WO2013065233A1 - Refrigeration cycle apparatus and air conditioner provided with same - Google Patents

Refrigeration cycle apparatus and air conditioner provided with same Download PDF

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Publication number
WO2013065233A1
WO2013065233A1 PCT/JP2012/006299 JP2012006299W WO2013065233A1 WO 2013065233 A1 WO2013065233 A1 WO 2013065233A1 JP 2012006299 W JP2012006299 W JP 2012006299W WO 2013065233 A1 WO2013065233 A1 WO 2013065233A1
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WIPO (PCT)
Prior art keywords
heat exchanger
compressor
refrigerant
way valve
pipe
Prior art date
Application number
PCT/JP2012/006299
Other languages
French (fr)
Japanese (ja)
Inventor
憲昭 山本
廣和 加守田
富之 野間
正雄 犬井
Original Assignee
パナソニック株式会社
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Application filed by パナソニック株式会社 filed Critical パナソニック株式会社
Priority to KR1020147005247A priority Critical patent/KR20140092803A/en
Priority to CN201280041931.5A priority patent/CN103765133B/en
Publication of WO2013065233A1 publication Critical patent/WO2013065233A1/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02Defrosting cycles
    • F25B47/022Defrosting cycles hot gas defrosting
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00Compression machines, plants or systems, with reversible cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/021Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
    • F25B2313/0211Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being only used during defrosting
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02731Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one three-way valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00General 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
    • F25B2400/24Storage receiver heat
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00Compressor arrangements
    • F25B31/006Cooling of compressor or motor

Definitions

  • the present invention relates to a refrigeration cycle apparatus having a mechanism for switching between a path for directly flowing a refrigerant in which frost attached to an evaporator is melted to a compressor and a path for flowing the refrigerant to an compressor through an auxiliary heat exchanger for heating the refrigerant, and It relates to air conditioners.
  • a heat pump air conditioner performs defrosting by switching a four-way valve from a heating cycle to a cooling cycle when the outdoor heat exchanger is frosted during heating operation.
  • this defrosting method although the indoor fan is stopped, there is a disadvantage that a feeling of heating is lost because cold air is gradually discharged from the indoor unit.
  • FIG. 6 shows an example of a conventional refrigeration cycle apparatus disclosed in Patent Document 1.
  • the compressor 100, the four-way valve 102, the outdoor heat exchanger 104, the capillary tube 106, and the indoor unit are provided in the outdoor unit.
  • the indoor heat exchanger 108 is connected by a refrigerant pipe, one end is connected to the first bypass circuit 110 that bypasses the capillary tube 106, and the discharge side pipe of the compressor 100, and the other end is connected to the outdoor side from the capillary tube 106.
  • a second bypass circuit 112 connected to the pipe leading to the heat exchanger 104 is provided.
  • the first bypass circuit 110 is provided with a two-way valve 114, a check valve 116, and a heat storage heat exchanger 118, and the second bypass circuit 112 is provided with a two-way valve 120 and a check valve 122.
  • a heat storage tank 124 is provided around the compressor 100, and the heat storage tank 124 is filled with a latent heat storage material 126 for exchanging heat with the heat storage heat exchanger 118.
  • the two two-way valves 114 and 120 are controlled to open, a part of the refrigerant discharged from the compressor 100 flows to the second bypass circuit 112, and the remaining refrigerant is four-way. It flows to the valve 102 and the indoor heat exchanger 108. Further, after the refrigerant flowing through the indoor heat exchanger 108 is used for heating, a small amount of refrigerant flows through the capillary tube 106 to the outdoor heat exchanger 104. On the other hand, most of the remaining refrigerant flows into the first bypass circuit 110, flows through the two-way valve 114 to the heat storage heat exchanger 118, takes heat away from the heat storage material 126, and passes through the check valve 116.
  • the refrigerant passes through the capillary tube 106 and flows to the outdoor heat exchanger 104. After that, it merges with the refrigerant flowing through the second bypass circuit 112 at the inlet of the outdoor heat exchanger 104, performs defrosting using the heat of the refrigerant, passes through the four-way valve 102, and then enters the compressor 100. Inhaled.
  • the hot gas discharged from the compressor 100 during defrosting is guided to the outdoor heat exchanger 104 and the pressure of the refrigerant flowing into the outdoor heat exchanger 104
  • the defrosting ability is improved by keeping high.
  • FIG. 7 shows a configuration of a conventional air conditioner in Patent Document 2, and this air conditioner is composed of an outdoor unit 2 and an indoor unit 4 connected to each other by refrigerant piping.
  • a compressor 6, a four-way valve 8, a strainer 10, an expansion valve 12, and an outdoor heat exchanger 14 are provided inside the outdoor unit 2.
  • an indoor heat exchanger 16 is provided inside the indoor unit 4, which are connected to each other via a refrigerant pipe to constitute a refrigeration cycle.
  • the compressor 6 and the indoor heat exchanger 16 are connected via a first pipe 18 provided with a four-way valve 8, and the indoor heat exchanger 16 and the expansion valve 12 are second pipe provided with a strainer 10. 20 is connected.
  • the expansion valve 12 and the outdoor heat exchanger 14 are connected via a third pipe 22, and the outdoor heat exchanger 14 and the compressor 6 are connected via a fourth pipe 24.
  • a four-way valve 8 is disposed in the middle of the fourth pipe 24, and an accumulator 26 for separating the liquid-phase refrigerant and the gas-phase refrigerant is provided in the fourth pipe 24 on the refrigerant suction side of the compressor 6. ing.
  • the compressor 6 and the third pipe 22 are connected via a fifth pipe 28, and the first solenoid valve 30 is provided in the fifth pipe 28.
  • the fifth pipe 28 and the first electromagnetic valve 30 constitute a discharge gas bypass mechanism.
  • a heat storage tank 32 is provided around the compressor 6, and a heat storage heat exchanger 34 is provided inside the heat storage tank 32 and is filled with a heat storage material 36 for exchanging heat with the heat storage heat exchanger 34.
  • the heat storage tank 32, the heat storage heat exchanger 34, and the heat storage material 36 constitute a heat storage device that serves as an auxiliary heat exchanger.
  • the second pipe 20 and the heat storage heat exchanger 34 are connected via a sixth pipe 38, and the heat storage heat exchanger 34 and the fourth pipe 24 are connected via a seventh pipe 40.
  • the pipe 38 is provided with a second electromagnetic valve 31.
  • An indoor heat exchanger 16 is provided inside the indoor unit 4, and the indoor heat exchanger 16 exchanges indoor heat with indoor air sucked into the indoor unit 4 by a blower fan (not shown). Heat exchange with the refrigerant flowing in the interior of the vessel 16 is performed, and air heated by heat exchange is blown into the room during heating, while air cooled by heat exchange is blown into the room during cooling.
  • the refrigerant discharged from the discharge port of the compressor 6 passes from the four-way valve 8 to the indoor heat exchanger 16 through the first pipe 18.
  • the refrigerant condensed by exchanging heat with the indoor air in the indoor heat exchanger 16 passes through the second pipe 20 through the indoor heat exchanger 16, expands through the strainer 10 that prevents foreign matter from entering the expansion valve 12.
  • To valve 12. The refrigerant decompressed by the expansion valve 12 reaches the outdoor heat exchanger 14 through the third pipe 22, and the refrigerant evaporated by exchanging heat with the outdoor air in the outdoor heat exchanger 14 is the fourth pipe 24 and the four-way valve 8. And returns to the suction port of the compressor 6 through the accumulator 26.
  • the fifth pipe 28 branched from the compressor 6 discharge port of the first pipe 18 and the four-way valve 8 is connected to the expansion valve 12 of the third pipe 22 and the outdoor heat exchanger 14 via the first electromagnetic valve 30.
  • the heat storage tank 32 that is joined in between and accommodates the heat storage material 36 and the heat storage heat exchanger 34 is arranged so as to be in contact with and surround the compressor 6, and heat generated in the compressor 6 is supplied to the heat storage material 36. Accumulated.
  • the first solenoid valve 30 and the second solenoid valve 31 are closed and no refrigerant flows through the refrigerant circuit.
  • the first solenoid valve 30 and the second solenoid valve 31 are controlled to open, and in addition to the refrigerant flow during the normal heating operation described above, the first solenoid valve 30 and the second solenoid valve 31 are discharged from the discharge port of the compressor 6. After a part of the vapor-phase refrigerant passes through the fifth pipe 28 and the first electromagnetic valve 30 and merges with the refrigerant passing through the third pipe 22, the outdoor heat exchanger 14 is heated, condensed, and converted into a liquid phase. Through the fourth pipe 24, the four-way valve 8 and the accumulator 26 are returned to the suction port of the compressor 6.
  • a part of the liquid-phase refrigerant that is divided between the indoor heat exchanger 16 and the strainer 10 in the second pipe 20 passes through the sixth pipe 38 and the second electromagnetic valve 31, and then is stored in the heat storage material 36 in the heat storage heat exchanger 34. From the accumulator 26 and returns to the suction port of the compressor 6 through the seventh pipe 40 and the refrigerant that passes through the fourth pipe 24.
  • the temperature of the outdoor heat exchanger 14 that has become below freezing due to the attachment of frost at the start of defrosting and heating is heated by the gas-phase refrigerant discharged from the discharge port of the compressor 6, and the frost is melted near zero degrees.
  • the temperature of the outdoor heat exchanger 14 begins to rise again.
  • a temperature sensor not shown
  • the structure is guided to the outdoor heat exchanger via the heat storage tank, or after the refrigerant flows through the outdoor heat exchanger, the outdoor heat exchanger and
  • the temperature of the refrigerant flowing through the heat storage tank becomes high, heat absorption from the heat storage tank is not sufficient, and if it is attempted to secure the capacity of the indoor unit, it takes time to defrost. There was a problem of having.
  • An object of the present invention is to solve the above-described conventional problems, and to provide an air conditioner that can shorten the defrosting time and further includes the refrigeration cycle device to improve comfort during heating operation.
  • the present invention provides: A compressor, A first heat exchanger connected to the compressor; An expansion valve connected to the first heat exchanger; A second heat exchanger connected to the expansion valve; A four-way valve to which the second heat exchanger and the compressor are connected; An auxiliary heat exchanger for heating the refrigerant disposed around the compressor; Between the suction pipe of the compressor and the four-way valve, a path for flowing the refrigerant directly from the four-way valve to the suction pipe of the compressor, and the refrigerant from the four-way valve to the suction pipe of the compressor through the auxiliary heat exchanger A switching device that enables switching with a flow path; With During the defrosting operation for melting frost adhering to the second heat exchanger, the switching device is controlled so that the refrigerant flowing through the first heat exchanger and the second heat exchanger passes through the four-way valve. Then, it flows through the auxiliary heat exchanger and is led to the suction pipe of the compressor.
  • the refrigerant after passing through the first heat exchanger and the second heat exchanger passes through the auxiliary heat exchanger during the defrosting operation. It becomes possible to make a heat exchanger into low temperature. Therefore, by quickly absorbing heat from the heat source, it is possible to shorten the defrosting time, to suppress a decrease in the room temperature of the defrosting operation during the heating operation, and to improve the comfort.
  • the block diagram of the air conditioner provided with the refrigeration cycle apparatus which concerns on Embodiment 1 of this invention.
  • coolant at the time of normal heating in the air conditioner provided with the same refrigeration cycle apparatus The schematic diagram which shows the flow of the refrigerant
  • Refrigeration cycle configuration diagram according to Embodiment 2 of the present invention Control time chart according to Embodiment 2 of the present invention
  • the first invention is A compressor, A first heat exchanger connected to the compressor; An expansion valve connected to the first heat exchanger; A second heat exchanger connected to the expansion valve; A four-way valve to which the second heat exchanger and the compressor are connected; An auxiliary heat exchanger for heating the refrigerant disposed around the compressor; Between the suction pipe of the compressor and the four-way valve, a path for flowing the refrigerant directly from the four-way valve to the suction pipe of the compressor, and the refrigerant from the four-way valve to the suction pipe of the compressor through the auxiliary heat exchanger A switching device that enables switching with a flow path; With During the defrosting operation for melting frost adhering to the second heat exchanger, the switching device is controlled so that the refrigerant flowing through the first heat exchanger and the second heat exchanger passes through the four-way valve.
  • the refrigeration cycle apparatus is characterized in that it flows through the auxiliary heat exchanger and is led to the suction pipe of the compressor.
  • the switching device is a three-way valve.
  • a discharge gas bypass mechanism connected between the expansion valve and the second heat exchanger from a discharge pipe of the compressor is provided. It is configured. With this configuration, it is possible to supply the high-temperature refrigerant from the compressor to the second heat exchanger, and the defrosting time can be greatly shortened.
  • a heat source of the auxiliary heat exchanger for heating the refrigerant is disposed so as to surround the compressor, and the compression It is a heat storage material that stores the heat generated by the machine.
  • the defrosting of a 2nd heat exchanger can be complete
  • the auxiliary heat exchanger that performs heat exchange with the heat storage material can be set to a low temperature, so that the maximum amount of heat absorbed from the heat storage material can be increased, and the defrosting time can be shortened.
  • the comfort can be improved by suppressing, for example, a decrease in room temperature in the defrosting operation during the heating operation.
  • the switching device provided between the four-way valve and the auxiliary heat exchanger and the auxiliary heat exchanger A throttle mechanism for increasing the refrigerant pressure loss is provided between them.
  • the refrigerant flowing through the auxiliary heat exchanger can be further lowered in temperature, and the heat absorption rate from the heat source can be improved.
  • a temperature sensor that detects a pipe temperature of the second heat exchanger, the compressor, the expansion valve, and the switching
  • the apparatus further includes a refrigeration cycle control device electrically connected to the device and the temperature sensor.
  • the refrigeration cycle control device switches from normal heating operation to defrosting / heating operation.
  • a switching instruction is output. Further, at the time of defrosting / heating operation, the temperature in the second heat exchanger melts frost when the temperature in the second heat exchanger is near zero, and the temperature in the second heat exchanger rises after the frost is melted.
  • the refrigeration cycle control device When the sensor detects, it is determined that the defrosting is completed, and the refrigeration cycle control device outputs a switching instruction from the defrosting / heating operation to the normal heating operation. Thereby, the start and completion of defrosting / heating operation can be performed efficiently, and efficient defrosting / heating operation can be performed.
  • the refrigeration cycle control apparatus once decreases the operation speed of the compressor after the determination of the completion of the defrosting operation, and the first After the expansion valve opening of the expansion valve is reduced to such an extent that the liquid refrigerant supercooled by the heat exchanger can be held in the pipe of the first heat exchanger, the switching device for the refrigerant path is moved from the four-way valve to the auxiliary heat. It is configured to switch from a path for flowing the refrigerant to the suction pipe of the compressor through the exchanger to a path for flowing the refrigerant directly from the four-way valve to the suction pipe of the compressor.
  • the pressure difference at the inlet / outlet of the switching device is kept smaller than the allowable pressure difference of the switching device while suppressing the decline in heating capacity as much as possible, and switching is performed reliably.
  • the device can be switched.
  • the eighth invention is an air conditioner in which the first heat exchanger of the first to seventh inventions is an indoor heat exchanger and the second heat exchanger is an outdoor heat exchanger.
  • the pressure difference at the inlet / outlet of the switching device is kept smaller than the allowable pressure difference of the switching device while suppressing the decline in heating capacity as much as possible. Can be.
  • FIG. 1 shows a configuration of an air conditioner including a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • the air conditioner includes an outdoor unit 2 and an indoor unit 4 that are connected to each other through refrigerant piping. It is configured.
  • a compressor 6, a four-way valve 8, a strainer 10, an expansion valve 12, and an outdoor heat exchanger (second heat exchanger) 14 are provided inside the outdoor unit 2.
  • An indoor heat exchanger (first heat exchanger) 16 is provided inside the indoor unit 4. These are connected to each other via a refrigerant pipe to constitute a refrigeration cycle.
  • the compressor 6 and the indoor heat exchanger 16 are connected via a pipe 18 provided with a four-way valve 8, and the indoor heat exchanger 16 and the expansion valve 12 are connected to a pipe 20 provided with a strainer 10. Connected through.
  • the expansion valve 12 and the outdoor heat exchanger 14 are connected via a pipe 22, and the outdoor heat exchanger 14 and the compressor 6 are connected via a pipe 24 and a pipe 25.
  • a four-way valve 8 is disposed between the pipe 24 and the pipe 25 connecting the outdoor heat exchanger 14 and the compressor 6.
  • a three-way valve (switching device) 42 is connected between the four-way valve 8 and the compressor 6 via a pipe 25.
  • the three-way valve 42 and the pipe 25 on the compressor refrigerant suction side are provided with an accumulator 26 for separating the liquid-phase refrigerant and the gas-phase refrigerant.
  • the piping 22 connecting the outdoor heat exchanger 14 and the indoor heat exchanger 16 is connected to the compressor 6 via the piping 28, and the piping 28 is provided with an electromagnetic valve 30.
  • the pipe 28 and the electromagnetic valve 30 constitute a discharge gas bypass mechanism.
  • a heat storage tank 32 is provided around the compressor 6.
  • the heat storage tank 32 is provided with a heat storage heat exchanger 34 and filled with a heat storage material (for example, ethylene glycol aqueous solution) 36 for exchanging heat with the heat storage heat exchanger 34.
  • a heat storage material for example, ethylene glycol aqueous solution
  • the three-way valve 42 and the heat storage heat exchanger 34 are connected via a pipe 38 including a capillary tube (throttle mechanism) 43, and the pipe 25 connecting the three-way valve 42 and the compressor 6 is connected to the heat storage heat via the pipe 40. It is connected to the exchanger 34.
  • a blower fan (not shown), upper and lower blades (not shown), and left and right blades (not shown) are provided inside the indoor unit 4.
  • the indoor heat exchanger 16 exchanges heat between the indoor air sucked into the indoor unit 4 by the blower fan and the refrigerant flowing inside the indoor heat exchanger 16, and the air heated by the heat exchange during heating is used. While air is blown out, air cooled by heat exchange is blown out into the room during cooling.
  • the upper and lower blades change the direction of the air blown from the indoor unit 4 up and down as necessary.
  • the left and right blades change the direction of the air blown from the indoor unit 4 to the left and right as necessary.
  • the compressor 6, the blower fan, the upper and lower blades, the left and right blades, the four-way valve 8, the expansion valve 12, the electromagnetic valve 30, the three-way valve 42, and the like are electrically connected to a control device (not shown, for example, a microcomputer) for control. It is controlled and operated by the device.
  • a control device not shown, for example, a microcomputer
  • the refrigerant discharged from the discharge port of the compressor 6 reaches the indoor heat exchanger 16 through the pipe 18 from the four-way valve 8.
  • Refrigerant condensed by exchanging heat with indoor air in the indoor heat exchanger 16 exits the indoor heat exchanger 16, passes through the piping 20, passes through the strainer 10 that prevents foreign matter from entering the expansion valve 12, and then expands the expansion valve 12.
  • the refrigerant decompressed by the expansion valve 12 reaches the outdoor heat exchanger 14 through the pipe 22.
  • the refrigerant evaporated by exchanging heat with the outdoor air in the outdoor heat exchanger 14 passes through the pipe 24, the four-way valve 8, the three-way valve 42, the pipe 25, and the accumulator 26 through the suction port of the compressor 6. Return to 6.
  • pipe 28 branched from the discharge port of the compressor 6 of the pipe 18 and the four-way valve 8 is joined between the expansion valve 12 of the pipe 22 and the outdoor heat exchanger 14 via the electromagnetic valve 30.
  • the heat storage tank 32 in which the heat storage material 36 and the heat storage heat exchanger 34 are housed is disposed so as to be in contact with and surrounded by the compressor 6, and the heat generated in the compressor 6 is accumulated in the heat storage material 36.
  • One side of the three-way valve 42 is connected to the suction pipe of the four-way valve 8, the other side is connected to the three-way valve 42 and the pipe 25 connecting the suction port of the compressor 6, and the other side is connected to the three-way valve 42 and heat storage heat.
  • a pipe 38 connected to the exchanger 34 is connected.
  • FIG. 2 schematically showing the operation during normal heating of the air conditioner and the flow of the refrigerant.
  • the solenoid valve 30 is controlled to be closed, and the refrigerant discharged from the discharge port of the compressor 6 reaches the indoor heat exchanger 16 from the four-way valve 8 through the pipe 18 as described above.
  • the refrigerant condensed by exchanging heat with the indoor air in the indoor heat exchanger 16 exits the indoor heat exchanger 16 and passes through the pipe 20 to the expansion valve 12.
  • the refrigerant decompressed by the expansion valve 12 reaches the outdoor heat exchanger 14 through the pipe 22.
  • the refrigerant evaporated by exchanging heat with the outdoor air in the outdoor heat exchanger 14 reaches the four-way valve 8 through the pipe 24.
  • the three-way valve 42 is controlled so that the refrigerant leads from the outdoor heat exchanger 14 to the suction port of the compressor 6, that is, the pipe 24 and the pipe 25 communicate with each other.
  • the refrigerant passes through the three-way valve 42 and returns to the suction port of the compressor 6.
  • the heat generated in the compressor 6 is stored in the heat storage material 36 housed in the heat storage tank 32 from the outer wall of the compressor 6 through the inner wall of the heat storage tank 32.
  • FIG. 3 schematically showing the operation of the air conditioner during defrosting / heating and the flow of refrigerant.
  • the solid line arrows indicate the flow of the refrigerant used for heating
  • the broken line arrows indicate the flow of the refrigerant used for defrosting.
  • the air conditioner according to the present invention is provided with a temperature sensor 51 that detects the piping temperature of the outdoor heat exchanger 14. When the temperature sensor 51 detects that the evaporating temperature has decreased as compared to non-frosting, an instruction to switch from the normal heating operation to the defrosting / heating operation is output from the control device.
  • the solenoid valve 30 When switching from the normal heating operation to the defrosting / heating operation, the solenoid valve 30 is controlled to open. In addition to the refrigerant flow during the normal heating operation described above, a part of the gas-phase refrigerant exiting from the discharge port of the compressor 6 passes through the pipe 28 and the electromagnetic valve 30 and merges with the refrigerant passing through the pipe 22 to be outdoors. The heat exchanger 14 is heated and condensed to form a liquid phase, and then the four-way valve 8 is reached.
  • the three-way valve 42 is controlled so that the path leading the refrigerant from the outdoor heat exchanger 14 to the heat storage heat exchanger 34, that is, the pipe 24 and the pipe 38 communicate with each other.
  • the refrigerant that has passed through the four-way valve 8 is depressurized by the capillary tube 43 and becomes a low temperature, absorbs the heat of the heat storage material 36 by the heat storage heat exchanger 34, reaches the accumulator 26 in the gas phase or in a high quality state, and reaches the compressor 6. Return to the inlet.
  • the heat storage heat exchanger 34 that exchanges heat with the heat storage material 36 can be cooled. Since the maximum amount of heat absorbed from the heat storage material 36 is proportional to the temperature difference between the temperature of the compressor 6 and the temperature of the heat storage heat exchanger 34, if the temperature of the heat storage heat exchanger 34 can be lowered, the compressor 6 The temperature difference between the temperature and the temperature of the heat storage heat exchanger 34 can be increased, the maximum amount of heat absorbed from the heat storage material 36 can be increased, the defrosting time can be shortened, and the room temperature by the defrosting operation during the heating operation can be increased. The comfort can be improved by suppressing the decrease.
  • the liquid refrigerant in the heat storage heat exchanger 34 since the evaporation of the liquid refrigerant in the heat storage heat exchanger 34 is promoted, the liquid refrigerant does not return to the compressor 6 and the reliability of the compressor 6 can be improved.
  • the temperature of the outdoor heat exchanger 14 that has become below freezing due to the attachment of frost at the start of defrosting / heating is the liquid phase or the gas-liquid two-phase returning from the gas-phase refrigerant that exits from the discharge port of the compressor 6 and the indoor heat exchanger 16.
  • the frost is melted at around zero degrees, and when the frost is completely melted, it starts rising again.
  • the temperature sensor 51 detects the temperature rise of the outdoor heat exchanger 14, it is determined that the defrosting is completed, and an instruction to switch from the defrosting / heating operation to the normal heating operation is output from the control device.
  • the discharge gas bypass path from the compressor 6 through the piping 28 through the solenoid valve 30 to the outdoor heat exchanger 14 is not necessarily required, and is configured to be eliminated unless a very large defrosting capacity is required. Also good.
  • the gas phase refrigerant flows from the discharge port of the compressor 6 through the pipe 18, the indoor heat exchanger 16, the pipe 20, and the pipe 22 to the outdoor heat exchanger 14, thereby defrosting the outdoor heat exchanger 14.
  • the pipe 18, the indoor heat exchanger 16, the pipe 20, and the pipe 22 to the outdoor heat exchanger 14, thereby defrosting the outdoor heat exchanger 14.
  • the capillary tube 43 is provided in the pipe 38 extending from the three-way valve 42 to the heat storage heat exchanger 34.
  • the opening of the three-way valve 42 communicating with the heat storage heat exchanger 34 is provided. It is good also as the specification which narrowed down. In this case, the capillary tube 43 can be removed, and a compact configuration can be achieved at low cost.
  • Embodiment 2 ⁇ Background of obtaining one embodiment of the present invention>
  • the air conditioner of Embodiment 1 shown in FIG. 1 has been proposed as an improved version of the conventional air conditioner shown in FIG. 7, and FIG. 1 shows an example of a refrigeration cycle apparatus with an improved defrosting system. Yes.
  • a three-way valve 42 serving as a switching device is connected between the four-way valve 8 and the compressor 6 via a pipe 25, and further, the three-way valve 42 and the compressor refrigerant suction.
  • the pipe 25 on the side is provided with an accumulator 26 for separating the liquid phase refrigerant and the gas phase refrigerant.
  • the three-way valve 42 and the heat storage heat exchanger 34 are connected via a pipe 38 including a capillary tube 43 serving as a throttle mechanism, and the pipe 25 connecting the heat storage heat exchanger 34, the three-way valve 42 and the compressor 6 is It is connected via a pipe 40.
  • One side of the three-way valve 42 is connected to the suction pipe of the four-way valve 8, the other side is connected to the three-way valve 42 and the pipe 25 connecting the suction port of the compressor 6, and the other side is connected to the three-way valve 42 and heat storage heat.
  • a pipe 38 connected to the exchanger 34 a path for introducing the refrigerant from the four-way valve 8 through the pipe 25 to the suction port of the compressor 6, and a compressor through the heat storage heat exchanger 34 through the pipe 38 from the four-way valve 8. It is possible to switch the path for guiding the refrigerant to the six suction ports.
  • the refrigerant discharged from the discharge port of the compressor 6 passes through the pipe 18 and reaches the indoor heat exchanger 16 from the four-way valve 8.
  • the refrigerant condensed by exchanging heat with the indoor air in the indoor heat exchanger 16 exits the indoor heat exchanger 16, reaches the expansion valve 12 through the pipe 20, and the refrigerant decompressed by the expansion valve 12 passes through the pipe 22. It passes through to the outdoor heat exchanger 14.
  • the refrigerant evaporated by exchanging heat with the outdoor air in the outdoor heat exchanger 14 reaches the four-way valve 8 through the pipe 24.
  • the three-way valve 42 is controlled so that the passage of the refrigerant from the outdoor heat exchanger 14 to the suction port of the compressor 6, that is, the pipe 24 and the pipe 25 communicate with each other, and the refrigerant passing through the four-way valve 8 is the three-way valve 42. And return to the suction port of the compressor 6.
  • the heat generated in the compressor 6 is accumulated in the heat storage material 36 housed in the heat storage tank 32 from the outer wall of the compressor 6 through the outer wall of the heat storage tank 32.
  • a temperature sensor (not shown) for detecting the piping temperature of the outdoor heat exchanger 14 is provided. When the temperature sensor detects that the evaporating temperature has decreased as compared with the time of non-frosting, the control device performs normal heating operation. Outputs an instruction for defrosting / heating operation.
  • the three-way valve 42 is controlled so that the refrigerant leads from the outdoor heat exchanger 14 to the heat storage heat exchanger 34, that is, the pipe 24 and the pipe 38 communicate with each other.
  • the pressure is reduced by the capillary tube 43 to a low temperature, the heat storage heat exchanger 34 absorbs the heat of the heat storage material 36, reaches the accumulator 26 in the gas phase or in a high dryness state, and returns to the suction port of the compressor 6.
  • the temperature of the outdoor heat exchanger 14 that has become below freezing due to the attachment of frost at the start of defrosting / heating is the liquid phase or the gas-liquid two-phase returning from the gas-phase refrigerant that exits from the discharge port of the compressor 6 and the indoor heat exchanger 16.
  • the temperature of the outdoor heat exchanger 14 begins to rise again.
  • the temperature increase of the outdoor heat exchanger 14 is detected by the temperature sensor, it is determined that the defrosting is completed, and an instruction from the defrosting / heating operation to the normal heating operation is output from the control device. .
  • the refrigerant that has flowed through the indoor heat exchanger 16 and the outdoor heat exchanger 14 flows through the heat storage heat exchanger 34 via the four-way valve 8, and is sucked into the compressor 6.
  • the indoor heat exchanger 16 is operated at a high temperature and the heat storage heat exchanger 34 is maintained at a low temperature, and the heat absorption from the heat source is quickly performed, thereby reducing the defrosting time and heating operation. It is possible to improve comfort by suppressing a decrease in room temperature during defrosting operation.
  • the present inventors set the pressure difference at the inlet / outlet of the three-way valve while suppressing the decrease in the heating capacity as much as possible when switching from the defrosting / heating operation to the normal heating operation.
  • FIG. 4 is a refrigeration cycle configuration diagram showing the configuration of the air conditioner including the refrigeration cycle apparatus according to Embodiment 2 of the present invention, and the same components as in Embodiment 1 of the present invention shown in FIG. The same number is attached and detailed explanation is omitted.
  • the air conditioner further includes a refrigeration cycle control device 50 that controls the operation thereof.
  • the refrigeration cycle control device 50 is electrically connected to the temperature sensor 51 and detects the temperature of the outdoor heat exchanger (first heat exchanger) 14.
  • the refrigeration cycle control device 50 is also electrically connected to the compressor 6, the expansion valve 12, and the three-way valve 42 serving as a switching device, so that the operating speed of the compressor 6, the throttle amount of the expansion valve 12, and the refrigerant of the three-way valve 42. Determine path switching and drive control.
  • the solenoid valve 30 is controlled to be closed, and the refrigerant discharged from the discharge port of the compressor 6 passes through the pipe 18 and reaches the indoor heat exchanger 16 from the four-way valve 8.
  • the refrigerant condensed by exchanging heat with the indoor air in the indoor heat exchanger 16 exits the indoor heat exchanger 16 and passes through the pipe 20 to the expansion valve 12.
  • the refrigerant decompressed by the expansion valve 12 passes through the pipe 22 and reaches the outdoor heat exchanger 14.
  • the refrigerant evaporated by exchanging heat with the outdoor air in the outdoor heat exchanger 14 reaches the four-way valve 8 through the pipe 24.
  • the three-way valve 42 is controlled so that the passage of the refrigerant from the outdoor heat exchanger 14 to the suction port of the compressor 6, that is, the pipe 24 and the pipe 25 communicate with each other, and the refrigerant passing through the four-way valve 8 is the three-way valve 42. And return to the suction port of the compressor 6.
  • the heat generated in the compressor 6 is accumulated in the heat storage material 36 accommodated in the heat storage tank 32 from the outer wall of the compressor 6 through the outer wall of the heat storage tank 32 constituting the auxiliary heat exchanger.
  • the refrigeration cycle control device 50 When the outdoor heat exchanger 14 is frosted during the above-described normal heating operation and the frosted frost grows, the ventilation resistance of the outdoor heat exchanger 14 increases and the air flow decreases, and the evaporation in the outdoor heat exchanger 14 increases. The temperature drops.
  • the temperature sensor 51 detects that the evaporation temperature has decreased as compared with the time of non-frosting, the refrigeration cycle control device 50 outputs a switching instruction from the normal heating operation to the defrosting / heating operation.
  • the solenoid valve 30 When switching from the normal heating operation to the defrosting / heating operation, the solenoid valve 30 is controlled to open. In addition to the refrigerant flow during the normal heating operation described above, a part of the gas-phase refrigerant exiting from the discharge port of the compressor 6 passes through the pipe 28 and the electromagnetic valve 30 serving as a discharge gas bypass mechanism, and passes through the pipe 22. , The outdoor heat exchanger 14 is heated, condensed and converted into a liquid phase, and then the four-way valve 8 is reached.
  • the three-way valve 42 is controlled so that the path leading the refrigerant from the outdoor heat exchanger 14 to the heat storage heat exchanger 34, that is, the pipe 24 and the pipe 38 communicate with each other.
  • the refrigerant that has passed through the four-way valve 8 is depressurized by the capillary tube 43 serving as a throttling mechanism and becomes a low temperature, absorbs the heat of the heat storage material 36 by the heat storage heat exchanger 34, and enters the accumulator 26 in the gas phase or high dryness state. Finally, it returns to the suction port of the compressor 6.
  • the temperature of the outdoor heat exchanger 14 that has become below freezing due to the attachment of frost at the start of defrosting / heating is the liquid phase or the gas-liquid two-phase returning from the gas-phase refrigerant that exits from the discharge port of the compressor 6 and the indoor heat exchanger 16.
  • the frost is melted at around zero degrees, and when the frost is completely melted, it starts rising again.
  • the temperature sensor 51 detects the temperature rise of the outdoor heat exchanger 14, it is determined that the defrosting has been completed, and the refrigeration cycle control device 50 outputs a switching instruction from the defrosting / heating operation to the normal heating operation.
  • FIGS. 5 (a) to 5 (f) show control time charts according to Embodiment 2 of the present invention, particularly at the timing of shifting to normal heating from the time when it is determined that the above-described defrosting is completed. Changes in compressor speed, expansion valve opening, three-way valve path state, refrigerant pressure (high and low pressure), and heating capacity are shown with time.
  • FIG. 5 (a) is defrosting determination, (b) is the compressor rotation speed, (c) is the expansion valve opening degree, (d) is the three-way valve path state, and (e) is the refrigerant pressure (high and low pressure). ) And (f) show changes in heating capacity.
  • a control time chart when the expansion valve opening degree of the expansion valve 12 is not throttled when switching from the defrosting / heating operation to the normal heating will be described.
  • Fig.5 (a) it determines with defrosting having been completed at the timing of time T1 and transfering to normal heating operation.
  • the time T1 indicates a time when the temperature of the outdoor heat exchanger 14 is equal to or higher than a predetermined temperature.
  • the predetermined temperature is a temperature at which the frost attached to the outdoor heat exchanger 14 is melted and the temperature in the outdoor heat exchanger 14 starts to rise. Further, the temperature of the outdoor heat exchanger 14 is detected by the temperature sensor 51.
  • time T1 is a temperature at which the frost attached to the outdoor heat exchanger 14 is melted and the temperature in the outdoor heat exchanger 14 starts to rise.
  • the refrigeration cycle control device 50 issues an instruction to reduce the rotational speed of the compressor 6, and the rotational speed that is the set value at the end of the defrosting / heating operation. Control is performed so as to gradually decrease from F1 and reach the rotational speed F2 by time T2.
  • the time T2 indicates a time point after a predetermined time has elapsed from the time T1.
  • the refrigeration cycle control device 50 issues an instruction to switch the three-way valve 42 from the defrosting side to the heating side at the time T2.
  • the three-way valve 42 is switched from a path through which refrigerant flows from the four-way valve 8 through the heat storage heat exchanger 34 to the suction pipe of the compressor 6 to a path through which refrigerant flows directly from the four-way valve 8 to the suction pipe of the compressor 6.
  • the rotation speed of the compressor 6 is lowered, the pressure on the high pressure side of the refrigerant pressure is lowered, and the pressure on the low pressure side is raised.
  • the high-low pressure difference ⁇ P between the high-pressure side and the low-pressure side of the refrigerant pressure at time T2 is smaller than the high-low pressure difference at time T1.
  • the inlet / outlet pressure of the three-way valve 42 can be smaller than the allowable pressure difference of the three-way valve 42 at time T2, the three-way valve 42 can be switched reliably.
  • FIG. 5 (f) there is a problem that the temperature of the indoor heat exchanger 16 is lowered and the heating capacity is lowered due to a decrease in the pressure on the high pressure side of the refrigerant pressure (indicated by a broken line in the figure). .
  • the above problem is solved by controlling the expansion valve opening of the expansion valve 12 to be reduced.
  • a control time chart when the expansion valve opening degree of the expansion valve 12 is throttled when switching from the defrosting / heating operation to the normal heating will be described.
  • Embodiment 2 of the present invention as shown in FIG. 5 (a), it is determined that the defrosting is completed at the timing of time T1 and the routine is shifted to the normal heating operation.
  • the refrigeration cycle control device 50 issues an instruction so as to decrease from the rotational speed F ⁇ b> 1 of the compressor 6.
  • the refrigeration cycle control device 50 issues an instruction to make the expansion valve opening degree of the expansion valve 12 narrow.
  • the expansion valve 12 is gradually throttled from the expansion valve opening P1 that is a set value at the end of the defrosting / heating operation, and is excessively passed by the indoor heat exchanger 16 by time T2.
  • the refrigeration cycle control device 50 issues an instruction to switch the three-way valve 42 from the defrosting side to the heating side at the timing of time T2. That is, the three-way valve 42 is switched from a path through which refrigerant flows from the four-way valve 8 through the heat storage heat exchanger 34 to the suction pipe of the compressor 6 to a path through which refrigerant flows directly from the four-way valve 8 to the suction pipe of the compressor 6.
  • the high / low pressure difference ⁇ P between the high pressure side and the low pressure side of the refrigerant pressure is larger than when the expansion valve opening degree of the expansion valve 12 is not throttled, but the switching of the three-way valve 42 is If the high / low pressure difference ⁇ P is smaller than the allowable pressure difference of the three-way valve 42, the operation can be performed without any problem.
  • the rotation speed of the compressor 6 and the expansion valve opening of the expansion valve 12 are as shown in FIGS. 5 (b) and 5 (c) at time T3.
  • control is performed so as to be an initial set value when heating is started.
  • the time T3 indicates a point in time when the rotation speed of the compressor 6 and the expansion valve opening of the expansion valve 12 become the initial set values at the time of normal heating activation.
  • the rotation speed of the compressor 6 and the expansion valve opening of the expansion valve 12 are controlled so as to be constant at the initial set values at the time of normal heating activation, but depending on the capacity control after a predetermined time has elapsed.
  • the set value may be changed.
  • the time T3 is higher on the high pressure side of the refrigerant pressure than the time T1, and the heating capacity is increased. ing. This is because after the time T2, in order to increase the heating capacity more quickly, the number of rotations of the compressor 6 is increased and the throttle of the expansion valve 12 is adjusted to increase the difference between the high and low pressures of the refrigerant pressure. is there.
  • the pressure difference at the inlet / outlet of the three-way valve 42 is set to the allowable pressure difference of the three-way valve 42 while suppressing a decrease in the heating capacity as much as possible.
  • the three-way valve itself can be used at a lower cost with a relatively small allowable pressure difference while keeping the three-way valve 42 to be switched reliably.
  • the discharge gas bypass path from the compressor 6 through the piping 28 through the electromagnetic valve 30 to the outdoor heat exchanger (first heat exchanger) is not necessarily required, and a very large defrosting capacity is required. It is good also as a structure which eliminates except the case.
  • the heat storage heat exchanger 34 provided so as to surround the compressor 6 as an auxiliary heat exchanger has been described as an example.
  • the present invention is not limited to this, and other configurations may be used. It ’s good.
  • the refrigeration cycle apparatus not only improves the heat absorption capability from the heat source and improves the defrosting capability, but also reduces the return of the liquid refrigerant to the compressor as much as possible and improves the reliability of the compressor. Can do. Moreover, since a low-cost refrigerant path switching device can be adopted while reducing the decrease in heating capacity during defrosting as much as possible, it is useful for air conditioners, refrigerators, heat pump water heaters, and the like.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

A three-way valve (switching device) (42) is provided between an intake tube of a compressor (6) and a four-way valve (8), making possible a switch between a tube (25) draining refrigerant directly from the four-way valve (8) into the intake tube of the compressor (6) and a tube (38) draining refrigerant from the four-way valve (8) into the intake tube of the compressor (6) through an alternate heat exchanger (heat storage tank (32), heat storage exchanger (34), heat storage material (36)) for refrigerant heating; and by controlling the three-way valve (switching device) (42) during defrosting operation, refrigerant flowing to an indoor heat exchanger (first heat exchanger) (16) and an outdoor heat exchanger (second heat exchanger) (14) flows to the alternate heat exchanger (heat storage tank (32), heat storage exchanger (34), heat storage material (36)) via the four-way valve (8), and is guided to the intake tube of the compressor (6).

Description

冷凍サイクル装置およびそれを備えた空気調和機Refrigeration cycle apparatus and air conditioner equipped with the same
 本発明は、蒸発器に付着した霜が融解した冷媒を圧縮機へ直接流す経路と冷媒加熱用の補助熱交換器を通じて圧縮機へと流す経路との切り替えを行う機構を備えた冷凍サイクル装置および空気調和機に関する。 The present invention relates to a refrigeration cycle apparatus having a mechanism for switching between a path for directly flowing a refrigerant in which frost attached to an evaporator is melted to a compressor and a path for flowing the refrigerant to an compressor through an auxiliary heat exchanger for heating the refrigerant, and It relates to air conditioners.
 従来、ヒートポンプ式空気調和機は、暖房運転時において室外熱交換器に着霜した場合、暖房サイクルから冷房サイクルに四方弁を切り替えて除霜を行っている。この除霜方式では、室内ファンは停止するものの、室内機から冷気が徐々に放出されることから暖房感が失われるという欠点がある。 Conventionally, a heat pump air conditioner performs defrosting by switching a four-way valve from a heating cycle to a cooling cycle when the outdoor heat exchanger is frosted during heating operation. In this defrosting method, although the indoor fan is stopped, there is a disadvantage that a feeling of heating is lost because cold air is gradually discharged from the indoor unit.
 そこで、室外機に設けられた圧縮機を熱源とする蓄熱槽を設け、暖房運転中に蓄熱槽に蓄えられた圧縮機の廃熱を利用して除霜するようにしたものが提案されている(例えば、特許文献1、2参照)。 Therefore, a heat storage tank has been proposed that uses a compressor provided in the outdoor unit as a heat source, and defrosts using the waste heat of the compressor stored in the heat storage tank during heating operation. (For example, refer to Patent Documents 1 and 2).
 図6は、特許文献1における従来の冷凍サイクル装置の一例を示しており、室外機に設けられた圧縮機100と四方弁102と室外熱交換器104とキャピラリチューブ106と、室内機に設けられた室内熱交換器108とを冷媒配管で接続するとともに、キャピラリチューブ106をバイパスする第1バイパス回路110と、圧縮機100の吐出側の配管に一端を接続し、他端をキャピラリチューブ106から室外熱交換器104へ至る配管に接続した第2バイパス回路112が設けられている。第1バイパス回路110には、二方弁114と逆止弁116と蓄熱熱交換器118が設けられ、第2バイパス回路112には、二方弁120と逆止弁122が設けられている。 FIG. 6 shows an example of a conventional refrigeration cycle apparatus disclosed in Patent Document 1. The compressor 100, the four-way valve 102, the outdoor heat exchanger 104, the capillary tube 106, and the indoor unit are provided in the outdoor unit. The indoor heat exchanger 108 is connected by a refrigerant pipe, one end is connected to the first bypass circuit 110 that bypasses the capillary tube 106, and the discharge side pipe of the compressor 100, and the other end is connected to the outdoor side from the capillary tube 106. A second bypass circuit 112 connected to the pipe leading to the heat exchanger 104 is provided. The first bypass circuit 110 is provided with a two-way valve 114, a check valve 116, and a heat storage heat exchanger 118, and the second bypass circuit 112 is provided with a two-way valve 120 and a check valve 122.
 さらに、圧縮機100の周囲には蓄熱槽124が設けられており、蓄熱槽124の内部は、蓄熱熱交換器118と熱交換するための潜熱蓄熱材126が充填されている。 Furthermore, a heat storage tank 124 is provided around the compressor 100, and the heat storage tank 124 is filled with a latent heat storage material 126 for exchanging heat with the heat storage heat exchanger 118.
 この冷凍サイクルにおいて、除霜運転時には、二つの二方弁114、120が開制御され、圧縮機100から吐出された冷媒の一部は、第2バイパス回路112へと流れ、残りの冷媒は四方弁102と室内熱交換器108へと流れる。また、室内熱交換器108を流れた冷媒は暖房に利用された後、わずかの冷媒がキャピラリチューブ106を通って室外熱交換器104へと流れる。一方、残りの大部分の冷媒は、第1バイパス回路110へ流入し、二方弁114を通って蓄熱熱交換器118へと流れて蓄熱材126より熱を奪い、逆止弁116を通った後、キャピラリチューブ106を通過した冷媒と合流して室外熱交換器104へと流れる。その後、室外熱交換器104の入口で第2バイパス回路112を流れてきた冷媒と合流し、冷媒が持つ熱を利用して除霜を行い、さらに四方弁102を通過した後、圧縮機100に吸入される。 In this refrigeration cycle, during the defrosting operation, the two two-way valves 114 and 120 are controlled to open, a part of the refrigerant discharged from the compressor 100 flows to the second bypass circuit 112, and the remaining refrigerant is four-way. It flows to the valve 102 and the indoor heat exchanger 108. Further, after the refrigerant flowing through the indoor heat exchanger 108 is used for heating, a small amount of refrigerant flows through the capillary tube 106 to the outdoor heat exchanger 104. On the other hand, most of the remaining refrigerant flows into the first bypass circuit 110, flows through the two-way valve 114 to the heat storage heat exchanger 118, takes heat away from the heat storage material 126, and passes through the check valve 116. Thereafter, the refrigerant passes through the capillary tube 106 and flows to the outdoor heat exchanger 104. After that, it merges with the refrigerant flowing through the second bypass circuit 112 at the inlet of the outdoor heat exchanger 104, performs defrosting using the heat of the refrigerant, passes through the four-way valve 102, and then enters the compressor 100. Inhaled.
 この冷凍サイクル装置においては、第2バイパス回路112を設けることで、除霜時に圧縮機100から吐出されたホットガスを室外熱交換器104に導くとともに、室外熱交換器104に流入する冷媒の圧力を高く保つことで、除霜能力を向上させている。 In this refrigeration cycle apparatus, by providing the second bypass circuit 112, the hot gas discharged from the compressor 100 during defrosting is guided to the outdoor heat exchanger 104 and the pressure of the refrigerant flowing into the outdoor heat exchanger 104 The defrosting ability is improved by keeping high.
 図7は、特許文献2における従来の空気調和機の構成を示しており、この空気調和機は、冷媒配管で互いに接続された室外機2と室内機4とで構成されている。室外機2の内部には、圧縮機6と四方弁8とストレーナ10と膨張弁12と室外熱交換器14とが設けられ、室内機4の内部には、室内熱交換器16が設けられ、これらは冷媒配管を介して互いに接続されることで冷凍サイクルを構成している。 FIG. 7 shows a configuration of a conventional air conditioner in Patent Document 2, and this air conditioner is composed of an outdoor unit 2 and an indoor unit 4 connected to each other by refrigerant piping. Inside the outdoor unit 2, a compressor 6, a four-way valve 8, a strainer 10, an expansion valve 12, and an outdoor heat exchanger 14 are provided. Inside the indoor unit 4, an indoor heat exchanger 16 is provided, These are connected to each other via a refrigerant pipe to constitute a refrigeration cycle.
 さらに、圧縮機6と室内熱交換器16は、四方弁8が設けられた第1配管18を介して接続され、室内熱交換器16と膨張弁12は、ストレーナ10が設けられた第2配管20を介して接続されている。また、膨張弁12と室外熱交換器14は第3配管22を介して接続され、室外熱交換器14と圧縮機6は、第4配管24を介して接続されている。 Furthermore, the compressor 6 and the indoor heat exchanger 16 are connected via a first pipe 18 provided with a four-way valve 8, and the indoor heat exchanger 16 and the expansion valve 12 are second pipe provided with a strainer 10. 20 is connected. The expansion valve 12 and the outdoor heat exchanger 14 are connected via a third pipe 22, and the outdoor heat exchanger 14 and the compressor 6 are connected via a fourth pipe 24.
 第4配管24の中間部には四方弁8が配置されており、圧縮機6の冷媒吸入側における第4配管24には、液相冷媒と気相冷媒を分離するためのアキュームレータ26が設けられている。また、圧縮機6と第3配管22は、第5配管28を介して接続されており、第5配管28には第1電磁弁30が設けられている。これら第5配管28と第1電磁弁30とは、吐出ガスバイパス機構を構成している。 A four-way valve 8 is disposed in the middle of the fourth pipe 24, and an accumulator 26 for separating the liquid-phase refrigerant and the gas-phase refrigerant is provided in the fourth pipe 24 on the refrigerant suction side of the compressor 6. ing. The compressor 6 and the third pipe 22 are connected via a fifth pipe 28, and the first solenoid valve 30 is provided in the fifth pipe 28. The fifth pipe 28 and the first electromagnetic valve 30 constitute a discharge gas bypass mechanism.
 さらに、圧縮機6の周囲には蓄熱槽32が設けられ、蓄熱槽32の内部には、蓄熱熱交換器34が設けられるとともに、蓄熱熱交換器34と熱交換するための蓄熱材36が充填されており、蓄熱槽32と蓄熱熱交換器34と蓄熱材36とで補助熱交換器となる蓄熱装置を構成している。 Furthermore, a heat storage tank 32 is provided around the compressor 6, and a heat storage heat exchanger 34 is provided inside the heat storage tank 32 and is filled with a heat storage material 36 for exchanging heat with the heat storage heat exchanger 34. The heat storage tank 32, the heat storage heat exchanger 34, and the heat storage material 36 constitute a heat storage device that serves as an auxiliary heat exchanger.
 また、第2配管20と蓄熱熱交換器34は、第6配管38を介して接続され、蓄熱熱交換器34と第4配管24は、第7配管40を介して接続されており、第6配管38には第2電磁弁31が設けられている。 The second pipe 20 and the heat storage heat exchanger 34 are connected via a sixth pipe 38, and the heat storage heat exchanger 34 and the fourth pipe 24 are connected via a seventh pipe 40. The pipe 38 is provided with a second electromagnetic valve 31.
 室内機4の内部には、室内熱交換器16が設けられており、室内熱交換器16は、送風ファン(図示せず)により室内機4の内部に吸込まれた室内空気と、室内熱交換器16の内部を流れる冷媒との熱交換を行い、暖房時には熱交換により暖められた空気を室内に吹き出す一方、冷房時には熱交換により冷却された空気を室内に吹き出す。 An indoor heat exchanger 16 is provided inside the indoor unit 4, and the indoor heat exchanger 16 exchanges indoor heat with indoor air sucked into the indoor unit 4 by a blower fan (not shown). Heat exchange with the refrigerant flowing in the interior of the vessel 16 is performed, and air heated by heat exchange is blown into the room during heating, while air cooled by heat exchange is blown into the room during cooling.
 上記のように構成された従来の空気調和機において、各部品の相互の接続関係と機能を、暖房運転時を例にとり冷媒の流れとともに説明する。 In the conventional air conditioner configured as described above, the mutual connection relationship and function of each component will be described along with the flow of the refrigerant, taking the heating operation as an example.
 圧縮機6の吐出口から吐出された冷媒は、第1配管18を通って四方弁8から室内熱交換器16へと至る。室内熱交換器16で室内空気と熱交換して凝縮した冷媒は、室内熱交換器16を出て第2配管20を通り、膨張弁12への異物侵入を防止するストレーナ10を通って、膨張弁12に至る。膨張弁12で減圧した冷媒は、第3配管22を通って室外熱交換器14に至り、室外熱交換器14で室外空気と熱交換して蒸発した冷媒は、第4配管24と四方弁8とアキュームレータ26を通って圧縮機6の吸入口へと戻る。 The refrigerant discharged from the discharge port of the compressor 6 passes from the four-way valve 8 to the indoor heat exchanger 16 through the first pipe 18. The refrigerant condensed by exchanging heat with the indoor air in the indoor heat exchanger 16 passes through the second pipe 20 through the indoor heat exchanger 16, expands through the strainer 10 that prevents foreign matter from entering the expansion valve 12. To valve 12. The refrigerant decompressed by the expansion valve 12 reaches the outdoor heat exchanger 14 through the third pipe 22, and the refrigerant evaporated by exchanging heat with the outdoor air in the outdoor heat exchanger 14 is the fourth pipe 24 and the four-way valve 8. And returns to the suction port of the compressor 6 through the accumulator 26.
 また、第1配管18の圧縮機6吐出口と四方弁8の間から分岐した第5配管28は、第1電磁弁30を介して第3配管22の膨張弁12と室外熱交換器14の間に合流しており、内部に蓄熱材36と蓄熱熱交換器34を収納した蓄熱槽32は、圧縮機6に接して取り囲むように配置され、圧縮機6で発生した熱を蓄熱材36に蓄積している。そして、第2配管20の室内熱交換器16とストレーナ10との間から分岐した第6配管38が、第2電磁弁31を経て蓄熱熱交換器34の入口へと至り、蓄熱熱交換器34の出口から出た第7配管40は、第4配管24における四方弁8とアキュームレータ26の間に合流する。 The fifth pipe 28 branched from the compressor 6 discharge port of the first pipe 18 and the four-way valve 8 is connected to the expansion valve 12 of the third pipe 22 and the outdoor heat exchanger 14 via the first electromagnetic valve 30. The heat storage tank 32 that is joined in between and accommodates the heat storage material 36 and the heat storage heat exchanger 34 is arranged so as to be in contact with and surround the compressor 6, and heat generated in the compressor 6 is supplied to the heat storage material 36. Accumulated. And the 6th piping 38 branched from between the indoor heat exchanger 16 and the strainer 10 of the 2nd piping 20 reaches the inlet of the thermal storage heat exchanger 34 through the 2nd electromagnetic valve 31, and the thermal storage heat exchanger 34 The seventh pipe 40 exiting from the outlet of the pipe joins between the four-way valve 8 and the accumulator 26 in the fourth pipe 24.
 通常暖房運転時、第1電磁弁30と第2電磁弁31は閉制御されており、該冷媒回路には冷媒は流れていない。 During the normal heating operation, the first solenoid valve 30 and the second solenoid valve 31 are closed and no refrigerant flows through the refrigerant circuit.
 次に、除霜・暖房時の動作及び冷媒の流れを説明する。 Next, the operation during defrosting and heating and the flow of refrigerant will be described.
 上述した通常暖房運転中に室外熱交換器14に着霜し、着霜した霜が成長すると、室外熱交換器14の通風抵抗が増加して風量が減少し、室外熱交換器14内の蒸発温度が低下する。室外熱交換器14の配管温度を検出する温度センサ(図示せず)により、非着霜時に比べて、蒸発温度が低下したことを検出すると、制御装置より通常暖房運転から除霜・暖房運転への指示が出力される。 When the outdoor heat exchanger 14 is frosted during the above-described normal heating operation and the frosted frost grows, the ventilation resistance of the outdoor heat exchanger 14 increases and the air flow decreases, and the evaporation in the outdoor heat exchanger 14 increases. The temperature drops. When a temperature sensor (not shown) for detecting the piping temperature of the outdoor heat exchanger 14 detects that the evaporation temperature has decreased as compared to the time of non-frosting, the control device switches from normal heating operation to defrosting / heating operation. Is output.
 通常暖房運転から除霜・暖房運転に移行すると、第1電磁弁30と第2電磁弁31は開制御され、上述した通常暖房運転時の冷媒の流れに加え、圧縮機6の吐出口から出た気相冷媒の一部は第5配管28と第1電磁弁30を通り、第3配管22を通る冷媒に合流して、室外熱交換器14を加熱し、凝縮して液相化した後、第4配管24を通って四方弁8とアキュームレータ26を介して圧縮機6の吸入口へと戻る。 When the normal heating operation is shifted to the defrosting / heating operation, the first solenoid valve 30 and the second solenoid valve 31 are controlled to open, and in addition to the refrigerant flow during the normal heating operation described above, the first solenoid valve 30 and the second solenoid valve 31 are discharged from the discharge port of the compressor 6. After a part of the vapor-phase refrigerant passes through the fifth pipe 28 and the first electromagnetic valve 30 and merges with the refrigerant passing through the third pipe 22, the outdoor heat exchanger 14 is heated, condensed, and converted into a liquid phase. Through the fourth pipe 24, the four-way valve 8 and the accumulator 26 are returned to the suction port of the compressor 6.
 また、第2配管20における室内熱交換器16とストレーナ10の間で分流した液相冷媒の一部は、第6配管38と第2電磁弁31を経て、蓄熱熱交換器34で蓄熱材36から吸熱し蒸発、気相化して、第7配管40を通って第4配管24を通る冷媒に合流し、アキュームレータ26から圧縮機6の吸入口へと戻る。 In addition, a part of the liquid-phase refrigerant that is divided between the indoor heat exchanger 16 and the strainer 10 in the second pipe 20 passes through the sixth pipe 38 and the second electromagnetic valve 31, and then is stored in the heat storage material 36 in the heat storage heat exchanger 34. From the accumulator 26 and returns to the suction port of the compressor 6 through the seventh pipe 40 and the refrigerant that passes through the fourth pipe 24.
 除霜・暖房開始時に霜の付着により氷点下となった室外熱交換器14の温度は、圧縮機6の吐出口から出た気相冷媒によって加熱されて、零度付近で霜が融解し、霜の融解が終わると、室外熱交換器14の温度は再び上昇し始める。この室外熱交換器14の温度上昇を温度センサ(図示せず)で検出すると、除霜が完了したと判断し、制御装置より除霜・暖房運転から通常暖房運転への指示が出力されるように構成されている。 The temperature of the outdoor heat exchanger 14 that has become below freezing due to the attachment of frost at the start of defrosting and heating is heated by the gas-phase refrigerant discharged from the discharge port of the compressor 6, and the frost is melted near zero degrees. When melting is finished, the temperature of the outdoor heat exchanger 14 begins to rise again. When this temperature increase in the outdoor heat exchanger 14 is detected by a temperature sensor (not shown), it is determined that the defrosting is completed, and an instruction from the defrosting / heating operation to the normal heating operation is output from the control device. It is configured.
特開平3-31666号公報JP-A-3-31666 特許第4666111号公報Japanese Patent No. 4666111
 しかしながら、前記従来の構成では、熱源の有する熱量が少ない場合、圧縮機から吐出されたホットガスの大部分を室外熱交換器に導く必要があり、それに伴い、室内熱交換器の圧力が低下することで、室内機の能力が低下し、快適性を損なうという課題があった。また、従来の方式同様、冷媒が室内熱交換器を流れた後、蓄熱槽を経由して室外熱交換器へ導かれる構成、もしくは冷媒が室外熱交換器を流れた後、室外熱交換器と蓄熱槽へ分配して導かれる構成とした場合は、蓄熱槽を流れる冷媒の温度が高くなり、蓄熱槽からの吸熱が十分できず、室内機の能力を確保しようとすると、除霜に時間を有するという課題があった。 However, in the conventional configuration, when the heat source has a small amount of heat, it is necessary to guide most of the hot gas discharged from the compressor to the outdoor heat exchanger, and accordingly, the pressure of the indoor heat exchanger decreases. As a result, there is a problem that the capacity of the indoor unit is reduced and the comfort is impaired. Further, as in the conventional method, after the refrigerant flows through the indoor heat exchanger, the structure is guided to the outdoor heat exchanger via the heat storage tank, or after the refrigerant flows through the outdoor heat exchanger, the outdoor heat exchanger and When it is configured to be distributed and guided to the heat storage tank, the temperature of the refrigerant flowing through the heat storage tank becomes high, heat absorption from the heat storage tank is not sufficient, and if it is attempted to secure the capacity of the indoor unit, it takes time to defrost. There was a problem of having.
 本発明は、前記従来の課題を解決するもので、除霜時間の短縮を可能とし、さらに、その冷凍サイクル装置を備えて暖房運転時の快適性を向上する空気調和機を提供することを目的とする。 An object of the present invention is to solve the above-described conventional problems, and to provide an air conditioner that can shorten the defrosting time and further includes the refrigeration cycle device to improve comfort during heating operation. And
 上記目的を達成するために、本発明は、
 圧縮機と、
 前記圧縮機に接続された第1熱交換器と、
 前記第1熱交換器と接続された膨張弁と、
 前記膨張弁と接続された第2熱交換器と、
 前記第2熱交換器と前記圧縮機とが接続された四方弁と、
 前記圧縮機の周囲に配置された冷媒加熱用の補助熱交換器と、
 前記圧縮機の吸入管と前記四方弁の間に、前記四方弁から前記圧縮機の吸入管へ直接冷媒を流す経路と前記四方弁から前記補助熱交換器を通じて前記圧縮機の吸入管へ冷媒を流す経路との切り替えを可能とする切り替え装置と、
を備え、
 前記第2熱交換器に付着した霜を融解する除霜運転時には、前記切り替え装置を制御して、前記第1熱交換器と前記第2熱交換器を流れた冷媒が、前記四方弁を介して前記補助熱交換器を流れ、前記圧縮機の吸入管へ導かれるようにしたものである。
In order to achieve the above object, the present invention provides:
A compressor,
A first heat exchanger connected to the compressor;
An expansion valve connected to the first heat exchanger;
A second heat exchanger connected to the expansion valve;
A four-way valve to which the second heat exchanger and the compressor are connected;
An auxiliary heat exchanger for heating the refrigerant disposed around the compressor;
Between the suction pipe of the compressor and the four-way valve, a path for flowing the refrigerant directly from the four-way valve to the suction pipe of the compressor, and the refrigerant from the four-way valve to the suction pipe of the compressor through the auxiliary heat exchanger A switching device that enables switching with a flow path;
With
During the defrosting operation for melting frost adhering to the second heat exchanger, the switching device is controlled so that the refrigerant flowing through the first heat exchanger and the second heat exchanger passes through the four-way valve. Then, it flows through the auxiliary heat exchanger and is led to the suction pipe of the compressor.
 本発明によれば、除霜運転時、第1熱交換器と第2熱交換器を通った後の冷媒が補助熱交換器を通る構成としているため、第1熱交換器を高温に、補助熱交換器を低温とすることが可能となる。したがって、熱源からの吸熱を速やかに行うことで、除霜時間を短縮し、暖房運転時における除霜運転の室温低下を抑制して快適性を向上させることができる。 According to the present invention, the refrigerant after passing through the first heat exchanger and the second heat exchanger passes through the auxiliary heat exchanger during the defrosting operation. It becomes possible to make a heat exchanger into low temperature. Therefore, by quickly absorbing heat from the heat source, it is possible to shorten the defrosting time, to suppress a decrease in the room temperature of the defrosting operation during the heating operation, and to improve the comfort.
本発明の実施の形態1に係る冷凍サイクル装置を備えた空気調和機の構成図The block diagram of the air conditioner provided with the refrigeration cycle apparatus which concerns on Embodiment 1 of this invention. 同冷凍サイクル装置を備えた空気調和機において通常暖房時の冷媒の流れを示す模式図The schematic diagram which shows the flow of the refrigerant | coolant at the time of normal heating in the air conditioner provided with the same refrigeration cycle apparatus 同冷凍サイクル装置を備えた空気調和機において除霜・暖房時の冷媒の流れを示す模式図The schematic diagram which shows the flow of the refrigerant | coolant at the time of defrost and heating in the air conditioner provided with the same refrigeration cycle apparatus 本発明の実施の形態2に係る冷凍サイクル構成図Refrigeration cycle configuration diagram according to Embodiment 2 of the present invention 本発明の実施の形態2に係る制御タイムチャートControl time chart according to Embodiment 2 of the present invention 従来の冷凍サイクル装置を備えた空気調和機の構成図Configuration diagram of an air conditioner equipped with a conventional refrigeration cycle apparatus 従来の一例による冷凍サイクル構成図Refrigeration cycle configuration diagram according to a conventional example
 第1の発明は、
 圧縮機と、
 前記圧縮機に接続された第1熱交換器と、
 前記第1熱交換器と接続された膨張弁と、
 前記膨張弁と接続された第2熱交換器と、
 前記第2熱交換器と前記圧縮機とが接続された四方弁と、
 前記圧縮機の周囲に配置された冷媒加熱用の補助熱交換器と、
 前記圧縮機の吸入管と前記四方弁の間に、前記四方弁から前記圧縮機の吸入管へ直接冷媒を流す経路と前記四方弁から前記補助熱交換器を通じて前記圧縮機の吸入管へ冷媒を流す経路との切り替えを可能とする切り替え装置と、
を備え、
 前記第2熱交換器に付着した霜を融解する除霜運転時には、前記切り替え装置を制御して、前記第1熱交換器と前記第2熱交換器を流れた冷媒が、前記四方弁を介して前記補助熱交換器を流れ、前記圧縮機の吸入管へ導かれるようにしたことを特徴とする冷凍サイクル装置である。
 これにより、除霜運転時、第1熱交換器と第2熱交換器を通った後の冷媒が補助熱交換器を通る構成としているため、第1熱交換器を高温に、補助熱交換器を低温とすることが可能になり、熱源からの吸熱を速やかに行うことで、除霜時間を短縮し、暖房運転時における除霜運転の室温低下を抑制して快適性を向上させることができる。
The first invention is
A compressor,
A first heat exchanger connected to the compressor;
An expansion valve connected to the first heat exchanger;
A second heat exchanger connected to the expansion valve;
A four-way valve to which the second heat exchanger and the compressor are connected;
An auxiliary heat exchanger for heating the refrigerant disposed around the compressor;
Between the suction pipe of the compressor and the four-way valve, a path for flowing the refrigerant directly from the four-way valve to the suction pipe of the compressor, and the refrigerant from the four-way valve to the suction pipe of the compressor through the auxiliary heat exchanger A switching device that enables switching with a flow path;
With
During the defrosting operation for melting frost adhering to the second heat exchanger, the switching device is controlled so that the refrigerant flowing through the first heat exchanger and the second heat exchanger passes through the four-way valve. The refrigeration cycle apparatus is characterized in that it flows through the auxiliary heat exchanger and is led to the suction pipe of the compressor.
Thereby, since the refrigerant after passing through the first heat exchanger and the second heat exchanger passes through the auxiliary heat exchanger during the defrosting operation, the first heat exchanger is set to a high temperature, and the auxiliary heat exchanger It is possible to reduce the defrosting time by quickly performing the heat absorption from the heat source, and it is possible to improve the comfort by suppressing the decrease in the room temperature of the defrosting operation during the heating operation. .
 第2の発明は、特に、第1の発明の冷凍サイクル装置において、前記切り替え装置を三方弁としている。この構成によって、装置の省スペースへの収納が可能となり、機器のコンパクト化が可能となる。 In the second invention, in particular, in the refrigeration cycle apparatus of the first invention, the switching device is a three-way valve. With this configuration, the apparatus can be stored in a space-saving manner, and the apparatus can be made compact.
 第3の発明は、特に、第1または第2の発明の冷凍サイクル装置において、前記圧縮機の吐出管から前記膨張弁と前記第2熱交換器の間に接続される吐出ガスバイパス機構を備える構成としている。この構成によって、圧縮機からの高温の冷媒を第2熱交換器に供給することが可能となり、除霜時間を大幅に短縮することができる。 In a third aspect of the invention, in particular, in the refrigeration cycle apparatus of the first or second aspect of the invention, a discharge gas bypass mechanism connected between the expansion valve and the second heat exchanger from a discharge pipe of the compressor is provided. It is configured. With this configuration, it is possible to supply the high-temperature refrigerant from the compressor to the second heat exchanger, and the defrosting time can be greatly shortened.
 第4の発明は、特に、第1~3のいずれか1つの発明の冷凍サイクル装置において、前記冷媒加熱用の前記補助熱交換器の熱源は、前記圧縮機を囲むように配置され、前記圧縮機で発生した熱を蓄熱する蓄熱材としている。このような構成とすることで、ヒータなどの補助電力無し、もしくは最低限の補助電力の供給で第2熱交換器の除霜を短時間で終了することができる。また、本構成とした場合、蓄熱材と熱交換を行う前記補助熱交換器を低温とすることができるので、蓄熱材からの最大吸収熱量を増加させることが可能となり、除霜時間を短縮し、暖房運転時における除霜運転の例えば室温低下を抑制して快適性を向上させることができる。 In a fourth aspect of the present invention, in particular, in the refrigeration cycle apparatus according to any one of the first to third aspects, a heat source of the auxiliary heat exchanger for heating the refrigerant is disposed so as to surround the compressor, and the compression It is a heat storage material that stores the heat generated by the machine. By setting it as such a structure, the defrosting of a 2nd heat exchanger can be complete | finished in a short time by the supply of minimum auxiliary power, such as a heater, without auxiliary power. Further, in the case of this configuration, the auxiliary heat exchanger that performs heat exchange with the heat storage material can be set to a low temperature, so that the maximum amount of heat absorbed from the heat storage material can be increased, and the defrosting time can be shortened. The comfort can be improved by suppressing, for example, a decrease in room temperature in the defrosting operation during the heating operation.
 第5の発明は、特に、第1~4のいずれか1つの発明の冷凍サイクル装置において、前記四方弁から前記補助熱交換器の間に設けられた前記切り替え装置と前記補助熱交換器との間に冷媒圧力損失を増大させる絞り機構を設けている。この機構を設けたことによって、補助熱交換器を流れる冷媒を更に低温とすることが可能となり、熱源からの吸熱速度を向上させることができる。 In a fifth aspect of the invention, in particular, in the refrigeration cycle apparatus according to any one of the first to fourth aspects, the switching device provided between the four-way valve and the auxiliary heat exchanger and the auxiliary heat exchanger A throttle mechanism for increasing the refrigerant pressure loss is provided between them. By providing this mechanism, the refrigerant flowing through the auxiliary heat exchanger can be further lowered in temperature, and the heat absorption rate from the heat source can be improved.
 第6の発明は、特に、第1~5のいずれか1つの発明の冷凍サイクル装置において、前記第2熱交換器の配管温度を検出する温度センサと、前記圧縮機と前記膨張弁と前記切り替え装置と前記温度センサと電気的に接続される冷凍サイクル制御装置を更に備えている。通常暖房運転時、前記第2熱交換器内の温度が非着霜時に比べて低下したことを前記温度センサが検出すると、前記冷凍サイクル制御装置は、通常暖房運転から除霜・暖房運転への切り替え指示を出力する。また、除霜・暖房運転時、前記第2熱交換器内の温度が零度付近で霜を融解し、霜の融解が終わって、前記第2熱交換器内の温度が上昇したことを前記温度センサが検出すると、除霜が完了したと判断し、前記冷凍サイクル制御装置は、除霜・暖房運転から通常暖房運転への切り替え指示を出力する。これにより、除霜・暖房運転の開始と完了を効率よく行うことができ、効率的な除霜・暖房運転を行うことができる。 In a sixth aspect of the invention, in particular, in the refrigeration cycle apparatus according to any one of the first to fifth aspects of the invention, a temperature sensor that detects a pipe temperature of the second heat exchanger, the compressor, the expansion valve, and the switching The apparatus further includes a refrigeration cycle control device electrically connected to the device and the temperature sensor. When the temperature sensor detects that the temperature in the second heat exchanger is lower than that during non-frosting during normal heating operation, the refrigeration cycle control device switches from normal heating operation to defrosting / heating operation. A switching instruction is output. Further, at the time of defrosting / heating operation, the temperature in the second heat exchanger melts frost when the temperature in the second heat exchanger is near zero, and the temperature in the second heat exchanger rises after the frost is melted. When the sensor detects, it is determined that the defrosting is completed, and the refrigeration cycle control device outputs a switching instruction from the defrosting / heating operation to the normal heating operation. Thereby, the start and completion of defrosting / heating operation can be performed efficiently, and efficient defrosting / heating operation can be performed.
 第7の発明は、特に、第6の発明の冷凍サイクル装置において、前記冷凍サイクル制御装置は、除霜運転終了の判定をした後に、前記圧縮機の運転速度を一旦低下させるとともに、前記第1熱交換器で過冷却した液冷媒を前記第1熱交換器の管内に保持できる程度に膨張弁の膨張弁開度を絞った後、前記冷媒経路の前記切り替え装置を前記四方弁から前記補助熱交換器を通じて前記圧縮機の吸入管へ冷媒を流す経路から前記四方弁から前記圧縮機の吸入管へ直接冷媒を流す経路に切り替える構成としている。これにより、除霜・暖房運転時から通常暖房運転に切り替える際に、暖房能力の低下を極力小さく抑えながら、切り替え装置の入口出口の圧力差を切り替え装置の許容圧力差より小さく抑え、確実に切り替え装置が切り替わるようにすることができる。また、切り替え装置自体も比較的、許容圧力差の小さい低コストなものを採用可能である合理的な冷凍サイクル装置を提供することができる。 According to a seventh aspect of the present invention, in the refrigeration cycle apparatus of the sixth aspect of the invention, the refrigeration cycle control apparatus once decreases the operation speed of the compressor after the determination of the completion of the defrosting operation, and the first After the expansion valve opening of the expansion valve is reduced to such an extent that the liquid refrigerant supercooled by the heat exchanger can be held in the pipe of the first heat exchanger, the switching device for the refrigerant path is moved from the four-way valve to the auxiliary heat. It is configured to switch from a path for flowing the refrigerant to the suction pipe of the compressor through the exchanger to a path for flowing the refrigerant directly from the four-way valve to the suction pipe of the compressor. As a result, when switching from defrosting / heating operation to normal heating operation, the pressure difference at the inlet / outlet of the switching device is kept smaller than the allowable pressure difference of the switching device while suppressing the decline in heating capacity as much as possible, and switching is performed reliably. The device can be switched. In addition, it is possible to provide a rational refrigeration cycle apparatus that can adopt a low-cost apparatus having a relatively small allowable pressure difference as the switching apparatus itself.
 第8の発明は、第1~7の発明の第1熱交換器を室内熱交換器、第2熱交換器を室外熱交換器とした空気調和機である。除霜・暖房運転時から通常暖房運転に切り替える際に、暖房能力の低下を極力小さく抑えながら、切り替え装置の入口出口の圧力差を切り替え装置の許容圧力差より小さく抑え、確実に切り替え装置が切り替わるようにすることができる。また、切り替え装置自体も比較的、許容圧力差の小さい低コストなものを採用可能である合理的な空気調和機を提供することができる。 The eighth invention is an air conditioner in which the first heat exchanger of the first to seventh inventions is an indoor heat exchanger and the second heat exchanger is an outdoor heat exchanger. When switching from defrosting / heating operation to normal heating operation, the pressure difference at the inlet / outlet of the switching device is kept smaller than the allowable pressure difference of the switching device while suppressing the decline in heating capacity as much as possible. Can be. In addition, it is possible to provide a rational air conditioner in which the switching device itself can adopt a relatively low cost with a small allowable pressure difference.
 以下、本発明の冷凍サイクル装置の実施の形態について、空気調和機に搭載した例として図面を参照しながら説明する。なお、この実施の形態によって本発明が限定されるものではない。 Hereinafter, embodiments of the refrigeration cycle apparatus of the present invention will be described with reference to the drawings as examples mounted on an air conditioner. Note that the present invention is not limited to the embodiments.
(実施の形態1)
 図1は、本発明の実施の形態1に係る冷凍サイクル装置を備えた空気調和機の構成を示しており、空気調和機は、冷媒配管で互いに接続された室外機2と室内機4とで構成されている。
(Embodiment 1)
FIG. 1 shows a configuration of an air conditioner including a refrigeration cycle apparatus according to Embodiment 1 of the present invention. The air conditioner includes an outdoor unit 2 and an indoor unit 4 that are connected to each other through refrigerant piping. It is configured.
 図1に示すように、室外機2の内部には、圧縮機6と四方弁8とストレーナ10と膨張弁12と室外熱交換器(第2熱交換器)14とが設けられている。室内機4の内部には、室内熱交換器(第1熱交換器)16が設けられている。これらは冷媒配管を介して互いに接続されることで冷凍サイクルを構成している。 As shown in FIG. 1, a compressor 6, a four-way valve 8, a strainer 10, an expansion valve 12, and an outdoor heat exchanger (second heat exchanger) 14 are provided inside the outdoor unit 2. An indoor heat exchanger (first heat exchanger) 16 is provided inside the indoor unit 4. These are connected to each other via a refrigerant pipe to constitute a refrigeration cycle.
 さらに詳述すると、圧縮機6と室内熱交換器16は、四方弁8が設けられた配管18を介して接続され、室内熱交換器16と膨張弁12は、ストレーナ10が設けられた配管20を介して接続されている。膨張弁12と室外熱交換器14は、配管22を介して接続され、室外熱交換器14と圧縮機6は、配管24および配管25を介して接続されている。室外熱交換器14と圧縮機6を接続する配管24および配管25の間には、四方弁8が配置されている。また、四方弁8と圧縮機6の間には三方弁(切り替え装置)42が配管25を介して接続されている。更に三方弁42と圧縮機冷媒吸入側における配管25には、液相冷媒と気相冷媒を分離するためのアキュームレータ26が設けられている。また、室外熱交換器14と室内熱交換器16を結ぶ配管22には、配管28を介して圧縮機6と接続されており、配管28には電磁弁30が設けられている。これら配管28と電磁弁30とは、吐出ガスバイパス機構を構成している。 More specifically, the compressor 6 and the indoor heat exchanger 16 are connected via a pipe 18 provided with a four-way valve 8, and the indoor heat exchanger 16 and the expansion valve 12 are connected to a pipe 20 provided with a strainer 10. Connected through. The expansion valve 12 and the outdoor heat exchanger 14 are connected via a pipe 22, and the outdoor heat exchanger 14 and the compressor 6 are connected via a pipe 24 and a pipe 25. A four-way valve 8 is disposed between the pipe 24 and the pipe 25 connecting the outdoor heat exchanger 14 and the compressor 6. A three-way valve (switching device) 42 is connected between the four-way valve 8 and the compressor 6 via a pipe 25. Further, the three-way valve 42 and the pipe 25 on the compressor refrigerant suction side are provided with an accumulator 26 for separating the liquid-phase refrigerant and the gas-phase refrigerant. The piping 22 connecting the outdoor heat exchanger 14 and the indoor heat exchanger 16 is connected to the compressor 6 via the piping 28, and the piping 28 is provided with an electromagnetic valve 30. The pipe 28 and the electromagnetic valve 30 constitute a discharge gas bypass mechanism.
 さらに、圧縮機6の周囲には蓄熱槽32が設けられている。蓄熱槽32の内部には、蓄熱熱交換器34が設けられるとともに蓄熱熱交換器34と熱交換するための蓄熱材(例えば、エチレングリコール水溶液)36が充填されている。このように、蓄熱槽32と蓄熱熱交換器34と蓄熱材36とで補助熱交換器となる蓄熱装置を構成している。 Furthermore, a heat storage tank 32 is provided around the compressor 6. The heat storage tank 32 is provided with a heat storage heat exchanger 34 and filled with a heat storage material (for example, ethylene glycol aqueous solution) 36 for exchanging heat with the heat storage heat exchanger 34. Thus, the heat storage tank 32, the heat storage heat exchanger 34, and the heat storage material 36 constitute a heat storage device that serves as an auxiliary heat exchanger.
 また、三方弁42と蓄熱熱交換器34は、キャピラリチューブ(絞り機構)43を含む配管38を介して接続され、三方弁42と圧縮機6を接続する配管25は配管40を介して蓄熱熱交換器34と接続されている。 The three-way valve 42 and the heat storage heat exchanger 34 are connected via a pipe 38 including a capillary tube (throttle mechanism) 43, and the pipe 25 connecting the three-way valve 42 and the compressor 6 is connected to the heat storage heat via the pipe 40. It is connected to the exchanger 34.
 室内機4の内部には、室内熱交換器16に加えて、送風ファン(図示せず)と上下羽根(図示せず)と左右羽根(図示せず)とが設けられている。室内熱交換器16は、送風ファンにより室内機4の内部に吸込まれた室内空気と、室内熱交換器16の内部を流れる冷媒との熱交換を行い、暖房時には熱交換により暖められた空気を室内に吹き出す一方、冷房時には熱交換により冷却された空気を室内に吹き出す。上下羽根は、室内機4から吹き出される空気の方向を必要に応じて上下に変更する。左右羽根は、室内機4から吹き出される空気の方向を必要に応じて左右に変更する。 In addition to the indoor heat exchanger 16, a blower fan (not shown), upper and lower blades (not shown), and left and right blades (not shown) are provided inside the indoor unit 4. The indoor heat exchanger 16 exchanges heat between the indoor air sucked into the indoor unit 4 by the blower fan and the refrigerant flowing inside the indoor heat exchanger 16, and the air heated by the heat exchange during heating is used. While air is blown out, air cooled by heat exchange is blown out into the room during cooling. The upper and lower blades change the direction of the air blown from the indoor unit 4 up and down as necessary. The left and right blades change the direction of the air blown from the indoor unit 4 to the left and right as necessary.
 なお、圧縮機6、送風ファン、上下羽根、左右羽根、四方弁8、膨張弁12、電磁弁30、三方弁42等は制御装置(図示せず、例えばマイコン)に電気的に接続され、制御装置により制御され動作する。 The compressor 6, the blower fan, the upper and lower blades, the left and right blades, the four-way valve 8, the expansion valve 12, the electromagnetic valve 30, the three-way valve 42, and the like are electrically connected to a control device (not shown, for example, a microcomputer) for control. It is controlled and operated by the device.
 上記構成の本発明に係る冷凍サイクル装置において、各部品の相互の接続関係と機能について、暖房運転時を例にとり、冷媒の流れとともに説明する。 In the refrigeration cycle apparatus according to the present invention having the above-described configuration, the mutual connection relationship and function of each component will be described together with the flow of the refrigerant, taking the heating operation as an example.
 圧縮機6の吐出口から吐出された冷媒は、四方弁8から配管18を通って室内熱交換器16へと至る。室内熱交換器16で室内空気と熱交換して凝縮した冷媒は、室内熱交換器16を出て配管20を通り、膨張弁12への異物侵入を防止するストレーナ10を通って、膨張弁12に至る。膨張弁12で減圧した冷媒は、配管22を通って室外熱交換器14に至る。また、室外熱交換器14で室外空気と熱交換して蒸発した冷媒は、配管24と四方弁8と三方弁42と配管25とアキュームレータ26を通って圧縮機6の吸入口を介して圧縮機6へと戻る。 The refrigerant discharged from the discharge port of the compressor 6 reaches the indoor heat exchanger 16 through the pipe 18 from the four-way valve 8. Refrigerant condensed by exchanging heat with indoor air in the indoor heat exchanger 16 exits the indoor heat exchanger 16, passes through the piping 20, passes through the strainer 10 that prevents foreign matter from entering the expansion valve 12, and then expands the expansion valve 12. To. The refrigerant decompressed by the expansion valve 12 reaches the outdoor heat exchanger 14 through the pipe 22. The refrigerant evaporated by exchanging heat with the outdoor air in the outdoor heat exchanger 14 passes through the pipe 24, the four-way valve 8, the three-way valve 42, the pipe 25, and the accumulator 26 through the suction port of the compressor 6. Return to 6.
 また、配管18の圧縮機6の吐出口と四方弁8の間から分岐した配管28は、電磁弁30を介して配管22の膨張弁12と室外熱交換器14の間に合流している。 Further, the pipe 28 branched from the discharge port of the compressor 6 of the pipe 18 and the four-way valve 8 is joined between the expansion valve 12 of the pipe 22 and the outdoor heat exchanger 14 via the electromagnetic valve 30.
 さらに、内部に蓄熱材36と蓄熱熱交換器34を収納した蓄熱槽32は、圧縮機6に接して取り囲むように配置され、圧縮機6で発生した熱を蓄熱材36に蓄積する。 Furthermore, the heat storage tank 32 in which the heat storage material 36 and the heat storage heat exchanger 34 are housed is disposed so as to be in contact with and surrounded by the compressor 6, and the heat generated in the compressor 6 is accumulated in the heat storage material 36.
 三方弁42は、一方が四方弁8の吸入配管と接続され、もう一方が三方弁42と圧縮機6の吸入口を接続する配管25とに接続され、更にもう一方が三方弁42と蓄熱熱交換器34と接続する配管38と接続されている。前記制御装置により、四方弁8から配管25を通じ圧縮機6の吸入口へ冷媒を導く経路と、四方弁8から配管38を通じ蓄熱熱交換器34を経て圧縮機6の吸入口へ冷媒を導く経路とを切り替えることが可能である。 One side of the three-way valve 42 is connected to the suction pipe of the four-way valve 8, the other side is connected to the three-way valve 42 and the pipe 25 connecting the suction port of the compressor 6, and the other side is connected to the three-way valve 42 and heat storage heat. A pipe 38 connected to the exchanger 34 is connected. A path for guiding the refrigerant from the four-way valve 8 to the suction port of the compressor 6 through the pipe 25 and a path for guiding the refrigerant from the four-way valve 8 to the suction port of the compressor 6 through the heat storage heat exchanger 34 through the pipe 38 by the control device. And can be switched.
 次に、空気調和機の通常暖房時の動作及び冷媒の流れを模式的に示す図2を参照しながら通常暖房時の動作を説明する。 Next, the operation during normal heating will be described with reference to FIG. 2 schematically showing the operation during normal heating of the air conditioner and the flow of the refrigerant.
 通常暖房運転時、電磁弁30は閉制御されており、上述したように圧縮機6の吐出口から吐出された冷媒は、配管18を通って四方弁8から室内熱交換器16に至る。室内熱交換器16で室内空気と熱交換して凝縮した冷媒は、室内熱交換器16を出て、配管20を通り膨張弁12に至る。膨張弁12で減圧した冷媒は、配管22を通って室外熱交換器14に至る。室外熱交換器14で室外空気と熱交換して蒸発した冷媒は、配管24を通って四方弁8に至る。通常暖房運転時、三方弁42は、室外熱交換器14から圧縮機6の吸入口へ冷媒を導く経路、即ち配管24と配管25が連通するように制御されており、四方弁8を通った冷媒は三方弁42を通り、圧縮機6の吸入口へと戻る。 During the normal heating operation, the solenoid valve 30 is controlled to be closed, and the refrigerant discharged from the discharge port of the compressor 6 reaches the indoor heat exchanger 16 from the four-way valve 8 through the pipe 18 as described above. The refrigerant condensed by exchanging heat with the indoor air in the indoor heat exchanger 16 exits the indoor heat exchanger 16 and passes through the pipe 20 to the expansion valve 12. The refrigerant decompressed by the expansion valve 12 reaches the outdoor heat exchanger 14 through the pipe 22. The refrigerant evaporated by exchanging heat with the outdoor air in the outdoor heat exchanger 14 reaches the four-way valve 8 through the pipe 24. During normal heating operation, the three-way valve 42 is controlled so that the refrigerant leads from the outdoor heat exchanger 14 to the suction port of the compressor 6, that is, the pipe 24 and the pipe 25 communicate with each other. The refrigerant passes through the three-way valve 42 and returns to the suction port of the compressor 6.
 また、圧縮機6で発生した熱は、圧縮機6の外壁から蓄熱槽32の内壁を介して蓄熱槽32の内部に収容された蓄熱材36に蓄熱される。 Further, the heat generated in the compressor 6 is stored in the heat storage material 36 housed in the heat storage tank 32 from the outer wall of the compressor 6 through the inner wall of the heat storage tank 32.
 次に、空気調和機の除霜・暖房時の動作及び冷媒の流れを模式的に示す図3を参照しながら除霜・暖房時の動作を説明する。図中、実線矢印は暖房に供する冷媒の流れを示しており、破線矢印は除霜に供する冷媒の流れを示している。 Next, the operation during defrosting / heating will be described with reference to FIG. 3 schematically showing the operation of the air conditioner during defrosting / heating and the flow of refrigerant. In the figure, the solid line arrows indicate the flow of the refrigerant used for heating, and the broken line arrows indicate the flow of the refrigerant used for defrosting.
 上述した通常暖房運転中に室外熱交換器14に着霜し、着霜した霜が成長すると、室外熱交換器14の通風抵抗が増加して風量が減少し、室外熱交換器14内の蒸発温度が低下する。本発明に係る空気調和機には、図3に示されるように、室外熱交換器14の配管温度を検出する温度センサ51が設けられている。非着霜時に比べて、蒸発温度が低下したことを温度センサ51で検出すると、制御装置より通常暖房運転から除霜・暖房運転へ切り替える指示が出力される。 When the outdoor heat exchanger 14 is frosted during the above-described normal heating operation and the frosted frost grows, the ventilation resistance of the outdoor heat exchanger 14 increases and the air flow decreases, and the evaporation in the outdoor heat exchanger 14 increases. The temperature drops. As shown in FIG. 3, the air conditioner according to the present invention is provided with a temperature sensor 51 that detects the piping temperature of the outdoor heat exchanger 14. When the temperature sensor 51 detects that the evaporating temperature has decreased as compared to non-frosting, an instruction to switch from the normal heating operation to the defrosting / heating operation is output from the control device.
 通常暖房運転から除霜・暖房運転に移行すると、電磁弁30は開制御される。上述した通常暖房運転時の冷媒の流れに加え、圧縮機6の吐出口から出た気相冷媒の一部は、配管28と電磁弁30を通り、配管22を通る冷媒に合流して、室外熱交換器14を加熱し、凝縮して液相化した後、四方弁8へ至る。 When switching from the normal heating operation to the defrosting / heating operation, the solenoid valve 30 is controlled to open. In addition to the refrigerant flow during the normal heating operation described above, a part of the gas-phase refrigerant exiting from the discharge port of the compressor 6 passes through the pipe 28 and the electromagnetic valve 30 and merges with the refrigerant passing through the pipe 22 to be outdoors. The heat exchanger 14 is heated and condensed to form a liquid phase, and then the four-way valve 8 is reached.
 除霜・暖房運転時、三方弁42は、室外熱交換器14から蓄熱熱交換器34へ冷媒を導く経路、即ち配管24と配管38が連通するように制御される。四方弁8を通った冷媒は、キャピラリチューブ43で減圧され低温となり、蓄熱熱交換器34で蓄熱材36の熱を吸熱し、気相、もしくは高クオリティー状態で、アキュームレータ26に至り、圧縮機6の吸入口へと戻る。 During the defrosting / heating operation, the three-way valve 42 is controlled so that the path leading the refrigerant from the outdoor heat exchanger 14 to the heat storage heat exchanger 34, that is, the pipe 24 and the pipe 38 communicate with each other. The refrigerant that has passed through the four-way valve 8 is depressurized by the capillary tube 43 and becomes a low temperature, absorbs the heat of the heat storage material 36 by the heat storage heat exchanger 34, reaches the accumulator 26 in the gas phase or in a high quality state, and reaches the compressor 6. Return to the inlet.
 このような構成とすることで、蓄熱材36と熱交換を行う蓄熱熱交換器34を低温とすることができる。そして、蓄熱材36からの最大吸収熱量は、圧縮機6の温度と蓄熱熱交換器34の温度との温度差に比例するので、蓄熱熱交換器34の温度を低温にできれば、圧縮機6の温度と蓄熱熱交換器34の温度との温度差をより大きくでき、蓄熱材36からの最大吸収熱量を増加させることが可能となり、除霜時間を短縮し、暖房運転時における除霜運転による室温低下を抑制して快適性を向上させることができる。 With such a configuration, the heat storage heat exchanger 34 that exchanges heat with the heat storage material 36 can be cooled. Since the maximum amount of heat absorbed from the heat storage material 36 is proportional to the temperature difference between the temperature of the compressor 6 and the temperature of the heat storage heat exchanger 34, if the temperature of the heat storage heat exchanger 34 can be lowered, the compressor 6 The temperature difference between the temperature and the temperature of the heat storage heat exchanger 34 can be increased, the maximum amount of heat absorbed from the heat storage material 36 can be increased, the defrosting time can be shortened, and the room temperature by the defrosting operation during the heating operation can be increased. The comfort can be improved by suppressing the decrease.
 更に、蓄熱熱交換器34での液冷媒の蒸発が促進されることで、液冷媒が圧縮機6に戻ることがなくなり、圧縮機6の信頼性も向上させることができる。 Furthermore, since the evaporation of the liquid refrigerant in the heat storage heat exchanger 34 is promoted, the liquid refrigerant does not return to the compressor 6 and the reliability of the compressor 6 can be improved.
 また、特許文献1における従来技術の図6のように蓄熱熱交換器118を通る冷媒をバイパス経路とすると、蓄熱熱交換器118を通る冷媒の循環量が低下する。蓄熱材126の温度が高温である場合、蓄熱熱交換器118の後半部で過熱度が高くなることで熱交換量が低下し、除霜能力が十分に発揮できないことがある。しかし、本構成では蓄熱熱交換器34に1つの経路で冷媒を流す構成としているため、過熱度のとり過ぎによる熱交換量の低下を防ぐことができ、除霜能力が十分に発揮できる。 Further, when the refrigerant passing through the heat storage heat exchanger 118 is used as a bypass path as shown in FIG. 6 of the prior art in Patent Document 1, the circulation amount of the refrigerant passing through the heat storage heat exchanger 118 is reduced. When the temperature of the heat storage material 126 is high, the degree of superheat increases in the second half of the heat storage heat exchanger 118, so that the amount of heat exchange decreases, and the defrosting ability may not be sufficiently exhibited. However, in this structure, since it is set as the structure which flows a refrigerant | coolant to the thermal storage heat exchanger 34 by one path | route, the fall of the amount of heat exchange by taking too much superheat degree can be prevented, and defrosting capability can fully be exhibited.
 除霜・暖房開始時に霜の付着により氷点下となった室外熱交換器14の温度は、圧縮機6の吐出口から出た気相冷媒と室内熱交換器16より戻る液相もしくは気液2相冷媒が混合された冷媒によって加熱されて、零度付近で霜が融解し、霜の融解が終わると、再び上昇し始める。この室外熱交換器14の温度上昇を温度センサ51で検出すると、除霜が完了したと判断し、制御装置より除霜・暖房運転から通常暖房運転へ切り替える指示が出力される。 The temperature of the outdoor heat exchanger 14 that has become below freezing due to the attachment of frost at the start of defrosting / heating is the liquid phase or the gas-liquid two-phase returning from the gas-phase refrigerant that exits from the discharge port of the compressor 6 and the indoor heat exchanger 16. When the refrigerant is heated by the mixed refrigerant, the frost is melted at around zero degrees, and when the frost is completely melted, it starts rising again. When the temperature sensor 51 detects the temperature rise of the outdoor heat exchanger 14, it is determined that the defrosting is completed, and an instruction to switch from the defrosting / heating operation to the normal heating operation is output from the control device.
 また、圧縮機6から配管28を経て電磁弁30を通り、室外熱交換器14に至る吐出ガスバイパス経路は、必ずしも必要ではなく、極めて大きな除霜能力が必要な場合を除いては無くす構成としても良い。 In addition, the discharge gas bypass path from the compressor 6 through the piping 28 through the solenoid valve 30 to the outdoor heat exchanger 14 is not necessarily required, and is configured to be eliminated unless a very large defrosting capacity is required. Also good.
 この場合、圧縮機6の吐出口から、配管18、室内熱交換器16、配管20、配管22を経て、室外熱交換器14へと気相冷媒が流れ、室外熱交換器14を除霜する構成となり、除霜能力は少し低下するが、低コストでコンパクトな構成が可能となる。 In this case, the gas phase refrigerant flows from the discharge port of the compressor 6 through the pipe 18, the indoor heat exchanger 16, the pipe 20, and the pipe 22 to the outdoor heat exchanger 14, thereby defrosting the outdoor heat exchanger 14. Although it becomes a structure and a defrosting capability falls a little, a low cost and compact structure is attained.
 また、本構成では、三方弁42から蓄熱熱交換器34に至る配管38にキャピラリチューブ43を設けた構成としているが、本構成の代わりに蓄熱熱交換器34に連通する三方弁42の開口部を絞った仕様としてもよい。この場合、キャピラリチューブ43を除くことが可能となり、低コストでコンパクトな構成が可能となる。 In this configuration, the capillary tube 43 is provided in the pipe 38 extending from the three-way valve 42 to the heat storage heat exchanger 34. However, instead of this configuration, the opening of the three-way valve 42 communicating with the heat storage heat exchanger 34 is provided. It is good also as the specification which narrowed down. In this case, the capillary tube 43 can be removed, and a compact configuration can be achieved at low cost.
(実施の形態2)   
<本発明に係る一形態を得るに至った経緯>
 図1に示す実施の形態1の空気調和機は、上記図7に示す従来の空気調和機の改良版として提案されており、図1は除霜方式を改良した冷凍サイクル装置の一例を示している。
(Embodiment 2)
<Background of obtaining one embodiment of the present invention>
The air conditioner of Embodiment 1 shown in FIG. 1 has been proposed as an improved version of the conventional air conditioner shown in FIG. 7, and FIG. 1 shows an example of a refrigeration cycle apparatus with an improved defrosting system. Yes.
 本発明の実施の形態1の空気調和機は、四方弁8と圧縮機6の間に切替え装置となる三方弁42が配管25を介して接続されており、更に三方弁42と圧縮機冷媒吸入側における配管25には、液相冷媒と気相冷媒を分離するためのアキュームレータ26が設けられている。また、三方弁42と蓄熱熱交換器34は、絞り機構となるキャピラリチューブ43を含む配管38を介して接続され、蓄熱熱交換器34と三方弁42と圧縮機6を接続する配管25は、配管40を介して接続されている。 In the air conditioner of Embodiment 1 of the present invention, a three-way valve 42 serving as a switching device is connected between the four-way valve 8 and the compressor 6 via a pipe 25, and further, the three-way valve 42 and the compressor refrigerant suction. The pipe 25 on the side is provided with an accumulator 26 for separating the liquid phase refrigerant and the gas phase refrigerant. The three-way valve 42 and the heat storage heat exchanger 34 are connected via a pipe 38 including a capillary tube 43 serving as a throttle mechanism, and the pipe 25 connecting the heat storage heat exchanger 34, the three-way valve 42 and the compressor 6 is It is connected via a pipe 40.
 三方弁42は、一方が四方弁8の吸入配管と接続され、もう一方が三方弁42と圧縮機6の吸入口を接続する配管25とに接続され、更にもう一方が三方弁42と蓄熱熱交換器34と接続する配管38と接続されており、四方弁8から配管25を通じ圧縮機6の吸入口へ冷媒を導く経路と、四方弁8から配管38を通じ蓄熱熱交換器34を経て圧縮機6の吸入口へ冷媒を導く経路とを切り替えることが可能である。 One side of the three-way valve 42 is connected to the suction pipe of the four-way valve 8, the other side is connected to the three-way valve 42 and the pipe 25 connecting the suction port of the compressor 6, and the other side is connected to the three-way valve 42 and heat storage heat. Connected to a pipe 38 connected to the exchanger 34, a path for introducing the refrigerant from the four-way valve 8 through the pipe 25 to the suction port of the compressor 6, and a compressor through the heat storage heat exchanger 34 through the pipe 38 from the four-way valve 8. It is possible to switch the path for guiding the refrigerant to the six suction ports.
 通常暖房運転時、圧縮機6の吐出口から吐出された冷媒は、配管18を通って四方弁8から室内熱交換器16に至る。室内熱交換器16で室内空気と熱交換して凝縮した冷媒は、室内熱交換器16を出て、配管20を通って膨張弁12に至り、膨張弁12で減圧した冷媒は、配管22を通って室外熱交換器14に至る。室外熱交換器14で室外空気と熱交換して蒸発した冷媒は、配管24を通って四方弁8に至る。三方弁42は、室外熱交換器14から圧縮機6の吸入口へ冷媒を導く経路、即ち配管24と配管25が連通するように制御されており、四方弁8を通った冷媒は三方弁42を通り、圧縮機6の吸入口へと戻る。 During normal heating operation, the refrigerant discharged from the discharge port of the compressor 6 passes through the pipe 18 and reaches the indoor heat exchanger 16 from the four-way valve 8. The refrigerant condensed by exchanging heat with the indoor air in the indoor heat exchanger 16 exits the indoor heat exchanger 16, reaches the expansion valve 12 through the pipe 20, and the refrigerant decompressed by the expansion valve 12 passes through the pipe 22. It passes through to the outdoor heat exchanger 14. The refrigerant evaporated by exchanging heat with the outdoor air in the outdoor heat exchanger 14 reaches the four-way valve 8 through the pipe 24. The three-way valve 42 is controlled so that the passage of the refrigerant from the outdoor heat exchanger 14 to the suction port of the compressor 6, that is, the pipe 24 and the pipe 25 communicate with each other, and the refrigerant passing through the four-way valve 8 is the three-way valve 42. And return to the suction port of the compressor 6.
 また、圧縮機6で発生した熱は、圧縮機6の外壁から蓄熱槽32の外壁を介して蓄熱槽32の内部に収容された蓄熱材36に蓄積される。 Further, the heat generated in the compressor 6 is accumulated in the heat storage material 36 housed in the heat storage tank 32 from the outer wall of the compressor 6 through the outer wall of the heat storage tank 32.
 上述した通常暖房運転中に室外熱交換器14に着霜し、着霜した霜が成長すると、室外熱交換器14の通風抵抗が増加して風量が減少し、室外熱交換器14内の蒸発温度が低下する。室外熱交換器14の配管温度を検出する温度センサ(図示せず)が設けられており、非着霜時に比べて、蒸発温度が低下したことを温度センサで検出すると、制御装置より通常暖房運転から除霜・暖房運転への指示が出力される。 When the outdoor heat exchanger 14 is frosted during the above-described normal heating operation and the frosted frost grows, the ventilation resistance of the outdoor heat exchanger 14 increases and the air flow decreases, and the evaporation in the outdoor heat exchanger 14 increases. The temperature drops. A temperature sensor (not shown) for detecting the piping temperature of the outdoor heat exchanger 14 is provided. When the temperature sensor detects that the evaporating temperature has decreased as compared with the time of non-frosting, the control device performs normal heating operation. Outputs an instruction for defrosting / heating operation.
 除霜・暖房運転時、三方弁42は、室外熱交換器14から蓄熱熱交換器34へ冷媒を導く経路、即ち配管24と配管38が連通するように制御され、四方弁8を通った冷媒はキャピラリチューブ43で減圧され低温となり、蓄熱熱交換器34で蓄熱材36の熱を吸熱し、気相、もしくは高乾き度状態で、アキュームレータ26に至り、圧縮機6の吸入口へと戻る。 During the defrosting / heating operation, the three-way valve 42 is controlled so that the refrigerant leads from the outdoor heat exchanger 14 to the heat storage heat exchanger 34, that is, the pipe 24 and the pipe 38 communicate with each other. The pressure is reduced by the capillary tube 43 to a low temperature, the heat storage heat exchanger 34 absorbs the heat of the heat storage material 36, reaches the accumulator 26 in the gas phase or in a high dryness state, and returns to the suction port of the compressor 6.
 除霜・暖房開始時に霜の付着により氷点下となった室外熱交換器14の温度は、圧縮機6の吐出口から出た気相冷媒と室内熱交換器16より戻る液相もしくは気液2相冷媒が混合された冷媒によって加熱されて、零度付近で霜が融解し、霜の融解が終わると、室外熱交換器14の温度は再び上昇し始める。この室外熱交換器14の温度上昇を温度センサで検出すると、除霜が完了したと判断し、制御装置から除霜・暖房運転から通常暖房運転への指示が出力されるように構成されている。 The temperature of the outdoor heat exchanger 14 that has become below freezing due to the attachment of frost at the start of defrosting / heating is the liquid phase or the gas-liquid two-phase returning from the gas-phase refrigerant that exits from the discharge port of the compressor 6 and the indoor heat exchanger 16. When the refrigerant is heated by the mixed refrigerant and frost is melted at around zero degrees, and the frost is completely melted, the temperature of the outdoor heat exchanger 14 begins to rise again. When the temperature increase of the outdoor heat exchanger 14 is detected by the temperature sensor, it is determined that the defrosting is completed, and an instruction from the defrosting / heating operation to the normal heating operation is output from the control device. .
 この三方弁42を用いたものは、除霜運転時には、室内熱交換器16と室外熱交換器14を流れた冷媒が四方弁8を介して蓄熱熱交換器34を流れ、圧縮機6の吸入管へ導かれる構成として、室内熱交換器16を高温に、蓄熱熱交換器34を低温に維持した運転を行い、熱源からの吸熱を速やかに行うことで、除霜時間を短縮し、暖房運転時における除霜運転の室温低下を抑制して快適性を向上させることができる。 In the case of using the three-way valve 42, during the defrosting operation, the refrigerant that has flowed through the indoor heat exchanger 16 and the outdoor heat exchanger 14 flows through the heat storage heat exchanger 34 via the four-way valve 8, and is sucked into the compressor 6. As the structure led to the pipe, the indoor heat exchanger 16 is operated at a high temperature and the heat storage heat exchanger 34 is maintained at a low temperature, and the heat absorption from the heat source is quickly performed, thereby reducing the defrosting time and heating operation. It is possible to improve comfort by suppressing a decrease in room temperature during defrosting operation.
 上述した本発明の実施の形態1の構成では、除霜・暖房運転時に三方弁42の入口から圧縮機6の吸入口に冷媒が流れる状態のとき、三方弁42の入口出口の圧力差が大きくなり、三方弁42の許容圧力差よりも大きくなって、通常暖房運転への切り替えができない場合があり、それを回避するために許容圧力差の大きな三方弁を採用しようとすると、コスト高になるという課題があった。 In the configuration of the first embodiment of the present invention described above, when refrigerant flows from the inlet of the three-way valve 42 to the inlet of the compressor 6 during the defrosting / heating operation, the pressure difference between the inlet and outlet of the three-way valve 42 is large. Therefore, there is a case where it is larger than the allowable pressure difference of the three-way valve 42 and cannot be switched to the normal heating operation. In order to avoid this, it is expensive to use a three-way valve having a large allowable pressure difference. There was a problem.
 そこで、本発明者らは、上記の課題を解決するため、除霜・暖房運転時から通常暖房運転に切り替える際に、暖房能力の低下を極力小さく抑えながら、三方弁の入口出口の圧力差を三方弁の許容圧力差より小さく抑え、確実に三方弁が切り替わるようにしながら、三方弁自体も比較的、許容圧力差の小さい低コストなものを採用可能な冷凍サイクル装置の構成を見出し、実施の形態2に係る冷凍サイクル装置を備えた空気調和機に至った。 Therefore, in order to solve the above-mentioned problems, the present inventors set the pressure difference at the inlet / outlet of the three-way valve while suppressing the decrease in the heating capacity as much as possible when switching from the defrosting / heating operation to the normal heating operation. Finding the configuration of a refrigeration cycle system that can be used with a low-cost one with a relatively small allowable pressure difference, while keeping the three-way valve to be surely switched while keeping it smaller than the allowable pressure difference of the three-way valve. It came to the air conditioner provided with the refrigerating cycle device concerning form 2.
 図4は、本発明の実施の形態2に係る冷凍サイクル装置を備えた空気調和機の構成を示す冷凍サイクル構成図であり、図1に示す本発明の実施の形態1と同じ構成要素には同一番号を付し、詳細な説明は省略する。 FIG. 4 is a refrigeration cycle configuration diagram showing the configuration of the air conditioner including the refrigeration cycle apparatus according to Embodiment 2 of the present invention, and the same components as in Embodiment 1 of the present invention shown in FIG. The same number is attached and detailed explanation is omitted.
 図4において、この空気調和機では、実施の形態1の構成に加えて、その運転を制御する冷凍サイクル制御装置50を更に備えている。冷凍サイクル制御装置50は、温度センサ51と電気的に接続され室外熱交換器(第1熱交換器)14の温度を検知する。また、冷凍サイクル制御装置50は、圧縮機6、膨張弁12、切替え装置となる三方弁42とも電気的に接続され、圧縮機6の運転速度、膨張弁12の絞り量、三方弁42の冷媒経路切り替えを決定し駆動制御する。 4, in addition to the configuration of the first embodiment, the air conditioner further includes a refrigeration cycle control device 50 that controls the operation thereof. The refrigeration cycle control device 50 is electrically connected to the temperature sensor 51 and detects the temperature of the outdoor heat exchanger (first heat exchanger) 14. The refrigeration cycle control device 50 is also electrically connected to the compressor 6, the expansion valve 12, and the three-way valve 42 serving as a switching device, so that the operating speed of the compressor 6, the throttle amount of the expansion valve 12, and the refrigerant of the three-way valve 42. Determine path switching and drive control.
 通常暖房運転時、電磁弁30は閉制御されており、圧縮機6の吐出口から吐出された冷媒は、配管18を通って四方弁8から室内熱交換器16に至る。室内熱交換器16で室内空気と熱交換して凝縮した冷媒は、室内熱交換器16を出て、配管20を通り膨張弁12に至る。また、膨張弁12で減圧した冷媒は、配管22を通って室外熱交換器14に至る。室外熱交換器14で室外空気と熱交換して蒸発した冷媒は、配管24を通って四方弁8に至る。三方弁42は、室外熱交換器14から圧縮機6の吸入口へ冷媒を導く経路、即ち配管24と配管25が連通するように制御されており、四方弁8を通った冷媒は三方弁42を通り、圧縮機6の吸入口へと戻る。 During normal heating operation, the solenoid valve 30 is controlled to be closed, and the refrigerant discharged from the discharge port of the compressor 6 passes through the pipe 18 and reaches the indoor heat exchanger 16 from the four-way valve 8. The refrigerant condensed by exchanging heat with the indoor air in the indoor heat exchanger 16 exits the indoor heat exchanger 16 and passes through the pipe 20 to the expansion valve 12. In addition, the refrigerant decompressed by the expansion valve 12 passes through the pipe 22 and reaches the outdoor heat exchanger 14. The refrigerant evaporated by exchanging heat with the outdoor air in the outdoor heat exchanger 14 reaches the four-way valve 8 through the pipe 24. The three-way valve 42 is controlled so that the passage of the refrigerant from the outdoor heat exchanger 14 to the suction port of the compressor 6, that is, the pipe 24 and the pipe 25 communicate with each other, and the refrigerant passing through the four-way valve 8 is the three-way valve 42. And return to the suction port of the compressor 6.
 また、圧縮機6で発生した熱は、圧縮機6の外壁から補助熱交換器を構成する蓄熱槽32の外壁を介して蓄熱槽32の内部に収容された蓄熱材36に蓄積される。 Further, the heat generated in the compressor 6 is accumulated in the heat storage material 36 accommodated in the heat storage tank 32 from the outer wall of the compressor 6 through the outer wall of the heat storage tank 32 constituting the auxiliary heat exchanger.
 上述した通常暖房運転中に室外熱交換器14に着霜し、着霜した霜が成長すると、室外熱交換器14の通風抵抗が増加して風量が減少し、室外熱交換器14内の蒸発温度が低下する。非着霜時に比べて、蒸発温度が低下したことを温度センサ51で検出すると、冷凍サイクル制御装置50は、通常暖房運転から除霜・暖房運転への切り替え指示を出力する。 When the outdoor heat exchanger 14 is frosted during the above-described normal heating operation and the frosted frost grows, the ventilation resistance of the outdoor heat exchanger 14 increases and the air flow decreases, and the evaporation in the outdoor heat exchanger 14 increases. The temperature drops. When the temperature sensor 51 detects that the evaporation temperature has decreased as compared with the time of non-frosting, the refrigeration cycle control device 50 outputs a switching instruction from the normal heating operation to the defrosting / heating operation.
 通常暖房運転から除霜・暖房運転に移行すると、電磁弁30は開制御される。上述した通常暖房運転時の冷媒の流れに加え、圧縮機6の吐出口から出た気相冷媒の一部は、吐出ガスバイパス機構となる配管28と電磁弁30を通り、配管22を通る冷媒に合流して、室外熱交換器14を加熱し、凝縮して液相化した後、四方弁8へ至る。 When switching from the normal heating operation to the defrosting / heating operation, the solenoid valve 30 is controlled to open. In addition to the refrigerant flow during the normal heating operation described above, a part of the gas-phase refrigerant exiting from the discharge port of the compressor 6 passes through the pipe 28 and the electromagnetic valve 30 serving as a discharge gas bypass mechanism, and passes through the pipe 22. , The outdoor heat exchanger 14 is heated, condensed and converted into a liquid phase, and then the four-way valve 8 is reached.
 除霜・暖房運転時、三方弁42は、室外熱交換器14から蓄熱熱交換器34へ冷媒を導く経路、即ち配管24と配管38が連通するように制御される。四方弁8を通った冷媒は、絞り機構となるキャピラリチューブ43で減圧され低温となり、蓄熱熱交換器34で蓄熱材36の熱を吸熱し、気相、もしくは高乾き度状態で、アキュームレータ26に至り、圧縮機6の吸入口へと戻る。 During the defrosting / heating operation, the three-way valve 42 is controlled so that the path leading the refrigerant from the outdoor heat exchanger 14 to the heat storage heat exchanger 34, that is, the pipe 24 and the pipe 38 communicate with each other. The refrigerant that has passed through the four-way valve 8 is depressurized by the capillary tube 43 serving as a throttling mechanism and becomes a low temperature, absorbs the heat of the heat storage material 36 by the heat storage heat exchanger 34, and enters the accumulator 26 in the gas phase or high dryness state. Finally, it returns to the suction port of the compressor 6.
 除霜・暖房開始時に霜の付着により氷点下となった室外熱交換器14の温度は、圧縮機6の吐出口から出た気相冷媒と室内熱交換器16より戻る液相もしくは気液2相冷媒が混合された冷媒によって加熱されて、零度付近で霜が融解し、霜の融解が終わると、再び上昇し始める。この室外熱交換器14の温度上昇を温度センサ51で検出すると、除霜が完了したと判断し、冷凍サイクル制御装置50は、除霜・暖房運転から通常暖房運転への切り替え指示を出力する。 The temperature of the outdoor heat exchanger 14 that has become below freezing due to the attachment of frost at the start of defrosting / heating is the liquid phase or the gas-liquid two-phase returning from the gas-phase refrigerant that exits from the discharge port of the compressor 6 and the indoor heat exchanger 16. When the refrigerant is heated by the mixed refrigerant, the frost is melted at around zero degrees, and when the frost is completely melted, it starts rising again. When the temperature sensor 51 detects the temperature rise of the outdoor heat exchanger 14, it is determined that the defrosting has been completed, and the refrigeration cycle control device 50 outputs a switching instruction from the defrosting / heating operation to the normal heating operation.
 図5(a)~(f)は、本発明の実施の形態2に係る制御タイムチャートを示しており、特に上述した除霜が完了したと判断される時点から、通常暖房へ移行するタイミングにおける圧縮機回転数、膨張弁開度、三方弁経路状態、冷媒圧力(高低圧)、暖房能力の変化を時間経過とともに示している。なお、図5において、(a)は除霜判定、(b)は圧縮機回転数、(c)は膨張弁開度、(d)は三方弁経路状態、(e)は冷媒圧力(高低圧)、(f)は暖房能力の変化を示す。 FIGS. 5 (a) to 5 (f) show control time charts according to Embodiment 2 of the present invention, particularly at the timing of shifting to normal heating from the time when it is determined that the above-described defrosting is completed. Changes in compressor speed, expansion valve opening, three-way valve path state, refrigerant pressure (high and low pressure), and heating capacity are shown with time. In FIG. 5, (a) is defrosting determination, (b) is the compressor rotation speed, (c) is the expansion valve opening degree, (d) is the three-way valve path state, and (e) is the refrigerant pressure (high and low pressure). ) And (f) show changes in heating capacity.
 まず、除霜・暖房運転から通常暖房へ切り替える際に膨張弁12の膨張弁開度を絞らない場合の制御タイムチャートについて説明する。
 図5(a)に示すように、時間T1のタイミングで除霜が完了し、通常暖房運転に移行すると判定される。ここで、時間T1とは、室外熱交換器14の温度が所定の温度以上になったときを示す。所定の温度とは、室外熱交換器14に付着した霜が融解して、室外熱交換器14内の温度が上昇し始める温度をいう。また、室外熱交換器14の温度は、温度センサ51で検出される。時間T1になると、図5(b)に示すように、冷凍サイクル制御装置50は、圧縮機6の回転数を下げるように指示を出し、除霜・暖房運転終了時の設定値である回転数F1から徐々に低下させ、時間T2までに回転数F2に至るように制御する。ここで、時間T2とは、時間T1から予め定められた所定時間経過した後の時点を示す。冷凍サイクル制御装置50は、図5(d)に示すように、時間T2のタイミングで三方弁42を除霜側から暖房側へ切り替えるように指示を出す。具体的には、三方弁42を四方弁8から蓄熱熱交換器34を通じて圧縮機6の吸入管へ冷媒を流す経路から四方弁8から圧縮機6の吸入管へ直接冷媒を流す経路に切り替える。上記のように制御すると、図5(e)に示すように、圧縮機6の回転数が低くなり、冷媒圧力の高圧側の圧力が下がって、低圧側の圧力が上がる状態になる。このとき、時間T2における冷媒圧力の高圧側と低圧側の高低圧差ΔPは、時間T1における高低圧差よりも小さくなっている。即ち、時間T2において三方弁42の入口出口圧力が三方弁42の許容圧力差よりも小さくできるため、確実に三方弁42を切り替えることができる。しかし、図5(f)に示すように、冷媒圧力の高圧側の圧力が下がることによって室内熱交換器16の温度が低下して暖房能力が下がるという問題がある(図中、破線で示す)。
First, a control time chart when the expansion valve opening degree of the expansion valve 12 is not throttled when switching from the defrosting / heating operation to the normal heating will be described.
As shown to Fig.5 (a), it determines with defrosting having been completed at the timing of time T1 and transfering to normal heating operation. Here, the time T1 indicates a time when the temperature of the outdoor heat exchanger 14 is equal to or higher than a predetermined temperature. The predetermined temperature is a temperature at which the frost attached to the outdoor heat exchanger 14 is melted and the temperature in the outdoor heat exchanger 14 starts to rise. Further, the temperature of the outdoor heat exchanger 14 is detected by the temperature sensor 51. At time T1, as shown in FIG. 5 (b), the refrigeration cycle control device 50 issues an instruction to reduce the rotational speed of the compressor 6, and the rotational speed that is the set value at the end of the defrosting / heating operation. Control is performed so as to gradually decrease from F1 and reach the rotational speed F2 by time T2. Here, the time T2 indicates a time point after a predetermined time has elapsed from the time T1. As shown in FIG. 5D, the refrigeration cycle control device 50 issues an instruction to switch the three-way valve 42 from the defrosting side to the heating side at the time T2. Specifically, the three-way valve 42 is switched from a path through which refrigerant flows from the four-way valve 8 through the heat storage heat exchanger 34 to the suction pipe of the compressor 6 to a path through which refrigerant flows directly from the four-way valve 8 to the suction pipe of the compressor 6. When the control is performed as described above, as shown in FIG. 5E, the rotation speed of the compressor 6 is lowered, the pressure on the high pressure side of the refrigerant pressure is lowered, and the pressure on the low pressure side is raised. At this time, the high-low pressure difference ΔP between the high-pressure side and the low-pressure side of the refrigerant pressure at time T2 is smaller than the high-low pressure difference at time T1. That is, since the inlet / outlet pressure of the three-way valve 42 can be smaller than the allowable pressure difference of the three-way valve 42 at time T2, the three-way valve 42 can be switched reliably. However, as shown in FIG. 5 (f), there is a problem that the temperature of the indoor heat exchanger 16 is lowered and the heating capacity is lowered due to a decrease in the pressure on the high pressure side of the refrigerant pressure (indicated by a broken line in the figure). .
 本発明の実施の形態2においては、膨張弁12の膨張弁開度を絞る制御をすることによって、上記問題を解決する。除霜・暖房運転から通常暖房へ切り替える際に膨張弁12の膨張弁開度を絞る場合の制御タイムチャートについて説明する。 In the second embodiment of the present invention, the above problem is solved by controlling the expansion valve opening of the expansion valve 12 to be reduced. A control time chart when the expansion valve opening degree of the expansion valve 12 is throttled when switching from the defrosting / heating operation to the normal heating will be described.
 本発明の実施の形態2においては、図5(a)に示すように、時間T1のタイミングで除霜が完了し、通常暖房運転に移行すると判定される。図5(b)に示すように、冷凍サイクル制御装置50が圧縮機6の回転数F1から低下するように指示を出す。それと同時に、冷凍サイクル制御装置50は、膨張弁12の膨張弁開度を絞り気味にするように指示を出す。特に、図5(c)に示すように、膨張弁12は除霜・暖房運転終了時の設定値である膨張弁開度P1から徐々に絞られ、時間T2までに室内熱交換器16で過冷却した液冷媒を室内熱交換器16の管内に保持できる程度の膨張弁開度P2まで絞るように指示を出す。その結果、図5(e)及び図5(f)に示すように、膨張弁12の膨張弁開度が絞られるにつれ冷媒圧力の高圧側の圧力低下が軽減し、それに伴って暖房能力の低下が軽減する(図中、実線で示す)。また、時間T2における冷媒圧力の高圧側と低圧側の高低圧差ΔPは、時間T1における高低圧差よりも小さくなっている。図5(d)に示すように、冷凍サイクル制御装置50は、時間T2のタイミングで三方弁42を除霜側から暖房側へ切り替えるように指示を出す。即ち、三方弁42を四方弁8から蓄熱熱交換器34を通じて圧縮機6の吸入管へ冷媒を流す経路から四方弁8から圧縮機6の吸入管へ直接冷媒を流す経路に切り替える。なお、本発明の実施の形態2では、膨張弁12の膨張弁開度を絞らない場合に比べ、冷媒圧力の高圧側と低圧側の高低圧差ΔPは大きくなるが、三方弁42の切り替えは、高低圧差ΔPが三方弁42の許容圧力差よりも小さければ問題なく行うことができる。 In Embodiment 2 of the present invention, as shown in FIG. 5 (a), it is determined that the defrosting is completed at the timing of time T1 and the routine is shifted to the normal heating operation. As shown in FIG. 5B, the refrigeration cycle control device 50 issues an instruction so as to decrease from the rotational speed F <b> 1 of the compressor 6. At the same time, the refrigeration cycle control device 50 issues an instruction to make the expansion valve opening degree of the expansion valve 12 narrow. In particular, as shown in FIG. 5 (c), the expansion valve 12 is gradually throttled from the expansion valve opening P1 that is a set value at the end of the defrosting / heating operation, and is excessively passed by the indoor heat exchanger 16 by time T2. An instruction is given to throttle the cooled liquid refrigerant to an expansion valve opening P2 that can hold the cooled liquid refrigerant in the pipe of the indoor heat exchanger 16. As a result, as shown in FIG. 5 (e) and FIG. 5 (f), as the expansion valve opening degree of the expansion valve 12 is reduced, the pressure drop on the high pressure side of the refrigerant pressure is reduced, and the heating capacity is reduced accordingly. Is reduced (indicated by the solid line in the figure). Further, the high / low pressure difference ΔP between the high pressure side and the low pressure side of the refrigerant pressure at time T2 is smaller than the high / low pressure difference at time T1. As shown in FIG. 5 (d), the refrigeration cycle control device 50 issues an instruction to switch the three-way valve 42 from the defrosting side to the heating side at the timing of time T2. That is, the three-way valve 42 is switched from a path through which refrigerant flows from the four-way valve 8 through the heat storage heat exchanger 34 to the suction pipe of the compressor 6 to a path through which refrigerant flows directly from the four-way valve 8 to the suction pipe of the compressor 6. In Embodiment 2 of the present invention, the high / low pressure difference ΔP between the high pressure side and the low pressure side of the refrigerant pressure is larger than when the expansion valve opening degree of the expansion valve 12 is not throttled, but the switching of the three-way valve 42 is If the high / low pressure difference ΔP is smaller than the allowable pressure difference of the three-way valve 42, the operation can be performed without any problem.
 時間T2以後では、通常暖房運転として動作させるために、圧縮機6の回転数及び膨張弁12の膨張弁開度は、図5(b)及び図5(c)に示すように、時間T3で通常暖房起動時の初期設定値になるように制御される。ここで、時間T3とは圧縮機6の回転数及び膨張弁12の膨張弁開度が通常暖房起動時の初期設定値になった時点を示す。また、時間T3以後は、圧縮機6の回転数及び膨張弁12の膨張弁開度が通常暖房起動時の初期設定値で一定となるように制御されるが、所定時間経過後に能力制御に応じて設定値を変化させてもよい。 After the time T2, in order to operate as a normal heating operation, the rotation speed of the compressor 6 and the expansion valve opening of the expansion valve 12 are as shown in FIGS. 5 (b) and 5 (c) at time T3. Usually, control is performed so as to be an initial set value when heating is started. Here, the time T3 indicates a point in time when the rotation speed of the compressor 6 and the expansion valve opening of the expansion valve 12 become the initial set values at the time of normal heating activation. Further, after the time T3, the rotation speed of the compressor 6 and the expansion valve opening of the expansion valve 12 are controlled so as to be constant at the initial set values at the time of normal heating activation, but depending on the capacity control after a predetermined time has elapsed. The set value may be changed.
 また、図5(e)及び図5(f)に示すように、冷媒圧力(高低圧)及び暖房能力において、時間T1に比べて時間T3の方が冷媒圧力の高圧側が高く、暖房能力が上がっている。これは、時間T2以後はよりすばやく暖房能力を上げるために、圧縮機6の回転数を上げ、膨張弁12の絞りを調整して冷媒圧力の高低圧差を増大するように制御しているからである。一方、時間T1以前は、除霜サイクルの中であるため、放熱側(高温高圧のガスで霜を融解する部分)が霜によって冷やされるので、冷媒圧力の高圧側は低下し、暖房能力も下がっている。 Further, as shown in FIGS. 5E and 5F, in the refrigerant pressure (high and low pressure) and the heating capacity, the time T3 is higher on the high pressure side of the refrigerant pressure than the time T1, and the heating capacity is increased. ing. This is because after the time T2, in order to increase the heating capacity more quickly, the number of rotations of the compressor 6 is increased and the throttle of the expansion valve 12 is adjusted to increase the difference between the high and low pressures of the refrigerant pressure. is there. On the other hand, before the time T1, since it is in the defrost cycle, the heat release side (the part that melts the frost with the high-temperature and high-pressure gas) is cooled by frost, so the high-pressure side of the refrigerant pressure decreases and the heating capacity also decreases. ing.
 以上のように動作させることで、除霜・暖房運転から通常暖房運転に切り替える際に、暖房能力の低下を極力小さく抑えながら、三方弁42の入口出口の圧力差を三方弁42の許容圧力差より小さく抑え、確実に三方弁42が切り替わるようにしながら、三方弁自体も比較的、許容圧力差の小さい低コストなものを採用可能とすることができる。 By operating as described above, when switching from the defrosting / heating operation to the normal heating operation, the pressure difference at the inlet / outlet of the three-way valve 42 is set to the allowable pressure difference of the three-way valve 42 while suppressing a decrease in the heating capacity as much as possible. The three-way valve itself can be used at a lower cost with a relatively small allowable pressure difference while keeping the three-way valve 42 to be switched reliably.
 なお、上述した圧縮機6から配管28を経て電磁弁30を通り、室外熱交換器(第1熱交換器)に至る吐出ガスバイパス経路は、必ずしも必要ではなく、極めて大きな除霜能力が必要な場合を除いては無くす構成としても良い。 The discharge gas bypass path from the compressor 6 through the piping 28 through the electromagnetic valve 30 to the outdoor heat exchanger (first heat exchanger) is not necessarily required, and a very large defrosting capacity is required. It is good also as a structure which eliminates except the case.
 また、この実施の形態2では補助熱交換器として圧縮機6を囲むように設けた蓄熱熱交換器34を例にして説明したが、これに限られることなく他の構成によるものであってもよいものである。 In the second embodiment, the heat storage heat exchanger 34 provided so as to surround the compressor 6 as an auxiliary heat exchanger has been described as an example. However, the present invention is not limited to this, and other configurations may be used. It ’s good.
 また、上記実施の形態2では空気調和機に適用した冷凍サイクルで説明したが、ヒートポンプ式給湯機等の他の装置であっても同様の効果が得られるものである。 In the second embodiment, the refrigeration cycle applied to the air conditioner has been described. However, the same effect can be obtained even with other devices such as a heat pump type hot water heater.
 本発明に係る冷凍サイクル装置は、熱源からの吸熱能力を向上させ、除霜能力を向上させるだけでなく、圧縮機への液冷媒の戻りを極力低減し、圧縮機の信頼性を向上させることができる。また、除霜中の暖房能力の低下を極力低減しながら、低コストな冷媒経路の切替え装置を採用できるので、空気調和機、冷蔵庫、ヒートポンプ式給湯器等に有用である。 The refrigeration cycle apparatus according to the present invention not only improves the heat absorption capability from the heat source and improves the defrosting capability, but also reduces the return of the liquid refrigerant to the compressor as much as possible and improves the reliability of the compressor. Can do. Moreover, since a low-cost refrigerant path switching device can be adopted while reducing the decrease in heating capacity during defrosting as much as possible, it is useful for air conditioners, refrigerators, heat pump water heaters, and the like.
 2 室外機
 4 室内機
 6 圧縮機
 8 四方弁
 10 ストレーナ
 12 膨張弁
 14 室外熱交換器(第2熱交換器)
 16 室内熱交換器(第1熱交換器)
 18、20、22、24、25 配管
 26 アキュムレータ
 28 配管(吐出ガスバイパス機構)
 30 電磁弁(吐出ガスバイパス機構)
 31 電磁弁
 32 蓄熱槽(補助熱交換器)
 34 蓄熱熱交換器(補助熱交換器)
 36 蓄熱材(補助熱交換器)
 38、40 配管
 42 三方弁(切り替え装置)
 43 キャピラリチューブ(絞り機構)
 50 冷凍サイクル制御装置
 51 温度センサ
2 Outdoor unit 4 Indoor unit 6 Compressor 8 Four-way valve 10 Strainer 12 Expansion valve 14 Outdoor heat exchanger (second heat exchanger)
16 Indoor heat exchanger (first heat exchanger)
18, 20, 22, 24, 25 Piping 26 Accumulator 28 Piping (Discharge gas bypass mechanism)
30 Solenoid valve (Discharge gas bypass mechanism)
31 Solenoid valve 32 Heat storage tank (auxiliary heat exchanger)
34 Heat storage heat exchanger (auxiliary heat exchanger)
36 Heat storage material (auxiliary heat exchanger)
38, 40 Piping 42 Three-way valve (switching device)
43 Capillary tube (throttle mechanism)
50 Refrigeration cycle control device 51 Temperature sensor

Claims (8)

  1.  圧縮機と、
     前記圧縮機に接続された第1熱交換器と、
     前記第1熱交換器と接続された膨張弁と、
     前記膨張弁と接続された第2熱交換器と、
     前記第2熱交換器と前記圧縮機とが接続された四方弁と、
     前記圧縮機の周囲に配置された冷媒加熱用の補助熱交換器と、
     前記圧縮機の吸入管と前記四方弁の間に、前記四方弁から前記圧縮機の吸入管へ直接冷媒を流す経路と前記四方弁から前記補助熱交換器を通じて前記圧縮機の吸入管へ冷媒を流す経路との切り替えを可能とする切り替え装置と、
    を備え、
     前記第2熱交換器に付着した霜を融解する除霜運転時には、前記切り替え装置を制御して、前記第1熱交換器と前記第2熱交換器を流れた冷媒が、前記四方弁を介して前記補助熱交換器を流れ、前記圧縮機の吸入管へ導かれるようにしたことを特徴とする冷凍サイクル装置。
    A compressor,
    A first heat exchanger connected to the compressor;
    An expansion valve connected to the first heat exchanger;
    A second heat exchanger connected to the expansion valve;
    A four-way valve to which the second heat exchanger and the compressor are connected;
    An auxiliary heat exchanger for heating the refrigerant disposed around the compressor;
    Between the suction pipe of the compressor and the four-way valve, a path for flowing the refrigerant directly from the four-way valve to the suction pipe of the compressor, and the refrigerant from the four-way valve to the suction pipe of the compressor through the auxiliary heat exchanger A switching device that enables switching with a flow path;
    With
    During the defrosting operation for melting frost adhering to the second heat exchanger, the switching device is controlled so that the refrigerant flowing through the first heat exchanger and the second heat exchanger passes through the four-way valve. The refrigeration cycle apparatus is characterized in that it flows through the auxiliary heat exchanger and is led to the suction pipe of the compressor.
  2.  前記切り替え装置に三方弁を用いたことを特徴とする請求項1に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to claim 1, wherein a three-way valve is used for the switching device.
  3.  前記圧縮機の吐出管から前記膨張弁と第2熱交換器の間に接続される吐出ガスバイパス機構を有する請求項1または2に記載の冷凍サイクル装置。 The refrigeration cycle apparatus according to claim 1 or 2, further comprising a discharge gas bypass mechanism connected between the expansion valve and the second heat exchanger from a discharge pipe of the compressor.
  4.  前記補助熱交換器の熱源は、前記圧縮機を囲むように配置され、前記圧縮機で発生した熱を蓄熱する蓄熱材であることを特徴とする請求項1乃至3のいずれか一項に記載の冷凍サイクル装置。 4. The heat source of the auxiliary heat exchanger is a heat storage material that is disposed so as to surround the compressor and stores heat generated by the compressor. 5. Refrigeration cycle equipment.
  5.  前記四方弁から前記補助熱交換器の間に設けられた前記切り替え装置と前記補助熱交換器との間に冷媒圧力損失を増大させる絞り機構を設けたことを特徴とする請求項1乃至4のいずれか一項に記載の冷凍サイクル装置。 The throttle mechanism for increasing refrigerant pressure loss is provided between the switching device provided between the four-way valve and the auxiliary heat exchanger and the auxiliary heat exchanger. The refrigeration cycle apparatus according to any one of the above.
  6.  前記第2熱交換器の配管温度を検出する温度センサと、
     前記圧縮機と前記膨張弁と前記切り替え装置と前記温度センサと電気的に接続される冷凍サイクル制御装置と、
    を更に備え、
     通常暖房運転時、前記第2熱交換器内の温度が非着霜時に比べて低下したことを前記温度センサが検出すると、前記冷凍サイクル制御装置は、通常暖房運転から除霜・暖房運転への切り替え指示を出力し、
     除霜・暖房運転時、前記第2熱交換器内の温度が零度付近で霜を融解し、霜の融解が終わって、前記第2熱交換器内の温度が上昇したことを前記温度センサが検出すると、除霜が完了したと判断し、前記冷凍サイクル制御装置は、除霜・暖房運転から通常暖房運転への切り替え指示を出力する請求項1乃至5のいずれか一項に記載の冷凍サイクル装置。
    A temperature sensor for detecting a pipe temperature of the second heat exchanger;
    A refrigeration cycle control device electrically connected to the compressor, the expansion valve, the switching device, and the temperature sensor;
    Further comprising
    When the temperature sensor detects that the temperature in the second heat exchanger is lower than that during non-frosting during normal heating operation, the refrigeration cycle control device switches from normal heating operation to defrosting / heating operation. Output a switching instruction,
    During the defrosting / heating operation, the temperature sensor indicates that the temperature in the second heat exchanger has melted when the temperature in the second heat exchanger is near zero, the frost has been melted, and the temperature in the second heat exchanger has increased. If it detects, it will judge that defrosting was completed and the said refrigeration cycle control apparatus will output the switching instruction | indication from defrost / heating operation to normal heating operation, The refrigeration cycle as described in any one of Claims 1 thru | or 5 apparatus.
  7.  前記冷凍サイクル制御装置は、除霜運転終了の判定をした後に、前記圧縮機の運転速度を一旦低下させるとともに、前記第1熱交換器で過冷却した液冷媒を前記第1熱交換器の管内に保持できる程度に膨張弁の膨張弁開度を絞った後、前記冷媒経路の前記切り替え装置を前記四方弁から前記補助熱交換器を通じて前記圧縮機の吸入管へ冷媒を流す経路から前記四方弁から前記圧縮機の吸入管へ直接冷媒を流す経路に切り替えることを特徴とする請求項6に記載の冷凍サイクル装置。 The refrigeration cycle control device, after determining the completion of the defrosting operation, temporarily reduces the operating speed of the compressor and supplies the liquid refrigerant supercooled by the first heat exchanger in the pipe of the first heat exchanger. After the expansion valve opening degree of the expansion valve is reduced to such an extent that the expansion valve can be held, the four-way valve from the path through which the refrigerant is switched from the four-way valve to the suction pipe of the compressor through the auxiliary heat exchanger The refrigeration cycle apparatus according to claim 6, wherein the refrigeration cycle apparatus is switched to a path through which a refrigerant flows directly from a suction pipe to a suction pipe of the compressor.
  8.  前記第1熱交換器を室内熱交換器、前記第2熱交換器を室外熱交換器とした請求項1乃至7のいずれか一項に記載の空気調和機。 The air conditioner according to any one of claims 1 to 7, wherein the first heat exchanger is an indoor heat exchanger, and the second heat exchanger is an outdoor heat exchanger.
PCT/JP2012/006299 2011-11-04 2012-10-02 Refrigeration cycle apparatus and air conditioner provided with same WO2013065233A1 (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109520169A (en) * 2018-09-11 2019-03-26 珠海格力电器股份有限公司 A kind of control method of air conditioner and air conditioner
CN111503928A (en) * 2020-05-15 2020-08-07 珠海格力电器股份有限公司 Air conditioning unit capable of effectively improving energy utilization rate and control method and device thereof
EP3663682A4 (en) * 2017-08-03 2021-04-28 Gree Electric Appliances (Wuhan) Co., Ltd. Control method for heat pump system and heat pump system
CN114508891A (en) * 2020-11-16 2022-05-17 合肥美的电冰箱有限公司 Refrigerator refrigerating system and refrigerator defrosting method
CN115614921A (en) * 2022-11-01 2023-01-17 宁波奥克斯电气股份有限公司 Auxiliary defrosting device, air conditioner, control method and device of air conditioner and storage medium
JP7398617B2 (en) 2020-02-17 2023-12-15 パナソニックIpマネジメント株式会社 air conditioner

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6380455B2 (en) * 2015-07-14 2018-08-29 株式会社デンソー Refrigeration cycle equipment
JP2020111193A (en) * 2019-01-11 2020-07-27 サンデン・オートモーティブクライメイトシステム株式会社 Vehicular air conditioner

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5988655U (en) * 1982-12-07 1984-06-15 三菱電機株式会社 Refrigeration equipment
JPS6122161A (en) * 1984-07-06 1986-01-30 株式会社東芝 Air conditioner
JPS6246166A (en) * 1985-08-21 1987-02-28 株式会社日立製作所 Refrostation control method of air conditioner
JPS63155972U (en) * 1987-04-01 1988-10-13
JPS63247573A (en) * 1987-04-03 1988-10-14 株式会社東芝 Air conditioner
JPH0642842A (en) * 1993-03-11 1994-02-18 Toshiba Corp Freezing cycle

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5912265A (en) * 1982-07-13 1984-01-21 太平洋工業株式会社 Cooling circuit combining air-conditioning
JP2894421B2 (en) * 1993-02-22 1999-05-24 三菱電機株式会社 Thermal storage type air conditioner and defrosting method

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5988655U (en) * 1982-12-07 1984-06-15 三菱電機株式会社 Refrigeration equipment
JPS6122161A (en) * 1984-07-06 1986-01-30 株式会社東芝 Air conditioner
JPS6246166A (en) * 1985-08-21 1987-02-28 株式会社日立製作所 Refrostation control method of air conditioner
JPS63155972U (en) * 1987-04-01 1988-10-13
JPS63247573A (en) * 1987-04-03 1988-10-14 株式会社東芝 Air conditioner
JPH0642842A (en) * 1993-03-11 1994-02-18 Toshiba Corp Freezing cycle

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3663682A4 (en) * 2017-08-03 2021-04-28 Gree Electric Appliances (Wuhan) Co., Ltd. Control method for heat pump system and heat pump system
US11193704B2 (en) 2017-08-03 2021-12-07 Gree Electric Appliances (Wuhan) Co., Ltd Heat pump reversing valve control based on the valve reversing pressure and the system pressure
CN109520169A (en) * 2018-09-11 2019-03-26 珠海格力电器股份有限公司 A kind of control method of air conditioner and air conditioner
JP7398617B2 (en) 2020-02-17 2023-12-15 パナソニックIpマネジメント株式会社 air conditioner
CN111503928A (en) * 2020-05-15 2020-08-07 珠海格力电器股份有限公司 Air conditioning unit capable of effectively improving energy utilization rate and control method and device thereof
CN114508891A (en) * 2020-11-16 2022-05-17 合肥美的电冰箱有限公司 Refrigerator refrigerating system and refrigerator defrosting method
CN115614921A (en) * 2022-11-01 2023-01-17 宁波奥克斯电气股份有限公司 Auxiliary defrosting device, air conditioner, control method and device of air conditioner and storage medium

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