WO2009142067A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2009142067A1
WO2009142067A1 PCT/JP2009/056662 JP2009056662W WO2009142067A1 WO 2009142067 A1 WO2009142067 A1 WO 2009142067A1 JP 2009056662 W JP2009056662 W JP 2009056662W WO 2009142067 A1 WO2009142067 A1 WO 2009142067A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
expander
compressor
pressure
heat exchanger
Prior art date
Application number
PCT/JP2009/056662
Other languages
English (en)
Japanese (ja)
Inventor
裕輔 島津
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2010512969A priority Critical patent/JP4906962B2/ja
Priority to CN2009801149519A priority patent/CN102016444B/zh
Priority to US12/921,848 priority patent/US20110023533A1/en
Priority to EP09750429.4A priority patent/EP2306120B1/fr
Publication of WO2009142067A1 publication Critical patent/WO2009142067A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F25B2313/02533—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements during heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
    • F25B2313/02541—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements during cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/072—Intercoolers therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle

Definitions

  • the present invention relates to a refrigeration cycle apparatus including a power recovery device that recovers power generated when a refrigerant is decompressed by an expander.
  • a first compressor that compresses a refrigerant
  • a radiator that dissipates the heat of the refrigerant compressed by the first compressor
  • an expander that depressurizes the refrigerant that has passed through the radiator
  • An evaporator that evaporates the refrigerant depressurized by an expander
  • a generator that is connected to the expander and collects power generated when the refrigerant is depressurized by the expander and converts it into electric power.
  • a refrigeration cycle apparatus provided is known (for example, see Patent Document 1).
  • a refrigeration cycle apparatus further provided with a second compressor that is provided in the expander and uses power recovered from the expander.
  • the refrigeration cycle apparatus that has been stopped for a long time has high viscosity due to the low temperature of the refrigerating machine oil inside the expander, and a large amount of power is required to start the expander.
  • the expander may not be activated.
  • the operation continues due to the inertia of the rotating part in the steady operation state. In the start-up operation state, there is a problem that there is no inertia of the rotating part and the expander stops.
  • An object of the present invention is to solve the above-described problems, and its purpose is to start up the first compressor even when a large amount of power is required to start up the expander.
  • a refrigeration cycle apparatus capable of starting an expander is provided.
  • the refrigeration cycle apparatus includes a first compressor that compresses a refrigerant, a radiator that dissipates heat of the refrigerant compressed by the first compressor, and the refrigerant that has passed through the radiator.
  • An expander that depressurizes, an evaporator that evaporates the refrigerant decompressed by the expander, and a power recovery device that is connected to the expander and collects power generated when the refrigerant is depressurized by the expander
  • a refrigerant movement control means for controlling a flow rate of the refrigerant that is provided in a flow path of the refrigerant from the expander to the evaporator and moves from the expander to the evaporator.
  • the first compressor is started and the refrigerant pressure inside the expander is increased.
  • the movement control means controls the flow rate of the refrigerant, and the expander can be activated by the dynamic pressure of the refrigerant.
  • FIG. 3A is a schematic diagram showing a breakdown of power transmitted from the expander to the second compressor at the steady state
  • FIG. 3B is transmitted from the expander to the second compressor at the time of start-up.
  • FIG. 4A is a diagram illustrating the refrigerant pressure, the refrigerant volume, and the mass of the refrigerant when the expander is in a steady state.
  • 4B is a diagram illustrating the refrigerant pressure and the refrigerant mass when the expander is activated. It is a figure which shows the volume and the mass of a refrigerant
  • FIG. FIG. 1 is a refrigerant circuit diagram during cooling operation of the air conditioner according to this embodiment
  • FIG. 2 is a refrigerant circuit diagram during heating operation of the air conditioner of FIG.
  • the air conditioner that is a refrigeration cycle apparatus according to this embodiment includes a first compressor 1 that compresses a refrigerant, and a radiator in which the internal refrigerant dissipates heat during cooling operation, and an internal
  • the outdoor heat exchanger 2 is an evaporator that evaporates the refrigerant, the expander 3 that depressurizes the refrigerant that passes through the interior, and an evaporator that evaporates the internal refrigerant during the cooling operation.
  • the air conditioner is provided on the downstream side of the expander 3 and is fully closed to suppress the movement of the refrigerant from the expander 3 to the downstream, and is fully opened to move downstream from the expander 3.
  • an on-off valve 6 which is a refrigerant movement control means for controlling the flow rate of the refrigerant.
  • this air conditioner uses carbon dioxide as a refrigerant, and this carbon dioxide has a zero ozone layer depletion coefficient and a low global warming coefficient as compared with conventional chlorofluorocarbon refrigerants.
  • the outdoor heat exchanger 2 has a first outdoor heat exchanger section 2a and a second outdoor heat exchanger section 2b, and the first outdoor heat exchanger section 2a and the second outdoor heat exchanger section.
  • the refrigerant flow path between 2b and 2b is provided with a switch 7a and a switch 7b that are closed during the cooling operation so that the refrigerant cannot pass and opened during the heating operation so that the refrigerant can pass therethrough.
  • the 1st outdoor heat exchanger part 2a and the 2nd outdoor heat exchanger part 2b have the 1st outdoor heat exchanger part 2a and the 2nd outdoor heat exchanger part 2b in series at the time of cooling operation.
  • the first outdoor heat exchanger section 2a and the second outdoor heat exchanger section 2b are connected in parallel during the heating operation.
  • the indoor heat exchanger 4 has a first indoor heat exchanger section 4a and a second indoor heat exchanger section 4b, and the first indoor heat exchanger section 4a and the second indoor heat exchanger section. 4b is connected in parallel.
  • An indoor expansion valve 8a is connected to the first indoor heat exchanger section 4a, and an indoor expansion valve 8b is connected to the second indoor heat exchanger section 4b.
  • the refrigerant is depressurized so that the refrigerant that has dissipated heat in the section 4a and the second indoor heat exchanger section 4b can be evaporated in the first outdoor heat exchanger section 2a and the second outdoor heat exchanger section 2b. .
  • the refrigerant that has passed through the first outdoor heat exchanger section 2a is compressed during the cooling operation.
  • a second compressor 9 is provided.
  • the second compressor 9 is connected to the expander 3 via the drive shaft 5, and the power generated by the expander 3 is recovered by the drive shaft 5 and transmitted to the second compressor 9. .
  • the refrigerant flow path between the first compressor 1 and the first outdoor heat exchanger section 2a and the second compressor 9 are provided with a switch 10a and a switch 10b that are opened during cooling operation so that the refrigerant can pass therethrough and closed during heating operation so that the refrigerant cannot pass therethrough.
  • a switch that allows the refrigerant to pass through the refrigerant flow path between the first compressor 1 and the second compressor 9 when closed during cooling operation, so that the refrigerant cannot pass during heating operation. 7c is provided.
  • a first foreign object trap 11 that captures foreign substances contained in the refrigerant that enters the expander 3 is provided.
  • a second foreign material catcher 12 that captures foreign matter contained in the refrigerant entering the second compressor 9 is provided.
  • the first foreign matter catcher 11 and the second foreign matter catcher 12 are composed of a strainer made of a metal mesh having a coarse mesh, and the coarseness of the metal mesh determines the size of the minimum foreign matter to be captured. .
  • the size of the smallest foreign matter captured by the first foreign matter catcher 11 is set to be smaller than the maximum clearance of the expansion chamber of the expander 3.
  • the size of the smallest foreign matter captured by the second foreign matter catcher 12 is set to be smaller than the maximum clearance of the compression chamber of the second compressor 9.
  • the size of the minimum foreign matter captured by the first foreign matter catcher 11 and the second foreign matter catcher 12 is 0.5 mm, whereby the first foreign matter catcher 11 and the second foreign matter catcher are captured.
  • the pressure loss due to the vessel 12 can be reduced, and the reduction of the recovered power can be suppressed.
  • an accumulator 13 is provided for storing refrigerant before entering the first compressor 1.
  • a first four-way valve 14 is provided in the refrigerant flow path between the outdoor heat exchanger 2, the second compressor 9, the indoor heat exchanger 4, and the accumulator 13.
  • the refrigerant flows from the second compressor 9 to the second outdoor heat exchanger section 2b during the cooling operation, the refrigerant flows from the indoor heat exchanger 4 to the accumulator 13, and during the heating operation, the second The refrigerant flows from the compressor 9 and the check valve 15 bypassing the second compressor 9 and the second foreign matter trap 12 to the indoor heat exchanger 4, and the refrigerant flows from the outdoor heat exchanger 2 to the accumulator 13.
  • the internal valve is switched to flow.
  • the check valve 15 may be built in the second compressor 9.
  • a second four-way valve 16 is provided in the refrigerant flow path between the outdoor heat exchanger 2, the expander 3, and the indoor heat exchanger 4, and the second four-way valve 16 is a cooling device.
  • the refrigerant flows from the second outdoor heat exchanger section 2b through the expander 3 to the indoor heat exchanger 4, and during heating operation, the refrigerant flows from the indoor heat exchanger 4 through the expander 3 to the outdoor heat exchanger 2.
  • the internal valve is switched so that the refrigerant flows into Due to the first four-way valve 14 and the second four-way valve 16, the direction of the refrigerant passing through the expander 3 and the second compressor 9 is the same regardless of the cooling operation and the heating operation.
  • the refrigerant flow path between the outdoor heat exchanger 2 and the indoor heat exchanger 4 passes through a bypass circuit 17 that bypasses the second four-way valve 16, the expander 3, and the on-off valve 6, and the bypass circuit 17. And a bypass valve 18 for adjusting the flow rate of the refrigerant.
  • a bypass valve 18 for adjusting the flow rate of the refrigerant.
  • pre-expansion for adjusting the flow rate of the refrigerant moving from the second four-way valve 16 to the first foreign matter catcher 11.
  • a valve 19 is provided.
  • the flow rate of the refrigerant passing through the second compressor 9 and the sum of the flow rates of the refrigerant passing through the expander 3 and the bypass circuit 17 are equalized. It has become. Thereby, the pressure on the high-pressure side can be adjusted to a desired pressure and adjusted, and the power from the expander 3 can be recovered, so that the refrigeration cycle can be maintained in a highly efficient state. It should be noted that the flow rate of the refrigerant passing through the second compressor 9 and the refrigerant passing through the expander 3 and the bypass circuit 17 are not limited to adjusting the bypass valve 18 and the pre-expansion valve 19. The flow rate may be made equal.
  • a pressure sensor 20 a that measures the pressure of the refrigerant that has exited the first compressor 1 is provided at the refrigerant outlet of the first compressor 1, and enters the expander 3 at the refrigerant inlet of the expander 3.
  • a pressure sensor 20 b that measures the pressure of the refrigerant is provided, and a pressure sensor 20 c that measures the pressure of the refrigerant that has exited the on-off valve 6 is provided at the outlet of the on-off valve 6.
  • the pressure sensor 20a, the pressure sensor 20b, and the pressure sensor 20c are not limited to these positions, and each of them includes the pressure of the refrigerant that has exited the first compressor 1, the pressure of the refrigerant that enters the expander 3, and the on-off valve 6.
  • the pressure sensor 20a, the pressure sensor 20b, and the pressure sensor 20c may be temperature sensors that measure the temperature of the refrigerant as long as the pressure can be estimated.
  • the pressure sensor 20a, the pressure sensor 20b, and the pressure sensor 20c are connected to a control device 21.
  • the control device 21 opens and closes according to the refrigerant pressure values measured by the pressure sensor 20a, the pressure sensor 20b, and the pressure sensor 20c.
  • the opening / closing of the valve 6, the bypass valve 18 and the pre-expansion valve 19 is controlled.
  • the control device 21 includes a determination unit (not shown) that determines whether the expander 3 is activated after the on-off valve 6 is fully opened, and a storage unit that stores the number of times that the expander 3 is determined not to be activated ( (Not shown) and display means (not shown) configured to display that an abnormality has occurred in the expander 3 when the number of times stored in the storage means reaches a predetermined number. is doing.
  • An outdoor unit 22 is configured by the valve 19, the pressure sensor 20a, the pressure sensor 20b, the pressure sensor 20c, and the control device 21.
  • the indoor unit 23a is comprised from the 1st indoor heat exchanger part 4a and the indoor expansion valve 8a, and the indoor unit 23a is comprised from the 2nd indoor heat exchanger part 4b and the indoor expansion valve 8b.
  • One end of a liquid main pipe 24 and a gas main pipe 25 is connected to the outdoor unit 22, and one end of a liquid branch pipe 26 a and a liquid branch pipe 26 b is connected to the other end of the liquid main pipe 24.
  • One end of the gas branch pipe 27a and the gas branch pipe 27b is connected to the other end.
  • the indoor expansion valve 8a is connected to the other end of the liquid branch pipe 26a, and the indoor expansion valve 8b is connected to the other end of the liquid branch pipe 26b.
  • the first indoor heat exchanger section 4a is connected to the other end of the gas branch pipe 27a, and the second indoor heat exchanger section 4b is connected to the other end of the gas branch pipe 27b.
  • the first compressor 1 is connected to a motor (not shown), and the first compressor 1 operates when the motor is driven.
  • the expander 3 and the second compressor 9 are of a positive displacement type, specifically a scroll type.
  • the expander 3 and the second compressor 9 are not limited to the scroll type but may be other positive displacement types.
  • the expander 3 and the second compressor 9 do not have a motor that is a heat source. Moreover, since the bearing load of the expander 3 and the 2nd compressor 9 is substantially equivalent, the loss which generate
  • the low-pressure refrigerant that has entered the first compressor 1 is compressed to a high temperature and intermediate pressure.
  • the refrigerant discharged from the first compressor 1 passes through the switch 10a and enters the first outdoor heat exchanger portion 2a of the outdoor heat exchanger 2.
  • the refrigerant that dissipates heat in the first outdoor heat exchanger section 2a and transfers heat to the outdoor air has a low temperature and intermediate pressure.
  • the refrigerant that has exited the first outdoor heat exchanger section 2a enters the second compressor 9 and is compressed to a high temperature and high pressure.
  • the refrigerant exiting the second compressor 9 passes through the first four-way valve 14 and enters the second outdoor heat exchanger section 2b, where the refrigerant dissipates heat and transfers heat to the outdoor air. Become high pressure.
  • the refrigerant that has exited the second outdoor heat exchanger section 2 b branches into a path toward the second four-way valve 16 and a path toward the bypass valve 18.
  • the refrigerant that has passed through the second four-way valve 16 passes through the pre-expansion valve 19 and the first foreign matter catcher 11, enters the expander 3, and is decompressed to a low pressure, resulting in a low dryness state. .
  • power is generated as the refrigerant is depressurized.
  • This power is recovered by the drive shaft 5 and transmitted to the second compressor 9, and the refrigerant is compressed by the second compressor 9. Used for.
  • the refrigerant that has left the expander 3 passes through the on-off valve 6 and the second four-way valve 16, and then merges with the refrigerant that has passed through the bypass circuit 17 toward the bypass valve 18, and then exits the outdoor unit 22. It passes through the main pipe 24, the liquid branch pipe 26a and the liquid branch pipe 26b, enters the indoor unit 23a and the indoor unit 23b, and enters the indoor expansion valve 8a and the indoor expansion valve 8b. In the indoor expansion valve 8a and the indoor expansion valve 8b, the refrigerant is further decompressed.
  • the refrigerant that has exited the indoor expansion valve 8a and the indoor expansion valve 8b absorbs heat from the indoor air in the first indoor heat exchanger section 4a and the second indoor heat exchanger section 4b and evaporates. Becomes high. Thereby, indoor air is cooled.
  • the refrigerant that has exited the first indoor heat exchanger section 4a and the second indoor heat exchanger section 4b exits the indoor unit 23a and the indoor unit 23b, and has a gas branch pipe 27a, a gas branch pipe 27b, and a gas main pipe 25.
  • Enters the outdoor unit 22 passes through the first four-way valve 14, enters the accumulator 13, and enters the first compressor 1 again. By repeating the operation described above, the heat of the indoor air is transmitted to the outdoor air, and the room is cooled.
  • the low-pressure refrigerant that has entered the first compressor 1 is compressed to a high temperature and a high pressure.
  • the refrigerant leaving the first compressor 1 passes through the switch 7c, the check valve 15 and the first four-way valve 14.
  • a part of the refrigerant that has passed through the switch 7 c passes through the second compressor 9, and then merges with the refrigerant that has passed through the check valve 15 and enters the first four-way valve 14.
  • the refrigerant that has passed through the second four-way valve 16 passes through the pre-expansion valve 19 and the first foreign matter catcher 11 and enters the expander 3, where it is decompressed to a low pressure, and the degree of dryness is low. At this time, in the expander 3, power is generated as the refrigerant is depressurized.
  • This power is recovered by the drive shaft 5 and transmitted to the second compressor 9, and the refrigerant is compressed by the second compressor 9. Used for.
  • the refrigerant that has left the expander 3 passes through the on-off valve 6 and the second four-way valve 16, and then merges with the refrigerant that has passed through the bypass circuit 17 toward the bypass valve 18. It enters into the outdoor heat exchanger part 2a and the second outdoor heat exchanger part 2b.
  • coolant absorbs heat from outdoor air and evaporates, and it will be in a state with a high dryness with a low pressure.
  • the heat of the outdoor air is transmitted to the indoor air, and the room is heated.
  • This air conditioner is used as a multi-air conditioner in a building, and in order to improve the annual operation efficiency, the operation efficiency in the cooling intermediate period, which is a period when the cooling load is not large, is made efficient. Therefore, the expander 3, the second compressor 9, the outdoor heat exchanger 2 and the indoor heat exchanger 4 are designed to be optimal in the cooling middle period, and during the heating operation, the expander 3 and the second heat exchanger 4 are designed to be optimal. There is an advantage in controlling the refrigerant not to pass through the second compressor 9. However, if the refrigerant is not passed through the expander 3 and the second compressor 9 during the heating operation, the refrigerant stagnates in the expander 3 and the second compressor 9, and the expander 3 and the second compressor 9.
  • the compressor 9 When starting up the compressor 9, there is a possibility that the expander 3 and the second compressor 9 may be damaged due to poor lubrication. Therefore, the refrigerant is passed through the expander 3 and the second compressor 9 even during the heating operation.
  • the second compressor 9 operates to the extent that the refrigerant is not compressed.
  • FIG. 3A is a schematic diagram showing a breakdown of the power transmitted from the expander 3 to the second compressor 9 at the steady state
  • FIG. 3B is a diagram showing the breakdown of the power transmitted from the expander 3 to the second compressor 9 at the time of startup. It is the schematic which shows the breakdown of the motive power transmitted to.
  • the power that the expander 3 receives from the dynamic pressure of the refrigerant is finally obtained by removing the loss that occurs in the expander 3 and the loss that occurs in the second compressor 9. Power to be recovered.
  • the air conditioner When the air conditioner has been in a stopped state for a long period of time, the refrigerating machine oil inside the expander 3 and the second compressor 9 has a high viscosity due to low temperature, and the air conditioner is started from this state.
  • the expander 3 When the expander 3 is started, the loss generated in the expander 3 and the loss generated in the second compressor 9 are further increased. Further, immediately after the air conditioner is manufactured and shipped, the operating time is short, so that the sliding parts of the expander 3 and the second compressor 9 are not sufficiently familiar, the friction is large, and the expander 3 The loss generated and the loss generated in the second compressor 9 are further increased.
  • FIG. 4A is a diagram showing the refrigerant pressure, the refrigerant volume, and the mass of the refrigerant when the expander 3 is in a steady state
  • FIG. 4B is a diagram illustrating the refrigerant pressure when the expander 3 is started
  • It is a figure which shows the volume of a refrigerant
  • the pressure of the refrigerant inside the expansion chamber of the expander 3 is equal to the inlet pressure, which is the pressure at the refrigerant inlet of the expander 3, in the middle of the expansion process.
  • the pressure at the end of the expansion process decreases from the start point to the end point, and the pressure at the end point of the expansion process becomes equal to the outlet pressure that is the pressure at the refrigerant outlet of the expander 3.
  • the volume inside the expansion chamber of the expander 3 increases as the expansion process proceeds from the start point to the end point.
  • the mass of the refrigerant inside the expansion chamber of the expander 3 does not change between the start point and end point of the expansion process.
  • the refrigerant pressure inside the expansion chamber of the expander 3 varies between the start point and end point of the expansion process.
  • the pressure changes discontinuously and becomes smaller, and becomes equal to the refrigerant pressure measured by the pressure sensor 20c.
  • the volume inside the expansion chamber of the expander 3 increases as the expansion process proceeds from the start point to the end point, as in the steady state.
  • the mass of the refrigerant in the expansion chamber of the expander 3 increases as the expansion process proceeds from the start point to the end point.
  • the area of the boundary between the expansion chamber and the space after the expansion process is large before and after the end point of the expansion process, and immediately after the on-off valve 6 is fully opened from the fully closed state, the pressure before and after the end point of the expansion process is large. Therefore, the recovery power determined by the area and pressure increases. From the above, immediately after the on-off valve 6 is fully opened from the fully closed state, the expander 3 can obtain a large recovery power. Thereby, even if the loss which generate
  • the high-pressure refrigerant causes the expander 3 and the first compressor 1 to be closed.
  • the viscosity of the refrigerating machine oil inside the second compressor 9 is lowered.
  • the loss generated in the expander 3 and the loss generated in the second compressor 9 immediately after the on-off valve 6 is fully opened can be reduced, so that the expander 3 can obtain a large recovery power. it can.
  • FIG. 5 is a flowchart showing the starting operation of the air conditioner of FIGS. 1 and 2.
  • the air conditioner determines which of the cooling operation and the heating operation is requested (step S2). If it determines with heating operation being requested
  • the switch 7a, the switch 7b, and the switch 7c are closed, the switch 10a and the switch 10a are opened, and the first four-way valve 14 is moved from the second compressor 9 to the second
  • the internal flow is switched so that the refrigerant flows to the outdoor heat exchanger section 2b and the refrigerant flows from the indoor heat exchanger 4 to the accumulator 13, and the second four-way valve 16 is connected to the second outdoor heat exchanger section 2b.
  • a first cooling circuit in which the internal valve is switched so that the refrigerant flows through the expander 3 to the indoor heat exchanger 4 is set (step S5).
  • step S6 the on-off valve 6 is fully closed, the pre-expansion valve 19 is fully opened (step S6), the other devices are set to the first cooling initial setting which is the initial state of the cooling operation (step S7), and air conditioning is performed.
  • the machine enters the first startup mode (step S8).
  • the air conditioner enters the first start mode, first, the first compressor 1 is started (step S9), the pressure sensor 20b measures the refrigerant pressure at the inlet of the expander 3, and the pressure sensor 20c The refrigerant pressure at the outlet of the on-off valve 6 is measured, and the control device 21 calculates the difference between the refrigerant pressure at the inlet of the expander 3 and the refrigerant pressure at the outlet of the on-off valve 6 (step S10).
  • the control device 21 determines whether or not a predetermined time Ta has elapsed since the first compressor 1 was started (step S11).
  • the predetermined time Ta is set in advance between 10 seconds and 60 seconds.
  • the predetermined time Ta is not limited to this time.
  • the control device 21 determines in step S11 that the predetermined time Ta has not elapsed since the first compressor 1 was started, the process returns to step S10.
  • the control device 21 determines in step S11 that the predetermined time Ta has elapsed, the refrigerant pressure at the inlet of the expander 3 is equal to or higher than the critical pressure, and at the inlet of the expander 3.
  • step S12 It is determined whether the difference between the refrigerant pressure and the refrigerant pressure at the outlet of the on-off valve 6 is equal to or higher than a predetermined pressure Pa (step S12).
  • the predetermined pressure Pa is preset between 2.5 MPa and 5 MPa.
  • the control device 21 determines that the refrigerant pressure at the inlet of the expander 3 is not equal to or higher than the critical pressure, or the refrigerant pressure at the inlet of the expander 3 and the refrigerant pressure at the outlet of the on-off valve 6.
  • the opening degree of the bypass valve 18 is decreased (step S13), and the process returns to step S10.
  • step S12 the control device 21 determines that the refrigerant pressure at the inlet of the expander 3 is equal to or higher than the critical pressure, and the refrigerant pressure at the inlet of the expander 3 and the refrigerant pressure at the outlet of the on-off valve 6. Is determined to be equal to or higher than the predetermined pressure Pa, the on-off valve 6 is fully opened (step S14).
  • the control device 21 determines whether or not a predetermined time Tb has elapsed from when the on-off valve 6 is fully opened (step S15).
  • the predetermined time Tb is shorter than the predetermined time Ta in step S11 and is set in advance between 5 seconds and 30 seconds.
  • the predetermined time Tb is not limited to this time.
  • step S15 is repeated.
  • the pressure sensor 20a measures the refrigerant pressure at the outlet of the first compressor 1, and the pressure sensor 20b expands.
  • the refrigerant pressure at the inlet of the machine 3 is measured, and the control device 21 calculates the difference between the refrigerant pressure at the inlet of the expander 3 and the refrigerant pressure at the outlet of the first compressor 1 (step S16). ).
  • the control device 21 determines whether or not the difference between the refrigerant pressure at the inlet of the expander 3 and the refrigerant pressure at the outlet of the first compressor 1 is equal to or higher than a predetermined pressure Pb (step S17). ).
  • the predetermined pressure Pb is set in advance between 0 MPa and 0.5 MPa. The predetermined pressure Pb is not limited to this pressure.
  • step S17 When the control device 21 determines in step S17 that the difference between the refrigerant pressure at the inlet of the expander 3 and the refrigerant pressure at the outlet of the first compressor 1 is equal to or higher than a predetermined pressure Pb, The determination unit determines that the start-up of the expander 3 has been successful, and the air conditioner ends the first start-up mode, and the first regular control in the steady state is performed (step S18). On the other hand, when the controller 21 determines in step S17 that the difference between the refrigerant pressure at the inlet of the expander 3 and the refrigerant pressure at the outlet of the first compressor 1 is not greater than or equal to the predetermined pressure Pb.
  • the determination means determines that the start-up of the expander 3 has failed, and the air conditioner enters the backup mode (step S19).
  • the storage means adds 1 to the number of failed activations (step S20), and further determines whether the number of failed activations is a predetermined number (step S21). ). This predetermined number of times is preset between 5 and 10. The predetermined number is not limited to this number. If the control device 21 determines in step S21 that the number of failed startups is smaller than the predetermined number, the process returns to step S5.
  • step S21 determines in step S21 that the number of failed startups is a predetermined number, it is considered that an abnormality has occurred in the expander 3 or the second compressor 9, and the air conditioner Starts backup control (step S22).
  • the backup control first, the first compressor 1 is stopped (step S23), and the display means of the control device 21 displays that an abnormality has occurred in the expander 3 or the second compressor 9 (step S23). S24), inform the administrator or user.
  • the second refrigerant circuit is set so that the refrigerant does not flow to the expander 3 and the second compressor 9 (step S25), the on-off valve 6 is fully closed, the pre-expansion valve 19 is closed, The bypass valve 18 is opened to prevent the refrigerant from passing through the expander 3 and the second compressor 9, and the other actuators are set to the second cooling initial setting that is the state before the cooling start (step S26).
  • the air conditioner enters a second start mode in which the expander 3 is not started (step S27), the first compressor 1 is started without operating the expander 3, and a steady-state operation is performed ( Step S28), and the cooling operation in which the refrigerant circulates continues as in the refrigerant circuit diagram shown in FIG.
  • the refrigerant does not pass through the expander 3 and the second compressor 9, so that the first compressor 1, the indoor expansion valve It can suppress that 8a, the indoor expansion valve 8b, etc. are damaged. Further, for example, even when an abnormality occurs in the expander 3 or the second compressor 9, the cooling operation can be continued.
  • the air conditioner according to this embodiment even when a large amount of power is required to activate the expander 3, the first compressor 1 is activated, After the pressure of the internal refrigerant increases, the on-off valve 6 is fully opened, so that the refrigerant passing through the on-off valve 6 increases, and the expander 3 can be activated by the dynamic pressure of the refrigerant.
  • the refrigerating machine oil inside the expander 3 and the second compressor 9 has a high viscosity due to low temperature, it opens and closes when the refrigerant pressure at the inlet of the expander 3 exceeds the critical pressure. Since the valve 6 is fully opened and the refrigerant passes through the on-off valve 6, the refrigerant that has reached the critical pressure or more acts on the refrigerating machine oil and the viscosity of the refrigerating machine oil decreases, so the expander 3 and the second compressor 9 Can reduce the loss.
  • the on-off valve 6 is fully opened and the refrigerant passes through the on-off valve 6.
  • the expander 3 can be activated by the dynamic pressure of the large refrigerant.
  • a determination unit that determines whether or not the expander 3 is activated
  • a storage unit that stores the number of times the expansion unit 3 has been determined not to be activated by the determination unit, and the storage
  • a display device for displaying that an abnormality has occurred in the expander 3 and the second compressor 9 when the number of times stored in the means reaches a predetermined number. The person or the user can easily know that an abnormality has occurred in the expander 3 and the second compressor 9.
  • a bypass circuit 17 connected in parallel to the expander 3 and the on-off valve 6 connected in series, and the bypass circuit 17 And a bypass valve 18 for adjusting the flow rate of the refrigerant passing through the refrigerant, the refrigerant passes through the bypass circuit 17 when the number of times stored in the storage means reaches a predetermined number.
  • the refrigerant circulates in the refrigerant flow path between the outdoor heat exchanger 2 and the indoor heat exchanger 4 even if an abnormality occurs in the compressor 9 and the expander 3 and the second compressor 9 do not operate. can do.
  • the refrigerant movement control means is fully closed, so that the movement of the refrigerant from the expander 3 to the indoor heat exchanger 4 is suppressed during the cooling operation, and is fully opened, so that the indoor heat exchange from the expander 3 during the cooling operation. Since the opening / closing valve 6 controls the flow rate of the refrigerant moving to the cooler 4, the movement of the refrigerant from the expander 3 to the indoor heat exchanger 4 can be controlled with a simple configuration.
  • a second compressor 9 is provided in the refrigerant flow path between the first compressor 1 and the outdoor heat exchanger 2, and power is supplied from the expander 3 via the drive shaft 5 during the cooling operation. Is transmitted to the second compressor 9, so that the power generated when the refrigerant is decompressed by the expander 3 can be used by the second compressor 9 to improve the efficiency of the air conditioner. Can do.
  • a first foreign matter catcher 11 that catches foreign matter that enters the expander 3 is provided at the refrigerant inlet of the expander 3, and the size of the smallest foreign matter that the first foreign matter catcher 11 catches. Is smaller than the maximum clearance of the expansion chamber of the expander 3, so that it is possible to prevent foreign matter from entering the expander 3 and causing an abnormality in the expander 3.
  • a second foreign matter catcher 12 that catches foreign matter that enters the second compressor 9 is provided at the refrigerant inlet of the second compressor 9, and the second foreign matter catcher 12 catches the second foreign matter catcher 12. Since the minimum size of the foreign matter is smaller than the maximum gap of the compression chamber of the second compressor 9, the foreign matter enters the second compressor 9 and the abnormality occurs in the second compressor 9. Can be suppressed.
  • the refrigerant is carbon dioxide
  • the destruction of the ozone layer can be reduced and the global warming can be reduced as compared with the conventional fluorocarbon refrigerant.
  • the indoor heat exchanger 4 having the first indoor heat exchanger section 4a and the second indoor heat exchanger section 4b has been described, but of course, the present invention is not limited to this.
  • the indoor heat exchanger 4 having an indoor heat exchanger section may be used, or the indoor heat exchanger 4 having three or more indoor heat exchanger sections may be used.
  • the indoor expansion valve 8a was connected to the 1st indoor heat exchanger part 4a and the indoor expansion valve 8b was connected to the 2nd indoor heat exchanger part 4b, the air conditioner was demonstrated.
  • the indoor heat exchanger unit 4a and the second indoor heat exchanger unit 4b may be an air conditioner in which one indoor expansion valve is connected, and the outdoor unit 22 is provided with an outdoor expansion valve.
  • An air conditioner may be used.
  • the opening / closing valve 6 that controls the flow rate of the refrigerant that moves from the expander 3 to the downstream by suppressing the movement of the refrigerant from the expander 3 by fully closing and the flow of the refrigerant that moves from the expander 3 to the downstream by fully opening has been described.
  • the flow rate adjustment that controls the flow rate of the refrigerant that moves from the expander 3 to the downstream by adjusting the opening degree by suppressing the movement of the refrigerant from the expander 3 to the downstream by being fully closed or almost fully closed. It may be a valve.
  • the second compressor 9 that operates only by the rotational power transmitted from the expander 3 has been described.
  • the second compressor 9 is not limited to this, but, for example, the rotational power transmitted from the expander 3 and the rotation from the motor. It may be the second compressor 9 that operates by power.
  • whether or not the expander 3 can be activated is determined by the difference between the refrigerant pressure at the refrigerant inlet of the expander 3 and the refrigerant pressure at the refrigerant outlet of the on-off valve 6, but of course not limited to this.
  • Starting the expander 3 by attaching a tachometer or a vibration meter to the expander 3 and the second compressor 9 and measuring the temperature of the refrigerant at the outlet or inside the refrigerant of the second compressor 9 It may be determined whether or not.
  • FIG. FIG. 7 is a refrigerant circuit diagram of the water heater according to this embodiment.
  • a water heater that is a refrigeration cycle apparatus according to this embodiment includes a compressor 28 that compresses refrigerant, a radiator 29 that dissipates heat of the refrigerant compressed by the compressor 28 and heats water, and a radiator.
  • the refrigerant is decompressed by the expander 30 connected to the expander 30, an expander 30 that depressurizes the refrigerant that has passed through 29, an evaporator 31 that absorbs and evaporates the refrigerant that has passed through the expander 30.
  • a generator 32 which is a power recovery device for recovering the power generated in the power generator.
  • the refrigerant flow path between the expander 30 and the evaporator 31 is fully closed or almost fully closed, thereby suppressing the movement of the refrigerant from the expander 30 to the evaporator 31 and adjusting the opening degree.
  • An opening adjustment valve 33 is provided as refrigerant movement control means for controlling the flow rate of the refrigerant moving from the expander 30 to the evaporator 31.
  • a pressure sensor 34 a for measuring the pressure of the refrigerant entering the compressor 28 is provided at the refrigerant inlet of the compressor 28, and a pressure for measuring the pressure of the refrigerant coming out of the compressor 28 is provided at the refrigerant outlet of the compressor 28.
  • a sensor 34b is provided.
  • the pressure sensor 34a and the pressure sensor 34b are connected to a control device 35.
  • the control device 35 controls the opening degree of the opening adjustment valve 33 according to the value of the refrigerant pressure measured by the pressure sensor 34a and the pressure sensor 34b. adjust.
  • the control device 35 determines a determination means (not shown) for determining whether or not the expander 30 is activated, and the number of times that the expander 30 is determined not to be activated.
  • store is comprised from the carbon dioxide.
  • the radiator 29 is provided with a water transport means 36 for sending water toward the radiator 29 and a hot water supply tank 37 for storing water heated by passing through the radiator 29.
  • the evaporator 31 is provided with a blower (not shown) that blows air toward the evaporator 31.
  • the low-temperature and low-pressure refrigerant that has entered the compressor 28 is compressed into a high-temperature and high-pressure state.
  • the refrigerant leaving the compressor 28 dissipates heat in the radiator 29 and becomes a low temperature and high pressure state.
  • the heat of the refrigerant is transmitted to the water via the radiator 29, and the water is heated.
  • the refrigerant exiting the radiator 29 is decompressed by the expander 30 and becomes a low temperature and low pressure state.
  • the power generated when the refrigerant is decompressed by the expander 30 is recovered by the generator 32.
  • the power recovered by the generator 32 becomes electric energy and is used for the compressor 28, the water transport means 36 and the blower.
  • the refrigerant exiting the expander 30 absorbs heat by the evaporator 31 and evaporates to a low pressure, which changes from a low dryness state to a high dryness state.
  • the blower blows air toward the evaporator 31, the refrigerant inside the evaporator 31 can effectively absorb heat.
  • the refrigerant that has left the evaporator 31 enters the compressor 28 again.
  • FIG. 8 is a flowchart showing the starting operation of the water heater shown in FIG.
  • the opening adjustment valve 33 is fully closed or almost fully closed (step S102).
  • the other devices are set to the initial operation state (step S103), the hot water supply device is in the start mode, and the compressor 28 is started (step S104).
  • the pressure sensor 34a and the pressure sensor 34b measure the refrigerant pressure at the inlet of the compressor 28 and the refrigerant pressure at the outlet, and the control device 35 controls the refrigerant pressure at the inlet and the outlet of the compressor 28.
  • a difference from the refrigerant pressure is calculated (step S105).
  • step S106 determines whether or not the difference between the refrigerant pressure at the inlet of the compressor 28 and the refrigerant pressure at the outlet is equal to or greater than a predetermined pressure.
  • the control device 35 determines in step S106 that the difference between the refrigerant pressure at the inlet of the compressor 28 and the refrigerant pressure at the outlet is smaller than a predetermined pressure, the process returns to step S105.
  • the opening adjustment valve 33 is opened. The degree increases (step S107).
  • step S108 determines whether or not a predetermined time has elapsed since the opening of the opening adjustment valve 33 is increased.
  • step S108 determines whether or not a predetermined time has elapsed since the opening of the opening adjustment valve 33 is increased.
  • step S108 is repeated.
  • the control device 35 determines in step S108 that the predetermined time has elapsed, the voltage of the generator 32 is measured (step S109).
  • step S110 determines whether or not the voltage of the generator 32 is equal to or higher than a predetermined voltage.
  • step S110 when the control device 35 determines that the voltage of the generator 32 is equal to or higher than the predetermined voltage, the determination unit regards that the starter of the expander 30 has succeeded, and the water heater sets the start mode. The routine is terminated and the steady-state timed control is performed (step S111).
  • step S111 when the control device 35 determines in step S110 that the voltage of the generator 32 is smaller than the predetermined voltage, the determination unit regards that the start-up of the expander 30 has failed, and the water heater is in the backup mode.
  • Step S112 When the water heater is in the backup mode, the storage unit of the control device 35 adds 1 to the number of times of activation failure, and further determines whether the number of failure of activation is a predetermined number or more.
  • control device 35 determines that the number of failed activations is smaller than the predetermined number, the process returns to step S102.
  • the control device 35 determines that the number of failed startups has reached a predetermined number, it is considered that an abnormality has occurred in the expander 30 or the generator 32, and the water heater starts backup control ( Step S113). In the backup control, the compressor 28 is stopped.
  • the power recovery device is the generator 32
  • the power recovered by the generator 32 becomes electric energy
  • the compressor 28 It can be used for the water transport means 36 and the blower.
  • Other effects are the same as those of the first embodiment.
  • FIG. 9 is a refrigerant circuit diagram of the water heater according to this embodiment.
  • the hot water heater according to this embodiment includes a first compressor 38 that compresses the refrigerant, a radiator 29 that dissipates the heat of the refrigerant compressed by the first compressor 38, and passes through the radiator 29. Occurs when the refrigerant is depressurized by the expander 30 connected to the expander 30, and the evaporator 31 that absorbs and evaporates the refrigerant that has passed through the expander 30.
  • a drive shaft 39 that is a power recovery device that recovers power is provided, and a second compressor 40 that is connected to the drive shaft 39 and compresses the refrigerant that enters the first compressor 38 from the evaporator 31.
  • Other configurations are the same as those of the second embodiment.
  • the low-temperature and low-pressure refrigerant that has entered the second compressor 40 is compressed into a high-temperature and medium-pressure state.
  • the refrigerant leaving the second compressor 40 enters the first compressor 38 and is compressed to a high temperature and high pressure state.
  • the refrigerant exiting the first compressor 38 dissipates heat in the radiator 29 and enters a low temperature and high pressure state.
  • the heat of the refrigerant is transmitted to the water via the radiator 29, and the water is heated.
  • the refrigerant exiting the radiator 29 is decompressed by the expander 30 and becomes a low temperature and low pressure state.
  • the power generated when the refrigerant is decompressed by the expander 30 is recovered by the drive shaft 39 and used by the second compressor 40.
  • the refrigerant exiting the expander 30 absorbs heat by the evaporator 31 and evaporates to a low pressure, which changes from a low dryness state to a high dryness state.
  • the blower blows air toward the evaporator 31, the refrigerant inside the evaporator 31 can effectively absorb heat.
  • the refrigerant that has left the evaporator 31 enters the second compressor 40 again.
  • the second compressor 40 is provided in the refrigerant flow path between the evaporator 31 and the first compressor 38, and the expansion is performed. Since the drive shaft 39 is connected between the compressor 30 and the second compressor 40, the power generated when the refrigerant is decompressed by the expander 30 can be used by the second compressor 40. it can. Other effects are the same as those of the first embodiment.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
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  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention porte sur un dispositif à cycle de réfrigération dans lequel, même si une puissance importante est requise pour démarrer un détendeur, ce dernier peut être démarré par le démarrage d'un compresseur. Un climatiseur comporte un premier compresseur (1) pour comprimer un fluide frigorigène, un échangeur de chaleur extérieur (2) pour dissiper la chaleur du fluide frigorigène comprimé par le premier compresseur (1), un détendeur (3) pour réduire la pression du fluide frigorigène qui est passé à travers l'échangeur de chaleur extérieur (2), un échangeur de chaleur intérieur (4) dans lequel le fluide frigorigène dont la pression a été réduite par le détendeur (3) est amené à s'évaporer, et un arbre d'entraînement (5) pour récupérer la puissance générée lorsque le fluide frigorigène voit sa pression réduite par le détendeur (3). Le climatiseur comporte une vanne tout ou rien (6) montée entre le détendeur (3) et l'échangeur de chaleur intérieur (4) et commandant le déplacement du fluide frigorigène du détendeur (3) à l'échangeur de chaleur intérieur (4). Après que le premier compresseur (1) a démarré en vue d'augmenter la pression du fluide frigorigène dans le détendeur (3) jusqu'à une pression critique ou supérieure, la vanne tout ou rien (6) est ouverte et le détendeur (3) est démarré par la pression dynamique du fluide frigorigène.
PCT/JP2009/056662 2008-05-22 2009-03-31 Dispositif à cycle de réfrigération WO2009142067A1 (fr)

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JP2010512969A JP4906962B2 (ja) 2008-05-22 2009-03-31 冷凍サイクル装置
CN2009801149519A CN102016444B (zh) 2008-05-22 2009-03-31 制冷循环装置
US12/921,848 US20110023533A1 (en) 2008-05-22 2009-03-31 Refrigerating cycle device
EP09750429.4A EP2306120B1 (fr) 2008-05-22 2009-03-31 Dispositif à cycle de réfrigération

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JP2008134298 2008-05-22

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CN102016444A (zh) 2011-04-13
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CN102016444B (zh) 2013-05-15
EP2306120A1 (fr) 2011-04-06

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