EP3296664A1 - Air conditioner - Google Patents
Air conditioner Download PDFInfo
- Publication number
- EP3296664A1 EP3296664A1 EP17191590.3A EP17191590A EP3296664A1 EP 3296664 A1 EP3296664 A1 EP 3296664A1 EP 17191590 A EP17191590 A EP 17191590A EP 3296664 A1 EP3296664 A1 EP 3296664A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant
- compressor
- flow channel
- air conditioner
- condenser
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 336
- 238000005057 refrigeration Methods 0.000 claims abstract description 94
- 238000011084 recovery Methods 0.000 claims abstract description 88
- 238000001816 cooling Methods 0.000 claims abstract description 84
- 238000004378 air conditioning Methods 0.000 claims abstract description 74
- 238000010438 heat treatment Methods 0.000 claims description 43
- 239000007788 liquid Substances 0.000 claims description 43
- 238000001704 evaporation Methods 0.000 claims description 5
- 239000007789 gas Substances 0.000 description 29
- 230000006870 function Effects 0.000 description 20
- 238000010586 diagram Methods 0.000 description 18
- 230000000694 effects Effects 0.000 description 10
- 230000003247 decreasing effect Effects 0.000 description 9
- 230000004044 response Effects 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 238000009434 installation Methods 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- 238000004781 supercooling Methods 0.000 description 3
- 230000002528 anti-freeze Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001151 other effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
Images
Classifications
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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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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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
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
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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
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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
-
- 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
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- 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
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- 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
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
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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
- F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
-
- 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
- F25B2400/16—Receivers
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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
- F25B2500/00—Problems to be solved
- F25B2500/16—Lubrication
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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
- F25B2600/2501—Bypass 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
- F25B2700/03—Oil level
Definitions
- the present invention relates to an air conditioner, and more particularly to an air conditioner that is capable of improving the operation efficiency thereof through heat exchange between an air-conditioning cycle for cooling the interior of a room and a refrigeration cycle for refrigerating food and of efficiently recovering refrigeration oil to a compressor.
- an air conditioner is an apparatus that cools or heats the interior of a room using an air-conditioning cycle including a compressor, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger. That is, the air conditioner may be configured as a cooler, which cools the interior of a room, or a heater, which heats the interior of a room. In addition, the air conditioner may be configured as a combined cooling/heating air conditioner, which selectively cools or heats the interior of a room.
- the air conditioner in the case in which the air conditioner is configured as a combined cooling/heating air conditioner, it includes a cooling/heating switching valve for changing the flow channel of a refrigerant compressed by a compressor depending on whether a cooling operation or a heating operation is being performed.
- the refrigerant compressed by the compressor flows into the outdoor heat exchanger via the cooling/heating switching valve and the outdoor heat exchanger serves as a condenser. Further, the refrigerant condensed by the outdoor heat exchanger is expanded by the expansion device and then flows into the indoor heat exchanger. In this case, the indoor heat exchanger serves as an evaporator and the refrigerant evaporated by the indoor heat exchanger flows into the compressor again via the cooling/heating switching valve.
- the refrigerant compressed by the compressor flows into the indoor heat exchanger via the cooling/heating switching valve and the indoor heat exchanger serves as a condenser. Further, the refrigerant condensed by the indoor heat exchanger is expanded by the expansion device and then flows into the outdoor heat exchanger.
- the outdoor heat exchanger serves as an evaporator and the refrigerant evaporated by the outdoor heat exchanger flows into the compressor again via the cooling/heating switching valve.
- a plurality of indoor units each having an indoor heat exchanger may be installed on such an air conditioner. Only some of the plurality of indoor units may operate as a partial load.
- a refrigerant of a low-pressure gas state is present within the indoor heat exchanger of the stopped indoor unit.
- the refrigerant is charged in consideration of the number of connected indoor units, the amount of refrigerant of an indoor unit that is in a non-operation mode moves to the outdoor heat exchanger, and thus a refrigerant circulation state is changed. Accordingly, the optimal amount of refrigerant may not be distributed to the air-conditioning cycle.
- the air conditioner performs the heating operation
- the functions of the outdoor heat exchanger and the indoor heat exchanger are changed.
- the ratio of the volumes of the outdoor heat exchanger and indoor heat exchanger is changed depending on the number of connected indoor units. Furthermore, it is necessary to control the amount of refrigerant in response to a change in cooling/heating operation mode.
- a receiver in which a refrigerant is stored is installed in the air-conditioning cycle in order to optimize the amount of refrigerant of the air-conditioning cycle.
- the receiver functions to move a refrigerant stored therein to the air-conditioning cycle when the amount of refrigerant in the air-conditioning cycle is insufficient and to store the refrigerant in the air-conditioning cycle when the amount of refrigerant in the air-conditioning cycle is excessive, so the amount of refrigerant in the air-conditioning cycle is set to an optimal amount.
- a supercooler for supercooling a refrigerant that has passed through the outdoor heat exchanger when the cooling operation is performed is installed on the air conditioner.
- the supercooler is disposed between the outdoor heat exchanger and the indoor heat exchanger and functions as an intercooler.
- a complex-type air conditioner in which an air-conditioning cycle circuit for air-conditioning the interior of a room and a refrigeration cycle circuit for refrigerating the low-temperature storage unit are integrated is installed in a building in which such a low-temperature storage unit is installed.
- the supercooler supercools a refrigerant that has passed through the condenser of the refrigeration cycle circuit and superheats a refrigerant that has passed through the condenser of the air-conditioning cycle circuit by performing heat exchange between the refrigerant passing through the condenser of the refrigeration cycle circuit and the refrigerant passing through the condenser of the air-conditioning cycle circuit.
- the evaporator of the refrigeration cycle circuit is disposed in the showcase, and the condenser is disposed outdoors.
- the viscosity of the refrigeration oil used in the air conditioner is increased as the temperature decreases.
- the temperature of the refrigerant in the evaporator used in the showcase of the refrigeration cycle circuit is substantially maintained in the range from -40°C to -5°C.
- the viscosity of the oil in the gas line which connects the discharge port of the evaporator to the suction port of the compressor in the refrigeration cycle circuit, is greatly increased and the fluidity thereof is decreased.
- the refrigeration oil remains in the gas line and does not return to the compressor, which results in a decrease in the reliability of the compressor.
- the length of the gas line between the evaporator and the compressor is generally from tens of meters to hundreds of meters.
- the installation length of the gas line is limited due to the refrigeration oil remaining in the gas line.
- the present invention has been made in view of the above problems, and it is an object of the present invention to provide a cooling receiver for an air conditioner in which a supercooler and a receiver are integrated and an air conditioner including the same.
- an air conditioner including an air-conditioning cycle circuit including a first compressor for compressing a first refrigerant, a first condenser for condensing the first refrigerant compressed by the first compressor, a first expansion device for expanding the first refrigerant that has passed through the first condenser, and a first evaporator for evaporating the first refrigerant that has passed through the first expansion device, the air-conditioning cycle circuit performing an air-conditioning operation through circulation of the first refrigerant, a refrigeration cycle circuit including a second compressor for compressing a second refrigerant, a second condenser for condensing the second refrigerant compressed by the second compressor, a second expansion device for expanding the second refrigerant that has passed through the second condenser, and a second evaporator for evaporating the second refrigerant that has passed through the second expansion device, the refrigeration cycle circuit refrigerating stored food through circulation of the second refrig
- spatially-relative terms such as “below”, “beneath”, “lower”, “above”, or “upper” may be used herein to describe one element's relationship to another element as illustrated in the Figures. It will be understood that spatially-relative terms are intended to encompass different orientations of the device in addition to the orientation depicted in the Figures. For example, if the device in one of the figures is turned over, elements described as “below” or “beneath” other elements would then be oriented “above” the other elements. The exemplary terms “below” or “beneath” can, therefore, encompass both an orientation of above and below. Since the device may be oriented in another direction, the spatially-relative terms may be interpreted in accordance with the orientation of the device.
- each layer is exaggerated, omitted, or schematically illustrated for convenience of description and clarity. Also, the size or area of each constituent element does not entirely reflect the actual size thereof.
- FIG. 1A is a configuration diagram showing an air conditioner according to an embodiment of the present invention
- FIG. 1B is a control block diagram of the air conditioner according to the embodiment of the present invention.
- the air conditioner includes an air-conditioning cycle circuit 1 and a refrigeration cycle circuit 2.
- the air-conditioning cycle circuit 1 may include an air-conditioning outdoor unit O1 that is installed outdoors and an air-conditioning indoor unit I1 that is installed indoors.
- the refrigeration cycle circuit 2 may include a refrigeration outdoor unit 02 that is installed outdoors and a refrigeration indoor unit I2 that is installed indoors.
- the air-conditioning cycle circuit 1 may air-condition (or cool/heat) the interior of a room.
- the refrigeration cycle circuit 2 may refrigerate (or cool/freeze) food stored in the refrigeration indoor unit I2.
- the air-conditioning cycle circuit 1 may include a first compressor 11, an outdoor heat exchanger 13, a first expansion device 14 and 15, and an indoor heat exchanger 16. That is, the air-conditioning cycle circuit 1 includes a first compressor 11 for compressing a first refrigerant, a first condenser for condensing the first refrigerant compressed by the first compressor 11, a first expansion device 14 and 15 for expanding the first refrigerant that has passed through the first condenser, and a first evaporator for evaporating the refrigerant that has passed through the first expansion device 14 and 15. The first refrigerant that has passed through the first evaporator is supplied to the first compressor 11 again.
- a refrigerant may sequentially circulate through the first compressor 11, the outdoor heat exchanger 13, the first expansion device 14 and 15, the indoor heat exchanger 16, and the first compressor 11.
- the outdoor heat exchanger 13 may function as a first condenser
- the indoor heat exchanger 16 may function as a first evaporator.
- a refrigerant may sequentially circulate through the first compressor 11, the indoor heat exchanger 16, the first expansion device 14 and 15, the outdoor heat exchanger 13, and the first compressor 11.
- the outdoor heat exchanger 13 may function as a first evaporator
- the indoor heat exchanger 16 may function as a first condenser.
- the air-conditioning cycle circuit 1 may further include a cooling/heating switching valve 12 configured to enable a refrigerant to circulate through the first compressor 11, the outdoor heat exchanger 13, the first expansion device 14 and 15, and the indoor heat exchanger 16 when the cooling operation is performed and to enable a refrigerant to circulate through the first compressor 11, the indoor heat exchanger 16, the first expansion device 14 and 15, and the outdoor heat exchanger 13 when the heating operation is performed.
- a cooling/heating switching valve 12 configured to enable a refrigerant to circulate through the first compressor 11, the outdoor heat exchanger 13, the first expansion device 14 and 15, and the indoor heat exchanger 16 when the cooling operation is performed and to enable a refrigerant to circulate through the first compressor 11, the indoor heat exchanger 16, the first expansion device 14 and 15, and the outdoor heat exchanger 13 when the heating operation is performed.
- the first compressor 11 may suck a refrigerant, may compress the refrigerant, and may then discharge the compressed refrigerant.
- a plurality of the first compressors 11 may be connected in parallel or in series.
- a suction flow channel 11a through which a refrigerant is sucked into the first compressor 11 may be connected to the first compressor 11.
- a discharge flow channel 11b through which a compressed refrigerant is discharged from the first compressor 11 may be connected to the first compressor 11.
- the suction flow channel 11a may be connected to the plurality of first compressors 11 in parallel
- the discharge flow channel 11b may be connected to the plurality of first compressors 11 in parallel.
- the outdoor heat exchanger 13 may function as the first condenser in which a refrigerant compressed by the first compressor 11 is condensed when the cooling operation is performed.
- the outdoor heat exchanger 13 may function as the first evaporator in which a refrigerant expanded by the first expansion device 14 and 15 is evaporated when the heating operation is performed.
- the outdoor heat exchanger 13 may be embodied as an air-refrigerant heat exchanger configured to perform heat exchange between outdoor air and a refrigerant.
- the outdoor heat exchanger 13 may be embodied as a water-refrigerant heat exchanger configured to perform heat exchange between heat source water, such as water or antifreeze, and a refrigerant.
- the first expansion device 14 and 15 may include an outdoor expansion valve 14 for expanding a refrigerant flowing toward the outdoor heat exchanger 13.
- the first expansion device 14 and 15 may include an indoor expansion valve 15 for controlling a refrigerant flowing into or out of the indoor heat exchanger 16.
- the outdoor expansion valve 14 may be installed between the indoor expansion valve 15 and the outdoor heat exchanger 13, and may be installed closer to the outdoor heat exchanger 13 than to the indoor heat exchanger 16.
- the outdoor expansion valve 14 may not expand a refrigerant when the cooling operation is performed, but may expand a refrigerant when the heating operation is performed.
- the outdoor expansion valve 14 may be fully open in the cooling operation, and the opening degree thereof may be controlled to a set value in the heating operation.
- the outdoor expansion valve 14 may be installed on a bypass pipe installed on a refrigerant pipe between the outdoor heat exchanger 13 and the indoor expansion valve 15.
- a check valve configured to enable a refrigerant to flow toward the indoor expansion valve 15 in the cooling operation and to enable a refrigerant to flow toward the outdoor expansion valve 14 by blocking the refrigerant in the heating operation may be installed on the refrigerant pipe between the outdoor heat exchanger 13 and the indoor expansion valve 15.
- the indoor expansion valve 15 may be installed between the outdoor heat exchanger 13 and the indoor heat exchanger 16, and may be installed closer to the indoor heat exchanger 16 than to the outdoor heat exchanger 13.
- the indoor heat exchanger 16 may function as the first evaporator in which a refrigerant expanded by the first expansion device 14 and 15 is evaporated when the cooling operation is performed.
- the indoor heat exchanger 16 may function as the first condenser in which a refrigerant compressed by the first compressor 11 is condensed when the heating operation is performed.
- the cooling/heating switching valve 12 may be formed of a 4-way valve. That is, the cooling/heating switching valve 12 may be connected to the first compressor 11 through the suction flow channel 11a of the first compressor 11, may be connected to the first compressor 11 through the discharge flow channel 11b of the first compressor 11, may be connected to the outdoor heat exchanger 13 through a suction/discharge flow channel 13a of the outdoor heat exchanger 13, and may be connected to the indoor heat exchanger 16 through an air-conditioning gas line 17.
- outdoor heat exchanger 13 and the indoor heat exchanger 16 may be connected to each other through an air-conditioning liquid line 18.
- An air-conditioning gas line valve 17a configured to open/shut the air-conditioning gas line 17 may be installed on the air-conditioning gas line 17.
- An air-conditioning liquid line valve 18a configured to open/shut the air-conditioning liquid line 18 may be installed on the air-conditioning liquid line 18.
- the air-conditioning cycle circuit 1 may further include a first accumulator (not shown) installed between the cooling/heating switching valve 12 and the first compressor 11.
- the first accumulator is installed on the suction flow channel 11a of the first compressor 11. Accordingly, a refrigerant that flows from the cooling/heating switching valve 12 toward the first compressor 11 may flow into the first accumulator.
- a liquid-state refrigerant, among the refrigerant that has flowed into the first accumulator may accumulate in the first accumulator, and a gaseous-state refrigerant, among the refrigerant that has flowed into the first accumulator, may be sucked into the first compressor 11.
- the refrigeration cycle circuit 2 may include a second compressor 21, a second condenser 23, a second expansion device 25, and a second evaporator 26.
- a second refrigerant may sequentially circulate through the second compressor 21, the second condenser 23, the second expansion device 25, the second evaporator 26, and the second compressor 21.
- the second compressor 21 may suck a refrigerant, may compress the refrigerant, and may discharge the compressed refrigerant.
- a plurality of the second compressors 21 may be connected in parallel or in series.
- a suction flow channel 21a through which a refrigerant is sucked into the second compressor 21 may be connected to the second compressor 21.
- a discharge flow channel 21c through which a compressed refrigerant is discharged from the second compressor 21 may be connected to the second compressor 21.
- the suction flow channel 21a may be connected to the plurality of second compressors 21 in parallel
- the discharge flow channel 21c may be connected to the plurality of second compressors 21 in parallel.
- the second condenser 23 condenses a refrigerant compressed by the second compressor 21.
- the second condenser 23 may be embodied as an air-refrigerant heat exchanger configured to perform heat exchange between outdoor air and a refrigerant.
- the second condenser 23 may be embodied as a water-refrigerant heat exchanger configured to perform heat exchange between heat source water, such as water or antifreeze, and a refrigerant.
- a condenser fan 23a for supplying outdoor air to the second condenser 23 may be disposed close to the second condenser 23.
- the second expansion device 25 expands a refrigerant that enters the second evaporator 26.
- the second expansion device 25 may be installed between the second condenser 23 and the second evaporator 26, and may be installed closer to the second evaporator 26 than to the second condenser 23.
- the second evaporator 26 may evaporate a refrigerant while refrigerating food stored in the refrigeration indoor unit I2 by performing heat exchange between the refrigerant expanded by the second expansion device 25 and the air within the refrigeration indoor unit I2.
- the second compressor 21 may be connected to the second evaporator 26 through the suction flow channel 21a. Further, the second compressor 21 may be connected to the second condenser 23 through the discharge flow channel 21c. Furthermore, the second condenser 23 and the second evaporator 26 may be connected to each other through a refrigeration liquid line 26a.
- a first suction flow channel valve 21b configured to open/shut the suction flow channel 21a is installed on the suction flow channel 21a of the second compressor 21.
- a second suction flow channel valve 26b configured to open/shut the refrigeration liquid line 26a is installed on the refrigeration liquid line 26a.
- the refrigeration cycle circuit 2 may further include a second accumulator 70 installed between the second evaporator 26 and the second compressor 21.
- the second accumulator 70 is installed on the suction flow channel 21a of the second compressor 21. Accordingly, a refrigerant flowing from the second evaporator 26 toward the second compressor 21 may flow into the second accumulator 70, a liquid-state refrigerant, among the refrigerant that has flowed into the second accumulator 70, may accumulate in the second accumulator 70, and a gaseous-state refrigerant, among the refrigerant that has flowed into the second accumulator 70, may be sucked into the second compressor 21.
- the air conditioner according to the embodiment of the present invention further includes a cooling receiver 50 configured to perform heat exchange between the refrigerant that has passed through the second condenser 23 and the refrigerant that has passed through one of the indoor heat exchanger 16 and the outdoor heat exchanger 13, which functions as the first condenser, and to store the heat-exchanged refrigerant.
- a cooling receiver 50 configured to perform heat exchange between the refrigerant that has passed through the second condenser 23 and the refrigerant that has passed through one of the indoor heat exchanger 16 and the outdoor heat exchanger 13, which functions as the first condenser, and to store the heat-exchanged refrigerant.
- the embodiment may further include an outdoor air temperature sensor 83 configured to measure the temperature of outdoor air.
- the outdoor air temperature sensor 83 measures the temperature of outdoor air and transmits the measured temperature to a control unit 90.
- the embodiment further includes an oil level sensor 22 configured to detect the amount of oil within the second compressor 21.
- the oil level sensor 22 detects the amount of oil within the second compressor 21 and transmits the information about the amount of oil to the control unit 90.
- a discharge temperature sensor 81 configured to measure the temperature of the second refrigerant discharged from the second evaporator 26 is mounted on the suction flow channel 21a of the second compressor 21.
- the discharge temperature sensor 81 transmits the information about the temperature of the refrigerant discharged from the second evaporator 26 to the control unit 90.
- the discharge temperature sensor 81 is disposed at a position of the suction flow channel 21a of the second compressor 21 that is close to the second evaporator 26. That is, the discharge temperature sensor 81 is disposed at a portion of the suction flow channel 21a of the second compressor 21 that is close to the second evaporator 26.
- a discharge pressure sensor 82 configured to detect the pressure of the second refrigerator discharged from the second evaporator 26 is installed on the suction flow channel 21a of the second compressor 21.
- the discharge pressure sensor 82 transmits the information about the pressure of the second refrigerant discharged from the second evaporator 26 to the control unit 90.
- a first bypass unit diverts a portion of the second refrigerant that has passed through the second compressor 21 so that the portion of the second refrigerant exchanges heat with the second refrigerant that has passed through the second evaporator 26.
- the first bypass unit When the cooling operation or the heating operation (normal operation) is performed, the first bypass unit is in a closed state.
- the first bypass unit supplies a portion of the high-temperature and high-pressure refrigerant discharged from the second compressor 21 to the suction flow channel 21a of the second compressor 21, which is the discharge port of the second evaporator 26.
- the first bypass unit enables a portion of the high-temperature and high-pressure refrigerant discharged from the second compressor 21 to bypass the second condenser 23, the second expansion device 25 and the second evaporator 26.
- the high-temperature and high-pressure refrigerant supplied to the suction flow channel 21a of the second compressor 21 by the first bypass unit increases the temperature of the second refrigerant within the suction flow channel 21a of the second compressor 21.
- the oil within the suction flow channel 21a of the second compressor 21 is increased in temperature and solubility and is decreased in viscosity.
- the oil, which has high viscosity and remains in the suction flow channel 21a of the second compressor 21 in normal operation, is decreased in viscosity and is therefore easily recovered to the second compressor 21 by the pressure of the refrigerant. Consequently, there is an effect in that the reliability of the second compressor 21 is improved.
- the first bypass unit includes a first bypass pipe 61, which connects the discharge flow channel 21c of the second compressor 21, which connects the second compressor 21 to the second condenser 23, to the suction flow channel 21a of the second compressor 21, which connects the second evaporator 26 to the second compressor 21, and a first control valve 63, which is installed on the first bypass pipe 61 in order to control the flow of the refrigerant.
- the first bypass pipe 61 guides a portion of the second refrigerant compressed by the second compressor 21 to the discharge port of the second evaporator 26.
- One end of the first bypass pipe 61 is connected to the discharge flow channel 21c of the second compressor 21 and the opposite end of the first bypass pipe 61 is connected to the suction flow channel 21a of the second compressor 21.
- the first control valve 63 controls the flow of the refrigerant passing through the first bypass pipe 61.
- the first control valve 63 may include a solenoid valve or an electronic expansion valve.
- the first control valve 63 includes an electronic expansion valve, which enables the opening degree thereof to be variably controlled.
- the opening degree of the first control valve 63 is controlled in response to the control signal from the control unit 90.
- the air conditioner according to the embodiment may perform the oil recovery operation during the cooling operation (normal operation) or may perform only the oil recovery operation while the cooling operation is stopped.
- "normal operation” refers to operation including the cooling operation, the heating operation and the refrigeration operation, other than the oil recovery operation.
- a second bypass unit diverts a portion of the second refrigerant that has passed through the second compressor 21 so that the portion of the second refrigerant exchanges heat with the second refrigerant that has passed through the second evaporator 26.
- the second bypass unit When the cooling operation or the heating operation is performed (i.e. upon normal operation), the second bypass unit is in a closed state.
- the second bypass unit additionally supplies a portion of the high-temperature and high-pressure refrigerant discharged from the second compressor 21 to the suction flow channel 21a of the second compressor 21, which is the discharge port of the second evaporator 26.
- the second bypass unit enables a portion of the high-temperature and high-pressure refrigerant discharged from the second compressor 21 to bypass the second condenser 23, the second expansion device 25 and the second evaporator 26.
- the high-temperature and high-pressure refrigerant supplied to the suction flow channel 21a of the second compressor 21 by the second bypass unit increases the temperature of the second refrigerant within the suction flow channel 21a of the second compressor 21.
- the oil within the suction flow channel 21a of the second compressor 21 is increased in temperature and solubility and is decreased in viscosity.
- the oil, which has high viscosity and remains in the suction flow channel 21a of the second compressor 21 in normal operation, is decreased in viscosity and is therefore easily recovered to the second compressor 21 by the pressure of the refrigerant. Consequently, there is an effect in that the reliability of the second compressor 21 is improved. That is, the second bypass unit functions to additionally increase the temperature of the second refrigerant within the suction flow channel 21a of the second compressor 21 in the environment in which the oil recovery operation is not smoothly performed by the first bypass unit.
- the second bypass unit includes a second bypass pipe 62, which connects the discharge flow channel 21c of the second compressor 21, which connects the second compressor 21 to the second condenser 23, to the suction flow channel 21a of the second compressor 21, which connects the second evaporator 26 to the second compressor 21, and a second control valve 64, which is installed on the second bypass pipe 62 in order to control the flow of the refrigerant.
- the second bypass pipe 62 guides a portion of the second refrigerant compressed by the second compressor 21 to the discharge port of the second evaporator 26.
- One end of the second bypass pipe 62 is connected to the discharge flow channel 21c of the second compressor 21 and the opposite end of the second bypass pipe 62 is connected to the suction flow channel 21a of the second compressor 21.
- the second control valve 64 controls the flow of the refrigerant passing through the second bypass pipe 62.
- the second control valve 64 may include a solenoid valve or an electronic expansion valve.
- the second control valve 64 includes an electronic expansion valve, which enables the opening degree thereof to be variably controlled. The opening degree of the second control valve 64 is controlled in response to the control signal from the control unit 90.
- connection positions of the first and second bypass pipes 61 and 62 are important.
- the connection position between the first bypass pipe 61 and the discharge flow channel of the second compressor 21 may be closer to the second compressor 21 than the connection position between the second bypass pipe 62 and the discharge flow channel of the second compressor 21, and the connection position between the first bypass pipe 61 and the suction flow channel of the second compressor 21 may be closer to the second compressor 21 than the connection position between the second bypass pipe 62 and the suction flow channel of the second compressor 21.
- the refrigerant When the temperature of the outdoor air is low, the refrigerant is guided to a position close to the second evaporator 26 through the second bypass pipe 62. Accordingly, the efficiency of the oil recovery operation may be enhanced and the operational load of the second accumulator may be reduced.
- the embodiment may further include a check valve, which is installed on the discharge flow channel of the second compressor 21 in order to prevent the second refrigerant that has passed through the second compressor 21 from flowing backward.
- the check valve may be disposed between the branch point of the first bypass pipe 61 and the branch point of the second bypass pipe 62.
- the refrigerant that flows into the suction flow channel 21a of the second compressor 21 through the first and second bypass pipes 61 and 62 may convert the refrigerant within the suction flow channel 21a of the second compressor 21 into a two-phase refrigerant. Therefore, the opposite end of the first bypass pipe 61 and the opposite end of the second bypass pipe 62, which are connected to the suction flow channel 21a of the second compressor 21, may be disposed between the second accumulator and the second evaporator 26. However, the opposite end of the first bypass pipe 61 and the opposite end of the second bypass pipe 62 may alternatively be disposed between the second accumulator and the second compressor 21.
- the control unit 90 controls the overall operation of the air conditioner.
- the control unit 90 may include a processing device, which performs a logical determination, and a memory.
- control unit 90 Based on various detected information, the control unit 90 performs control such that the air conditioner selectively performs normal operation or an oil recovery operation. During the oil recovery operation, the control unit 90 may perform control such that normal operation is performed or is stopped.
- the control unit 90 determines that the oil recovery operation is needed and starts the oil recovery operation. In an example, when the oil level value transmitted from the oil level sensor 22 is lower than a reference oil level value, the control unit 90 performs the oil recovery operation. When the oil level value transmitted from the oil level sensor 22 is higher than the reference oil level value, the control unit 90 performs normal operation. In another example, when a predetermined time has elapsed since the start of operation of the air conditioner, the control unit 90 may perform the oil recovery operation. Here, the predetermined time may be set within the range from 2 hours to 5 hours. Specifically, the control process in which the oil recovery operation is performed on the basis of time is used when communication with the second evaporator 26 installed in the showcase is impossible.
- the control unit 90 may determine that the oil recovery operation is needed and may start the oil recovery operation.
- the control unit 90 performs the oil recovery operation.
- the control unit 90 performs normal operation.
- control unit 90 controls the first bypass unit such that the second refrigerant that has been discharged from the second compressor 21 and the second refrigerant that has passed through the second evaporator 26 perform heat exchange with each other. That is, the control unit 90 controls the first bypass unit so as to guide the second refrigerant discharged from the second compressor 21 to the discharge port of the second evaporator 26.
- control unit 90 drives the second compressor 21 so as to supply cool air to the showcase.
- control unit 90 drives the second compressor 21 and opens the first control valve 63 so as to supply the high-temperature and high-pressure refrigerant to the suction flow channel 21a of the second compressor 21.
- control unit 90 may control the opening degree and the opening time of the first control valve 63.
- the control unit 90 in the oil recovery operation, the control unit 90 fully opens the first control valve 63.
- the control unit 90 controls the second control valve 64 so as to be open.
- the control unit 90 controls the second control valve 64 so as to be closed.
- control unit 90 may increase the operation speed of the second compressor 21 above the operation speed at the time of normal operation. In this case, the flow rate of the second refrigerant is increased and thus the recovery of the oil is smoothly achieved.
- control unit 90 may rotate the condenser fan 23a at a maximum speed.
- control unit 90 may stop the condenser fan 23a or may rotate the condenser fan 23a at a lower speed than in the refrigeration operation.
- the refrigeration load of the refrigeration cycle circuit may be reduced by varying the speed of the condenser fan 23a.
- the control unit 90 may perform control such that the above-described specific embodiments associated with the oil recovery operation are performed at the same time or at different times or such that only one of the embodiments is performed.
- FIG. 2 is a detailed view of the cooling receiver shown in FIG. 1
- FIG. 3 is a sectional view taken along line A-A in FIG. 2 .
- the cooling receiver 50 includes a cooling unit 51 and a receiver unit 54 in which at least one end of the cooling unit 51 is disposed.
- the cooling unit 51 includes at least one first refrigerant flow channel 52 through which a refrigerant that has passed through the second condenser 23 flows and a second refrigerant flow channel 53 configured to surround the outer circumference of some of the at least one first refrigerant flow channel 52.
- the refrigerant that has passed through one of the outdoor heat exchanger 13 and the indoor heat exchanger 16, which functions as the first condenser exchanges heat with the refrigerant flowing through the first refrigerant flow channel 52 while flowing through the inside of the second refrigerant flow channel 53. Accordingly, the refrigerant flowing through the first refrigerant flow channel 52 is supercooled, and the refrigerant flowing through the second refrigerant flow channel 53 is gasified.
- At least one end of the cooling unit 51 is disposed in the receiver unit 54, and a supercooled refrigerant flowing out of the first refrigerant flow channel 52 is stored in the receiver unit 54.
- the cooling unit 51 and the receiver unit 54 are formed to have a cylindrical shape having an empty space inside and are formed to be long in upward and downward directions.
- the diameter of the first refrigerant flow channel 52 may be the smallest, the diameter of the second refrigerant flow channel 53 may be greater than that of the first refrigerant flow channel 52, and the diameter of the receiver unit 54 may be greater than that of the second refrigerant flow channel 53.
- the first refrigerant flow channel 52 may be formed of seven smalldiameter pipes.
- the cooling unit 51 may have an upper end inserted and disposed in the receiver unit 54 and may have a lower end protruding below the receiver unit 54 so as to be exposed outside the receiver unit 54.
- the upper end of the first refrigerant flow channel 52 which is disposed within the receiver unit 54, is open, and the upper end of the second refrigerant flow channel 53 is closed.
- the open upper end of the first refrigerant flow channel 52 may protrude upwards from the upper end of the second refrigerant flow channel 53. Accordingly, refrigerant flowing through the first refrigerant flow channel 52 may be supercooled through heat exchange with a refrigerant flowing through the second refrigerant flow channel 53. Subsequently, the supercooled refrigerant may flow out of the open upper end of the first refrigerant flow channel 52 and may be stored in the internal space of the receiver unit 54.
- a first inlet flow channel 52a and a second inlet flow channel 53a are disposed in a portion of the cooling unit 51 that protrudes below the receiver unit 54. Further, a first outlet flow channel 53b is disposed above the receiver unit 54, and a second outlet flow channel 54a is disposed below the receiver unit 54.
- the first inlet flow channel 52a is connected to the first refrigerant flow channel 52 through the second refrigerant flow channel 53.
- the first inlet flow channel 52a supplies the first refrigerant flow channel 52 with refrigerant that has passed through the second condenser 23.
- the first inlet flow channel 52a may branch into a plurality of first inlet flow channels within the second refrigerant flow channel 53 and the plurality of first inlet flow channels may be connected to the plurality of first refrigerant flow channels 52.
- the second inlet flow channel 53a is connected to the second refrigerant flow channel 53.
- the second inlet flow channel 53a supplies the second refrigerant flow channel 53 with refrigerant that has passed through one of the outdoor heat exchanger 13 and the indoor heat exchanger 16, which functions as the first condenser.
- the second refrigerant flow channel 53 is connected to the air-conditioning liquid line 18 via a heat-recovery liquid line 34 branching from the air-conditioning liquid line 18 that connects the second outdoor heat exchanger 13 and the indoor heat exchanger 16. That is, the heat-recovery liquid line 34 connects the second refrigerant flow channel 53 and the air-conditioning liquid line 18.
- a heat recovery expansion device 34a is installed on the heat-recovery liquid line 34.
- a portion of the refrigerant that has passed through the first condenser may move to the first evaporator through the air-conditioning liquid line 18.
- the remainder of the refrigerant may move to the heat-recovery liquid line 34, may be expanded by the heat recovery expansion device 34a, and may then move to the second inlet flow channel 53a.
- the refrigerant that has moved to the second inlet flow channel 53a may be supplied to the second refrigerant flow channel 53.
- the first outlet flow channel 53b is connected to the upper portion of the second refrigerant flow channel 53 within the receiver unit 54 through the upper end of the receiver unit 54. Accordingly, refrigerant supplied to the second refrigerant flow channel 53 through the second inlet flow channel 53a may pass through the second refrigerant flow channel 53 and may then escape through the first outlet flow channel 53b.
- the first outlet flow channel 53b protruding above the receiver unit 54 is connected to the suction flow channel 11a of the first compressor 11 via a heat-recovery gas line 35. Accordingly, the refrigerant that has escaped through the first outlet flow channel 53b may move to the suction flow channel 11a of the first compressor 11 through the heat-recovery gas line 35 and may then be supplied to the first compressor 11.
- the second outlet flow channel 54a is connected to the refrigeration liquid line 26a. Accordingly, supercooled refrigerant that has escaped through the upper end of the first refrigerant flow channel 52 and is stored in the receiver unit 54 may escape through the second outlet flow channel 54a, may move to the refrigeration liquid line 26a, and may then be supplied to the second evaporator 26.
- a cap 54b configured to cover the upper end of the receiver unit 54 may be disposed in the upper end of the receiver unit 54.
- the first outlet flow channel 53b may penetrate the cap 54b.
- the mounting bracket 55 may be disposed in the lower portion of the receiver unit 54.
- the mounting bracket 55 may include a ring-shaped main body unit 55a configured to surround the outer circumferential surface of the receiver unit 54 and a plurality of mounting units 55b disposed on the outer circumferential surface of the main body unit 55a while being equidistantly spaced apart from each other.
- the mounting bracket 55 may include three mounting units 55b.
- the mounting unit 55b may be mounted on the refrigeration outdoor unit 02 so as to couple the receiver unit 54 to the refrigeration outdoor unit 02.
- a heat-recovery liquid line valve 34b configured to open/shut the heat-recovery liquid line 34 is installed on the heat-recovery liquid line 34.
- Heat-recovery gas line valves 35a and 35b configured to open/shut the heat-recovery gas line 35 are installed on the heat-recovery gas line 35.
- the heat-recovery gas line valves 35a and 35b include a first heat-recovery gas line valve 35a disposed in the refrigeration outdoor unit 02 and a second heat-recovery gas line valve 35b disposed in the air-conditioning outdoor unit O1.
- the air-conditioning gas line valve 17a, the air-conditioning liquid line valve 18a, the first suction flow channel valve 21b, the second suction flow channel valve 26b, the heat-recovery liquid line valve 34b, and the heat-recovery gas line valves 35a and 35b may be open at normal times and may be shut by a worker when maintenance or repair of the air conditioner (for example, filling with a refrigerant or correcting a malfunction) is performed.
- the first compressor 11, the four-way valve 12, the outdoor heat exchanger 13, the outdoor expansion valve 14, the air-conditioning gas line valve 17a, the air-conditioning liquid line valve 18a, and the second heat-recovery gas line valve 35b may be included in the air-conditioning outdoor unit O1.
- the second compressor 21, the second condenser 23, the cooling receiver 50, the first suction flow channel valve 21b, the second suction flow channel valve 26b, the heat-recovery liquid line valve 34b, and the first heat-recovery gas line valve 35a may be included in the refrigeration outdoor unit 02.
- the indoor heat exchanger 16 and the indoor expansion valve 15 may be included in the air-conditioning indoor unit I1.
- the second evaporator 26 and the second expansion device 25 may be included in the refrigeration indoor unit I2.
- FIG. 4 is a diagram showing the flow of refrigerant when the cooling operation and the refrigeration operation of the air conditioner according to the embodiment of the present invention are performed at the same time.
- the air conditioner according to the embodiment of the present invention may perform a cooling operation for cooling the interior of a room and a refrigeration operation for refrigerating food within the refrigeration indoor unit 12 at the same time.
- the first compressor 11 when the cooling operation of the air-conditioning cycle circuit 1 is performed, the first compressor 11 is driven to discharge a refrigerant.
- the refrigerant discharged by the first compressor 11 moves to the cooling/heating switching valve 12 through the discharge flow channel 11b of the first compressor 11.
- the refrigerant that has moved to the cooling/heating switching valve 12 moves to the outdoor heat exchanger 13 through the suction/discharge flow channel 13a of the outdoor heat exchanger 13.
- the outdoor heat exchanger 13 When the cooling operation of the air-conditioning cycle circuit 1 is performed, the outdoor heat exchanger 13 functions as the first condenser.
- a portion of the refrigerant that has passed through the outdoor heat exchanger 13 moves to the indoor heat exchanger 16 through the air-conditioning liquid line 18.
- the remainder of the refrigerant that has passed through the outdoor heat exchanger 13 moves to the cooling receiver 50 through the heat-recovery liquid line 34.
- a portion of the refrigerant that belongs to the refrigerant that has passed through the outdoor heat exchanger 13 and that moves to the indoor heat exchanger 16 through the air-conditioning liquid line 18 is supplied to the indoor heat exchanger 16 in the state in which the refrigerant has been expanded by the first expansion device 15.
- the indoor heat exchanger 16 functions as the first evaporator.
- the refrigerant that has moved to the indoor heat exchanger 16 may refrigerate indoor air and may be evaporated through heat exchange with the indoor air.
- the refrigerant evaporated by the indoor heat exchanger 16 may move to the cooling/heating switching valve 12 through the air-conditioning gas line 17 and may then be supplied to the first compressor 11 again through the suction flow channel 11a of the first compressor 11.
- the second compressor 21 is driven to discharge a refrigerant.
- the refrigerant discharged by the second compressor 21 moves to the second condenser 23 through the discharge flow channel 21c of the second compressor 21.
- the refrigerant that has moved to the second condenser 23 moves to the second evaporator 26 through the refrigeration liquid line 26a.
- the refrigerant that has passed through the second condenser 23 is supplied to the second evaporator 26 in the state in which the refrigerant has been expanded by the second expansion device 25.
- the refrigerant that has moved to the second evaporator 26 may refrigerate food within the refrigeration indoor unit I2 and may be evaporated through heat exchange with air within the refrigeration indoor unit I2.
- the refrigerant evaporated by the second evaporator 26 may be supplied to the second compressor 21 again through the suction flow channel 21a of the second compressor 21.
- the remaining refrigerant that belongs to the refrigerant that has passed through the outdoor heat exchanger 13 of the air-conditioning cycle circuit 1 and that moves to the cooling receiver 50 through the heat-recovery liquid line 34 may be expanded by the heat recovery expansion device 34a, may move to the second refrigerant flow channel 53, and may be gasified through heat exchange with the refrigerant that has passed through the second condenser 23 of the refrigeration cycle circuit 2 within the cooling receiver 50 while supercooling the refrigerant that has passed through the second condenser 23.
- the cooling receiver 50 may be installed between the second condenser 23 and the second expansion device 25 on the refrigeration liquid line 26a.
- the refrigerant that has passed through the second condenser 23 may exchange heat with the refrigerant flowing through the second refrigerant flow channel 53 and may be supercooled while flowing through the first refrigerant flow channel 52.
- the refrigerant supercooled while flowing through the first refrigerant flow channel 52 may escape through the open upper end of the first refrigerant flow channel 52 and may then be stored in the receiver unit 54.
- the refrigerant gasified while flowing through the second refrigerant flow channel 53 may escape from the first outlet flow channel 53b, may move to the suction flow channel 11a of the first compressor 11 through the heat-recovery gas line 35, and may then be supplied to the first compressor 11. Furthermore, the supercooled refrigerant stored in the receiver unit 54 may escape through the second outlet flow channel 54a, may move to the refrigeration liquid line 26a, and may then be supplied to the second evaporator 26 in the state in which the refrigerant has been expanded by the second expansion device 25. At least one of the opening time and the opening degree of the second expansion device 25 is controlled by the control unit so that the amount of refrigerant within the refrigeration cycle circuit 2 is optimized.
- the control unit 90 opens the heat recovery expansion device 34a at a minimum opening degree when the cooling operation is performed. Accordingly, it is possible to prevent deterioration of the efficiency of the air-conditioning cycle circuit due to excessive heat absorption in the refrigeration cycle circuit when the cooling operation is performed.
- FIG. 5 is a diagram showing the flow of refrigerant when the heating operation and the refrigeration operation of the air conditioner according to the embodiment of the present invention are performed at the same time.
- the air conditioner according to the embodiment of the present invention may perform a heating operation for heating the interior of a room and a refrigeration operation for refrigerating food within the refrigeration indoor unit I2 at the same time.
- the first compressor 11 when the heating operation of the air-conditioning cycle circuit 1 is performed, the first compressor 11 is driven to discharge a refrigerant.
- the refrigerant discharged by the first compressor 11 moves to the cooling/heating switching valve 12 through the discharge flow channel 11b of the first compressor 11.
- the refrigerant that has moved to the cooling/heating switching valve 12 moves to the indoor heat exchanger 16 through the air-conditioning gas line 17.
- the indoor heat exchanger 16 functions as the first condenser.
- a portion of the refrigerant that has passed through the indoor heat exchanger 16 moves to the outdoor heat exchanger 13 through the air-conditioning liquid line 18.
- the remainder of the refrigerant that has passed through the indoor heat exchanger 16 moves to the cooling receiver 50 through the heat-recovery liquid line 34.
- a portion of the refrigerant that belongs to the refrigerant that has passed through the indoor heat exchanger 16 and that moves to the outdoor heat exchanger 13 through the air-conditioning liquid line 18 is supplied to the outdoor heat exchanger 13 in the state in which the refrigerant has been expanded by the first expansion device 14.
- the outdoor heat exchanger 13 functions as the first evaporator.
- the refrigerant that has moved to the outdoor heat exchanger 13 may be evaporated while exchanging heat with outdoor air.
- the refrigerant evaporated by the outdoor heat exchanger 13 may move to the cooling/heating switching valve 12 through the suction/discharge flow channel 13a of the outdoor heat exchanger 13 and may then be supplied to the first compressor 11 again through the suction flow channel 11a of the first compressor 11.
- the second compressor 21 is driven to discharge a refrigerant.
- the refrigerant discharged by the second compressor 21 moves to the second condenser 23 through the discharge flow channel 21c of the second compressor 21.
- the refrigerant that has moved to the second condenser 23 moves to the second evaporator 26 through the refrigeration liquid line 26a.
- the refrigerant that has passed through the second condenser 23 is supplied to the second evaporator 26 in the state in which the refrigerant has been expanded by the second expansion device 25.
- the refrigerant that has moved to the second evaporator 26 may refrigerate food within the refrigeration indoor unit I2 and may be evaporated through heat exchange with air within the refrigeration indoor unit I2.
- the refrigerant evaporated by the second evaporator 26 may be supplied to the second compressor 21 again through the suction flow channel 21a of the second compressor 21.
- the remaining refrigerant that belongs to the refrigerant that has passed through the indoor heat exchanger 16 of the air-conditioning cycle circuit 1 and that moves to the cooling receiver 50 through the heat-recovery liquid line 34 may be expanded by the heat recovery expansion device 34a, may move to the second refrigerant flow channel 53, and may be gasified through heat exchange with the refrigerant that has passed through the second condenser 23 of the refrigeration cycle circuit 2 within the cooling receiver 50 while supercooling the refrigerant that has passed through the second condenser 23.
- the refrigerant that has passed through the second condenser 23 may be supercooled through heat exchange with the refrigerant flowing through the second refrigerant flow channel 53 while flowing through the first refrigerant flow channel 52.
- the refrigerant supercooled while flowing through the first refrigerant flow channel 52 may escape through the open upper end of the first refrigerant flow channel 52 and may be stored in the receiver unit 54.
- the refrigerant gasified while flowing through the second refrigerant flow channel 53 may escape from the first outlet flow channel 53b, may move to the suction flow channel 11a of the first compressor 11 through the heat-recovery gas line 35, and may then be supplied to the first compressor 11.
- the supercooled refrigerant stored in the receiver unit 54 may escape through the second outlet flow channel 54a, may move to the refrigeration liquid line 26a, and may then be supplied to the second evaporator 26 in the state in which the refrigerant has been expanded by the second expansion device 25.
- At least one of the opening time and the opening degree of the second expansion device 25 is controlled by the control unit so that the amount of refrigerant within the refrigeration cycle circuit 2 is optimized.
- the control unit 90 opens the heat recovery expansion device 34a to the maximum opening degree when the heating operation is performed. Accordingly, it is possible to use as much waste heat from the refrigeration cycle circuit for the air-conditioning cycle circuit as possible in the cooling operation, thereby improving the efficiency of the air-conditioning cycle circuit.
- FIG. 6 is a diagram showing the flow of refrigerant when only the refrigeration operation of the air conditioner according to the embodiment of the present invention is performed.
- the air conditioner according to the embodiment of the present invention may perform only a refrigeration operation for refrigerating food within the refrigeration indoor unit I2. That is, the air-conditioning cycle circuit 1 may not operate, and only the refrigeration cycle circuit 2 may operate.
- the second compressor 21 is driven to discharge a refrigerant.
- the refrigerant discharged by the second compressor 21 moves to the second condenser 23 through the discharge flow channel 21c of the second compressor 21.
- the refrigerant that has moved to the second condenser 23 moves to the second evaporator 26 through the refrigeration liquid line 26a.
- the refrigerant that has passed through the second condenser 23 is supplied to the second evaporator 26 in the state in which the refrigerant has been expanded by the second expansion device 25.
- the refrigerant that has moved to the second evaporator 26 may refrigerate food within the refrigeration indoor unit I2 and may be evaporated through heat exchange with air within the refrigeration indoor unit I2.
- the refrigerant evaporated by the second evaporator 26 may be supplied to the second compressor 21 again through the suction flow channel 21a of the second compressor 21.
- the refrigerant that has passed through the second condenser 23 may not be subjected to heat exchange while flowing through the first refrigerant flow channel 52, but may escape through the open upper end of the first refrigerant flow channel 52 and may then be stored in the receiver unit 54.
- the stored refrigerant may escape through the second outlet flow channel 54a, may move to the refrigeration liquid line 26a, and may then be supplied to the second evaporator 26 in the state in which the refrigerant has been expanded by the second expansion device 25.
- At least one of the opening time and the opening degree of the second expansion device 25 may be controlled by the control unit so that the amount of refrigerant within the refrigeration cycle circuit 2 is optimized.
- FIG. 7 is a diagram showing the flow of refrigerant when the cooling operation, the refrigeration operation and the oil recovery operation of the air conditioner according to the embodiment of the present invention are performed at the same time.
- the second refrigerant compressed by the second compressor 21 is supplied to the suction flow channel 21a of the second compressor 21 by the first bypass unit.
- the high-temperature and high-pressure refrigerant increases the temperature of the second refrigerant within the suction flow channel 21a of the second compressor 21.
- the oil within the suction flow channel 21a of the second compressor 21 is increased in temperature and solubility and is decreased in viscosity.
- control unit 90 When the oil recovery operation is performed and the temperature of the outdoor air is lower than a predetermined temperature, the control unit 90 additionally opens the second control valve 64. Accordingly, the refrigerant compressed by the second compressor 21 is additionally supplied to the suction flow channel 21a of the second compressor 21 through the second bypass pipe 62.
- FIG. 8A is a configuration diagram showing an air conditioner according to another embodiment of the present invention
- FIG. 8B is a control block diagram of the air conditioner according to another embodiment of the present invention.
- the air conditioner according to another embodiment further includes a third bypass unit, in contrast with the above-described embodiment shown in FIG. 1 .
- the third bypass unit in this embodiment functions to guide a portion of the refrigerant that has been discharged from the second condenser 23 to the discharge port of the second evaporator 26.
- the third bypass unit When the cooling operation (normal operation) is performed, the third bypass unit is in a closed state.
- the third bypass unit supplies a portion of the high-temperature and high-pressure refrigerant that has been discharged from the second condenser 23 to the suction flow channel 21a of the second compressor 21, which is the discharge port of the second evaporator 26.
- the high-temperature and high-pressure refrigerant supplied to the suction flow channel 21a of the second compressor 21 by the third bypass unit converts the refrigerant within the suction flow channel 21a of the second compressor 21 into a two-phase refrigerant and increases the temperature.
- the oil within the suction flow channel 21a of the second compressor 21 is increased in temperature and solubility and is decreased in viscosity.
- the oil which has high viscosity and remains in the suction flow channel 21a of the second compressor 21 in normal operation, is decreased in viscosity and is therefore easily recovered to the compressor 21 by the pressure of the refrigerant. Consequently, there is an effect in that the reliability of the compressor 21 is improved.
- the third bypass unit includes a third bypass pipe 71, which connects the refrigeration liquid line 26a, which connects the second condenser 23 to the second evaporator 26, to the suction flow channel 21a of the second compressor 21, which connects the second evaporator 26 to the second compressor 21, and a control valve 72, which is installed on the third bypass pipe 71 in order to control the flow of the refrigerant.
- the third bypass pipe 71 guides a portion of the refrigerant condensed by the second condenser 23 to the discharge port of the second evaporator 26.
- One end of the third bypass pipe 71 is connected to the refrigeration liquid line 26a and the opposite end of the third bypass pipe 71 is connected to the suction flow channel 21a of the second compressor 21.
- connection position of the third bypass pipe 71 is important. In terms of the length and efficiency of the pipe, the connection position between the third bypass pipe 71 and the suction flow channel 21a of the second compressor 21 may be closer to the second evaporator 26 than to the second compressor 21.
- the third bypass pipe 71 is connected to a portion of the suction flow channel 21a of the second compressor 21 that is located close to the second evaporator 26.
- connection positon between the opposite end of the third bypass pipe 71 and the suction flow channel 21a of the second compressor 21 is closer to the second evaporator 26 than the connection position between the opposite end of the first or second bypass pipe 61 or 62 and the suction flow channel 21a of the second compressor 21.
- the control valve 72 controls the flow of the refrigerant passing through the third bypass pipe 71.
- the control valve 72 may include a solenoid valve or an electronic expansion valve.
- the control valve 72 includes an electronic expansion valve, which enables the opening degree thereof to be variably controlled.
- the opening degree of the control valve 72 is controlled in response to the control signal from the control unit 90.
- the air conditioner according to the embodiment may perform the oil recovery operation during the cooling operation (normal operation) or may perform only the oil recovery operation while the cooling operation is stopped.
- FIG. 9 is a diagram showing the flow of refrigerant when the cooling operation, the refrigeration operation and the oil recovery operation of the air conditioner according to another embodiment of the present invention are performed at the same time.
- the operation of the air conditioner shown in FIG. 9 has a difference from the operation of the air conditioner shown in FIG. 7 as to the operation of the third bypass unit.
- the operation of the air conditioner according to another embodiment shown in FIG. 9 and the operation shown in FIG. 7 will be described.
- the control unit 90 when the oil recovery operation is performed, the control unit 90 performs control such that the third bypass unit enables heat exchange between the second refrigerant that has been discharged from the second condenser 23 and the second refrigerant that has passed through the second evaporator 26. That is, the control unit 90 performs control such that the third bypass unit guides the second refrigerant discharged from the second condenser 23 to the discharge port of the second evaporator 26.
- control unit 90 drives the second compressor 21 so as to supply cool air to the showcase.
- control unit 90 drives the second compressor 21 and opens the control valve 72 so as to supply the second refrigerant discharged from the second condenser 23 to the suction flow channel 21a of the second compressor 21.
- the control unit 90 may control the opening degree and the opening time of the control valve 72.
- the high-pressure refrigerant supplied by the third bypass unit increases the temperature of the second refrigerant within the suction flow channel 21a of the second compressor 21.
- the oil within the suction flow channel 21a of the second compressor 21 is increased in temperature and solubility and is decreased in viscosity.
- a supercooler and a receiver are integrated, which leads to a compact design, a simple structure, a low price and improved refrigeration efficiency.
- the air conditioner according to the embodiment of the present invention has an effect in that two or more components are combined into a single unit, thus leading to a compact design and a simple structure.
- the air conditioner according to the embodiment of the present invention has effects of a low price and improved refrigeration efficiency.
- the air conditioner according to the embodiment of the present invention has an effect of overcoming a problem in which recovery of oil is not smoothly performed due to the considerably low temperature of an evaporator of a showcase.
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Abstract
Description
- The present invention relates to an air conditioner, and more particularly to an air conditioner that is capable of improving the operation efficiency thereof through heat exchange between an air-conditioning cycle for cooling the interior of a room and a refrigeration cycle for refrigerating food and of efficiently recovering refrigeration oil to a compressor.
- In general, an air conditioner is an apparatus that cools or heats the interior of a room using an air-conditioning cycle including a compressor, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger. That is, the air conditioner may be configured as a cooler, which cools the interior of a room, or a heater, which heats the interior of a room. In addition, the air conditioner may be configured as a combined cooling/heating air conditioner, which selectively cools or heats the interior of a room.
- In the case in which the air conditioner is configured as a combined cooling/heating air conditioner, it includes a cooling/heating switching valve for changing the flow channel of a refrigerant compressed by a compressor depending on whether a cooling operation or a heating operation is being performed.
- When the air conditioner performs the cooling operation, the refrigerant compressed by the compressor flows into the outdoor heat exchanger via the cooling/heating switching valve and the outdoor heat exchanger serves as a condenser. Further, the refrigerant condensed by the outdoor heat exchanger is expanded by the expansion device and then flows into the indoor heat exchanger. In this case, the indoor heat exchanger serves as an evaporator and the refrigerant evaporated by the indoor heat exchanger flows into the compressor again via the cooling/heating switching valve.
- When the air conditioner performs the heating operation, the refrigerant compressed by the compressor flows into the indoor heat exchanger via the cooling/heating switching valve and the indoor heat exchanger serves as a condenser. Further, the refrigerant condensed by the indoor heat exchanger is expanded by the expansion device and then flows into the outdoor heat exchanger. In this case, the outdoor heat exchanger serves as an evaporator and the refrigerant evaporated by the outdoor heat exchanger flows into the compressor again via the cooling/heating switching valve.
- A plurality of indoor units each having an indoor heat exchanger may be installed on such an air conditioner. Only some of the plurality of indoor units may operate as a partial load. When some of the connected indoor units are stopped, a refrigerant of a low-pressure gas state is present within the indoor heat exchanger of the stopped indoor unit. When the refrigerant is charged in consideration of the number of connected indoor units, the amount of refrigerant of an indoor unit that is in a non-operation mode moves to the outdoor heat exchanger, and thus a refrigerant circulation state is changed. Accordingly, the optimal amount of refrigerant may not be distributed to the air-conditioning cycle.
- Further, when the air conditioner performs the heating operation, the functions of the outdoor heat exchanger and the indoor heat exchanger are changed. The ratio of the volumes of the outdoor heat exchanger and indoor heat exchanger is changed depending on the number of connected indoor units. Furthermore, it is necessary to control the amount of refrigerant in response to a change in cooling/heating operation mode.
- Accordingly, a receiver in which a refrigerant is stored is installed in the air-conditioning cycle in order to optimize the amount of refrigerant of the air-conditioning cycle. The receiver functions to move a refrigerant stored therein to the air-conditioning cycle when the amount of refrigerant in the air-conditioning cycle is insufficient and to store the refrigerant in the air-conditioning cycle when the amount of refrigerant in the air-conditioning cycle is excessive, so the amount of refrigerant in the air-conditioning cycle is set to an optimal amount.
- Furthermore, a supercooler for supercooling a refrigerant that has passed through the outdoor heat exchanger when the cooling operation is performed is installed on the air conditioner. The supercooler is disposed between the outdoor heat exchanger and the indoor heat exchanger and functions as an intercooler.
- Recently, a low-temperature storage unit for storing food in a low-temperature state, such as a showcase, has been installed in large-scale supermarkets. A complex-type air conditioner in which an air-conditioning cycle circuit for air-conditioning the interior of a room and a refrigeration cycle circuit for refrigerating the low-temperature storage unit are integrated is installed in a building in which such a low-temperature storage unit is installed.
- In the case of a complex-type air conditioner, the supercooler supercools a refrigerant that has passed through the condenser of the refrigeration cycle circuit and superheats a refrigerant that has passed through the condenser of the air-conditioning cycle circuit by performing heat exchange between the refrigerant passing through the condenser of the refrigeration cycle circuit and the refrigerant passing through the condenser of the air-conditioning cycle circuit.
- However, such a conventional air conditioner has problems in that an installation space is limited because the receiver and the supercooler are separately formed. Further, because a great number of refrigerant pipes must be used to form the receiver and the supercooler into a cycle circuit, the structure is complicated, the manufacturing cost is increased, and the refrigeration efficiency is low.
- The evaporator of the refrigeration cycle circuit is disposed in the showcase, and the condenser is disposed outdoors.
- In the air conditioner including the refrigeration cycle circuit, in order to ensure the reliability of the compressor, there is a need to appropriately recover refrigeration oil, which has been discharged with the refrigerant from the compressor, to the compressor and thus to prevent depletion of the refrigeration oil in the compressor.
- In general, the viscosity of the refrigeration oil used in the air conditioner is increased as the temperature decreases. The temperature of the refrigerant in the evaporator used in the showcase of the refrigeration cycle circuit is substantially maintained in the range from -40°C to -5°C.
- Therefore, the viscosity of the oil in the gas line, which connects the discharge port of the evaporator to the suction port of the compressor in the refrigeration cycle circuit, is greatly increased and the fluidity thereof is decreased. The refrigeration oil remains in the gas line and does not return to the compressor, which results in a decrease in the reliability of the compressor.
- Further, the length of the gas line between the evaporator and the compressor is generally from tens of meters to hundreds of meters. However, there is a problem in that the installation length of the gas line is limited due to the refrigeration oil remaining in the gas line.
- As shown in
FIG. 10 , most refrigeration oil that does not return to the compressor remains in the gas line. - Therefore, the present invention has been made in view of the above problems, and it is an object of the present invention to provide a cooling receiver for an air conditioner in which a supercooler and a receiver are integrated and an air conditioner including the same.
- It is another object of the present invention to provide an air conditioner in which the length of a gas line is extended, thereby improving installation freedom, enhancing operational efficiency, improving the reliability of a compressor, and facilitating the recovery of oil to the compressor.
- These objects are achieved with the features of the claims.
- In accordance with an aspect of the present invention, there is provided an air conditioner including an air-conditioning cycle circuit including a first compressor for compressing a first refrigerant, a first condenser for condensing the first refrigerant compressed by the first compressor, a first expansion device for expanding the first refrigerant that has passed through the first condenser, and a first evaporator for evaporating the first refrigerant that has passed through the first expansion device, the air-conditioning cycle circuit performing an air-conditioning operation through circulation of the first refrigerant, a refrigeration cycle circuit including a second compressor for compressing a second refrigerant, a second condenser for condensing the second refrigerant compressed by the second compressor, a second expansion device for expanding the second refrigerant that has passed through the second condenser, and a second evaporator for evaporating the second refrigerant that has passed through the second expansion device, the refrigeration cycle circuit refrigerating stored food through circulation of the second refrigerant, a cooling receiver for performing heat exchange between the first refrigerant that has passed through the first condenser and the second refrigerant that has passed through the second condenser, a first bypass unit for diverting a portion of the second refrigerant that has passed through the second compressor so as to exchange heat with the second refrigerant that has passed through the second evaporator, and a control unit for controlling overall operation of the air conditioner. When an oil recovery operation is performed, the control unit performs control such that the first bypass unit enables heat exchange between the second refrigerant discharged from the second compressor and the second refrigerant that has passed through the second evaporator.
- The objectives and other advantages of the invention may be realized and attained by the structure particularly pointed out in the written description and claims hereof as well as the appended drawings.
- The above and other objects, features and other advantages of the present invention will be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings, in which:
-
FIG. 1A is a configuration diagram showing an air conditioner according to an embodiment of the present invention; -
FIG. 1B is a control block diagram of the air conditioner according to the embodiment of the present invention; -
FIG. 2 is a detailed view of a cooling receiver shown inFIG. 1 ; -
FIG. 3 is a sectional view taken along line A-A inFIG. 2 ; -
FIG. 4 is a diagram showing the flow of refrigerant when the cooling operation and the refrigeration operation of the air conditioner according to the embodiment of the present invention are performed at the same time; -
FIG. 5 is a diagram showing the flow of refrigerant when the heating operation and the refrigeration operation of the air conditioner according to the embodiment of the present invention are performed at the same time; -
FIG. 6 is a diagram showing the flow of refrigerant when only the refrigeration operation of the air conditioner according to the embodiment of the present invention is performed; -
FIG. 7 is a diagram showing the flow of refrigerant when the cooling operation, the refrigeration operation and the oil recovery operation of the air conditioner according to the embodiment of the present invention are performed at the same time; -
FIG. 8A is a configuration diagram showing an air conditioner according to another embodiment of the present invention; -
FIG. 8B is a control block diagram of the air conditioner according to another embodiment of the present invention; -
FIG. 9 is a diagram showing the flow of refrigerant when the cooling operation, the refrigeration operation and the oil recovery operation of the air conditioner according to another embodiment of the present invention are performed at the same time; and -
FIG. 10 is a view showing the amount of residual oil in respective parts of a conventional air conditioner. - Advantages and features of the present invention and methods for achieving those of the present invention will become apparent upon referring to embodiments described later in detail with reference to the attached drawings. However, embodiments are not limited to the embodiments disclosed hereinafter and may be embodied in different ways. The embodiments are provided for perfection of disclosure and for informing persons skilled in this field of art of the scope of the present invention. The same reference numerals may refer to the same elements throughout the specification.
- Spatially-relative terms such as "below", "beneath", "lower", "above", or "upper" may be used herein to describe one element's relationship to another element as illustrated in the Figures. It will be understood that spatially-relative terms are intended to encompass different orientations of the device in addition to the orientation depicted in the Figures. For example, if the device in one of the figures is turned over, elements described as "below" or "beneath" other elements would then be oriented "above" the other elements. The exemplary terms "below" or "beneath" can, therefore, encompass both an orientation of above and below. Since the device may be oriented in another direction, the spatially-relative terms may be interpreted in accordance with the orientation of the device.
- The terminology used in the present disclosure is for the purpose of describing particular embodiments only and is not intended to limit the disclosure. As used in the disclosure and the appended claims, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless context clearly indicates otherwise. It will be further understood that the terms "comprises" and/or "comprising," when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof.
- Unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and the present disclosure, and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
- In the drawings, the thickness or size of each layer is exaggerated, omitted, or schematically illustrated for convenience of description and clarity. Also, the size or area of each constituent element does not entirely reflect the actual size thereof.
- Hereinafter, exemplary embodiments of the present invention will be described with reference to the accompanying drawings.
-
FIG. 1A is a configuration diagram showing an air conditioner according to an embodiment of the present invention, andFIG. 1B is a control block diagram of the air conditioner according to the embodiment of the present invention. - Referring to
FIG. 1 , the air conditioner according to the embodiment of the present invention includes an air-conditioning cycle circuit 1 and arefrigeration cycle circuit 2. The air-conditioning cycle circuit 1 may include an air-conditioning outdoor unit O1 that is installed outdoors and an air-conditioning indoor unit I1 that is installed indoors. Therefrigeration cycle circuit 2 may include a refrigerationoutdoor unit 02 that is installed outdoors and a refrigeration indoor unit I2 that is installed indoors. The air-conditioning cycle circuit 1 may air-condition (or cool/heat) the interior of a room. Therefrigeration cycle circuit 2 may refrigerate (or cool/freeze) food stored in the refrigeration indoor unit I2. - First, the air-
conditioning cycle circuit 1 will now be described. - The air-
conditioning cycle circuit 1 may include afirst compressor 11, anoutdoor heat exchanger 13, afirst expansion device indoor heat exchanger 16. That is, the air-conditioning cycle circuit 1 includes afirst compressor 11 for compressing a first refrigerant, a first condenser for condensing the first refrigerant compressed by thefirst compressor 11, afirst expansion device first expansion device first compressor 11 again. - In the air-
conditioning cycle circuit 1, when the cooling operation is performed, a refrigerant may sequentially circulate through thefirst compressor 11, theoutdoor heat exchanger 13, thefirst expansion device indoor heat exchanger 16, and thefirst compressor 11. In the air-conditioning cycle circuit 1, when the cooling operation is performed, theoutdoor heat exchanger 13 may function as a first condenser, and theindoor heat exchanger 16 may function as a first evaporator. - Further, in the air-
conditioning cycle circuit 1, when the heating operation is performed, a refrigerant may sequentially circulate through thefirst compressor 11, theindoor heat exchanger 16, thefirst expansion device outdoor heat exchanger 13, and thefirst compressor 11. In the air-conditioning cycle circuit 1, when the heating operation is performed, theoutdoor heat exchanger 13 may function as a first evaporator, and theindoor heat exchanger 16 may function as a first condenser. - The air-
conditioning cycle circuit 1 may further include a cooling/heating switching valve 12 configured to enable a refrigerant to circulate through thefirst compressor 11, theoutdoor heat exchanger 13, thefirst expansion device indoor heat exchanger 16 when the cooling operation is performed and to enable a refrigerant to circulate through thefirst compressor 11, theindoor heat exchanger 16, thefirst expansion device outdoor heat exchanger 13 when the heating operation is performed. - The
first compressor 11 may suck a refrigerant, may compress the refrigerant, and may then discharge the compressed refrigerant. A plurality of thefirst compressors 11 may be connected in parallel or in series. Asuction flow channel 11a through which a refrigerant is sucked into thefirst compressor 11 may be connected to thefirst compressor 11. Adischarge flow channel 11b through which a compressed refrigerant is discharged from thefirst compressor 11 may be connected to thefirst compressor 11. When a plurality offirst compressors 11 is connected in parallel, thesuction flow channel 11a may be connected to the plurality offirst compressors 11 in parallel, and thedischarge flow channel 11b may be connected to the plurality offirst compressors 11 in parallel. - The
outdoor heat exchanger 13 may function as the first condenser in which a refrigerant compressed by thefirst compressor 11 is condensed when the cooling operation is performed. Theoutdoor heat exchanger 13 may function as the first evaporator in which a refrigerant expanded by thefirst expansion device outdoor heat exchanger 13 may be embodied as an air-refrigerant heat exchanger configured to perform heat exchange between outdoor air and a refrigerant. Alternatively, theoutdoor heat exchanger 13 may be embodied as a water-refrigerant heat exchanger configured to perform heat exchange between heat source water, such as water or antifreeze, and a refrigerant. - The
first expansion device outdoor expansion valve 14 for expanding a refrigerant flowing toward theoutdoor heat exchanger 13. Thefirst expansion device indoor expansion valve 15 for controlling a refrigerant flowing into or out of theindoor heat exchanger 16. Theoutdoor expansion valve 14 may be installed between theindoor expansion valve 15 and theoutdoor heat exchanger 13, and may be installed closer to theoutdoor heat exchanger 13 than to theindoor heat exchanger 16. Theoutdoor expansion valve 14 may not expand a refrigerant when the cooling operation is performed, but may expand a refrigerant when the heating operation is performed. Theoutdoor expansion valve 14 may be fully open in the cooling operation, and the opening degree thereof may be controlled to a set value in the heating operation. Theoutdoor expansion valve 14 may be installed on a bypass pipe installed on a refrigerant pipe between theoutdoor heat exchanger 13 and theindoor expansion valve 15. A check valve configured to enable a refrigerant to flow toward theindoor expansion valve 15 in the cooling operation and to enable a refrigerant to flow toward theoutdoor expansion valve 14 by blocking the refrigerant in the heating operation may be installed on the refrigerant pipe between theoutdoor heat exchanger 13 and theindoor expansion valve 15. Theindoor expansion valve 15 may be installed between theoutdoor heat exchanger 13 and theindoor heat exchanger 16, and may be installed closer to theindoor heat exchanger 16 than to theoutdoor heat exchanger 13. - The
indoor heat exchanger 16 may function as the first evaporator in which a refrigerant expanded by thefirst expansion device indoor heat exchanger 16 may function as the first condenser in which a refrigerant compressed by thefirst compressor 11 is condensed when the heating operation is performed. - The cooling/
heating switching valve 12 may be formed of a 4-way valve. That is, the cooling/heating switching valve 12 may be connected to thefirst compressor 11 through thesuction flow channel 11a of thefirst compressor 11, may be connected to thefirst compressor 11 through thedischarge flow channel 11b of thefirst compressor 11, may be connected to theoutdoor heat exchanger 13 through a suction/discharge flow channel 13a of theoutdoor heat exchanger 13, and may be connected to theindoor heat exchanger 16 through an air-conditioning gas line 17. - Further, the
outdoor heat exchanger 13 and theindoor heat exchanger 16 may be connected to each other through an air-conditioning liquid line 18. - An air-conditioning
gas line valve 17a configured to open/shut the air-conditioning gas line 17 may be installed on the air-conditioning gas line 17. An air-conditioningliquid line valve 18a configured to open/shut the air-conditioning liquid line 18 may be installed on the air-conditioning liquid line 18. - The air-
conditioning cycle circuit 1 may further include a first accumulator (not shown) installed between the cooling/heating switching valve 12 and thefirst compressor 11. The first accumulator is installed on thesuction flow channel 11a of thefirst compressor 11. Accordingly, a refrigerant that flows from the cooling/heating switching valve 12 toward thefirst compressor 11 may flow into the first accumulator. A liquid-state refrigerant, among the refrigerant that has flowed into the first accumulator, may accumulate in the first accumulator, and a gaseous-state refrigerant, among the refrigerant that has flowed into the first accumulator, may be sucked into thefirst compressor 11. - Second, the
refrigeration cycle circuit 2 will now be described. - The
refrigeration cycle circuit 2 may include asecond compressor 21, asecond condenser 23, asecond expansion device 25, and asecond evaporator 26. - In the
refrigeration cycle circuit 2, a second refrigerant may sequentially circulate through thesecond compressor 21, thesecond condenser 23, thesecond expansion device 25, thesecond evaporator 26, and thesecond compressor 21. - The
second compressor 21 may suck a refrigerant, may compress the refrigerant, and may discharge the compressed refrigerant. A plurality of thesecond compressors 21 may be connected in parallel or in series. Asuction flow channel 21a through which a refrigerant is sucked into thesecond compressor 21 may be connected to thesecond compressor 21. A discharge flow channel 21c through which a compressed refrigerant is discharged from thesecond compressor 21 may be connected to thesecond compressor 21. When a plurality ofsecond compressors 21 is connected in parallel, thesuction flow channel 21a may be connected to the plurality ofsecond compressors 21 in parallel, and the discharge flow channel 21c may be connected to the plurality ofsecond compressors 21 in parallel. - The
second condenser 23 condenses a refrigerant compressed by thesecond compressor 21. Thesecond condenser 23 may be embodied as an air-refrigerant heat exchanger configured to perform heat exchange between outdoor air and a refrigerant. Alternatively, thesecond condenser 23 may be embodied as a water-refrigerant heat exchanger configured to perform heat exchange between heat source water, such as water or antifreeze, and a refrigerant. Acondenser fan 23a for supplying outdoor air to thesecond condenser 23 may be disposed close to thesecond condenser 23. - The
second expansion device 25 expands a refrigerant that enters thesecond evaporator 26. Thesecond expansion device 25 may be installed between thesecond condenser 23 and thesecond evaporator 26, and may be installed closer to thesecond evaporator 26 than to thesecond condenser 23. - The
second evaporator 26 may evaporate a refrigerant while refrigerating food stored in the refrigeration indoor unit I2 by performing heat exchange between the refrigerant expanded by thesecond expansion device 25 and the air within the refrigeration indoor unit I2. - The
second compressor 21 may be connected to thesecond evaporator 26 through thesuction flow channel 21a. Further, thesecond compressor 21 may be connected to thesecond condenser 23 through the discharge flow channel 21c. Furthermore, thesecond condenser 23 and thesecond evaporator 26 may be connected to each other through arefrigeration liquid line 26a. - A first suction
flow channel valve 21b configured to open/shut thesuction flow channel 21a is installed on thesuction flow channel 21a of thesecond compressor 21. A second suctionflow channel valve 26b configured to open/shut therefrigeration liquid line 26a is installed on therefrigeration liquid line 26a. - The
refrigeration cycle circuit 2 may further include asecond accumulator 70 installed between thesecond evaporator 26 and thesecond compressor 21. Thesecond accumulator 70 is installed on thesuction flow channel 21a of thesecond compressor 21. Accordingly, a refrigerant flowing from thesecond evaporator 26 toward thesecond compressor 21 may flow into thesecond accumulator 70, a liquid-state refrigerant, among the refrigerant that has flowed into thesecond accumulator 70, may accumulate in thesecond accumulator 70, and a gaseous-state refrigerant, among the refrigerant that has flowed into thesecond accumulator 70, may be sucked into thesecond compressor 21. - Further, the air conditioner according to the embodiment of the present invention further includes a cooling
receiver 50 configured to perform heat exchange between the refrigerant that has passed through thesecond condenser 23 and the refrigerant that has passed through one of theindoor heat exchanger 16 and theoutdoor heat exchanger 13, which functions as the first condenser, and to store the heat-exchanged refrigerant. A detailed explanation of the coolingreceiver 50 will be made later with reference toFIGs. 2 and3 . - The embodiment may further include an outdoor
air temperature sensor 83 configured to measure the temperature of outdoor air. The outdoorair temperature sensor 83 measures the temperature of outdoor air and transmits the measured temperature to acontrol unit 90. - The embodiment further includes an
oil level sensor 22 configured to detect the amount of oil within thesecond compressor 21. Theoil level sensor 22 detects the amount of oil within thesecond compressor 21 and transmits the information about the amount of oil to thecontrol unit 90. - A
discharge temperature sensor 81 configured to measure the temperature of the second refrigerant discharged from thesecond evaporator 26 is mounted on thesuction flow channel 21a of thesecond compressor 21. Thedischarge temperature sensor 81 transmits the information about the temperature of the refrigerant discharged from thesecond evaporator 26 to thecontrol unit 90. Thedischarge temperature sensor 81 is disposed at a position of thesuction flow channel 21a of thesecond compressor 21 that is close to thesecond evaporator 26. That is, thedischarge temperature sensor 81 is disposed at a portion of thesuction flow channel 21a of thesecond compressor 21 that is close to thesecond evaporator 26. - A
discharge pressure sensor 82 configured to detect the pressure of the second refrigerator discharged from thesecond evaporator 26 is installed on thesuction flow channel 21a of thesecond compressor 21. Thedischarge pressure sensor 82 transmits the information about the pressure of the second refrigerant discharged from thesecond evaporator 26 to thecontrol unit 90. - A first bypass unit diverts a portion of the second refrigerant that has passed through the
second compressor 21 so that the portion of the second refrigerant exchanges heat with the second refrigerant that has passed through thesecond evaporator 26. When the cooling operation or the heating operation (normal operation) is performed, the first bypass unit is in a closed state. When the oil recovery operation is performed, the first bypass unit supplies a portion of the high-temperature and high-pressure refrigerant discharged from thesecond compressor 21 to thesuction flow channel 21a of thesecond compressor 21, which is the discharge port of thesecond evaporator 26. When the oil recovery operation is performed, the first bypass unit enables a portion of the high-temperature and high-pressure refrigerant discharged from thesecond compressor 21 to bypass thesecond condenser 23, thesecond expansion device 25 and thesecond evaporator 26. - The high-temperature and high-pressure refrigerant supplied to the
suction flow channel 21a of thesecond compressor 21 by the first bypass unit increases the temperature of the second refrigerant within thesuction flow channel 21a of thesecond compressor 21. The oil within thesuction flow channel 21a of thesecond compressor 21 is increased in temperature and solubility and is decreased in viscosity. The oil, which has high viscosity and remains in thesuction flow channel 21a of thesecond compressor 21 in normal operation, is decreased in viscosity and is therefore easily recovered to thesecond compressor 21 by the pressure of the refrigerant. Consequently, there is an effect in that the reliability of thesecond compressor 21 is improved. - The first bypass unit includes a
first bypass pipe 61, which connects the discharge flow channel 21c of thesecond compressor 21, which connects thesecond compressor 21 to thesecond condenser 23, to thesuction flow channel 21a of thesecond compressor 21, which connects thesecond evaporator 26 to thesecond compressor 21, and afirst control valve 63, which is installed on thefirst bypass pipe 61 in order to control the flow of the refrigerant. - The
first bypass pipe 61 guides a portion of the second refrigerant compressed by thesecond compressor 21 to the discharge port of thesecond evaporator 26. One end of thefirst bypass pipe 61 is connected to the discharge flow channel 21c of thesecond compressor 21 and the opposite end of thefirst bypass pipe 61 is connected to thesuction flow channel 21a of thesecond compressor 21. - The
first control valve 63 controls the flow of the refrigerant passing through thefirst bypass pipe 61. Thefirst control valve 63 may include a solenoid valve or an electronic expansion valve. Thefirst control valve 63 includes an electronic expansion valve, which enables the opening degree thereof to be variably controlled. The opening degree of thefirst control valve 63 is controlled in response to the control signal from thecontrol unit 90. Depending on the control of the opening degree of thefirst control valve 63, the air conditioner according to the embodiment may perform the oil recovery operation during the cooling operation (normal operation) or may perform only the oil recovery operation while the cooling operation is stopped. Here, "normal operation" refers to operation including the cooling operation, the heating operation and the refrigeration operation, other than the oil recovery operation. - A second bypass unit diverts a portion of the second refrigerant that has passed through the
second compressor 21 so that the portion of the second refrigerant exchanges heat with the second refrigerant that has passed through thesecond evaporator 26. When the cooling operation or the heating operation is performed (i.e. upon normal operation), the second bypass unit is in a closed state. When the oil recovery operation is performed and the temperature of outdoor air is lower than a predetermined temperature, the second bypass unit additionally supplies a portion of the high-temperature and high-pressure refrigerant discharged from thesecond compressor 21 to thesuction flow channel 21a of thesecond compressor 21, which is the discharge port of thesecond evaporator 26. When the oil recovery operation is performed, the second bypass unit enables a portion of the high-temperature and high-pressure refrigerant discharged from thesecond compressor 21 to bypass thesecond condenser 23, thesecond expansion device 25 and thesecond evaporator 26. - The high-temperature and high-pressure refrigerant supplied to the
suction flow channel 21a of thesecond compressor 21 by the second bypass unit increases the temperature of the second refrigerant within thesuction flow channel 21a of thesecond compressor 21. The oil within thesuction flow channel 21a of thesecond compressor 21 is increased in temperature and solubility and is decreased in viscosity. The oil, which has high viscosity and remains in thesuction flow channel 21a of thesecond compressor 21 in normal operation, is decreased in viscosity and is therefore easily recovered to thesecond compressor 21 by the pressure of the refrigerant. Consequently, there is an effect in that the reliability of thesecond compressor 21 is improved. That is, the second bypass unit functions to additionally increase the temperature of the second refrigerant within thesuction flow channel 21a of thesecond compressor 21 in the environment in which the oil recovery operation is not smoothly performed by the first bypass unit. - The second bypass unit includes a
second bypass pipe 62, which connects the discharge flow channel 21c of thesecond compressor 21, which connects thesecond compressor 21 to thesecond condenser 23, to thesuction flow channel 21a of thesecond compressor 21, which connects thesecond evaporator 26 to thesecond compressor 21, and asecond control valve 64, which is installed on thesecond bypass pipe 62 in order to control the flow of the refrigerant. - The
second bypass pipe 62 guides a portion of the second refrigerant compressed by thesecond compressor 21 to the discharge port of thesecond evaporator 26. One end of thesecond bypass pipe 62 is connected to the discharge flow channel 21c of thesecond compressor 21 and the opposite end of thesecond bypass pipe 62 is connected to thesuction flow channel 21a of thesecond compressor 21. - The
second control valve 64 controls the flow of the refrigerant passing through thesecond bypass pipe 62. Thesecond control valve 64 may include a solenoid valve or an electronic expansion valve. Thesecond control valve 64 includes an electronic expansion valve, which enables the opening degree thereof to be variably controlled. The opening degree of thesecond control valve 64 is controlled in response to the control signal from thecontrol unit 90. - In order to efficiently recover the oil from the
suction flow channel 21a of thesecond compressor 21, the connection positions of the first andsecond bypass pipes first bypass pipe 61 and the discharge flow channel of thesecond compressor 21 may be closer to thesecond compressor 21 than the connection position between thesecond bypass pipe 62 and the discharge flow channel of thesecond compressor 21, and the connection position between thefirst bypass pipe 61 and the suction flow channel of thesecond compressor 21 may be closer to thesecond compressor 21 than the connection position between thesecond bypass pipe 62 and the suction flow channel of thesecond compressor 21. When the temperature of the outdoor air is high, the refrigerant is guided to a position close to thesecond compressor 21 through thefirst bypass pipe 61. When the temperature of the outdoor air is low, the refrigerant is guided to a position close to thesecond evaporator 26 through thesecond bypass pipe 62. Accordingly, the efficiency of the oil recovery operation may be enhanced and the operational load of the second accumulator may be reduced. - Further, the embodiment may further include a check valve, which is installed on the discharge flow channel of the
second compressor 21 in order to prevent the second refrigerant that has passed through thesecond compressor 21 from flowing backward. The check valve may be disposed between the branch point of thefirst bypass pipe 61 and the branch point of thesecond bypass pipe 62. - The refrigerant that flows into the
suction flow channel 21a of thesecond compressor 21 through the first andsecond bypass pipes suction flow channel 21a of thesecond compressor 21 into a two-phase refrigerant. Therefore, the opposite end of thefirst bypass pipe 61 and the opposite end of thesecond bypass pipe 62, which are connected to thesuction flow channel 21a of thesecond compressor 21, may be disposed between the second accumulator and thesecond evaporator 26. However, the opposite end of thefirst bypass pipe 61 and the opposite end of thesecond bypass pipe 62 may alternatively be disposed between the second accumulator and thesecond compressor 21. - The
control unit 90 controls the overall operation of the air conditioner. Thecontrol unit 90 may include a processing device, which performs a logical determination, and a memory. - Based on various detected information, the
control unit 90 performs control such that the air conditioner selectively performs normal operation or an oil recovery operation. During the oil recovery operation, thecontrol unit 90 may perform control such that normal operation is performed or is stopped. - When the oil within the
compressor 21 is insufficient, thecontrol unit 90 determines that the oil recovery operation is needed and starts the oil recovery operation. In an example, when the oil level value transmitted from theoil level sensor 22 is lower than a reference oil level value, thecontrol unit 90 performs the oil recovery operation. When the oil level value transmitted from theoil level sensor 22 is higher than the reference oil level value, thecontrol unit 90 performs normal operation. In another example, when a predetermined time has elapsed since the start of operation of the air conditioner, thecontrol unit 90 may perform the oil recovery operation. Here, the predetermined time may be set within the range from 2 hours to 5 hours. Specifically, the control process in which the oil recovery operation is performed on the basis of time is used when communication with thesecond evaporator 26 installed in the showcase is impossible. - When the temperature of the
suction flow channel 21a of thesecond compressor 21 is low, thecontrol unit 90 may determine that the oil recovery operation is needed and may start the oil recovery operation. When the discharge temperature value transmitted from thedischarge temperature sensor 81 is lower than a reference discharge temperature value, thecontrol unit 90 performs the oil recovery operation. When the discharge temperature value transmitted from thedischarge temperature sensor 81 is higher than the reference discharge temperature value, thecontrol unit 90 performs normal operation. - In the oil recovery operation, the
control unit 90 controls the first bypass unit such that the second refrigerant that has been discharged from thesecond compressor 21 and the second refrigerant that has passed through thesecond evaporator 26 perform heat exchange with each other. That is, thecontrol unit 90 controls the first bypass unit so as to guide the second refrigerant discharged from thesecond compressor 21 to the discharge port of thesecond evaporator 26. - In an example, in normal operation, the
control unit 90 drives thesecond compressor 21 so as to supply cool air to the showcase. In the oil recovery operation, thecontrol unit 90 drives thesecond compressor 21 and opens thefirst control valve 63 so as to supply the high-temperature and high-pressure refrigerant to thesuction flow channel 21a of thesecond compressor 21. In the oil recovery operation, thecontrol unit 90 may control the opening degree and the opening time of thefirst control valve 63. - In another example, in the oil recovery operation, the
control unit 90 fully opens thefirst control valve 63. When the temperature of the outdoor air is lower than a predetermined temperature (-15°C to 5°C), thecontrol unit 90 controls thesecond control valve 64 so as to be open. When the temperature of the outdoor air is higher than the predetermined temperature, thecontrol unit 90 controls thesecond control valve 64 so as to be closed. - In a further example, in the oil recovery operation, the
control unit 90 may increase the operation speed of thesecond compressor 21 above the operation speed at the time of normal operation. In this case, the flow rate of the second refrigerant is increased and thus the recovery of the oil is smoothly achieved. - When the oil recovery operation is performed during the cooling operation, the
control unit 90 may rotate thecondenser fan 23a at a maximum speed. When the oil recovery operation is performed during the heating operation, thecontrol unit 90 may stop thecondenser fan 23a or may rotate thecondenser fan 23a at a lower speed than in the refrigeration operation. The refrigeration load of the refrigeration cycle circuit may be reduced by varying the speed of thecondenser fan 23a. - The
control unit 90 may perform control such that the above-described specific embodiments associated with the oil recovery operation are performed at the same time or at different times or such that only one of the embodiments is performed. -
FIG. 2 is a detailed view of the cooling receiver shown inFIG. 1 , andFIG. 3 is a sectional view taken along line A-A inFIG. 2 . - Referring to
FIGs. 1 to 3 , the coolingreceiver 50 includes acooling unit 51 and areceiver unit 54 in which at least one end of the coolingunit 51 is disposed. - The cooling
unit 51 includes at least one firstrefrigerant flow channel 52 through which a refrigerant that has passed through thesecond condenser 23 flows and a secondrefrigerant flow channel 53 configured to surround the outer circumference of some of the at least one firstrefrigerant flow channel 52. The refrigerant that has passed through one of theoutdoor heat exchanger 13 and theindoor heat exchanger 16, which functions as the first condenser, exchanges heat with the refrigerant flowing through the firstrefrigerant flow channel 52 while flowing through the inside of the secondrefrigerant flow channel 53. Accordingly, the refrigerant flowing through the firstrefrigerant flow channel 52 is supercooled, and the refrigerant flowing through the secondrefrigerant flow channel 53 is gasified. - At least one end of the cooling
unit 51 is disposed in thereceiver unit 54, and a supercooled refrigerant flowing out of the firstrefrigerant flow channel 52 is stored in thereceiver unit 54. - The cooling
unit 51 and thereceiver unit 54 are formed to have a cylindrical shape having an empty space inside and are formed to be long in upward and downward directions. The diameter of the firstrefrigerant flow channel 52 may be the smallest, the diameter of the secondrefrigerant flow channel 53 may be greater than that of the firstrefrigerant flow channel 52, and the diameter of thereceiver unit 54 may be greater than that of the secondrefrigerant flow channel 53. Further, the firstrefrigerant flow channel 52 may be formed of seven smalldiameter pipes. - The cooling
unit 51 may have an upper end inserted and disposed in thereceiver unit 54 and may have a lower end protruding below thereceiver unit 54 so as to be exposed outside thereceiver unit 54. - In the
cooling unit 51, the upper end of the firstrefrigerant flow channel 52, which is disposed within thereceiver unit 54, is open, and the upper end of the secondrefrigerant flow channel 53 is closed. The open upper end of the firstrefrigerant flow channel 52 may protrude upwards from the upper end of the secondrefrigerant flow channel 53. Accordingly, refrigerant flowing through the firstrefrigerant flow channel 52 may be supercooled through heat exchange with a refrigerant flowing through the secondrefrigerant flow channel 53. Subsequently, the supercooled refrigerant may flow out of the open upper end of the firstrefrigerant flow channel 52 and may be stored in the internal space of thereceiver unit 54. - A first
inlet flow channel 52a and a secondinlet flow channel 53a are disposed in a portion of the coolingunit 51 that protrudes below thereceiver unit 54. Further, a firstoutlet flow channel 53b is disposed above thereceiver unit 54, and a secondoutlet flow channel 54a is disposed below thereceiver unit 54. - The first
inlet flow channel 52a is connected to the firstrefrigerant flow channel 52 through the secondrefrigerant flow channel 53. The firstinlet flow channel 52a supplies the firstrefrigerant flow channel 52 with refrigerant that has passed through thesecond condenser 23. In the case in which a plurality of firstrefrigerant flow channels 52 is disposed within the secondrefrigerant flow channel 53, the firstinlet flow channel 52a may branch into a plurality of first inlet flow channels within the secondrefrigerant flow channel 53 and the plurality of first inlet flow channels may be connected to the plurality of firstrefrigerant flow channels 52. - The second
inlet flow channel 53a is connected to the secondrefrigerant flow channel 53. The secondinlet flow channel 53a supplies the secondrefrigerant flow channel 53 with refrigerant that has passed through one of theoutdoor heat exchanger 13 and theindoor heat exchanger 16, which functions as the first condenser. The secondrefrigerant flow channel 53 is connected to the air-conditioning liquid line 18 via a heat-recovery liquid line 34 branching from the air-conditioning liquid line 18 that connects the secondoutdoor heat exchanger 13 and theindoor heat exchanger 16. That is, the heat-recovery liquid line 34 connects the secondrefrigerant flow channel 53 and the air-conditioning liquid line 18. A heatrecovery expansion device 34a is installed on the heat-recovery liquid line 34. Accordingly, a portion of the refrigerant that has passed through the first condenser may move to the first evaporator through the air-conditioning liquid line 18. The remainder of the refrigerant may move to the heat-recovery liquid line 34, may be expanded by the heatrecovery expansion device 34a, and may then move to the secondinlet flow channel 53a. The refrigerant that has moved to the secondinlet flow channel 53a may be supplied to the secondrefrigerant flow channel 53. - The first
outlet flow channel 53b is connected to the upper portion of the secondrefrigerant flow channel 53 within thereceiver unit 54 through the upper end of thereceiver unit 54. Accordingly, refrigerant supplied to the secondrefrigerant flow channel 53 through the secondinlet flow channel 53a may pass through the secondrefrigerant flow channel 53 and may then escape through the firstoutlet flow channel 53b. The firstoutlet flow channel 53b protruding above thereceiver unit 54 is connected to thesuction flow channel 11a of thefirst compressor 11 via a heat-recovery gas line 35. Accordingly, the refrigerant that has escaped through the firstoutlet flow channel 53b may move to thesuction flow channel 11a of thefirst compressor 11 through the heat-recovery gas line 35 and may then be supplied to thefirst compressor 11. - The second
outlet flow channel 54a is connected to therefrigeration liquid line 26a. Accordingly, supercooled refrigerant that has escaped through the upper end of the firstrefrigerant flow channel 52 and is stored in thereceiver unit 54 may escape through the secondoutlet flow channel 54a, may move to therefrigeration liquid line 26a, and may then be supplied to thesecond evaporator 26. - A
cap 54b configured to cover the upper end of thereceiver unit 54 may be disposed in the upper end of thereceiver unit 54. When thecap 54b is disposed, the firstoutlet flow channel 53b may penetrate thecap 54b. - Further, at least one mounting
bracket 55 may be disposed in the lower portion of thereceiver unit 54. The mountingbracket 55 may include a ring-shapedmain body unit 55a configured to surround the outer circumferential surface of thereceiver unit 54 and a plurality of mountingunits 55b disposed on the outer circumferential surface of themain body unit 55a while being equidistantly spaced apart from each other. The mountingbracket 55 may include three mountingunits 55b. The mountingunit 55b may be mounted on the refrigerationoutdoor unit 02 so as to couple thereceiver unit 54 to the refrigerationoutdoor unit 02. - A heat-recovery
liquid line valve 34b configured to open/shut the heat-recovery liquid line 34 is installed on the heat-recovery liquid line 34. Heat-recoverygas line valves recovery gas line 35 are installed on the heat-recovery gas line 35. The heat-recoverygas line valves gas line valve 35a disposed in the refrigerationoutdoor unit 02 and a second heat-recoverygas line valve 35b disposed in the air-conditioning outdoor unit O1. - The air-conditioning
gas line valve 17a, the air-conditioningliquid line valve 18a, the first suctionflow channel valve 21b, the second suctionflow channel valve 26b, the heat-recoveryliquid line valve 34b, and the heat-recoverygas line valves - The
first compressor 11, the four-way valve 12, theoutdoor heat exchanger 13, theoutdoor expansion valve 14, the air-conditioninggas line valve 17a, the air-conditioningliquid line valve 18a, and the second heat-recoverygas line valve 35b may be included in the air-conditioning outdoor unit O1. Further, thesecond compressor 21, thesecond condenser 23, the coolingreceiver 50, the first suctionflow channel valve 21b, the second suctionflow channel valve 26b, the heat-recoveryliquid line valve 34b, and the first heat-recoverygas line valve 35a may be included in the refrigerationoutdoor unit 02. Furthermore, theindoor heat exchanger 16 and theindoor expansion valve 15 may be included in the air-conditioning indoor unit I1. Furthermore, thesecond evaporator 26 and thesecond expansion device 25 may be included in the refrigeration indoor unit I2. - The operation of the air conditioner having the above-described construction according to the embodiment of the present invention will now be described.
-
FIG. 4 is a diagram showing the flow of refrigerant when the cooling operation and the refrigeration operation of the air conditioner according to the embodiment of the present invention are performed at the same time. - Referring to
FIG. 4 , the air conditioner according to the embodiment of the present invention may perform a cooling operation for cooling the interior of a room and a refrigeration operation for refrigerating food within the refrigerationindoor unit 12 at the same time. - That is, when the cooling operation of the air-
conditioning cycle circuit 1 is performed, thefirst compressor 11 is driven to discharge a refrigerant. The refrigerant discharged by thefirst compressor 11 moves to the cooling/heating switching valve 12 through thedischarge flow channel 11b of thefirst compressor 11. The refrigerant that has moved to the cooling/heating switching valve 12 moves to theoutdoor heat exchanger 13 through the suction/discharge flow channel 13a of theoutdoor heat exchanger 13. When the cooling operation of the air-conditioning cycle circuit 1 is performed, theoutdoor heat exchanger 13 functions as the first condenser. - A portion of the refrigerant that has passed through the
outdoor heat exchanger 13 moves to theindoor heat exchanger 16 through the air-conditioning liquid line 18. The remainder of the refrigerant that has passed through theoutdoor heat exchanger 13 moves to the coolingreceiver 50 through the heat-recovery liquid line 34. - A portion of the refrigerant that belongs to the refrigerant that has passed through the
outdoor heat exchanger 13 and that moves to theindoor heat exchanger 16 through the air-conditioning liquid line 18 is supplied to theindoor heat exchanger 16 in the state in which the refrigerant has been expanded by thefirst expansion device 15. When the cooling operation of the air-conditioning cycle circuit 1 is performed, theindoor heat exchanger 16 functions as the first evaporator. The refrigerant that has moved to theindoor heat exchanger 16 may refrigerate indoor air and may be evaporated through heat exchange with the indoor air. The refrigerant evaporated by theindoor heat exchanger 16 may move to the cooling/heating switching valve 12 through the air-conditioning gas line 17 and may then be supplied to thefirst compressor 11 again through thesuction flow channel 11a of thefirst compressor 11. - In the
refrigeration cycle circuit 2, thesecond compressor 21 is driven to discharge a refrigerant. The refrigerant discharged by thesecond compressor 21 moves to thesecond condenser 23 through the discharge flow channel 21c of thesecond compressor 21. The refrigerant that has moved to thesecond condenser 23 moves to thesecond evaporator 26 through therefrigeration liquid line 26a. - The refrigerant that has passed through the
second condenser 23 is supplied to thesecond evaporator 26 in the state in which the refrigerant has been expanded by thesecond expansion device 25. The refrigerant that has moved to thesecond evaporator 26 may refrigerate food within the refrigeration indoor unit I2 and may be evaporated through heat exchange with air within the refrigeration indoor unit I2. The refrigerant evaporated by thesecond evaporator 26 may be supplied to thesecond compressor 21 again through thesuction flow channel 21a of thesecond compressor 21. - The remaining refrigerant that belongs to the refrigerant that has passed through the
outdoor heat exchanger 13 of the air-conditioning cycle circuit 1 and that moves to the coolingreceiver 50 through the heat-recovery liquid line 34 may be expanded by the heatrecovery expansion device 34a, may move to the secondrefrigerant flow channel 53, and may be gasified through heat exchange with the refrigerant that has passed through thesecond condenser 23 of therefrigeration cycle circuit 2 within the coolingreceiver 50 while supercooling the refrigerant that has passed through thesecond condenser 23. - Further, the cooling
receiver 50 may be installed between thesecond condenser 23 and thesecond expansion device 25 on therefrigeration liquid line 26a. The refrigerant that has passed through thesecond condenser 23 may exchange heat with the refrigerant flowing through the secondrefrigerant flow channel 53 and may be supercooled while flowing through the firstrefrigerant flow channel 52. The refrigerant supercooled while flowing through the firstrefrigerant flow channel 52 may escape through the open upper end of the firstrefrigerant flow channel 52 and may then be stored in thereceiver unit 54. The refrigerant gasified while flowing through the secondrefrigerant flow channel 53 may escape from the firstoutlet flow channel 53b, may move to thesuction flow channel 11a of thefirst compressor 11 through the heat-recovery gas line 35, and may then be supplied to thefirst compressor 11. Furthermore, the supercooled refrigerant stored in thereceiver unit 54 may escape through the secondoutlet flow channel 54a, may move to therefrigeration liquid line 26a, and may then be supplied to thesecond evaporator 26 in the state in which the refrigerant has been expanded by thesecond expansion device 25. At least one of the opening time and the opening degree of thesecond expansion device 25 is controlled by the control unit so that the amount of refrigerant within therefrigeration cycle circuit 2 is optimized. - There is an effect in that the efficiency of the air conditioner is improved due to the heat exchange through the cooling
receiver 50. Thecontrol unit 90 opens the heatrecovery expansion device 34a at a minimum opening degree when the cooling operation is performed. Accordingly, it is possible to prevent deterioration of the efficiency of the air-conditioning cycle circuit due to excessive heat absorption in the refrigeration cycle circuit when the cooling operation is performed. -
FIG. 5 is a diagram showing the flow of refrigerant when the heating operation and the refrigeration operation of the air conditioner according to the embodiment of the present invention are performed at the same time. - Referring to
FIG. 5 , the air conditioner according to the embodiment of the present invention may perform a heating operation for heating the interior of a room and a refrigeration operation for refrigerating food within the refrigeration indoor unit I2 at the same time. - That is, when the heating operation of the air-
conditioning cycle circuit 1 is performed, thefirst compressor 11 is driven to discharge a refrigerant. The refrigerant discharged by thefirst compressor 11 moves to the cooling/heating switching valve 12 through thedischarge flow channel 11b of thefirst compressor 11. The refrigerant that has moved to the cooling/heating switching valve 12 moves to theindoor heat exchanger 16 through the air-conditioning gas line 17. When the heating operation of the air-conditioning cycle circuit 1 is performed, theindoor heat exchanger 16 functions as the first condenser. - A portion of the refrigerant that has passed through the
indoor heat exchanger 16 moves to theoutdoor heat exchanger 13 through the air-conditioning liquid line 18. The remainder of the refrigerant that has passed through theindoor heat exchanger 16 moves to the coolingreceiver 50 through the heat-recovery liquid line 34. - A portion of the refrigerant that belongs to the refrigerant that has passed through the
indoor heat exchanger 16 and that moves to theoutdoor heat exchanger 13 through the air-conditioning liquid line 18 is supplied to theoutdoor heat exchanger 13 in the state in which the refrigerant has been expanded by thefirst expansion device 14. When the heating operation of the air-conditioning cycle circuit 1 is performed, theoutdoor heat exchanger 13 functions as the first evaporator. The refrigerant that has moved to theoutdoor heat exchanger 13 may be evaporated while exchanging heat with outdoor air. The refrigerant evaporated by theoutdoor heat exchanger 13 may move to the cooling/heating switching valve 12 through the suction/discharge flow channel 13a of theoutdoor heat exchanger 13 and may then be supplied to thefirst compressor 11 again through thesuction flow channel 11a of thefirst compressor 11. - In the
refrigeration cycle circuit 2, thesecond compressor 21 is driven to discharge a refrigerant. The refrigerant discharged by thesecond compressor 21 moves to thesecond condenser 23 through the discharge flow channel 21c of thesecond compressor 21. The refrigerant that has moved to thesecond condenser 23 moves to thesecond evaporator 26 through therefrigeration liquid line 26a. - The refrigerant that has passed through the
second condenser 23 is supplied to thesecond evaporator 26 in the state in which the refrigerant has been expanded by thesecond expansion device 25. The refrigerant that has moved to thesecond evaporator 26 may refrigerate food within the refrigeration indoor unit I2 and may be evaporated through heat exchange with air within the refrigeration indoor unit I2. The refrigerant evaporated by thesecond evaporator 26 may be supplied to thesecond compressor 21 again through thesuction flow channel 21a of thesecond compressor 21. - The remaining refrigerant that belongs to the refrigerant that has passed through the
indoor heat exchanger 16 of the air-conditioning cycle circuit 1 and that moves to the coolingreceiver 50 through the heat-recovery liquid line 34 may be expanded by the heatrecovery expansion device 34a, may move to the secondrefrigerant flow channel 53, and may be gasified through heat exchange with the refrigerant that has passed through thesecond condenser 23 of therefrigeration cycle circuit 2 within the coolingreceiver 50 while supercooling the refrigerant that has passed through thesecond condenser 23. - Further, the refrigerant that has passed through the
second condenser 23 may be supercooled through heat exchange with the refrigerant flowing through the secondrefrigerant flow channel 53 while flowing through the firstrefrigerant flow channel 52. The refrigerant supercooled while flowing through the firstrefrigerant flow channel 52 may escape through the open upper end of the firstrefrigerant flow channel 52 and may be stored in thereceiver unit 54. The refrigerant gasified while flowing through the secondrefrigerant flow channel 53 may escape from the firstoutlet flow channel 53b, may move to thesuction flow channel 11a of thefirst compressor 11 through the heat-recovery gas line 35, and may then be supplied to thefirst compressor 11. Furthermore, the supercooled refrigerant stored in thereceiver unit 54 may escape through the secondoutlet flow channel 54a, may move to therefrigeration liquid line 26a, and may then be supplied to thesecond evaporator 26 in the state in which the refrigerant has been expanded by thesecond expansion device 25. At least one of the opening time and the opening degree of thesecond expansion device 25 is controlled by the control unit so that the amount of refrigerant within therefrigeration cycle circuit 2 is optimized. - There is an effect in that the efficiency of the air conditioner is improved due to the heat exchange through the cooling
receiver 50. Thecontrol unit 90 opens the heatrecovery expansion device 34a to the maximum opening degree when the heating operation is performed. Accordingly, it is possible to use as much waste heat from the refrigeration cycle circuit for the air-conditioning cycle circuit as possible in the cooling operation, thereby improving the efficiency of the air-conditioning cycle circuit. -
FIG. 6 is a diagram showing the flow of refrigerant when only the refrigeration operation of the air conditioner according to the embodiment of the present invention is performed. - Referring to
FIG. 6 , the air conditioner according to the embodiment of the present invention may perform only a refrigeration operation for refrigerating food within the refrigeration indoor unit I2. That is, the air-conditioning cycle circuit 1 may not operate, and only therefrigeration cycle circuit 2 may operate. - In the
refrigeration cycle circuit 2, thesecond compressor 21 is driven to discharge a refrigerant. The refrigerant discharged by thesecond compressor 21 moves to thesecond condenser 23 through the discharge flow channel 21c of thesecond compressor 21. The refrigerant that has moved to thesecond condenser 23 moves to thesecond evaporator 26 through therefrigeration liquid line 26a. - The refrigerant that has passed through the
second condenser 23 is supplied to thesecond evaporator 26 in the state in which the refrigerant has been expanded by thesecond expansion device 25. The refrigerant that has moved to thesecond evaporator 26 may refrigerate food within the refrigeration indoor unit I2 and may be evaporated through heat exchange with air within the refrigeration indoor unit I2. The refrigerant evaporated by thesecond evaporator 26 may be supplied to thesecond compressor 21 again through thesuction flow channel 21a of thesecond compressor 21. - Further, since the air-
conditioning cycle circuit 1 does not operate, the refrigerant that has passed through thesecond condenser 23 may not be subjected to heat exchange while flowing through the firstrefrigerant flow channel 52, but may escape through the open upper end of the firstrefrigerant flow channel 52 and may then be stored in thereceiver unit 54. The stored refrigerant may escape through the secondoutlet flow channel 54a, may move to therefrigeration liquid line 26a, and may then be supplied to thesecond evaporator 26 in the state in which the refrigerant has been expanded by thesecond expansion device 25. At least one of the opening time and the opening degree of thesecond expansion device 25 may be controlled by the control unit so that the amount of refrigerant within therefrigeration cycle circuit 2 is optimized. -
FIG. 7 is a diagram showing the flow of refrigerant when the cooling operation, the refrigeration operation and the oil recovery operation of the air conditioner according to the embodiment of the present invention are performed at the same time. - Here, only differences from the state shown in
FIG. 4 , in which the cooling operation and the refrigeration operation are performed at the same time, will be described. - Referring to
FIG. 7 , when the oil recovery operation is performed, the second refrigerant compressed by thesecond compressor 21 is supplied to thesuction flow channel 21a of thesecond compressor 21 by the first bypass unit. The high-temperature and high-pressure refrigerant increases the temperature of the second refrigerant within thesuction flow channel 21a of thesecond compressor 21. The oil within thesuction flow channel 21a of thesecond compressor 21 is increased in temperature and solubility and is decreased in viscosity. - When the oil recovery operation is performed and the temperature of the outdoor air is lower than a predetermined temperature, the
control unit 90 additionally opens thesecond control valve 64. Accordingly, the refrigerant compressed by thesecond compressor 21 is additionally supplied to thesuction flow channel 21a of thesecond compressor 21 through thesecond bypass pipe 62. -
FIG. 8A is a configuration diagram showing an air conditioner according to another embodiment of the present invention, andFIG. 8B is a control block diagram of the air conditioner according to another embodiment of the present invention. - The same parts as those of the air conditioner according to the above-described embodiment shown in
FIG. 1 are denoted by the same reference numerals and a detailed explanation thereof will be omitted. Only differences from the above-described embodiment will be described. - Referring to
FIGs. 8A and8B , the air conditioner according to another embodiment further includes a third bypass unit, in contrast with the above-described embodiment shown inFIG. 1 . - The third bypass unit in this embodiment functions to guide a portion of the refrigerant that has been discharged from the
second condenser 23 to the discharge port of thesecond evaporator 26. - When the cooling operation (normal operation) is performed, the third bypass unit is in a closed state. When the oil recovery operation is performed, the third bypass unit supplies a portion of the high-temperature and high-pressure refrigerant that has been discharged from the
second condenser 23 to thesuction flow channel 21a of thesecond compressor 21, which is the discharge port of thesecond evaporator 26. The high-temperature and high-pressure refrigerant supplied to thesuction flow channel 21a of thesecond compressor 21 by the third bypass unit converts the refrigerant within thesuction flow channel 21a of thesecond compressor 21 into a two-phase refrigerant and increases the temperature. The oil within thesuction flow channel 21a of thesecond compressor 21 is increased in temperature and solubility and is decreased in viscosity. The oil, which has high viscosity and remains in thesuction flow channel 21a of thesecond compressor 21 in normal operation, is decreased in viscosity and is therefore easily recovered to thecompressor 21 by the pressure of the refrigerant. Consequently, there is an effect in that the reliability of thecompressor 21 is improved. - The third bypass unit includes a
third bypass pipe 71, which connects therefrigeration liquid line 26a, which connects thesecond condenser 23 to thesecond evaporator 26, to thesuction flow channel 21a of thesecond compressor 21, which connects thesecond evaporator 26 to thesecond compressor 21, and acontrol valve 72, which is installed on thethird bypass pipe 71 in order to control the flow of the refrigerant. - The
third bypass pipe 71 guides a portion of the refrigerant condensed by thesecond condenser 23 to the discharge port of thesecond evaporator 26. One end of thethird bypass pipe 71 is connected to therefrigeration liquid line 26a and the opposite end of thethird bypass pipe 71 is connected to thesuction flow channel 21a of thesecond compressor 21. - In order to efficiently recover the oil from the
suction flow channel 21a of thesecond compressor 21, the connection position of thethird bypass pipe 71 is important. In terms of the length and efficiency of the pipe, the connection position between thethird bypass pipe 71 and thesuction flow channel 21a of thesecond compressor 21 may be closer to thesecond evaporator 26 than to thesecond compressor 21. Thethird bypass pipe 71 is connected to a portion of thesuction flow channel 21a of thesecond compressor 21 that is located close to thesecond evaporator 26. Specifically, the connection positon between the opposite end of thethird bypass pipe 71 and thesuction flow channel 21a of thesecond compressor 21 is closer to thesecond evaporator 26 than the connection position between the opposite end of the first orsecond bypass pipe suction flow channel 21a of thesecond compressor 21. - The
control valve 72 controls the flow of the refrigerant passing through thethird bypass pipe 71. Thecontrol valve 72 may include a solenoid valve or an electronic expansion valve. Thecontrol valve 72 includes an electronic expansion valve, which enables the opening degree thereof to be variably controlled. The opening degree of thecontrol valve 72 is controlled in response to the control signal from thecontrol unit 90. As a result of the opening degree of thecontrol valve 72 being controlled, the air conditioner according to the embodiment may perform the oil recovery operation during the cooling operation (normal operation) or may perform only the oil recovery operation while the cooling operation is stopped. -
FIG. 9 is a diagram showing the flow of refrigerant when the cooling operation, the refrigeration operation and the oil recovery operation of the air conditioner according to another embodiment of the present invention are performed at the same time. - The operation of the air conditioner shown in
FIG. 9 has a difference from the operation of the air conditioner shown inFIG. 7 as to the operation of the third bypass unit. Hereinafter, only differences between the operation of the air conditioner according to another embodiment shown inFIG. 9 and the operation shown inFIG. 7 will be described. - Referring to
FIG. 9 , when the oil recovery operation is performed, thecontrol unit 90 performs control such that the third bypass unit enables heat exchange between the second refrigerant that has been discharged from thesecond condenser 23 and the second refrigerant that has passed through thesecond evaporator 26. That is, thecontrol unit 90 performs control such that the third bypass unit guides the second refrigerant discharged from thesecond condenser 23 to the discharge port of thesecond evaporator 26. - Specifically, when normal operation is performed, the
control unit 90 drives thesecond compressor 21 so as to supply cool air to the showcase. When the oil recovery operation is performed, thecontrol unit 90 drives thesecond compressor 21 and opens thecontrol valve 72 so as to supply the second refrigerant discharged from thesecond condenser 23 to thesuction flow channel 21a of thesecond compressor 21. When the oil recovery operation is performed, thecontrol unit 90 may control the opening degree and the opening time of thecontrol valve 72. - When the oil recovery operation is performed, the high-pressure refrigerant supplied by the third bypass unit increases the temperature of the second refrigerant within the
suction flow channel 21a of thesecond compressor 21. The oil within thesuction flow channel 21a of thesecond compressor 21 is increased in temperature and solubility and is decreased in viscosity. - As is apparent from the above description, in a cooling receiver for an air conditioner and an air conditioner including the same according to the embodiment of the present invention, a supercooler and a receiver are integrated, which leads to a compact design, a simple structure, a low price and improved refrigeration efficiency.
- The air conditioner according to the embodiment of the present invention has an effect in that two or more components are combined into a single unit, thus leading to a compact design and a simple structure.
- In addition, the air conditioner according to the embodiment of the present invention has effects of a low price and improved refrigeration efficiency.
- In addition, the air conditioner according to the embodiment of the present invention has an effect of overcoming a problem in which recovery of oil is not smoothly performed due to the considerably low temperature of an evaporator of a showcase.
- The effects of the invention are not limited to the above-mentioned effects, and other effects not mentioned will be clearly understood by those skilled in the art from the accompanying claims.
Claims (15)
- An air conditioner comprising:an air-conditioning cycle circuit (1) including a first compressor (11) for compressing a first refrigerant, a first condenser (13) for condensing the first refrigerant compressed by the first compressor (11), a first expansion device (14, 15) for expanding the first refrigerant that has passed through the first condenser (13), and a first evaporator (16) for evaporating the first refrigerant that has passed through the first expansion device (14, 15), the air-conditioning cycle circuit (1) performing an air-conditioning operation through circulation of the first refrigerant;a refrigeration cycle circuit (2) including a second compressor (21) for compressing a second refrigerant, a second condenser (23) for condensing the second refrigerant compressed by the second compressor (21), a second expansion device (25) for expanding the second refrigerant that has passed through the second condenser (23), and a second evaporator (26) for evaporating the second refrigerant that has passed through the second expansion device (25), the refrigeration cycle circuit (2) refrigerating stored food through circulation of the second refrigerant;a cooling receiver (50) for performing heat exchange between the first refrigerant that has passed through the first condenser (13) and the second refrigerant that has passed through the second condenser (23);a first bypass unit for diverting a portion of the second refrigerant that has passed through the second compressor (21) so as to exchange heat with the second refrigerant that has passed through the second evaporator (26); anda control unit (90) for controlling overall operation of the air conditioner,wherein, when an oil recovery operation is performed, the control unit (90) is configured to perform control such that the first bypass unit enables heat exchange between the second refrigerant discharged from the second compressor (21) and the second refrigerant that has passed through the second evaporator (26).
- The air conditioner according to claim 1, wherein the first bypass unit includes:a first bypass pipe (61) connecting a discharge flow channel (21c) of the second compressor (21), the discharge flow channel connecting the second compressor (21) to the second condenser (23), to a suction flow channel (21a) of the second compressor (21), the suction flow channel connecting the second evaporator (26) to the second compressor (21); anda first control valve (63) installed on the first bypass pipe (61) in order to control flow of refrigerant.
- The air conditioner according to claim 2, further comprising:a second bypass unit for diverting a portion of the second refrigerant that has passed through the second compressor (21) so as to exchange heat with the second refrigerant that has passed through the second evaporator (26).
- The air conditioner according to claim 3, wherein the second bypass unit includes:a second bypass pipe (62) connecting the discharge flow channel (21c) of the second compressor (21) to the suction flow channel (21a) of the second compressor (21); anda second control valve (64) installed on the second bypass pipe (62) in order to control flow of refrigerant,wherein the first bypass pipe (61) and the second bypass pipe (62) are arranged such that a connection position between the first bypass pipe (61) and the discharge flow channel (21c) of the second compressor (21) is closer to the second compressor (21) than a connection position between the second bypass pipe (62) and the discharge flow channel (21c) of the second compressor (21) and such that a connection position between the first bypass pipe (61) and the suction flow channel (21a) of the second compressor (21) is closer to the second compressor (21) than a connection position between the second bypass pipe (62) and the suction flow channel (21a) of the second compressor (21).
- The air conditioner according to claim 4, further comprising:a check valve installed on the discharge flow channel (21c) of the second compressor (21) in order to prevent the second refrigerant that has passed through the second compressor (21) from flowing backward,wherein the check valve is disposed between a branch point of the first bypass pipe (61) and a branch point of the second bypass pipe (62).
- The air conditioner according to any one of claims 1 to 5, wherein, when a predetermined time has elapsed since a start of operation of the air conditioner, the control unit (90) is configured to perform the oil recovery operation.
- The air conditioner according to any one of claims 1 to 6, further comprising:an oil level sensor (22) for detecting an amount of oil within the second compressor (21),wherein, when an oil level value transmitted from the oil level sensor (22) is lower than a reference oil level value, the control unit (90) performs the oil recovery operation.
- The air conditioner according to claim 4, wherein, when the oil recovery operation is performed, the control unit (90) is configured to perform control such that the first control valve (63) is open.
- The air conditioner according to claim 8, further comprising:an outdoor air temperature sensor (83) for measuring a temperature of outdoor air,wherein, when the oil recovery operation is performed and the temperature of outdoor air is lower than a predetermined temperature, the control unit (90) is configured to perform control such that the second control valve (64) is open, andwhen the oil recovery operation is performed and the temperature of outdoor air is higher than the predetermined temperature, the control unit (90) is configured to perform control such that the second control valve (64) is closed.
- The air conditioner according to any one of claims 1 to 9, wherein, when the oil recovery operation is performed, the control unit increases an operation speed of the second compressor (21) to be higher than in normal operation.
- The air conditioner according to any one of claims 1 to 10, further comprising:a condenser fan (23a) for supplying outdoor air to the second condenser (23),wherein, when the oil recovery operation is performed during a cooling operation, the control unit (90) is configured to rotate the condenser fan (23a) at a maximum speed, andwhen the oil recovery operation is performed during a heating operation, the control unit stops the condenser fan (23a).
- The air conditioner according to claim 1, further comprising:a third bypass unit for diverting a portion of refrigerant discharged from the second condenser (23) to a discharge port of the second evaporator (26).
- The air conditioner according to claim 12, wherein the third bypass unit includes:a third bypass pipe (71) connecting a refrigeration liquid line, the refrigeration liquid line connecting the second condenser (23) to the second evaporator (26), to a suction flow channel (21a) of the second compressor (21), the suction flow channel (21a) connecting the second evaporator (26) to the second compressor (21); anda control valve (72) installed on the third bypass pipe (71) in order to control flow of refrigerant.
- The air conditioner according to claim 12, or 13, wherein, when the oil recovery operation is performed, the control unit (90) is configured to perform control such that the third bypass unit diverts the second refrigerant discharged from the second condenser (23) to the discharge port of the second evaporator (26).
- The air conditioner according to claim 1, further comprising:a discharge temperature sensor (81) for measuring a temperature of a refrigerant discharged from the second evaporator (26),wherein, when a discharge temperature value transmitted from the discharge temperature sensor (81) is lower than a reference discharge temperature value, the control unit (90) performs the oil recovery operation.
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KR1020160119464A KR102032283B1 (en) | 2016-09-19 | 2016-09-19 | Air conditioner |
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EP3296664A1 true EP3296664A1 (en) | 2018-03-21 |
EP3296664B1 EP3296664B1 (en) | 2019-05-15 |
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EP17191590.3A Active EP3296664B1 (en) | 2016-09-19 | 2017-09-18 | Air conditioner |
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CN108375150A (en) * | 2018-04-26 | 2018-08-07 | 郑州云海信息技术有限公司 | A kind of air-conditioning system |
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Also Published As
Publication number | Publication date |
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KR102032283B1 (en) | 2019-10-15 |
EP3296664B1 (en) | 2019-05-15 |
KR20180031256A (en) | 2018-03-28 |
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