator according to the present invention has following advantage.
First; When heating; In first compressor and second compressor, flow to first heat exchanger after the compressed refrigerant mixed; Because the gaseous refrigerant in the cold-producing medium that in first expansion valve, is inflated is for the first time walked around second expansion valve and second heat exchanger and in second compressor, is compressed; Liquid refrigerant in the cold-producing medium that in first expansion valve, is inflated for the first time is compressed in first compressor through second expansion valve and second heat exchanger, therefore compares with the cold-producing medium of a compressor compresses low-temp low-pressure time, has the electric weight that in whole compressor, is consumed is minimized.
The second, when heating load hour, only second driven compressor is dealt with load, and heats load when big, and first compressor and second compressor drive simultaneously deals with load.
The 3rd; Because the gaseous refrigerant in the cold-producing medium that is inflated for the first time is compressed in second compressor; Therefore compare with suction the cold-producing medium that is inflated for the first time more low pressure cold-producing medium and in second compressor, compare during compression; The density of cold-producing medium is high, just can tackle required flow through second compressor littler than first compressor capacity.
The above embodiments are not restrictive, but exemplary, all embodiment in appended claim and the equivalency range thereof are included in the category of the present invention.
Claims (15)
1. an air regulator is characterized in that, comprising:
First compressor;
Second compressor makes the respectively parallel connection and being connected with said first compressor of refrigerant suction pipe and refrigerant discharge leader;
First heat exchanger makes the cold-producing medium evaporation when refrigeration, when heating, make condensation of refrigerant;
Second heat exchanger makes condensation of refrigerant when refrigeration, when heating, make the cold-producing medium evaporation;
First expansion valve is located between said first heat exchanger and second heat exchanger;
Second expansion valve is located between said first expansion valve and second heat exchanger;
Bypass mechanism; Be connected between the branch point and said second compressor of said refrigerant suction pipe, so that passed through that a part in the cold-producing medium of said first expansion valve is walked around said second expansion valve and said second heat exchanger is directed between the branch point and said second compressor of said refrigerant suction pipe; And
Check valve is located between the tie point of branch point and said bypass mechanism of said refrigerant suction pipe, is used to block the cold-producing medium that has passed through said bypass mechanism and flows to the branch point of said refrigerant suction pipe.
2. air regulator according to claim 1 is characterized in that the running capacity of said second compressor is less than the running capacity of said first compressor.
3. air regulator according to claim 2 is characterized in that, said first compressor is a compressor with variable volume, and said second compressor is a constant speed compressor.
4. air regulator according to claim 1 is characterized in that,
Said air regulator has the second compressor single driving operation mode and first compressor-second compressor drives operation mode simultaneously,
Under the said second compressor single driving operation mode, said second compressor is able to drive, and makes the cold-producing medium that has passed through said first expansion valve flow to said second compressor afterwards through said second expansion valve and said second heat exchanger,
Drive simultaneously under the operation mode at said first compressor, one second compressor; Said first compressor and second compressor are able to drive; And make a part in the cold-producing medium that has passed through said first expansion valve walk around said second expansion valve and said second heat exchanger flow to said second compressor, and make remainder in the cold-producing medium that has passed through said first expansion valve through flowing to said first compressor after said second expansion valve and said second heat exchanger.
5. air regulator according to claim 4 is characterized in that, the said second compressor single driving operation mode optionally implemented by said air regulator and said first compressor-second compressor drives operation mode simultaneously.
6. air regulator according to claim 4; It is characterized in that; Said air regulator also has the first compressor single driving operation mode; Under this first compressor single driving operation mode, said first compressor is able to drive, and makes the cold-producing medium that has passed through said first expansion valve through flowing to said first compressor after said second expansion valve and said second heat exchanger.
7. air regulator according to claim 6; It is characterized in that said air regulator is optionally implemented the said second compressor single driving operation mode, said first compressor-second compressor drives the operation mode and the first compressor single driving operation mode simultaneously.
8. air regulator according to claim 1 is characterized in that, said bypass mechanism comprises:
Inner heat exchanger, it comprises second stream that first stream that cold-producing medium flows and the cold-producing medium that makes cold-producing medium with said first stream carry out heat exchange are passed through between said first expansion valve and second expansion valve;
First bypass flow path, one of which end are connected between first stream and first expansion valve of said inner heat exchanger, and the other end is connected said second stream; And
Second bypass flow path, one of which end are connected said second stream, and the other end is connected the suction line of said second compressor.
9. air regulator according to claim 8 is characterized in that, said bypass mechanism also comprises the 3rd expansion valve that is located on said first bypass flow path.
10. air regulator according to claim 9 is characterized in that, the capacity of said the 3rd expansion valve is less than the capacity of said first expansion valve and second expansion valve.
11. air regulator according to claim 9 is characterized in that,
When said air regulator is in when heating part load condition, said second compressor is able to drive, and said first compressor stops, and said the 3rd expansion valve cuts out;
When said air regulator is in when heating the full load state, said first compressor and second compressor are able to drive, and said the 3rd expansion valve is open.
12. air regulator according to claim 1 is characterized in that, said bypass mechanism comprises:
Gas-liquid separator, it is located between said first expansion valve and second expansion valve; And
Gas-liquid separator connects stream, and the one of which end is connected said gas-liquid separator, and the other end is connected the suction line of said second compressor, so that the gaseous refrigerant of said gas-liquid separator flow to the suction line of said second compressor.
13. air regulator according to claim 12 is characterized in that, said bypass mechanism comprises that also being located at said gas-liquid separator connects the 3rd expansion valve on the stream.
14. air regulator according to claim 13 is characterized in that, the capacity of said the 3rd expansion valve is less than the capacity of said first expansion valve and second expansion valve.
15. air regulator according to claim 13 is characterized in that,
When said air regulator is in when heating part load condition, said second compressor is able to drive, and said first compressor stops, and said the 3rd expansion valve cuts out;
When said air regulator is in when heating the full load state, said first compressor and second compressor are able to drive, and said the 3rd expansion valve is open.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020100110417A KR101212681B1 (en) | 2010-11-08 | 2010-11-08 | air conditioner |
| KR10-2010-0110417 | 2010-11-08 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102466361A true CN102466361A (en) | 2012-05-23 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011100710859A Pending CN102466361A (en) | 2010-11-08 | 2011-03-21 | Air conditioner |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20120111050A1 (en) |
| EP (1) | EP2450647A3 (en) |
| KR (1) | KR101212681B1 (en) |
| CN (1) | CN102466361A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104501437A (en) * | 2014-11-25 | 2015-04-08 | 珠海格力电器股份有限公司 | Heat pump system and method for operating the same |
| CN113063235A (en) * | 2019-12-31 | 2021-07-02 | Lg电子株式会社 | Multistage compression type refrigerating device |
| WO2024098966A1 (en) * | 2022-11-07 | 2024-05-16 | 珠海格力电器股份有限公司 | Heat pump system and control method for heat pump system |
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| KR101212698B1 (en) * | 2010-11-01 | 2013-03-13 | 엘지전자 주식회사 | Heat pump type speed heating apparatus |
| KR101203579B1 (en) | 2010-11-05 | 2012-11-21 | 엘지전자 주식회사 | Speed heating apparatus with air conditioner and Control process of the same |
| KR102163859B1 (en) * | 2013-04-15 | 2020-10-12 | 엘지전자 주식회사 | Air Conditioner and Controlling method for the same |
| KR102240071B1 (en) * | 2014-03-20 | 2021-04-13 | 엘지전자 주식회사 | Air Conditioner |
| KR102240070B1 (en) * | 2014-03-20 | 2021-04-13 | 엘지전자 주식회사 | Air Conditioner and Controlling method for the same |
| KR101566747B1 (en) * | 2014-04-14 | 2015-11-13 | 현대자동차 주식회사 | Heat pump system for vehicle |
| WO2016004988A1 (en) | 2014-07-09 | 2016-01-14 | Carrier Corporation | Refrigeration system |
| KR101591191B1 (en) | 2014-08-14 | 2016-02-02 | 엘지전자 주식회사 | An air conditioner and a method controlling the same |
| KR102330490B1 (en) * | 2019-12-27 | 2021-11-23 | 주식회사에이멕스엔지니어링 | Cooling and heating and hot water system |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP2450647A3 (en) | 2015-01-07 |
| KR101212681B1 (en) | 2012-12-17 |
| US20120111050A1 (en) | 2012-05-10 |
| EP2450647A2 (en) | 2012-05-09 |
| KR20120049440A (en) | 2012-05-17 |
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Application publication date: 20120523 |