WO2009098862A1 - Refrigeration device - Google Patents

Refrigeration device Download PDF

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Publication number
WO2009098862A1
WO2009098862A1 PCT/JP2009/000405 JP2009000405W WO2009098862A1 WO 2009098862 A1 WO2009098862 A1 WO 2009098862A1 JP 2009000405 W JP2009000405 W JP 2009000405W WO 2009098862 A1 WO2009098862 A1 WO 2009098862A1
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WO
WIPO (PCT)
Prior art keywords
oil
refrigerant
compression
compression mechanism
heat exchanger
Prior art date
Application number
PCT/JP2009/000405
Other languages
French (fr)
Japanese (ja)
Inventor
Tetsuya Okamoto
Kazuhiro Furusho
Takayuki Kawano
Shinichi Kasahara
Masakazu Okamoto
Takahiro Yamaguchi
Michio Moriwaki
Syuuji Furui
Atsushi Yoshimi
Shuuji Fujimoto
Original Assignee
Daikin Industries, Ltd.
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 Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to CN2009801042738A priority Critical patent/CN101939599A/en
Priority to AU2009210984A priority patent/AU2009210984B2/en
Priority to KR1020107019618A priority patent/KR101185307B1/en
Priority to US12/812,111 priority patent/US20100275634A1/en
Priority to EP09707244.1A priority patent/EP2251621A4/en
Publication of WO2009098862A1 publication Critical patent/WO2009098862A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B2313/027—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
    • F25B2400/14—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
    • 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
    • F25B2400/141—Power generation using energy from the expansion of the refrigerant the extracted power is not recycled back in the refrigerant circuit

Definitions

  • the present invention relates to a refrigeration apparatus including a refrigerant circuit that performs a refrigeration cycle by circulating refrigerant, and particularly relates to energy saving measures for the refrigeration apparatus.
  • Patent Document 1 discloses this type of refrigeration apparatus.
  • a compressor, a cyclone (oil separator), a radiator, a use side heat exchanger, and the like are connected to the refrigerant circuit of the refrigeration apparatus to form a refrigerant circuit.
  • the high-pressure refrigerant compressed by the compressor flows into the oil separator.
  • oil separator oil is separated from the high-pressure refrigerant.
  • the separated oil is cooled through a radiator and then supplied to the suction side of the compressor.
  • the refrigerant is cooled by the oil. For this reason, during the compression stroke of the compressor, the temperature of the refrigerant hardly rises, and the refrigerant is compressed in a state close to isothermal compression.
  • the present invention has been made in view of such a point, and an object thereof is to provide a refrigeration apparatus capable of effectively reducing the power of the compression mechanism.
  • a first invention is directed to a refrigeration apparatus including a refrigerant circuit (11) connected to a compression mechanism (20) to perform a refrigeration cycle.
  • the refrigerant circuit (11) is compressed by the compression mechanism (20).
  • Oil separating means (60) for separating oil from the high-pressure refrigerant, and oil separated by the oil separating means (60) so as to cool the refrigerant in the compression stroke of the compression mechanism (20).
  • an oil supply circuit (70) for supplying oil to the oil supply circuit (70), and a recovery mechanism (40) for recovering the energy of the oil flowing through the oil supply circuit (70). It is characterized by.
  • high-pressure oil is separated from the high-pressure refrigerant compressed by the compression mechanism (20) by the oil separation means (60).
  • the separated oil is supplied to the compression mechanism (20) through the oil supply circuit (70) so as to cool the refrigerant in the compression stroke of the compression mechanism (20).
  • the oil supply circuit (70) of the present invention is provided with a recovery mechanism (40) for recovering oil energy.
  • the oil separated from the high-pressure refrigerant by the oil separation means (60) is used to convert the power used for boosting the oil in the compression mechanism (20) into kinetic energy, potential energy, pressure energy, etc. I have it as energy.
  • the recovery mechanism (40) recovers the power of the oil after separation (that is, the energy of the oil). For this reason, even if a large amount of oil is supplied to the compression mechanism (20) via the oil supply circuit (70) and the power required for boosting the oil increases, the power required for boosting the oil is recovered by the recovery mechanism (40 ) Can be recovered. Therefore, in the present invention, the power required for compressing the refrigerant can be reduced by supplying a large amount of oil to the compression mechanism (20), and the power required for pressurizing the large amount of oil is not wasted.
  • the oil supply circuit (70) is configured so that the refrigerant is isothermally compressed during at least a part of the compression stroke of the compression mechanism (20). It is characterized by supplying oil to (20).
  • the oil supply circuit (70) of the second invention supplies oil to the compression mechanism (20) so that the refrigerant is isothermally compressed during at least a part of the compression stroke of the compression mechanism (20).
  • the temperature of the refrigerant hardly rises, thereby reducing the power required for the compression of the refrigerant in the compression mechanism (20).
  • the power required to pressurize the oil in the compression mechanism (20) increases.
  • the recovery mechanism (40) recovers the energy of the oil in the oil supply circuit (70), the power required for boosting the oil in the compression mechanism (20) is not wasted.
  • the refrigerant circuit (11) is configured to perform a refrigeration cycle in which the refrigerant is compressed to a critical pressure or higher by the compression mechanism (20). It is a feature.
  • a refrigeration cycle is performed in which the high-pressure refrigerant is equal to or higher than the critical pressure.
  • a refrigeration cycle hereinafter referred to as a supercritical cycle
  • the effect of reducing the compression power of the refrigerant due to the introduction of low-temperature oil into the compression mechanism (20) is increased.
  • the refrigerant in the supercritical cycle, even if the refrigerant is cooled in the compression stroke of the compression mechanism (20), the refrigerant is not pressurized and condensed as superheated steam. That is, in the compression stroke of the supercritical cycle, even if the refrigerant is cooled, the refrigerant does not reach the gas-liquid two-phase region (condensation region). Therefore, in the present invention, compared with a general refrigeration cycle (a refrigeration cycle in which the refrigerant is compressed in a range smaller than the critical pressure), the effect of reducing the compression power of the refrigerant by so-called isothermal compression can be improved.
  • a general refrigeration cycle a refrigeration cycle in which the refrigerant is compressed in a range smaller than the critical pressure
  • the oil supply circuit (70) supplies oil during the compression stroke of the compression mechanism (20). It is characterized by being.
  • the oil cooled to a relatively low temperature by the cooling means (80) is in the middle of the compression stroke of the compression mechanism (20) (that is, the intermediate pressure between the suction pressure and the discharge pressure of the refrigerant).
  • the refrigerant has already been compressed (adiabatic compression) and heated up. Therefore, it is possible to avoid the refrigerant from becoming cooler than the oil by introducing the low-temperature oil into this portion. Thereby, it can avoid that a refrigerant
  • coolant is heated with oil and overheated in a subsequent compression process. Therefore, it can be avoided that the effect of reducing the compression power of the refrigerant is impaired due to such overheat compression.
  • the oil supply circuit (70) is configured to supply oil to the suction side of the compression mechanism (20).
  • the oil that has been cooled by the cooling means (80) and has a relatively low temperature is supplied to the suction side of the compression mechanism (20).
  • the recovery mechanism (40) includes a movable part (50) that is rotationally driven by oil, and the movable part (50). And an output shaft (42) to be connected.
  • the recovery mechanism (40) is provided with the movable part (50) and the output shaft (42).
  • the movable part (50) is rotationally driven by the oil separated from the high-pressure refrigerant.
  • the output shaft (42) connected to the movable part (50) also rotates.
  • Such rotational power of the output shaft (42) is used, for example, as driving power for a generator or other equipment.
  • the compression mechanism (20) is configured to be connected to and driven by the output shaft (42) of the recovery mechanism (40). It is a feature.
  • the power of oil recovered by the recovery mechanism (40) (that is, the energy of the oil) is used as a power source of the compression mechanism (20) via the output shaft (42).
  • the compression mechanism (20) The power required to pressurize the oil increases.
  • the power recovered by the recovery mechanism (40) increases, and the power of the compression mechanism (20) decreases by the increase in this power. .
  • the low-temperature oil is positively introduced into the compression mechanism (20), so that the compression power of the refrigerant can be effectively reduced and the power that can be recovered by the recovery mechanism (40) can be increased.
  • power is effectively reduced as a whole of the compression mechanism (20), and the efficiency of the compression mechanism (20) is effectively improved.
  • the refrigerant circuit (11) is driven to rotate by the refrigerant and is connected to the output shaft (42) of the recovery mechanism (40).
  • An expansion mechanism (30) having a portion is provided.
  • the refrigerant circuit (11) of the eighth invention is provided with an expansion mechanism (30) that is rotationally driven by the refrigerant.
  • the movable part of the expansion mechanism (30) is also coupled to the output shaft (42) of the recovery mechanism (40). That is, the output shaft (42) is rotationally driven by both the power recovered by the recovery mechanism (40) and the power (ie, expansion power) obtained by the expansion of the refrigerant by the expansion mechanism (30). .
  • Such rotational power of the output shaft (42) is used for driving power of the compression mechanism (20) of the seventh invention.
  • a generator (45) that is driven in connection with the output shaft (42) of the recovery mechanism (40) is provided. It is characterized by this.
  • the energy of the oil recovered by the recovery mechanism (40) is used as drive power for the generator (45) via the output shaft (42).
  • electric power can be generated by the generator (45), and this electric power can be used as a power source for other component machines and the like.
  • a tenth aspect of the invention is the refrigeration apparatus according to any one of the first to ninth aspects of the invention, wherein the oil supply circuit (70) includes oil cooling heat for cooling the oil separated by the oil separation means (60).
  • a switch (80) is connected.
  • the oil supply circuit (70) is provided with the oil cooling heat exchanger (80). That is, the oil separated by the oil separation means (60) is cooled by exchanging heat with a predetermined fluid by the oil cooling heat exchanger (80). The cooled oil is supplied to the compression mechanism (20) in order to cool the refrigerant during the compression stroke of the compression mechanism (20).
  • An eleventh invention is the refrigeration apparatus of the tenth invention, wherein the refrigerant circuit (11) has an indoor heat exchanger (13) installed indoors and flows through the indoor heat exchanger (13).
  • the oil cooling heat exchanger (80) is installed indoors and is configured to release oil heat to the indoor air during the heating operation. It is characterized by being.
  • the refrigerant circuit (11) of the eleventh invention is configured to perform a heating operation for heating indoor air. That is, indoor heating is performed by sending the refrigerant compressed by the compression mechanism (20) to the indoor heat exchanger (13) and releasing the heat of the refrigerant into the indoor air.
  • the oil cooling heat exchanger (80) of the present invention functions as an indoor auxiliary heater when installed indoors. That is, during heating operation, when the oil separated by the oil separation means (60) flows through the oil cooling heat exchanger (80), the oil in the oil cooling heat exchanger (80) and the room air exchange heat, Oil heat is released into the room air. Thereby, since indoor air is heated, indoor heating capability improves. At the same time, in the oil cooling heat exchanger (80), the oil is cooled by room air. The cooled oil is supplied to the compression mechanism (20) in order to cool the refrigerant during the compression stroke of the compression mechanism (20).
  • a twelfth invention is the refrigeration apparatus of the tenth invention, wherein the refrigerant circuit (11) has an indoor heat exchanger (13) installed indoors and flows through the indoor heat exchanger (13).
  • the air supply circuit (70) includes a heating operation for heating the indoor air and a cooling operation for cooling the indoor air with the refrigerant flowing through the indoor heat exchanger (13).
  • a first oil-cooling heat exchanger (80a) that is installed in the room and releases heat of the oil to the room air during the heating operation, and is disposed outside and discharges the heat of the oil to the room air during the cooling operation.
  • the second oil cooling heat exchanger (80b) is connected.
  • the refrigerant circuit (11) of the twelfth aspect of the invention is configured to be switched between a heating operation for heating the indoor air and a cooling operation for cooling the indoor air. That is, indoor heating is performed by sending the refrigerant compressed by the compression mechanism (20) to the indoor heat exchanger (13) and releasing the heat of the refrigerant into the indoor air. Moreover, indoor cooling is performed by sending low-pressure gas refrigerant to the indoor heat exchanger (13) and absorbing heat from the indoor air to the refrigerant.
  • the oil supply circuit (70) of the present invention is provided with a first oil cooling heat exchanger (80a) installed indoors and a second oil cooling heat exchanger (80b) installed outdoor. .
  • the oil separated by the oil separation means (60) flows through the first oil cooling heat exchanger (80a), and the heat of the oil in the first oil cooling heat exchanger (80a) is transferred to the room air. Released. Thereby, the indoor heating capability improves.
  • the oil separated by the oil separation means (60) flows through the second oil cooling heat exchanger (80b), and the heat of the oil in the second oil cooling heat exchanger (80b) is the outdoor air. Is released. Thereby, since the heat of oil is not discharged
  • the power required for compressing the refrigerant in the compression mechanism (20) is reduced by supplying oil to the compression mechanism (20) by the oil supply circuit (70) and cooling the oil in the compression stroke.
  • the energy of the oil flowing through the oil supply circuit (70) is recovered by the recovery mechanism (40).
  • coolant in a compression process can be reliably cooled with oil, the compression power of a refrigerant
  • the temperature of the refrigerant discharged from the compression mechanism (20) can be kept low.
  • the system abnormality of the refrigeration apparatus and the damage to the compression mechanism (20) due to the temperature rise of the discharged refrigerant can be avoided in advance.
  • the temperature rise of each sliding part of a compression mechanism (20) can also be suppressed, the seizing of each sliding part can be prevented reliably, and deterioration of oil (refrigeration machine oil) can also be prevented. As a result, the reliability of the refrigeration apparatus can be further improved.
  • the temperature around the motor of the compression mechanism (20) can be kept low.
  • the efficiency of the motor can be improved and the input of the compression mechanism (20) can be further reduced.
  • oil is supplied so that the refrigerant is isothermally compressed during at least a part of the compression stroke of the compression mechanism (20), so that a relatively large amount of oil is supplied to the compression mechanism (20). Need to be supplied to.
  • the recovery mechanism (40) since the recovery mechanism (40) recovers energy from such a large amount of oil as power, the compression power of the refrigerant can be effectively reduced by isothermal compression, and the recovery mechanism ( The power (ie energy) recovered by 40) can be increased.
  • the low temperature oil is introduced into the compression mechanism (20) while performing a supercritical cycle in which the high pressure refrigerant is compressed to a critical pressure or higher. Accordingly, in the compression stroke of the compression mechanism (20), the refrigerant can be compressed in a state close to an isothermal change without condensing the refrigerant, and the compression power of the refrigerant can be effectively reduced.
  • low temperature oil is supplied during the compression of the compression mechanism (20).
  • the refrigerant coolant after temperature rising can be cooled with oil.
  • the refrigerant can be reliably cooled by the low-temperature oil, and the effect of reducing the compression power by isothermal compression can be further improved.
  • low temperature oil is supplied to the suction side of the compression mechanism (20).
  • coolant can be cooled with low temperature oil from the start of the compression process of a compression mechanism (20), and the reduction effect of the compression power by isothermal compression can further be improved.
  • the output shaft (42) can be rotated by the energy of the oil recovered by the recovery mechanism (40), and this rotational power can be used as a predetermined power source.
  • the rotational power of an output shaft (42) can be utilized as a drive power of a compression mechanism (20).
  • the output shaft (42) can be rotated by both the energy of the refrigerant recovered by the expansion mechanism (30) and the energy of the oil recovered by the recovery mechanism (40), The rotational power generated at the output shaft (42) can be increased.
  • electric power can be generated by the generator (45) using the rotational power of the output shaft (42), and this electric power can be used as a power source for each element machine of the refrigeration apparatus. It can be used as appropriate.
  • the oil separated by the oil separation means (60) is cooled by the oil cooling heat exchanger (80), and the cooled oil is supplied to the compression mechanism (20).
  • the refrigerant in the compression stroke can be effectively cooled.
  • the oil in the oil cooling heat exchanger (80) is discharged into the room to cool the oil.
  • indoor air can be heated with both a refrigerant
  • the room heating capacity can be sufficiently obtained.
  • the heat of the oil in the first oil cooling heat exchanger (80a) is discharged into the room to cool the oil, and during the indoor cooling operation, The heat of the oil in the second oil cooling heat exchanger (80b) is discharged to the outside to cool the oil.
  • indoor air can be heated with both a refrigerant
  • FIG. 1 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Embodiment 1.
  • FIG. 2 is an enlarged longitudinal sectional view of the recovery mechanism.
  • FIG. 3 is a cross-sectional view showing the inside of the recovery mechanism, and shows the operation of the piston.
  • FIG. 4 shows an ideal refrigeration cycle of the present embodiment.
  • FIG. 4 (A) shows a Ph diagram and
  • FIG. 4 (B) shows a PV diagram.
  • FIG. 5 shows a general refrigeration cycle.
  • FIG. 5 (A) shows a Ph diagram and FIG. 5 (B) shows a PV diagram.
  • FIG. 6 is a graph showing the relationship between the oil injection amount and the power of the compression mechanism.
  • FIG. 7 is a graph showing the relationship between the oil injection amount and the COP improvement rate.
  • FIG. 1 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Embodiment 1.
  • FIG. 2 is an enlarged longitudinal sectional view of the recovery mechanism
  • FIG. 8 is a piping system diagram illustrating a schematic configuration of an air-conditioning apparatus according to a modification of the first embodiment.
  • FIG. 9 is a piping diagram illustrating a schematic configuration of the air-conditioning apparatus according to Embodiment 2.
  • FIG. 10 is a piping diagram illustrating a schematic configuration of the air-conditioning apparatus according to Embodiment 3.
  • FIG. 11 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Embodiment 4.
  • FIG. 12 is a cross-sectional view illustrating a first state during operation of the compression mechanism in the air-conditioning apparatus according to Embodiment 5.
  • FIG. 13 is a cross-sectional view illustrating a second state during operation of the compression mechanism in the air-conditioning apparatus according to Embodiment 5.
  • FIG. 14 is a block diagram showing the configuration of the controller.
  • FIG. 15 is a block diagram illustrating a configuration of a controller of the air-conditioning apparatus according to Embodiment 6.
  • FIG. 16 is a cross-sectional view showing a first state of the compression mechanism.
  • FIG. 17 is a cross-sectional view showing a second state of the compression mechanism.
  • FIG. 18 is a graph showing the power reduction effect by isothermal compression in the compressor of the comparative example.
  • FIG. 19 is a graph showing the power reduction effect by isothermal compression in the compression mechanism of the sixth embodiment.
  • FIG. 20 is a piping diagram illustrating a schematic configuration of the air-conditioning apparatus according to Embodiment 7.
  • FIG. 20 is a piping diagram illustrating a schematic configuration of the air-conditioning apparatus according to Embodiment 7.
  • FIG. 21 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus (during heating operation) according to the eighth embodiment.
  • FIG. 22 is a piping diagram illustrating a schematic configuration of the air-conditioning apparatus (during cooling operation) according to the eighth embodiment.
  • FIG. 23 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Modification 1 of the other embodiment.
  • FIG. 24 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Modification 2 of the other embodiment.
  • FIG. 25 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Modification 3 of the other embodiment.
  • FIG. 26 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Modification 4 of the other embodiment.
  • FIG. 27 is a Ph diagram illustrating an example of another refrigeration cycle in which isothermal compression is performed.
  • FIG. 28 is a cross-sectional view of a compression mechanism according to a comparative example.
  • Air conditioning equipment (refrigeration equipment) 11 Refrigerant circuit 12 Indoor heat exchanger 13 Indoor heat exchanger 20 Compression mechanism 30 Expansion mechanism 40 Recovery mechanism 42 Output shaft 45 Generator 50 piston (movable part) 60 Oil separator (Oil separation means) 70 Oil introduction pipe (oil supply circuit) 80 Oil cooler (oil cooling heat exchanger) 80a Indoor oil cooler (first oil cooling heat exchanger) 80b Outdoor oil cooler (second oil cooling heat exchanger)
  • the refrigeration apparatus constitutes an air conditioner (10) that performs indoor air conditioning.
  • the air conditioner (10) is configured to switch between a cooling operation and a heating operation.
  • the air conditioner (10) includes a refrigerant circuit (11).
  • a refrigeration cycle is performed by circulating the refrigerant.
  • the refrigerant circuit (11) is filled with carbon dioxide (CO 2 ) as a refrigerant.
  • CO 2 carbon dioxide
  • a refrigeration cycle (so-called supercritical cycle) in which the refrigerant is compressed to a critical pressure or higher is performed.
  • the refrigerant circuit (11) contains oil (refrigerating machine oil) made of polyalkylene glycol (PAG).
  • the refrigerant circuit (11) includes an oil power recovery type compression unit (C / O), an expansion unit (E), an outdoor heat exchanger (12), an indoor heat exchanger (13), and a first four-way switching.
  • a valve (14) and a second four-way switching valve (15) are provided.
  • the refrigerant circuit (11) is provided with an oil separator (60), an oil introduction path (70), and an oil cooler (80).
  • the oil power recovery type compression unit (C / O) includes a compression mechanism (20), a recovery mechanism (40), and an electric motor (25) housed in a casing (not shown).
  • the compression mechanism (20) constitutes a rotary positive displacement compressor.
  • the recovery mechanism (40) has a main body (41) and an output shaft (42).
  • the main body (41) of the recovery mechanism (40) constitutes a rotary positive displacement fluid machine.
  • the output shaft (42) connects the compression mechanism (20) and the main body (41).
  • the electric motor (25) constitutes a motor that rotationally drives the output shaft (42), and is configured as an inverter type in which the output frequency (that is, the rotational speed of the output shaft) is variable.
  • the oil power recovery type compression unit (C / O) has a suction pipe (22) for sucking refrigerant into the compression mechanism (20) and a discharge pipe for discharging refrigerant compressed by the compression mechanism (20). (23) is provided.
  • the oil power recovery type compression unit (C / O) has an oil inflow pipe (43) through which oil (refrigeration oil) flows into the main body (41) of the recovery mechanism (40), and the main body ( 41) and an oil spill pipe (44) for spilling the oil.
  • the expansion unit (E) includes an expansion mechanism (30), an expansion side output shaft (31), and an expansion side generator (35) housed in a casing (not shown).
  • the expansion mechanism (30) constitutes a rotary positive displacement expansion mechanism.
  • the refrigerant expands and decompresses in the expansion chamber.
  • a piston (not shown) as a movable portion is rotationally driven by the refrigerant expanding in the expansion chamber, and the expansion-side output shaft (31) connected to the piston is further rotationally driven.
  • an expansion side generator (35) is driven and electric power generation is performed. That is, the expansion-side generator (35) constitutes a drive target that is driven by being connected to the expansion-side output shaft (31) of the expansion mechanism (30).
  • the electric power generated by the expansion unit (E) is used as power for the oil power recovery type compression unit (C / O) and other element machines.
  • the expansion unit (E) is provided with an inflow pipe (33) for allowing the refrigerant to flow into the expansion mechanism (30) and an outflow pipe (34) for allowing the refrigerant to flow out from the expansion mechanism (30). ing.
  • the outdoor heat exchanger (12) is an air heat exchanger for exchanging heat between the refrigerant and outdoor air.
  • the indoor heat exchanger (13) is an air heat exchanger for exchanging heat between the refrigerant and room air.
  • the first four-way switching valve (14) and the second four-way switching valve (15) have first to fourth ports, respectively.
  • a first port is connected to the discharge pipe (23) via a discharge line (18), and a second port is connected to the suction pipe (17) via a suction line (17). 22) is connected.
  • the third port is connected to one end of the outdoor heat exchanger (12), and the fourth port is connected to one end of the indoor heat exchanger (13).
  • the first port is connected to the inflow pipe (33), and the second port is connected to the outflow pipe (34).
  • the third port is connected to the other end of the outdoor heat exchanger (12), and the fourth port is connected to the other end of the indoor heat exchanger (13). Yes.
  • the first four-way switching valve (14) and the second four-way switching valve (15) are respectively a first port and a third port that communicate with each other and a second port and a fourth port that communicate with each other.
  • 1 state state indicated by a solid line in FIG. 1
  • 2nd state state indicated by a broken line in FIG. 1 in which the first port and the fourth port communicate with each other and the second port and the third port communicate with each other. It is comprised so that it may switch to.
  • the oil separator (60) is provided in the middle of the discharge line (18).
  • the oil separator (60) is composed of a vertically long, substantially cylindrical sealed container, and constitutes an oil separating means for separating oil from the high-pressure refrigerant.
  • the oil separator (60) is connected with a refrigerant / oil inflow pipe (61) at its body, with a refrigerant discharge pipe (62) at its top and with an oil discharge pipe (63) at its bottom. ing.
  • oil is separated from the refrigerant flowing in from the refrigerant / oil inflow pipe (61).
  • the oil separator (60) there are a method of centrifugal separation of oil using a swirl flow, a method of sedimentation separation of oil using a specific gravity difference between refrigerant and oil, and the like. Can be mentioned.
  • the refrigerant after the oil is separated flows out of the refrigerant discharge pipe (62), and the oil after the separation flows out of the oil discharge pipe (63).
  • the oil introduction path (70) constitutes an oil supply circuit for supplying the oil separated by the oil separator (60) to the compression mechanism (20).
  • the oil introduction path (70) includes a first oil guide pipe (71) and a second oil guide pipe (72).
  • the first oil guiding pipe (71) has a start end connected to the oil discharge pipe (63) of the oil separator (60) and a terminal end connected to the oil inflow pipe (43).
  • the first oil guide pipe (71) is provided with the oil cooler (80).
  • the oil cooler (80) is a cooling means for cooling the oil separated by the oil separator (60), and constitutes an oil cooling heat exchanger.
  • the oil cooler (80) of the present embodiment is configured by an air-cooled heat exchanger.
  • the second oil guide pipe (72) has its start end connected to the oil outflow pipe (44) and its end connected to the oil injection port (24) of the compression mechanism (20).
  • the oil injection port (24) of the compression mechanism (20) opens in the middle of the compression stroke in the compression chamber. That is, the oil introduction path (70) of the present embodiment is connected to the compression mechanism (20) so as to supply the oil separated by the oil separator (60) in the middle of the compression stroke of the compression mechanism (20). Yes.
  • the oil introduction path (70) configured as described above is an oil that supplies the oil separated by the oil separation means (60) to the compression mechanism (20) so as to cool the refrigerant during the compression stroke of the compression mechanism (20).
  • a supply circuit is configured.
  • the oil introduction path (70) is configured to supply oil to the compression mechanism (20) so that the refrigerant is isothermally compressed during at least a part of the compression stroke of the compression mechanism (20).
  • the configuration of the recovery mechanism (40) will be further described with reference to FIGS.
  • the recovery mechanism (40) recovers the power of the oil (that is, the energy of the oil).
  • the oil separated from the high-pressure refrigerant has the power used to pressurize the oil in the compression mechanism (20) as energy such as kinetic energy, potential energy, and pressure energy. Therefore, the recovery mechanism (40) recovers such oil energy as power.
  • the main body (41) of the recovery mechanism (40) is constituted by a so-called oscillating piston type rotary fluid machine.
  • the output shaft (42) has one end connected to the main body (41) and the other end connected to the movable part (piston) of the compression mechanism (20).
  • the compression mechanism (20) constitutes a drive target that is driven by being connected to the output shaft (42) of the recovery mechanism (40).
  • the output shaft (42) is formed with a main shaft portion (42a) and an eccentric portion (42b).
  • the eccentric part (42b) is eccentric by a predetermined amount with respect to the main shaft part (42a) and is configured to have a larger diameter than the main shaft part (42a).
  • the main body (41) of the recovery mechanism is provided with a front head (46), a cylinder (47), and a rear head (48) in that order from the bottom to the top.
  • the cylinder (47) is formed in a cylindrical shape through which the output shaft (42) passes vertically.
  • the cylinder (47) has a lower end closed by the front head (46) and an upper end closed by the rear head (48).
  • a piston (50) as a movable part is accommodated in the cylinder (47) (cylinder chamber).
  • the piston (50) is formed in an annular shape or a cylindrical shape.
  • the eccentric portion (42b) of the output shaft (42) is engaged and connected to the inside of the piston (50).
  • the piston (50) has its outer peripheral surface in sliding contact with the inner peripheral surface of the cylinder (47), one end surface in sliding contact with the front head (46), and the other end surface in contact with the rear head (48).
  • An oil chamber (49) is formed in the cylinder (47) between its inner peripheral surface and the outer peripheral surface of the piston (50).
  • the oil chamber (49) communicates with the oil inflow pipe (43) and the oil outflow pipe (44).
  • the piston (50) is integrally provided with a blade (51).
  • the blade (51) is formed in a plate shape extending in the radial direction of the piston (50), and projects outward from the outer peripheral surface of the piston (50).
  • the blade (51) is inserted into the blade groove (52) of the cylinder (47).
  • the blade groove (52) of the cylinder (47) penetrates the cylinder (47) in the thickness direction, and opens to the inner peripheral surface of the cylinder (47).
  • the cylinder (47) is provided with a pair of bushes (53).
  • Each bush (53) is a small piece formed such that the inner surface is a flat surface and the outer surface is a circular arc surface.
  • the pair of bushes (53) are inserted into the bush holes (54) and sandwich the blade (51).
  • the inner surface of the bush (53) is in sliding contact with the blade (51), and the outer surface of the bush (53) slides with the cylinder (47).
  • the blade (51) integrated with the piston (50) is supported by the cylinder (47) via the bush (53), and can rotate and advance and retract with respect to the cylinder (47).
  • the oil chamber (49) in the cylinder (47) is partitioned by the piston (50) and the blade (51).
  • the left chamber of the blade (51) in FIG. 3 communicates with the oil inflow pipe (43), and the right chamber communicates with the oil outflow pipe (44).
  • the operation of the air conditioner (10) according to Embodiment 1 will be described.
  • the air conditioner (10) can perform a cooling operation and a heating operation according to the settings of the first four-way switching valve (14) and the second four-way switching valve (15).
  • First, the basic operation during the cooling operation of the air conditioner (10) will be described.
  • the first four-way switching valve (14) and the second four-way switching valve (15) are set to the first state (the state indicated by the solid line in FIG. 1), and the refrigerant circulates in the refrigerant circuit (11).
  • a compression refrigeration cycle is performed.
  • a refrigeration cycle in which the outdoor heat exchanger (12) serves as a radiator (condenser) and the indoor heat exchanger (13) serves as an evaporator is performed.
  • the high pressure is set to a value higher than the critical pressure of carbon dioxide, which is a refrigerant, and a so-called supercritical cycle is performed.
  • the compression mechanism (20) In the oil power recovery type compression unit (C / O), the compression mechanism (20) is rotationally driven by the electric motor (25). In the compression mechanism (20), the refrigerant sucked into the compression chamber from the suction pipe (22) is compressed, and the compressed refrigerant is discharged from the discharge pipe (23). The refrigerant discharged from the compression mechanism (20) flows through the discharge line (18) and flows into the oil separator (60) through the refrigerant / oil inflow pipe (61).
  • the oil separator (60) Inside the oil separator (60), the oil is separated from the refrigerant, the refrigerant after the oil is separated accumulates at the top, and the separated oil accumulates at the bottom.
  • the separated refrigerant flows out of the refrigerant discharge pipe (62) and flows through the outdoor heat exchanger (12).
  • the outdoor heat exchanger (12) In the outdoor heat exchanger (12), the high-pressure refrigerant radiates heat to the outdoor air.
  • the refrigerant that has flowed out of the outdoor heat exchanger (12) flows into the expansion mechanism (30) of the expansion unit (E) through the inflow pipe (33).
  • the expansion mechanism (30) the high-pressure refrigerant expands in the expansion chamber, whereby the expansion-side output shaft (31) is rotationally driven. As a result, the expansion-side generator (35) is driven and electric power is generated from the expansion-side generator (35). This electric power is supplied to the compression mechanism (20) and other element machines.
  • the refrigerant expanded by the expansion mechanism (30) is sent out from the expansion unit (E) through the outflow pipe (34).
  • the refrigerant that has flowed out of the expansion unit (E) flows through the indoor heat exchanger (13).
  • the refrigerant absorbs heat from the indoor air and evaporates. As a result, the room air is cooled and cooling is performed.
  • the refrigerant flowing out of the indoor heat exchanger (13) is sucked into the compression mechanism (20) through the suction pipe (22) and compressed again.
  • an oil injection operation is performed in order to improve the coefficient of performance (COP) of the air conditioner (10).
  • the oil separated by the oil separator (60) flows through the first oil guide pipe (71) through the oil discharge pipe (63).
  • This refrigerant is cooled to a predetermined temperature by the oil cooler (80).
  • the cooled oil flows into the main body (41) of the recovery mechanism (40) of the oil power recovery type compression unit (C / O) through the oil inflow pipe (43).
  • the piston (50) In the main body (41) of the recovery mechanism (40), the piston (50) is rotationally driven by the oil flowing through the oil chamber (49), and the piston (50) moves inside the cylinder (47) in FIG. (B) ⁇ (C) ⁇ (D) ⁇ (A) ⁇ . With the eccentric rotation of the piston (50), the eccentric portion (42b) and further the main shaft portion (42a) are rotationally driven. As a result, this rotational power is used as driving power for driving the compression mechanism (20). As described above, in the oil power recovery type compression unit (C / O), the energy of the oil recovered by the recovery mechanism (40) is recovered as drive power of the compression mechanism (20), and the compression mechanism (20) Power is reduced.
  • the oil whose energy has been recovered in the oil chamber (49) is depressurized to a predetermined pressure and then flows out from the main body (41) of the recovery mechanism (40) through the oil outflow pipe (44).
  • the oil after flowing out flows into the oil injection port (24) of the compression mechanism (20) through the second oil guide pipe (72).
  • the compression mechanism (20) low temperature oil is supplied during the compression stroke in the compression chamber, and an oil injection operation is performed.
  • FIG. 4 (A) is a Ph diagram showing a refrigeration cycle in ideal isothermal compression
  • FIG. 4 (B) shows a PV corresponding to the refrigeration cycle in FIG. 4 (A).
  • the refrigerant is compressed along an isotherm (for example, about 40 ° C.) shown in FIG. 4A and reaches a target high pressure (point C).
  • a target high pressure point C
  • the power required to compress the refrigerant by the compression mechanism (20) is effectively reduced.
  • a part of the compression process from the compression of the low-pressure refrigerant to the high-pressure refrigerant that is, the process from the point A to the point C).
  • the refrigerant is isothermally compressed during the period from point B to point C.
  • the supercritical cycle is performed using carbon dioxide as a refrigerant.
  • the compression power reduction effect of the compression mechanism (20) is improved. This will be described below.
  • the refrigerant circuit (11) of the present embodiment As described above, the refrigerant is compressed in the compression stroke so that the carbon dioxide becomes equal to or higher than the critical pressure (pressure indicated by the point cP in FIG. 4A). Yes. For this reason, it is possible to avoid the refrigerant reaching the gas-liquid two-phase region (condensation region) when the refrigerant is compressed while being cooled from the point B to the point C in the compression stroke. That is, in the supercritical cycle, it is possible to avoid the cold oil from being used for the condensation of the refrigerant, so that the refrigerant can be effectively lowered in temperature and the behavior of the refrigerant can be brought close to an isotherm.
  • the critical pressure pressure indicated by the point cP in FIG. 4A
  • the refrigerant is compressed in a range smaller than the critical pressure. Therefore, when the oil injection operation is applied to this refrigeration cycle, the refrigerant reaches the gas-liquid two-phase region (condensation region) when the refrigerant is compressed at point A1 and the refrigerant is cooled by oil from point B1. End up. As a result, in this refrigeration cycle, isothermal compression can be performed only in the range of point B1 to point C1.
  • the power of the oil is recovered by the recovery mechanism (40).
  • the compression mechanism (20) In addition to the compression power of the refrigerant (Wr in FIG. 6), the power required to pressurize the oil (Wo in FIG. 6) is consumed.
  • the compression power Wr of the refrigerant is reduced by the effect of isothermal compression by the oil injection operation. Accordingly, the compression power Wr of the refrigerant decreases as the amount of low-temperature oil (oil injection amount Goil) supplied to the compression mechanism (20) increases.
  • the oil injection amount Goil increases as described above, the compression power Wo required for pressurizing the oil increases in the compression mechanism (20).
  • the relationship between the overall power Wt (that is, Wr + Wo) and the oil injection amount Goil is as shown in FIG. 6, and the oil injection amount Goil is a predetermined value (Gb). If it is larger than the range, the overall power Wt of the compression mechanism (20) may increase.
  • the recovery mechanism (40) is used to recover the compression power Wo required for boosting the oil.
  • the compression power Wo required for boosting the oil also increases, but in the oil power recovery type compression unit (C / O), The power (energy) of the pressurized oil is recovered as drive power for the compression mechanism (20).
  • this air conditioner (10) even if the oil injection amount Goil is increased, a relatively high COP improvement rate (effect by isothermal compression) can be obtained with this air conditioner (10).
  • a high COP improvement rate can be obtained even if the amount of oil injection is increased.
  • Embodiment 1- oil is separated from the high-pressure refrigerant by the oil separator (60), and the energy of the oil is recovered by the recovery mechanism (40) and used as driving power for the compression mechanism (20). Yes. For this reason, the power required to pressurize the oil by the compression mechanism (20) can be recovered by the recovery mechanism (40), and the energy saving of the air conditioner (10) can be improved.
  • the oil separated by the oil separator (60) is cooled by the oil cooler (80), and the low temperature oil is supplied to the compression mechanism (20).
  • the refrigerant can be compressed so as to approach the isothermal compression behavior as shown in FIG. 4 (that is, the point A ⁇ the point B ⁇ the point C). It can be greatly reduced.
  • the cooling effect of the refrigerant is improved and the compression power of the refrigerant is further reduced, while the energy of the oil recovered by the recovery mechanism (40) is also increased.
  • the COP improvement rate of the air conditioner (10) can be greatly improved, and the energy saving performance can be further improved.
  • the oil injection amount (mass flow rate) for effectively improving the COP improvement rate of the air conditioner (10) is approximately the amount of refrigerant sucked into the compression mechanism (20) (mass flow rate).
  • the range is preferably 0.5 times or more and about 6.0 times or less.
  • the compression mechanism (20) by increasing the amount of oil injection in this way and actively introducing low temperature oil into the compression mechanism (20), the following secondary effects can be obtained. Specifically, first, the temperature rise of the refrigerant discharged from the compression mechanism (20) can be prevented, and system abnormality of the air conditioner (10) and mechanical damage to the compression mechanism (20) can be avoided. Further, in the compression mechanism (20), the sliding portions such as pistons and bearings are sufficiently lubricated, and the heat dissipation effect of the sliding portions is improved. As a result, increase in mechanical loss and seizure at these sliding portions can be prevented. Furthermore, in the compression mechanism (20), since the oil can be suppressed to a relatively low temperature, it is possible to avoid deterioration due to excessive oil temperature.
  • the ambient temperature can be suppressed to a relatively low temperature.
  • the temperature in the casing is also relatively low.
  • the low-temperature oil is introduced into the compression mechanism (20) while performing a supercritical cycle in which the high-pressure refrigerant is compressed to a critical pressure or higher.
  • the refrigerant in the compression stroke of the compression mechanism (20), the refrigerant can be compressed so as to approach the isotherm without condensing the refrigerant (see, for example, FIG. 4), and compared with a normal refrigeration cycle (see, for example, FIG. 5).
  • the compression power can be effectively reduced.
  • Embodiment 1 described above low temperature oil is supplied during the compression of the compression mechanism (20).
  • the refrigerant after the temperature rise can be cooled with oil.
  • coolant mixed with oil becomes temperature lower than oil, and it can prevent that a refrigerant
  • the refrigerant can be reliably cooled by the low-temperature oil, and the effect of reducing the compression power by isothermal compression can be further improved.
  • the expansion mechanism (30) composed of a positive displacement fluid machine is used as the expansion mechanism for expanding the refrigerant.
  • the refrigerant may be decompressed using an electronic expansion valve (38) whose opening degree is adjustable as an expansion mechanism.
  • Embodiment 2 of the Invention A second embodiment of the present invention will be described.
  • the configuration of the refrigerant circuit (11) is different from that of the first embodiment.
  • the compression mechanism (20) and the expansion mechanism (30) are integrated into the expansion / compression unit (C / E), and the recovery mechanism ( 40) is installed in the oil power recovery unit (O).
  • the expansion / compression unit (C / E) includes a compression mechanism (20), an expansion mechanism (30), an expansion side output shaft (31), and an electric motor (25) housed in a casing (not shown). It is configured.
  • the compression mechanism (20) and the expansion mechanism (30) are connected to each other via the expansion side output shaft (31). That is, in the expansion / compression unit (C / E), the energy of the refrigerant recovered by the expansion mechanism (30) is used as drive power for the compression mechanism (20).
  • the compression mechanism (20) constitutes a drive target that is driven by being connected to the expansion-side output shaft (31) of the expansion mechanism (30).
  • the oil power recovery unit (O) includes a recovery mechanism (40) and a generator (45) housed in a casing (not shown).
  • the output shaft (42) of the recovery mechanism (40) is connected to the generator (45).
  • the generator (45) is driven by the power of the oil recovered by the recovery mechanism (40) (that is, the energy of the oil), and electric power is generated by this generator (45). To do.
  • the electric power generated by the generator (45) is used as driving power for the compression mechanism (20) and other element machines.
  • the refrigerant compressed by the compression mechanism (20) of the compression / expansion unit (C / E) flows into the oil separator (60).
  • the refrigerant from which the oil has been separated by the oil separator (60) is radiated by the outdoor heat exchanger (12) and then expanded by the expansion mechanism (30) of the compression / expansion unit (C / E).
  • the power (that is, expansion power) obtained by the refrigerant expanding in the expansion mechanism (30) is used as drive power for the compression mechanism (20).
  • the refrigerant expanded by the expansion mechanism (30) is evaporated by the indoor heat exchanger (13) and used for indoor cooling, and then sucked into the compression mechanism (20) of the compression / expansion unit (C / E).
  • the oil separated by the oil separator (60) is cooled by the oil cooler (80) and then flows into the recovery mechanism (40) of the oil power recovery unit (O).
  • the recovery mechanism (40) the output shaft (42) is rotationally driven by the oil in the oil chamber (49), and the generator (45) is driven. As a result, electric power is generated by the generator (45).
  • the compression mechanism (20) the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm. As a result, the power required for refrigerant compression is reduced.
  • the compression power of the refrigerant is reduced by the isothermal compression effect, and the power of oil recovered from the oil after the pressure increase ( That is, the energy of oil) also increases.
  • the COP of the air conditioner (10) is effectively improved.
  • Embodiment 3 of the Invention will be described.
  • the configuration of the refrigerant circuit (11) is different from those in the above embodiments.
  • the compression mechanism (20) is incorporated in the compression unit (C), and the expansion mechanism (30) and the recovery mechanism (40) are integrated into oil.
  • the power recovery expansion unit (E / O) Built into the power recovery expansion unit (E / O).
  • the compression unit (C) includes a compression mechanism (20), a drive shaft (21), and an electric motor (25) housed in a casing (not shown).
  • the compression mechanism (20) and the electric motor (25) are connected to each other via the drive shaft (21). That is, in the compression unit (C), the compression mechanism (20) is driven by the electric motor (25).
  • the oil power recovery type expansion unit (E / O) includes an expansion mechanism (30), a recovery mechanism (40), and a generator (45) housed in a casing (not shown).
  • the expansion mechanism (30) is connected to an end portion of the output shaft (42) of the recovery mechanism (40), and a generator (45) is connected to an intermediate portion thereof. That is, in the oil power recovery type expansion unit (E / O), the refrigerant energy is recovered by the expansion mechanism (30), and the oil energy is recovered by the recovery mechanism (40). These energies are used as driving power for the generator (45) via the output shaft (42).
  • the generator (45) constitutes a drive target that is driven by being connected to the recovery mechanism (40) and the expansion mechanism (30) via the output shaft (42). As a result, the generator (45) generates a larger amount of power than the expansion unit (E) of the first embodiment.
  • the electric power generated by the generator (45) is used as driving power for the compression mechanism (20) and other element machines.
  • the refrigerant compressed by the compression mechanism (20) of the compression unit (C) flows into the oil separator (60).
  • the refrigerant from which the oil has been separated by the oil separator (60) is radiated by the outdoor heat exchanger (12) and then expanded by the expansion mechanism (30) of the oil power recovery type expansion unit (E / O).
  • the power obtained by the refrigerant expanding in the expansion mechanism (30) is used for power generation by the generator (45).
  • the refrigerant expanded in the expansion mechanism (30) evaporates in the indoor heat exchanger (13), is used for indoor cooling, and is then sucked into the compression mechanism (20) of the compression unit (C).
  • the oil separated by the oil separator (60) is cooled by the oil cooler (80) and then flows into the recovery mechanism (40) of the oil power recovery type expansion unit (E / O).
  • the recovery mechanism (40) the output shaft (42) is rotated by the power of the oil in the oil chamber (49), and the generator (45) is driven. As a result, electric power is generated by the generator (45).
  • the oil whose power is recovered by the recovery mechanism (40) and depressurized flows out of the oil power recovery type expansion unit (E / O) and flows to the oil injection port (24) of the compression mechanism (20) of the compression unit (C) Inflow.
  • the compression mechanism (20) the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm.
  • the power required for refrigerant compression is reduced.
  • the COP of the air conditioner (10) is effectively improved.
  • Embodiment 4 of the Invention will be described.
  • the configuration of the refrigerant circuit (11) is different from those in the above embodiments.
  • the compression mechanism (20), the expansion mechanism (30), and the recovery mechanism (40) are integrated into an oil power recovery type expansion / compression unit (C / E / O).
  • the oil power recovery type expansion / compression unit (C / E / O) includes a compression mechanism (20), an expansion mechanism (30), a recovery mechanism (40), and an electric motor (25) in a casing (not shown). Contained and configured.
  • the output mechanism (40) of the recovery mechanism (40) has an expansion mechanism (30) connected to the end thereof and a compression mechanism (20) connected to an intermediate portion thereof.
  • An electric motor (25) is coupled to the output shaft (42) between the expansion mechanism (30) and the compression mechanism (20).
  • both of these energies are used as power for rotationally driving the compression mechanism (20) via the output shaft (42).
  • the compression mechanism (20) constitutes a drive target that is driven by being connected to the recovery mechanism (40) and the expansion mechanism (30) via the output shaft (42).
  • the oil power recovery type expansion / compression unit (C / E / O) compared with the oil power recovery type compression unit (C / O) of the first embodiment, the compression mechanism (20) by the electric motor (25). The driving power is reduced.
  • the refrigerant compressed by the compression mechanism (20) of the oil power recovery type expansion / compression unit (C / E / O) flows into the oil separator (60).
  • the refrigerant from which the oil has been separated by the oil separator (60) is radiated by the outdoor heat exchanger (12) and then expanded by the expansion mechanism (30).
  • the energy of the refrigerant expanded by the expansion mechanism (30) is used as driving power for the compression mechanism (20) via the output shaft (42).
  • the refrigerant expanded in the expansion mechanism (30) evaporates in the indoor heat exchanger (13), is used for indoor cooling, and is then sucked into the compression mechanism (20) of the compression unit (C).
  • the oil separated by the oil separator (60) is cooled by the oil cooler (80) and then flows into the recovery mechanism (40).
  • the output shaft (42) is rotationally driven by the oil in the oil chamber (49), and the rotational power of the output shaft (42) is used as the driving power of the compression mechanism (20).
  • the compression mechanism (20) the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm.
  • the power required for refrigerant compression is reduced.
  • the COP of the air conditioner (10) is effectively improved.
  • Embodiment 5 of the Invention ⁇ Embodiment 5 of the present invention will be described.
  • the air conditioner (10) of the fifth embodiment is provided with an oil injection mechanism (100) and a controller (95) for each of the embodiments described above.
  • the compression mechanism (20) is composed of a oscillating piston type rotary fluid machine, similar to the recovery mechanism (40).
  • the compression mechanism (20) has a compression chamber (26), and is configured to suck carbon dioxide as a working fluid into the compression chamber (26) and compress it.
  • the oil injection mechanism (100) is configured to open and close the oil injection port (24), and is configured to supply refrigeration oil to the compression chamber (26) at a predetermined timing.
  • This compression mechanism (20) is housed in the casing of the oil power recovery type compression unit (C / O) as described above.
  • the compression mechanism (20) is configured to suck and compress the refrigerant by the operation of the piston (28) in the cylinder (27) having the compression chamber (26).
  • the compression mechanism (20) is configured such that the compression chamber (26) is formed in a circular cross section, and the piston (28) performs an eccentric rotational motion in the compression chamber (26).
  • the piston (28) is formed integrally with an annular portion (28a) that engages with a crankpin (42c) of a crankshaft (42) that is an output shaft and performs eccentric rotational motion, and the annular portion (28a).
  • the blade (28b) has a plate shape and extends outward in the radial direction of the annular portion (28a).
  • the cylinder (27) has a swing bush (29) that slidably holds the blade (28b).
  • the swing bush (29) is composed of a substantially semicircular suction side bush (29a) and a discharge side bush (29b). The suction side bush (29a) and the discharge side bush (29b) may be partly connected and integrated.
  • the cylinder (27) is formed with a suction port (22a) having one end opened to the compression chamber (26) so as to suck the refrigerant into the compression chamber (26).
  • the other end of the suction port (22a) communicates with the suction pipe (22) of the suction line (17).
  • the cylinder (27) has two end plates (27a, 27b) (the end plate (27a) on the motor side) that closes both end surfaces in the axial direction as the front mechanism, similar to the recovery mechanism (40).
  • the end plate (27b) opposite to the electric motor is referred to as a rear head).
  • One of the front head (27a) and the rear head (27b) has a discharge port (for discharging the refrigerant compressed in the compression chamber (26) to the space in the casing of the oil power recovery type compression unit (C / O)).
  • 23a) is formed.
  • This discharge port (23a) is provided with a reed valve (not shown) as a discharge valve, and the pressure in the compression chamber (26) and the pressure in the casing of the oil power recovery type compression unit (C / O) When the pressure difference between and reaches a predetermined value, the discharge port (23a) opens.
  • the discharge pipe (23) is directly connected to the casing of the oil power recovery type compression unit (C / O), and the refrigerant flowing out of the discharge port (23a) passes through the discharge pipe (23) to form a refrigerant circuit. It is discharged to the discharge line (18) of (11).
  • the suction port (22a) is provided at a position that is angled by ⁇ s in the right direction of the horizontal axis when the upward direction of the vertical axis in FIG.
  • the oil injection mechanism (100) has an injection nozzle portion (101) provided in the cylinder (27), and the injection nozzle portion (101) is provided at a position having an angle ⁇ i, and the oil injection It communicates with the compression chamber (26) through the port (24).
  • the suction port (22a) and the oil injection port (24) are arranged at positions that communicate with each other via the compression chamber (26) during the suction stroke shown in FIG.
  • the injection nozzle part (101) of the oil injection mechanism (100) includes a cylindrical injection case (102), a spool (103) slidable in the axial direction of the injection case (102), and the spool (103) And a drive mechanism (104) for driving the motor.
  • An oil injection port (105) communicating with the oil injection port (24) is formed at one end of the injection case (102).
  • the other end of the injection case (102) is connected to an oil supply pipe (106) connected to the second oil guide pipe (72) of the oil introduction path (70).
  • the spool (103) has an end on the oil injection port (105) side formed as a tapered valve portion (107).
  • the oil injection port (105) is a valve seat (108) formed on the inner surface side of the injection case (102) by a tapered surface having the same angle as the valve portion (107) of the spool (103).
  • the oil supply pipe ( The refrigerating machine oil supplied from 106) is injected into the compression chamber (26) from the oil injection port (24) through the gap between the valve portion (107) and the valve seat (108).
  • the solenoid mechanism (109) is used as the drive mechanism (104) for moving the spool (103) back and forth in the axial direction.
  • the solenoid mechanism (109) includes an iron core (110) fixed to the spool (103) and a coil (111) fixed to the injection case (102).
  • a coil spring (112) that applies a spring force in a direction to retract the spool (103).
  • the spool (103) receives a spring receiver (113) that receives one end of the coil spring (112). Is fixed.
  • the other end of the coil spring (112) is in contact with the end surface on the oil injection port (105) side of the injection case (102).
  • the air conditioner (10) of Embodiment 5 has a controller (95) as a control means for controlling the oil injection mechanism (100).
  • the controller (control means) (95) for controlling the compression mechanism (20) is configured as shown in the block diagram of FIG.
  • the controller (95) includes an input value (specification) reading unit (96), a measurement value (or set value) reading unit (97), and a calculated value determination unit (98).
  • the input value reading unit (96) and the measured value reading unit (97) are connected to the calculated value determining unit (98) so as to send a signal to the calculated value determining unit (98).
  • the position ⁇ s of the suction port (22a), the position ⁇ i of the oil injection port (24), the rotational speed ⁇ of the crankshaft (42), and the rotational angle of the crankshaft (42) The injection timing is obtained based on the current value ⁇ c, and a control signal is sent from the controller (95) to the oil injection mechanism (100). Based on this control signal, the solenoid mechanism (109) is turned on and off, and the oil injection timing is controlled.
  • the controller (95) is at least part of the range from the injection start point to the injection end point, with the piston (28 reaching the position where it passes through the oil injection port (24)) as the injection end point.
  • the oil injection mechanism (100) is controlled so as to perform the oil injection operation.
  • the controller (95) is configured to perform the oil injection operation in the entire range from the injection start point to the injection end point in order to perform isothermal compression over the entire range.
  • the controller (95) the position ⁇ s of the suction port (22a) and the position ⁇ i of the oil injection mechanism (100) are input to the input value reading unit (96) as preset positions.
  • the rotational speed ⁇ of the crankshaft (42) during operation and the current value ⁇ c of the rotational angle of the crankshaft (42) are measured by the measured value reading unit (97).
  • the calculation value determination unit (98) obtains the injection timing based on these values.
  • the position at which the suction stroke ends is set as the injection start point ⁇ s, and the position before the discharge stroke ends (specifically, the piston
  • the point at which (28) reaches the position where it passes through the oil injection port (24)) is set as the injection end point ⁇ i, and at least part of the range from the injection start point ⁇ s to the injection end point ⁇ , or all of the range It is determined to perform an oil injection operation.
  • the oil injection operation is performed in the entire range, as shown in FIG.
  • the controller (95) determines the injection timing so that the oil injection port (105) is opened only during the injection time ⁇ t determined by the calculated value determination unit (98) in FIG. 100)
  • the oil injection port (105) is opened and closed, and the oil injection operation to the compression mechanism (20) is controlled.
  • the suction port (22a) and the oil injection port (24) are not connected. Since the oil injection port (24) is opened, the above-described isothermal compression effect can be sufficiently obtained by performing the oil injection operation during that time. Further, the oil injection port (24) is closed while the suction port (22a) and the oil injection port (24) are in communication with each other during the operation of the piston (28). Can be prevented. If the oil injection port (24) is open while the suction port (22a) and the oil injection port (24) are in communication with the piston (28), the oil injection port (24) will move to the compression chamber (26).
  • the required cooling amount is calculated from many values such as the compressor rotation speed, suction pressure, discharge pressure, enthalpy, and refrigerant circulation amount to calculate the opening time and injection amount of the liquid refrigerant injection device.
  • the calculation logic to measure the compressor input so that it becomes the minimum value in the controller (95), and simply set the suction port (22a) position as the injection start point ⁇ s. Since the oil injection port (24) is set to the injection end point ⁇ i, and the oil injection operation is performed within the range, the calculation of the injection timing in the oil injection mechanism (100) is very easy. Therefore, effective oil injection is possible simply by implementing simple calculation logic.
  • Embodiment 6 of the Invention Embodiment 6 of the present invention will be described.
  • the air conditioner (10) of the sixth embodiment has the same oil injection mechanism (100) as that of the fifth embodiment, but differs from the fifth embodiment in the configuration of the controller (95).
  • the controller (95) of the sixth embodiment is configured as shown in the block diagram of FIG.
  • the controller (95) includes an input value (specification) reading unit (96), a measurement value (or set value) reading unit (97), and a calculated value determination unit (98).
  • the input value reading unit (96) and the measured value reading unit (97) are connected to the calculated value determining unit (98) in order to send a signal to the calculated value determining unit (98).
  • the cylinder volume Vc, the suction port position ⁇ s, the oil injection position ⁇ i (hereinafter, the data of the input value reading unit (96)), the rotational speed ⁇ of the crankshaft (42), The current value ⁇ c of the rotation angle of the crankshaft (42), the intake gas temperature Ts, the low pressure Lp of the refrigerant circuit (11), the high pressure Hp of the refrigerant circuit (11), the injection oil temperature To, and the injection oil
  • the timing of the oil injection operation is determined based on the pressure Po (the data of the measured value reading unit (97)).
  • the refrigerant gas temperature Tr during compression and the refrigerant gas pressure Pr during compression are the compressor specifications such as the cylinder volume Vc and the suction port position ⁇ s, the suction gas temperature Ts, the low pressure Lp of the refrigerant circuit (11), It is calculated from measured values such as the high pressure Hp of the refrigerant circuit (11) and refrigerant physical property data recorded in advance in the controller.
  • the calculation of the injection start position ⁇ 1 and the injection end point ⁇ 2 in FIG. 15 includes a calculation process (refrigerant temperature detection means and refrigerant pressure detection means) of the refrigerant gas temperature Tr during compression and the refrigerant gas pressure Pr during compression. ing.
  • the position at which the refrigerant temperature Tr in the compression chamber (26) becomes the temperature of the injected oil To is the injection start point.
  • the position at which the refrigerant pressure Tr in the compression chamber (26) reaches the discharge pressure Hp is defined as ⁇ 1
  • the controller (95) is at least partially in the range from the injection start point ⁇ 1 to the injection end point ⁇ 2.
  • the oil injection mechanism (100) is controlled so as to perform the oil injection operation. In particular, it is preferable to configure the controller (95) so that the oil injection operation is performed in the entire range from the injection start point ⁇ 1 to the injection end point ⁇ 2, in order to perform isothermal compression over the entire range.
  • the cylinder volume Vc, the suction port position ⁇ s, and the oil injection position ⁇ i are input to the controller (95) as preset positions in the input value reading unit (96).
  • the rotational speed ⁇ of the crankshaft (42), the current value ⁇ c of the rotational angle of the crankshaft (42), the intake gas temperature Ts, the low pressure Lp of the refrigerant circuit (11), the refrigerant The high pressure Hp of the circuit (11), the injection oil temperature To, and the injection oil pressure Po are measured by the measured value reading unit (97). Then, in the calculated value determining unit (98), the injection timing is obtained based on these values.
  • Tr To when the refrigerant gas temperature during compression is Tr
  • the position at which the refrigerant temperature Tr in the compression chamber (26) becomes the temperature of the injected oil To during the operation in which the suction stroke, the compression stroke, and the discharge stroke are one cycle is the injection start point.
  • the position at which the refrigerant pressure Pr in the compression chamber (26) reaches the discharge pressure Hp is defined as ⁇ 1, and the controller (95) is at least part of the range from the injection start point ⁇ 1 to the injection end point ⁇ 2. Or the entire range of the oil injection operation.
  • the oil injection operation is performed in the entire range, the entire range from the point ⁇ 1 to the point ⁇ 2 in FIG. 16 is performed.
  • the spool (103) of the oil injection mechanism (100) is moved backward. Open the oil injection port (105).
  • the spool (103) of the oil injection mechanism (100) is advanced to close the oil injection port (105). become.
  • the controller (95) opens and closes the oil injection port (105) of the oil injection mechanism (100) based on the injection timing obtained by the calculated value determination unit (98), and the oil injection operation to the compression mechanism (20) To control.
  • the position at which the temperature To becomes the injection start point ⁇ 1, and the position at which the refrigerant pressure in the compression chamber (26) reaches the discharge pressure is the injection end point ⁇ 2, and at least one of the range from the injection start point ⁇ 1 to the injection end point ⁇ 2.
  • the oil injection operation is performed in the part or all of the range.
  • the oil injection operation is performed only within the range of ⁇ 1 to ⁇ 2, the work amount due to overheat compression is prevented from occurring as shown in FIG. Can be increased. From the above, according to this embodiment, a large amount of oil necessary for cooling can be injected, and power loss due to overheat compression does not occur, so that effective isothermal compression can be realized, System performance can be improved.
  • Embodiment 7 of the Invention is a heating-only air conditioner that only heats the room.
  • the refrigerant circuit (11) of the air conditioner (10) includes an oil power recovery type compression unit (C / O), an expansion unit (E), an outdoor unit, as in the first embodiment.
  • a heat exchanger (12), an indoor heat exchanger (13), an oil separator (60), and the like are provided.
  • the refrigerant circuit (11) of Embodiment 7 has a configuration in which, for example, two four-way switching valves (14, 15) as in Embodiment 1 are omitted. That is, in the refrigerant circuit (11), the refrigerant discharge pipe (62) of the oil separator (60) is connected to the inflow end of the indoor heat exchanger (13), and the outflow end of the indoor heat exchanger (13) is expanded. Connected to the inlet pipe (33) of the unit (E). The outflow pipe (34) of the expansion unit (E) is connected to the inflow end of the outdoor heat exchanger (12), and the outflow end of the outdoor heat exchanger (12) is connected to the compression mechanism (17) via the suction line (17). It is connected to the suction pipe (22) of 20). And the refrigerant circuit (11) of this embodiment is comprised so that the heating operation which heats indoor air with the refrigerant
  • the oil cooler (80) of the seventh embodiment constitutes an oil cooling heat exchanger for cooling the oil separated by the oil separator (60), and assists in releasing oil heat into the room during heating operation. Also serves as a heater. Specifically, the oil cooler (80) is installed in the same room as the room in which the indoor heat exchanger (13) is installed.
  • the refrigerant compressed by the compression mechanism (20) flows into the oil separator (60), and the oil is separated from the refrigerant by the oil separator (60). Is done.
  • the separated refrigerant flows through the indoor heat exchanger (13).
  • the indoor heat exchanger (13) the high-pressure refrigerant radiates heat to the room air, thereby heating the room air, thereby heating the room.
  • the refrigerant flowing out of the indoor heat exchanger (13) is decompressed by the expansion unit (E), evaporated by the outdoor heat exchanger (12), and then sucked into the compression mechanism (20).
  • the oil injection operation is performed in the same manner as in the above embodiments. That is, the oil separated by the oil separator (60) is cooled by the oil cooler (80) and then flows into the recovery mechanism (40). In the recovery mechanism (40), the output shaft (42) is rotationally driven by the oil in the oil chamber (49), and the rotational power of the output shaft (42) is used as the driving power of the compression mechanism (20).
  • the compression mechanism (20) the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm.
  • the power required for refrigerant compression is reduced.
  • the compression power of the refrigerant is reduced by the isothermal compression effect, and the energy of the oil recovered from the oil after the pressure increase is also increased. Become more.
  • the oil cooler (80) is used as an auxiliary heater in order to compensate for a decrease in heating capacity accompanying the oil injection operation. This point will be described in detail.
  • the refrigerant is compressed so as to approach the isotherm, so the compression power of the refrigerant is reduced.
  • the refrigerant is compressed so as to approach the isotherm in this way, the enthalpy of the compressed refrigerant becomes smaller than that of a normal refrigeration cycle that does not perform a so-called oil injection operation.
  • the indoor heat exchanger (13) of the refrigerant circuit (11) during the heating operation the amount of heat released from the refrigerant is reduced, and the heating capacity is reduced.
  • the oil cooler (80) is installed indoors, and the heat of the oil flowing through the oil cooler (80) is released to the indoor air. That is, in the oil injection operation during the heating operation, when the oil separated by the oil separator (60) flows through the oil cooler (80), the oil cooler (80) exchanges heat between the oil and the room air. As a result, the heat of the oil having a relatively high temperature is applied to the indoor air, and indoor heating is promoted. On the other hand, the oil flowing through the oil cooler (80) is cooled by room air. As described above, during the heating operation, the oil in the oil cooler (80) is cooled, and at the same time, the indoor air is heated by the oil, so that the oil injection operation can be performed while preventing the heating capacity from being lowered.
  • the air conditioning apparatus (10) according to Embodiment 8 is a heat pump type air conditioning apparatus that performs switching between cooling and heating.
  • the refrigerant circuit (11) of the air conditioner (10) includes, for example, an oil power recovery type compression unit (C / O), a first four-way switching valve, as in the first embodiment. (14), an outdoor heat exchanger (12), an indoor heat exchanger (13), an oil separator (60), and the like are provided.
  • an expansion valve (38) as a pressure reducing mechanism is used instead of the expansion unit (E) of the first embodiment.
  • the oil supply circuit (70) of the eighth embodiment is configured such that the oil flow path is switched between the cooling operation and the heating operation.
  • the oil supply circuit (70) of the eighth embodiment is provided with two oil coolers (80, 80) and an oil flow path switching mechanism (81).
  • the oil flow path switching mechanism (81) is composed of a four-way switching valve having four ports.
  • the oil flow path switching mechanism (81) includes a state in which the first port and the fourth port communicate with each other and a state in which the second port and the third port communicate with each other (state shown in FIG. 21), and the first port and the third port. And the second port and the fourth port communicate with each other (state shown in FIG. 22).
  • the first port of the oil flow path switching mechanism (81) is connected to the oil discharge pipe (63) via the first oil guide pipe (71).
  • the second port of the oil flow path switching mechanism (81) is connected to the suction line (17) via the low pressure communication pipe (75).
  • the third port of the oil flow path switching mechanism (81) is connected to the oil inflow pipe (43) via the outdoor oil flow path (74).
  • the fourth port of the oil flow path switching mechanism (81) is connected to the oil inflow pipe (43) via the indoor oil flow path (73).
  • the indoor oil cooler (80a) installed in the same room as the indoor heat exchanger (13) is connected to the indoor oil flow path (73).
  • the indoor oil cooler (80a) constitutes a first oil cooling heat exchanger that releases oil heat to the indoor air during the heating operation.
  • An outdoor oil cooler (80b) installed outside the room is connected to the outdoor oil flow path (74).
  • the outdoor oil cooler (80b) constitutes a second oil cooling heat exchanger that releases oil heat to the outdoor air during the cooling operation.
  • the oil separated by the oil separator (60) is selectively supplied to either the indoor oil cooler (80a) or the outdoor oil cooler (80b). Supplied.
  • the first four-way switching valve (14) and the oil flow path switching mechanism (81) are set to the state shown in FIG.
  • the refrigerant compressed by the compression mechanism (20) flows into the oil separator (60), and the oil is separated by the oil separator (60).
  • the separated refrigerant flows through the indoor heat exchanger (13).
  • the indoor heat exchanger (13) the high-pressure refrigerant radiates heat to the room air, thereby heating the room air, thereby heating the room.
  • the refrigerant condensed in the indoor heat exchanger (13) is decompressed by the expansion valve (38), evaporated by the outdoor heat exchanger (12), and then sucked into the compression mechanism (20).
  • the oil separated by the oil separator (60) flows through the indoor oil cooler (80a) through the indoor oil passage (73).
  • the indoor oil cooler (80a) the heat of oil is released to the indoor air.
  • an indoor side oil cooler (80a) functions as an auxiliary
  • the oil cooled by the indoor oil cooler (80a) as described above flows into the recovery mechanism (40).
  • the output shaft (42) is rotationally driven by the oil in the oil chamber (49), and the rotational power of the output shaft (42) is used as the driving power of the compression mechanism (20).
  • the compression mechanism (20) the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm.
  • the power required for refrigerant compression is reduced.
  • the compression power of the refrigerant is reduced by the isothermal compression effect, and the energy of the oil recovered from the oil after the pressure increase is also increased. Become more.
  • the heat of the oil flowing through the indoor oil cooler (80a) is used for heating.
  • the COP of the air conditioner (10) is effectively improved.
  • the first four-way switching valve (14) and the oil flow path switching mechanism (81) are set to the state shown in FIG.
  • the refrigerant compressed by the compression mechanism (20) flows into the oil separator (60), and the oil is separated by the oil separator (60).
  • the separated refrigerant is condensed in the outdoor heat exchanger (12), depressurized by the expansion valve (38), and then flows through the indoor heat exchanger (13).
  • the indoor heat exchanger (13) the refrigerant absorbs heat from the indoor air and evaporates. Thereby, indoor air is cooled and air_conditioning
  • the refrigerant evaporated in the indoor heat exchanger (13) is sucked into the compression mechanism (20).
  • the oil separated by the oil separator (60) flows through the outdoor oil cooler (80b) through the outdoor oil passage (74).
  • the heat of oil is released to the outdoor air.
  • the oil flowing through the outdoor oil cooler (80b) is cooled by the outdoor air.
  • the oil separated by the oil separator (60) does not flow through the indoor oil cooler (80a). Therefore, the heat of the oil is not released into the room from the indoor side oil cooler (80a), thereby preventing the indoor cooling load from increasing.
  • the oil cooled by the outdoor oil cooler (80b) flows into the recovery mechanism (40).
  • the output shaft (42) is rotationally driven by the oil in the oil chamber (49), and the rotational power of the output shaft (42) is used as the driving power of the compression mechanism (20).
  • the compression mechanism (20) the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm. As a result, the power required for refrigerant compression is reduced.
  • the oil separated from the refrigerant by the oil separator (60) is supplied to the suction side (low pressure side) of the compression mechanism (20), not during the compression of the compression mechanism (20). Also good. That is, for example, as shown in FIG. 23, the oil introduction path (70) of each of the above embodiments may be configured to supply the separated oil to the suction side of the compression mechanism (20). In the example of FIG. 23, the end of the second oil guide pipe (72) of the oil introduction path (70) is connected to the suction line (17) in the first embodiment. Also in this modification, the refrigerant cooled by the compression mechanism (20) can be simultaneously cooled by the oil cooled by the oil cooler (80), and the isothermal compression effect as described above can be obtained.
  • the oil cooled by the oil cooler (80) is not supplied to the recovery mechanism (40), but the oil recovered by the recovery mechanism (40) is cooled by the oil cooler (80). Also good. That is, for example, as shown in FIG. 24, in each of the above embodiments, the oil cooler (80) may be arranged on the downstream side of the recovery mechanism (40) in the oil introduction path (70). In the example of FIG. 24, the oil cooler (80) is disposed on the downstream side of the recovery mechanism (40) in the first embodiment.
  • the energy of the oil can be recovered by the recovery mechanism (40) and the oil cooled by the oil cooler (80) is supplied to the compression mechanism (20), so that the effect of isothermal compression as described above can be achieved.
  • the oil immediately before being supplied to the compression mechanism (20) can be cooled by the oil cooler (80), so that the oil can be stably supplied to the compression mechanism (20). Can supply.
  • the above-mentioned isothermal compression effect can be further improved.
  • an internal heat exchanger (90) may be added to the refrigerant circuit (11).
  • the internal heat exchanger (90) is connected to the refrigerant circuit (11) in the above-described modification 2 (example of FIG. 24).
  • the internal heat exchanger (90) has a first flow path (91) and a second flow path (92), and exchanges heat between the refrigerants flowing through both flow paths (91, 92).
  • the first flow path (91) is a high pressure through which the refrigerant before flowing into the expansion mechanism (30) flows after the heat is radiated by the radiator (for example, the outdoor heat exchanger (12) during cooling operation) in the refrigerant circuit (11).
  • the second channel (92) is connected to the suction line (17). Therefore, in the internal heat exchanger (90), the first flow path (91) is cooled by the high pressure refrigerant and the low pressure refrigerant flowing in the second flow path (92).
  • the oil separator (60) may be provided at another location.
  • the oil separator (60) is arranged in the high-pressure line (19) described in the modification 3 in the first embodiment. Also in this modified example, since the oil pressurized by the compression mechanism (20) accumulates in the oil separator (60), the oil energy is recovered by sending the oil to the recovery mechanism (40). be able to.
  • the oil which accumulates in the oil separator (60) during the cooling operation becomes oil after heat dissipation in the outdoor heat exchanger (12).
  • the refrigerant separated by the oil separator (60) is supplied to the compression mechanism (20) so that the refrigerant is isothermally compressed in the compression stroke of the compression mechanism (20) (FIG. 4). See).
  • the refrigerant is isothermally compressed during a part of the compression stroke (that is, from the point B to the point C). May be compressed isothermally.
  • the partial period of the compression stroke is not limited to the example of FIG. 4 and may be at different timing.
  • the refrigerant is compressed so as to substantially follow the isothermal line during the compression stroke.
  • FIG. 4 merely illustrates ideal isothermal compression as described above, and the isothermal compression of the present invention does not necessarily have the behavior shown in FIG.
  • the isothermal compression of the present invention may be performed in such a manner that the refrigerant cooled by the oil is gradually separated from the isotherm.
  • the “isothermal compression” of the present invention is that the refrigerant in the compression stroke is cooled by the oil, and in the compression stroke, the refrigerant is compressed so as to approach the isotherm as compared with general adiabatic compression. (That is, so-called pseudo-isothermal compression).
  • the recovery mechanism (40) of the present invention is applied to what performs so-called isothermal compression by actively supplying the oil separated by the oil separator (60) to the compression mechanism (20).
  • a refrigerant circuit that returns oil that has flowed out of the compression mechanism (20) to the suction side of the compression mechanism (20) via an oil return pipe to prevent poor lubrication of the compression mechanism (20).
  • the recovery mechanism (40) of the present invention may be applied to the oil return pipe. Even in this case, the energy of the high-pressure oil can be recovered by the recovery mechanism (40), and the COP of the refrigeration apparatus can be improved.
  • the main body (41) of the recovery mechanism (40) of each embodiment described above is composed of a rotary positive displacement fluid machine.
  • the main body portion (41) may be constituted by, for example, a scroll type positive displacement fluid machine, or may be constituted by, for example, a non positive displacement type fluid machine (eg, a turbine type non positive displacement type fluid machine).
  • the compression mechanism (20) and the expansion mechanism (30) may be formed of other types of fluid machines.
  • another refrigerant may be used as the refrigerant charged in the refrigerant circuit (11).
  • this invention is applied about the air conditioning apparatus (10) which air-conditions a room
  • this invention is applied to the freezing apparatus which cools the inside of a refrigerator or a freezer, for example, and another freezing apparatus. It may be applied.
  • the present invention is useful for a refrigeration apparatus including a refrigerant circuit that performs a refrigeration cycle by circulating refrigerant.

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Abstract

A refrigeration circuit (11) has an oil separator (60) for separating oil from a high-pressure refrigerant and also has an oil supply circuit (70) for supplying the oil, separated by the oil separator (60), to a compression mechanism (20) so that the oil in compression strokes of the compression mechanism (20) is cooled. The oil supply circuit (70) has a recovery mechanism (40) for recovering energy of the oil separated by the oil separator (60). In the compression mechanism (20), the refrigerant is cooled by the oil, and this reduces power of the compression mechanism (20). At the same time, the recovery mechanism (40) recovers power consumed by the compression mechanism (20) to increase the pressure of the oil.

Description

冷凍装置Refrigeration equipment
　本発明は、冷媒が循環して冷凍サイクルを行う冷媒回路を備えた冷凍装置に関し、特に冷凍装置の省エネ対策に係るものである。 The present invention relates to a refrigeration apparatus including a refrigerant circuit that performs a refrigeration cycle by circulating refrigerant, and particularly relates to energy saving measures for the refrigeration apparatus.
　従来より、冷凍サイクルを行う冷媒回路を備えた冷凍装置は、室内の空調を行う空気調和装置等に広く適用されている。 Conventionally, a refrigeration apparatus including a refrigerant circuit that performs a refrigeration cycle has been widely applied to an air conditioner that performs indoor air conditioning.
　特許文献１には、この種の冷凍装置が開示されている。この冷凍装置の冷媒回路には、圧縮機、サイクロン（油分離器）、放熱器、利用側熱交換器等が接続されて冷媒回路が構成されている。圧縮機で圧縮された高圧冷媒は、油分離器へ流入する。油分離器では、高圧冷媒中から油が分離される。分離後の油は、放熱器を通じて冷却された後、圧縮機の吸入側へ供給される。これにより、圧縮機の圧縮行程では、冷媒が油によって冷却される。このため、圧縮機の圧縮行程中には、冷媒の温度がほとんど上昇せず、等温圧縮に近い状態で冷媒が圧縮される。従って、この圧縮機の圧縮行程では、一般的な圧縮機の圧縮行程（断熱変化に近い状態での圧縮行程）と比較して圧縮機の動力が小さくなる。その結果、この冷凍装置では、圧縮機の動力の削減に伴いＣＯＰ（成績係数）の向上が図られている。
特開平４－１１６３４８号公報 Patent Document 1 discloses this type of refrigeration apparatus. A compressor, a cyclone (oil separator), a radiator, a use side heat exchanger, and the like are connected to the refrigerant circuit of the refrigeration apparatus to form a refrigerant circuit. The high-pressure refrigerant compressed by the compressor flows into the oil separator. In the oil separator, oil is separated from the high-pressure refrigerant. The separated oil is cooled through a radiator and then supplied to the suction side of the compressor. Thereby, in the compression stroke of the compressor, the refrigerant is cooled by the oil. For this reason, during the compression stroke of the compressor, the temperature of the refrigerant hardly rises, and the refrigerant is compressed in a state close to isothermal compression. Therefore, in the compression stroke of this compressor, the power of the compressor is smaller than that of a general compressor (compression stroke in a state close to adiabatic change). As a result, in this refrigeration apparatus, COP (coefficient of performance) is improved with the reduction in power of the compressor.
Japanese Patent Laid-Open No. 4-116348
　ところで、特許文献１に開示の冷凍装置のようにして、圧縮機の圧縮行程中の冷媒を冷却するためには、油分離器で分離した油を多量に圧縮機へ供給する必要がある。つまり、圧縮機へ供給する油の量が多ければ多いほど、油による冷媒の冷却効果が大きくなるので、これに伴って冷媒の圧縮に要する動力も小さくなる。しかしながら、このようにして圧縮機構へ供給される油の量が多くなると、圧縮機では、供給された油の昇圧に要する動力も増大してしまう。その結果、圧縮機では、油の昇圧に要した動力（エネルギー）を無駄に消費してしまうという問題が生ずる。 Incidentally, in order to cool the refrigerant during the compression stroke of the compressor as in the refrigeration apparatus disclosed in Patent Document 1, it is necessary to supply a large amount of oil separated by the oil separator to the compressor. That is, the greater the amount of oil supplied to the compressor, the greater the effect of cooling the refrigerant by the oil, and accordingly, the power required to compress the refrigerant also decreases. However, when the amount of oil supplied to the compression mechanism in this way increases, the power required for boosting the supplied oil also increases in the compressor. As a result, the compressor has a problem that power (energy) required for boosting the oil is wasted.
　本発明は、かかる点に鑑みてなされたものであり、その目的は、圧縮機構の動力を効果的に削減できる冷凍装置を提供することである。 The present invention has been made in view of such a point, and an object thereof is to provide a refrigeration apparatus capable of effectively reducing the power of the compression mechanism.
　第１の発明は、圧縮機構（20）が接続されて冷凍サイクルを行う冷媒回路（11）を備えた冷凍装置を対象とし、上記冷媒回路（11）には、上記圧縮機構（20）で圧縮した高圧冷媒中から油を分離する油分離手段（60）と、上記圧縮機構（20）の圧縮行程中の冷媒を冷却するように上記油分離手段（60）で分離した油を圧縮機構（20）へ供給する油供給回路（70）とが設けられ、上記油供給回路（70）には、油供給回路（70）を流れる油のエネルギーを回収する回収機構（40）が設けられていることを特徴とするものである。 A first invention is directed to a refrigeration apparatus including a refrigerant circuit (11) connected to a compression mechanism (20) to perform a refrigeration cycle. The refrigerant circuit (11) is compressed by the compression mechanism (20). Oil separating means (60) for separating oil from the high-pressure refrigerant, and oil separated by the oil separating means (60) so as to cool the refrigerant in the compression stroke of the compression mechanism (20). And an oil supply circuit (70) for supplying oil to the oil supply circuit (70), and a recovery mechanism (40) for recovering the energy of the oil flowing through the oil supply circuit (70). It is characterized by.
　第１の発明の冷媒回路（11）では、圧縮機構（20）で圧縮された高圧冷媒中から、油分離手段（60）によって高圧の油が分離される。分離後の油は、圧縮機構（20）の圧縮行程中の冷媒を冷却するように油供給回路（70）を通じて圧縮機構（20）へ供給される。その結果、圧縮機構（20）の圧縮行程では、冷媒の温度上昇が抑制され、これにより、圧縮機構（20）での冷媒の圧縮に要する動力が低減される。 In the refrigerant circuit (11) of the first invention, high-pressure oil is separated from the high-pressure refrigerant compressed by the compression mechanism (20) by the oil separation means (60). The separated oil is supplied to the compression mechanism (20) through the oil supply circuit (70) so as to cool the refrigerant in the compression stroke of the compression mechanism (20). As a result, in the compression stroke of the compression mechanism (20), the temperature rise of the refrigerant is suppressed, and thereby the power required for the compression of the refrigerant in the compression mechanism (20) is reduced.
　一方、上述のように、圧縮機構（20）の圧縮行程中の冷媒を油によって冷却しようとするためには、油供給回路（70）から圧縮機構（20）へ多量の油を供給する必要がある。このため、従来の圧縮機構では、油の昇圧に要する動力が増大してしまうという問題が生じていた。 On the other hand, as described above, in order to cool the refrigerant in the compression stroke of the compression mechanism (20) with oil, it is necessary to supply a large amount of oil from the oil supply circuit (70) to the compression mechanism (20). is there. For this reason, in the conventional compression mechanism, the problem that the motive power required for pressure | voltage rise of oil will arise.
　そこで、本発明の油供給回路（70）には、油のエネルギーを回収する回収機構（40）が設けられている。具体的には、油分離手段（60）によって高圧冷媒中から分離された油は、圧縮機構（20）において油を昇圧させるために使われた動力を、運動エネルギー、位置エネルギー、圧力エネルギー等のエネルギーとして保有している。回収機構（40）は、分離後の油の動力（即ち、油の持つエネルギー）を回収する。このため、油供給回路（70）を介して圧縮機構（20）へ多量の油が供給されて油の昇圧に要する動力が増大しても、この油の昇圧に要した動力を回収機構（40）で回収することができる。従って、本発明では、圧縮機構（20）へ多量の油を供給することで冷媒の圧縮に要する動力を低減でき、且つ多量の油の昇圧に要する動力が無駄となってしまうこともない。 Therefore, the oil supply circuit (70) of the present invention is provided with a recovery mechanism (40) for recovering oil energy. Specifically, the oil separated from the high-pressure refrigerant by the oil separation means (60) is used to convert the power used for boosting the oil in the compression mechanism (20) into kinetic energy, potential energy, pressure energy, etc. I have it as energy. The recovery mechanism (40) recovers the power of the oil after separation (that is, the energy of the oil). For this reason, even if a large amount of oil is supplied to the compression mechanism (20) via the oil supply circuit (70) and the power required for boosting the oil increases, the power required for boosting the oil is recovered by the recovery mechanism (40 ) Can be recovered. Therefore, in the present invention, the power required for compressing the refrigerant can be reduced by supplying a large amount of oil to the compression mechanism (20), and the power required for pressurizing the large amount of oil is not wasted.
　第２の発明は、第１の発明の冷凍装置において、上記油供給回路（70）は、上記圧縮機構（20）の圧縮行程の少なくとも一部の期間で冷媒が等温圧縮されるように圧縮機構（20）へ油を供給することを特徴とするものである。 According to a second aspect of the present invention, in the refrigeration apparatus of the first aspect, the oil supply circuit (70) is configured so that the refrigerant is isothermally compressed during at least a part of the compression stroke of the compression mechanism (20). It is characterized by supplying oil to (20).
　第２の発明の油供給回路（70）は、圧縮機構（20）の圧縮行程の少なくとも一部の期間で冷媒が等温圧縮されるように圧縮機構（20）へ油を供給する。その結果、圧縮機構（20）の圧縮行程では、冷媒の温度がほとんど上昇せず、これにより圧縮機構（20）での冷媒の圧縮に要する動力が低減される。一方、このように圧縮機構（20）の圧縮行程の少なくとも一部の期間で冷媒を等温圧縮させるためには、油供給回路（70）から圧縮機構（20）へ多量の油を供給する必要があり、これに伴い圧縮機構（20）での油の昇圧に要する動力が増大してしまう。しかしながら、本発明では、回収機構（40）が油供給回路（70）の油のエネルギーを回収するので、圧縮機構（20）で油の昇圧に要した動力が無駄となってしまうことはない。 The oil supply circuit (70) of the second invention supplies oil to the compression mechanism (20) so that the refrigerant is isothermally compressed during at least a part of the compression stroke of the compression mechanism (20). As a result, in the compression stroke of the compression mechanism (20), the temperature of the refrigerant hardly rises, thereby reducing the power required for the compression of the refrigerant in the compression mechanism (20). On the other hand, it is necessary to supply a large amount of oil from the oil supply circuit (70) to the compression mechanism (20) in order to isothermally compress the refrigerant during at least a part of the compression stroke of the compression mechanism (20). Along with this, the power required to pressurize the oil in the compression mechanism (20) increases. However, in the present invention, since the recovery mechanism (40) recovers the energy of the oil in the oil supply circuit (70), the power required for boosting the oil in the compression mechanism (20) is not wasted.
　第３の発明は、第３の発明の冷凍装置において、上記冷媒回路（11）は、上記圧縮機構（20）によって冷媒を臨界圧力以上まで圧縮する冷凍サイクルを行うように構成されていることを特徴とするものである。 According to a third invention, in the refrigeration apparatus according to the third invention, the refrigerant circuit (11) is configured to perform a refrigeration cycle in which the refrigerant is compressed to a critical pressure or higher by the compression mechanism (20). It is a feature.
　第３の発明の冷媒回路（11）では、高圧冷媒が臨界圧力以上となる冷凍サイクルが行われる。このような冷凍サイクル（以下、超臨界サイクルという）では、上述の圧縮機構（20）への低温油の導入による冷媒の圧縮動力の低減効果が大きくなる。 In the refrigerant circuit (11) of the third invention, a refrigeration cycle is performed in which the high-pressure refrigerant is equal to or higher than the critical pressure. In such a refrigeration cycle (hereinafter referred to as a supercritical cycle), the effect of reducing the compression power of the refrigerant due to the introduction of low-temperature oil into the compression mechanism (20) is increased.
　具体的には、上記超臨界サイクルでは、圧縮機構（20）の圧縮行程で冷媒を冷却しても、この冷媒が過熱蒸気のまま昇圧されて凝縮することがない。つまり、超臨界サイクルの圧縮行程では、冷媒を冷却しても、この冷媒が気液二相領域（凝縮領域）に至ることがない。従って、本発明では、一般的な冷凍サイクル（冷媒を臨界圧力よりも小さい範囲で圧縮する冷凍サイクル）と比較して、いわゆる等温圧縮による冷媒の圧縮動力の低減効果を向上できる。 Specifically, in the supercritical cycle, even if the refrigerant is cooled in the compression stroke of the compression mechanism (20), the refrigerant is not pressurized and condensed as superheated steam. That is, in the compression stroke of the supercritical cycle, even if the refrigerant is cooled, the refrigerant does not reach the gas-liquid two-phase region (condensation region). Therefore, in the present invention, compared with a general refrigeration cycle (a refrigeration cycle in which the refrigerant is compressed in a range smaller than the critical pressure), the effect of reducing the compression power of the refrigerant by so-called isothermal compression can be improved.
　第４の発明は、第１乃至第３のいずれか１つの発明の冷凍装置において、上記油供給回路（70）は、上記圧縮機構（20）の圧縮行程の途中に油を供給するように構成されていることを特徴とするものである。 According to a fourth aspect of the present invention, in the refrigeration apparatus according to any one of the first to third aspects, the oil supply circuit (70) supplies oil during the compression stroke of the compression mechanism (20). It is characterized by being.
　第４の発明では、冷却手段（80）で冷却されて比較的低温となった油が、圧縮機構（20）の圧縮行程の途中（即ち、冷媒が吸入圧力と吐出圧力との間の中間圧力となる箇所）へ供給される。ここで、圧縮機構（20）の圧縮行程の途中では、既に冷媒が圧縮（断熱圧縮）されて昇温されている。従って、この箇所に低温の油を導入することで、冷媒が油よりも低温になることを回避できる。これにより、その後の圧縮行程では、冷媒が油によって加熱されて過熱圧縮されることを回避できる。従って、このような過熱圧縮に起因して、冷媒の圧縮動力の低減効果が損なわれるのを回避できる。 In the fourth invention, the oil cooled to a relatively low temperature by the cooling means (80) is in the middle of the compression stroke of the compression mechanism (20) (that is, the intermediate pressure between the suction pressure and the discharge pressure of the refrigerant). To the location). Here, in the middle of the compression stroke of the compression mechanism (20), the refrigerant has already been compressed (adiabatic compression) and heated up. Therefore, it is possible to avoid the refrigerant from becoming cooler than the oil by introducing the low-temperature oil into this portion. Thereby, it can avoid that a refrigerant | coolant is heated with oil and overheated in a subsequent compression process. Therefore, it can be avoided that the effect of reducing the compression power of the refrigerant is impaired due to such overheat compression.
　第５の発明は、第１乃至３のいずれか１つ発明の冷凍装置において、上記油供給回路（70）は、上記圧縮機構（20）の吸入側に油を供給するように構成されていることを特徴とする冷凍装置。 According to a fifth invention, in the refrigeration apparatus according to any one of the first to third inventions, the oil supply circuit (70) is configured to supply oil to the suction side of the compression mechanism (20). A refrigeration apparatus characterized by that.
　第５の発明では、冷却手段（80）で冷却されて比較的低温となった油が、圧縮機構（20）の吸入側へ供給される。これにより、圧縮機構（20）では、圧縮行程の開始時から冷媒が油によって冷却されるので、冷媒の圧縮動力の低減効果を向上できる。 In the fifth invention, the oil that has been cooled by the cooling means (80) and has a relatively low temperature is supplied to the suction side of the compression mechanism (20). Thereby, in a compression mechanism (20), since a refrigerant | coolant is cooled with oil from the time of the start of a compression process, the reduction effect of the compression power of a refrigerant | coolant can be improved.
　第６の発明は、第１乃至第５のいずれか１つの発明の冷凍装置において、上記回収機構（40）は、油によって回転駆動される可動部（50）と、該可動部（50）に連結する出力軸（42）とを有することを特徴とするものである。 According to a sixth aspect of the present invention, in the refrigeration apparatus according to any one of the first to fifth aspects, the recovery mechanism (40) includes a movable part (50) that is rotationally driven by oil, and the movable part (50). And an output shaft (42) to be connected.
　第６の発明では、回収機構（40）に可動部（50）と出力軸（42）とが設けられる。回収機構（40）では、高圧冷媒中から分離された油によって可動部（50）が回転駆動される。その結果、可動部（50）と連結する出力軸（42）も回転する。このような出力軸（42）の回転動力は、例えば発電機や他の機器の駆動動力として利用される。 In the sixth invention, the recovery mechanism (40) is provided with the movable part (50) and the output shaft (42). In the recovery mechanism (40), the movable part (50) is rotationally driven by the oil separated from the high-pressure refrigerant. As a result, the output shaft (42) connected to the movable part (50) also rotates. Such rotational power of the output shaft (42) is used, for example, as driving power for a generator or other equipment.
　第７の発明は、第６の発明の冷凍装置において、上記圧縮機構（20）は、上記回収機構（40）の出力軸（42）と連結して駆動されるように構成されていることを特徴とするものである。 According to a seventh aspect, in the refrigeration apparatus according to the sixth aspect, the compression mechanism (20) is configured to be connected to and driven by the output shaft (42) of the recovery mechanism (40). It is a feature.
　第７の発明では、回収機構（40）で回収された油の動力（即ち、油のエネルギー）が、出力軸（42）を介して圧縮機構（20）の動力源として利用される。ここで、上述のように、圧縮機構（20）へ供給する油の導入量が多くなると、上記の等温圧縮による冷媒の圧縮動力が低減されるが、この際には、圧縮機構（20）での油の昇圧に要する動力も大きくなる。しかしながら、本発明では、このように油の導入量を多くすることで、回収機構（40）で回収される動力が大きくなり、この動力の増大分だけ圧縮機構（20）の動力が低減される。即ち、本発明では、圧縮機構（20）へ低温油を積極的に導入することで、冷媒の圧縮動力を効果的に低減でき、且つ回収機構（40）で回収できる動力を増大できる。その結果、本発明では、圧縮機構（20）の全体として動力が効果的に削減され、圧縮機構（20）の効率が効果的に向上する。 In the seventh invention, the power of oil recovered by the recovery mechanism (40) (that is, the energy of the oil) is used as a power source of the compression mechanism (20) via the output shaft (42). Here, as described above, when the amount of oil to be supplied to the compression mechanism (20) increases, the compression power of the refrigerant due to the isothermal compression is reduced. In this case, the compression mechanism (20) The power required to pressurize the oil increases. However, in the present invention, by increasing the amount of oil introduced in this way, the power recovered by the recovery mechanism (40) increases, and the power of the compression mechanism (20) decreases by the increase in this power. . That is, in the present invention, the low-temperature oil is positively introduced into the compression mechanism (20), so that the compression power of the refrigerant can be effectively reduced and the power that can be recovered by the recovery mechanism (40) can be increased. As a result, in the present invention, power is effectively reduced as a whole of the compression mechanism (20), and the efficiency of the compression mechanism (20) is effectively improved.
　第８の発明では、第６又は第７の発明の冷凍装置において、上記冷媒回路（11）には、冷媒によって回転駆動されると共に上記回収機構（40）の出力軸（42）と連結する可動部を有する膨張機構（30）が設けられていることを特徴とするものである。 In the eighth invention, in the refrigeration apparatus of the sixth or seventh invention, the refrigerant circuit (11) is driven to rotate by the refrigerant and is connected to the output shaft (42) of the recovery mechanism (40). An expansion mechanism (30) having a portion is provided.
　第８の発明の冷媒回路（11）には、冷媒によって回転駆動される膨張機構（30）が設けられる。そして、回収機構（40）の出力軸（42）には、膨張機構（30）の可動部も連結される。つまり、出力軸（42）は、回収機構（40）で回収された動力と、膨張機構（30）で冷媒の膨張により得られた動力（即ち、膨張動力）との双方によって、回転駆動される。このような出力軸（42）の回転動力は、第７の発明の圧縮機構（20）の駆動動力等に利用される。 The refrigerant circuit (11) of the eighth invention is provided with an expansion mechanism (30) that is rotationally driven by the refrigerant. The movable part of the expansion mechanism (30) is also coupled to the output shaft (42) of the recovery mechanism (40). That is, the output shaft (42) is rotationally driven by both the power recovered by the recovery mechanism (40) and the power (ie, expansion power) obtained by the expansion of the refrigerant by the expansion mechanism (30). . Such rotational power of the output shaft (42) is used for driving power of the compression mechanism (20) of the seventh invention.
　第９の発明は、第６乃至第８のいずれか１つの発明の冷凍装置において、上記回収機構（40）の出力軸（42）と連結して駆動される発電機（45）を備えていることを特徴とするものである。 According to a ninth invention, in the refrigeration apparatus according to any one of the sixth to eighth inventions, a generator (45) that is driven in connection with the output shaft (42) of the recovery mechanism (40) is provided. It is characterized by this.
　第９の発明では、回収機構（40）で回収された油のエネルギーが、出力軸（42）を介して発電機（45）の駆動動力として利用される。その結果、本発明では、発電機（45）で電力を発生することができ、この電力を他の要素機械等の動力源として利用できる。 In the ninth invention, the energy of the oil recovered by the recovery mechanism (40) is used as drive power for the generator (45) via the output shaft (42). As a result, in the present invention, electric power can be generated by the generator (45), and this electric power can be used as a power source for other component machines and the like.
　第１０の発明は、第１乃至第９のいずれか１つの発明の冷凍装置において、上記油供給回路（70）には、油分離手段（60）で分離した油を冷却するための油冷却熱交換器（80）が接続されていることを特徴とする。 A tenth aspect of the invention is the refrigeration apparatus according to any one of the first to ninth aspects of the invention, wherein the oil supply circuit (70) includes oil cooling heat for cooling the oil separated by the oil separation means (60). A switch (80) is connected.
　第１０の発明では、油供給回路（70）に油冷却熱交換器（80）が設けられる。つまり、油分離手段（60）で分離した油は、油冷却熱交換器（80）で所定の流体と熱交換して冷却される。冷却後の油は、圧縮機構（20）の圧縮行程中の冷媒を冷却するために、該圧縮機構（20）へ供給される。 In the tenth aspect of the invention, the oil supply circuit (70) is provided with the oil cooling heat exchanger (80). That is, the oil separated by the oil separation means (60) is cooled by exchanging heat with a predetermined fluid by the oil cooling heat exchanger (80). The cooled oil is supplied to the compression mechanism (20) in order to cool the refrigerant during the compression stroke of the compression mechanism (20).
　第１１の発明は、第１０の発明の冷凍装置において、上記冷媒回路（11）は、室内に設置される室内熱交換器（13）を有して該室内熱交換器（13）を流れる冷媒で室内空気を加熱する暖房動作を行うように構成され、上記油冷却熱交換器（80）は、室内に設置されて上記暖房動作中に油の熱を室内空気へ放出するように構成されていることを特徴とする。 An eleventh invention is the refrigeration apparatus of the tenth invention, wherein the refrigerant circuit (11) has an indoor heat exchanger (13) installed indoors and flows through the indoor heat exchanger (13). The oil cooling heat exchanger (80) is installed indoors and is configured to release oil heat to the indoor air during the heating operation. It is characterized by being.
　第１１の発明の冷媒回路（11）は、室内空気を加熱する暖房動作を行うように構成されている。つまり、圧縮機構（20）で圧縮された冷媒を室内熱交換器（13）へ送り、冷媒の熱を室内空気へ放出させることで、室内の暖房が行われる。 The refrigerant circuit (11) of the eleventh invention is configured to perform a heating operation for heating indoor air. That is, indoor heating is performed by sending the refrigerant compressed by the compression mechanism (20) to the indoor heat exchanger (13) and releasing the heat of the refrigerant into the indoor air.
　本発明の油冷却熱交換器（80）は、室内に設置されることで室内の補助暖房器として機能する。即ち、暖房動作中において、油分離手段（60）で分離した油が油冷却熱交換器（80）を流れると、油冷却熱交換器（80）内の油と室内空気とが熱交換し、油の熱が室内空気へ放出される。これにより、室内空気が加熱されるので、室内の暖房能力が向上する。同時に、油冷却熱交換器（80）では、油が室内空気によって冷却される。冷却後の油は、圧縮機構（20）の圧縮行程中の冷媒を冷却するために、該圧縮機構（20）へ供給される。 The oil cooling heat exchanger (80) of the present invention functions as an indoor auxiliary heater when installed indoors. That is, during heating operation, when the oil separated by the oil separation means (60) flows through the oil cooling heat exchanger (80), the oil in the oil cooling heat exchanger (80) and the room air exchange heat, Oil heat is released into the room air. Thereby, since indoor air is heated, indoor heating capability improves. At the same time, in the oil cooling heat exchanger (80), the oil is cooled by room air. The cooled oil is supplied to the compression mechanism (20) in order to cool the refrigerant during the compression stroke of the compression mechanism (20).
　第１２の発明は、第１０の発明の冷凍装置において、上記冷媒回路（11）は、室内に設置される室内熱交換器（13）を有して該室内熱交換器（13）を流れる冷媒で室内空気を加熱する暖房動作と、該室内熱交換器（13）を流れる冷媒で室内空気を冷却する冷房動作とを切り換えて行うように構成され、上記油供給回路（70）には、室内に設置されて上記暖房動作中に油の熱を室内空気へ放出する第１の油冷却熱交換器（80a）と、室外に設置されて上記冷房動作中に油の熱を室内空気へ放出する第２の油冷却熱交換器（80b）とが接続されていることを特徴とする。 A twelfth invention is the refrigeration apparatus of the tenth invention, wherein the refrigerant circuit (11) has an indoor heat exchanger (13) installed indoors and flows through the indoor heat exchanger (13). The air supply circuit (70) includes a heating operation for heating the indoor air and a cooling operation for cooling the indoor air with the refrigerant flowing through the indoor heat exchanger (13). A first oil-cooling heat exchanger (80a) that is installed in the room and releases heat of the oil to the room air during the heating operation, and is disposed outside and discharges the heat of the oil to the room air during the cooling operation. The second oil cooling heat exchanger (80b) is connected.
　第１２の発明の冷媒回路（11）は、室内空気を加熱する暖房動作と、室内空気を冷却する冷房動作とが切り換えて行われるように構成されている。つまり、圧縮機構（20）で圧縮された冷媒を室内熱交換器（13）へ送り、冷媒の熱を室内空気へ放出させることで、室内の暖房が行われる。また、低圧のガス冷媒を室内熱交換器（13）へ送り、室内空気から冷媒へ吸熱させることで、室内の冷房が行われる。 The refrigerant circuit (11) of the twelfth aspect of the invention is configured to be switched between a heating operation for heating the indoor air and a cooling operation for cooling the indoor air. That is, indoor heating is performed by sending the refrigerant compressed by the compression mechanism (20) to the indoor heat exchanger (13) and releasing the heat of the refrigerant into the indoor air. Moreover, indoor cooling is performed by sending low-pressure gas refrigerant to the indoor heat exchanger (13) and absorbing heat from the indoor air to the refrigerant.
　本発明の油供給回路（70）には、室内に設置される第１の油冷却熱交換器（80a）と、室外に設置される第２の油冷却熱交換器（80b）とが設けられる。暖房動作中において、油分離手段（60）で分離した油が第１の油冷却熱交換器（80a）を流れ、第１の油冷却熱交換器（80a）内の油の熱が室内空気へ放出される。これにより、室内の暖房能力が向上する。冷房動作中には、油分離手段（60）で分離した油が第２の油冷却熱交換器（80b）を流れ、第２の油冷却熱交換器（80b）内の油の熱が室外空気へ放出される。これにより、油の熱が室内へ放出されることがないので、室内の冷房能力が低下してしまうこともない。 The oil supply circuit (70) of the present invention is provided with a first oil cooling heat exchanger (80a) installed indoors and a second oil cooling heat exchanger (80b) installed outdoor. . During the heating operation, the oil separated by the oil separation means (60) flows through the first oil cooling heat exchanger (80a), and the heat of the oil in the first oil cooling heat exchanger (80a) is transferred to the room air. Released. Thereby, the indoor heating capability improves. During the cooling operation, the oil separated by the oil separation means (60) flows through the second oil cooling heat exchanger (80b), and the heat of the oil in the second oil cooling heat exchanger (80b) is the outdoor air. Is released. Thereby, since the heat of oil is not discharged | emitted indoors, the indoor cooling capability will not fall.
　本発明によれば、油供給回路（70）によって圧縮機構（20）へ油を供給して圧縮行程中の油を冷却することで、圧縮機構（20）での冷媒の圧縮に要する動力を低減すると共に、油供給回路（70）を流れる油のエネルギーを回収機構（40）によって回収している。これにより、本発明によれば、圧縮行程中の冷媒を油によって確実に冷却して冷媒の圧縮動力を低減でき、且つ油の昇圧に要する圧縮機構（20）の動力を回収することができる。つまり、圧縮機構（20）の冷媒を冷却するために油を積極的に圧縮機構（20）へ供給すると、圧縮機構（20）では、油の昇圧に要する動力も増大してしまうが、本発明では、このように昇圧された油のエネルギーを動力として回収しているので、冷凍装置全体としての動力を大幅に低減することが可能となる。 According to the present invention, the power required for compressing the refrigerant in the compression mechanism (20) is reduced by supplying oil to the compression mechanism (20) by the oil supply circuit (70) and cooling the oil in the compression stroke. In addition, the energy of the oil flowing through the oil supply circuit (70) is recovered by the recovery mechanism (40). Thereby, according to this invention, the refrigerant | coolant in a compression process can be reliably cooled with oil, the compression power of a refrigerant | coolant can be reduced, and the motive power of the compression mechanism (20) required for pressure | voltage rise of oil can be collect | recovered. That is, when oil is positively supplied to the compression mechanism (20) to cool the refrigerant of the compression mechanism (20), the compression mechanism (20) also increases the power required for boosting the oil. Then, since the oil energy thus boosted is recovered as power, the power of the entire refrigeration apparatus can be greatly reduced.
　また、このように多量の油を圧縮機構（20）へ導入すると、圧縮機構（20）から吐出される冷媒の温度を低く抑えることができる。その結果、吐出冷媒の温度上昇に起因する冷凍装置のシステム異常や、圧縮機構（20）の損傷を未然に回避できる。また、圧縮機構（20）の各摺動部の温度上昇も抑えることができ、各摺動部の焼き付きを確実に防止できると共に油（冷凍機油）の劣化も防止できる。その結果、冷凍装置の信頼性を更に向上できる。 Moreover, when a large amount of oil is introduced into the compression mechanism (20) in this way, the temperature of the refrigerant discharged from the compression mechanism (20) can be kept low. As a result, the system abnormality of the refrigeration apparatus and the damage to the compression mechanism (20) due to the temperature rise of the discharged refrigerant can be avoided in advance. Moreover, the temperature rise of each sliding part of a compression mechanism (20) can also be suppressed, the seizing of each sliding part can be prevented reliably, and deterioration of oil (refrigeration machine oil) can also be prevented. As a result, the reliability of the refrigeration apparatus can be further improved.
　加えて、圧縮機構（20）へ油を多量に導入することで、圧縮機構（20）のモータの周囲の温度も低く抑えることができる。その結果、モータの効率を向上させて、圧縮機構（20）の入力を更に削減することができる。 In addition, by introducing a large amount of oil into the compression mechanism (20), the temperature around the motor of the compression mechanism (20) can be kept low. As a result, the efficiency of the motor can be improved and the input of the compression mechanism (20) can be further reduced.
　特に、第２の発明では、圧縮機構（20）の圧縮行程の少なくとも一部の期間で冷媒が等温圧縮されるように油を供給しているので、比較的多量の油を圧縮機構（20）へ供給する必要がある。しかしながら、本発明によれば、回収機構（40）が、このような多量の油からエネルギーを動力として回収しているので、等温圧縮によって冷媒の圧縮動力を効果的に低減でき、且つ回収機構（40）によって回収される動力（即ち、エネルギー）を増大させることができる。 In particular, in the second invention, oil is supplied so that the refrigerant is isothermally compressed during at least a part of the compression stroke of the compression mechanism (20), so that a relatively large amount of oil is supplied to the compression mechanism (20). Need to be supplied to. However, according to the present invention, since the recovery mechanism (40) recovers energy from such a large amount of oil as power, the compression power of the refrigerant can be effectively reduced by isothermal compression, and the recovery mechanism ( The power (ie energy) recovered by 40) can be increased.
　第３の発明では、高圧冷媒を臨界圧力以上まで圧縮する、超臨界サイクルを行いながら、低温油を圧縮機構（20）へ導入するようにしている。これにより、圧縮機構（20）の圧縮行程では、冷媒を凝縮させることなく、等温変化に近い状態で圧縮でき、冷媒の圧縮動力を効果的に削減できる。 In the third invention, the low temperature oil is introduced into the compression mechanism (20) while performing a supercritical cycle in which the high pressure refrigerant is compressed to a critical pressure or higher. Accordingly, in the compression stroke of the compression mechanism (20), the refrigerant can be compressed in a state close to an isothermal change without condensing the refrigerant, and the compression power of the refrigerant can be effectively reduced.
　更に、第４の発明では、低温油を圧縮機構（20）の圧縮途中へ供給するようにしている。これにより、本発明では、圧縮機構（20）で冷媒を有る程度昇温させてから、昇温後の冷媒を油で冷却することができる。その結果、低温油によって冷媒を確実に冷却することができ、等温圧縮による圧縮動力の低減効果を更に向上させることができる。 Furthermore, in the fourth aspect of the invention, low temperature oil is supplied during the compression of the compression mechanism (20). Thereby, in this invention, after raising a temperature to a certain extent with a compression mechanism (20), the refrigerant | coolant after temperature rising can be cooled with oil. As a result, the refrigerant can be reliably cooled by the low-temperature oil, and the effect of reducing the compression power by isothermal compression can be further improved.
　また、第５の発明では、低温油を圧縮機構（20）の吸入側へ供給するようにしている。これにより、本発明では、圧縮機構（20）の圧縮行程の開始時から冷媒を低温油によって冷却することができ、等温圧縮による圧縮動力の低減効果を更に向上させることができる。 In the fifth invention, low temperature oil is supplied to the suction side of the compression mechanism (20). Thereby, in this invention, a refrigerant | coolant can be cooled with low temperature oil from the start of the compression process of a compression mechanism (20), and the reduction effect of the compression power by isothermal compression can further be improved.
　第６の発明では、回収機構（40）で回収した油のエネルギーによって出力軸（42）を回転させることができ、この回転動力を所定の動力源として利用できる。そして、第７の発明によれば、出力軸（42）の回転動力を圧縮機構（20）の駆動動力として利用できる。また、第８の発明によれば、膨張機構（30）で回収した冷媒のエネルギーと、回収機構（40）で回収した油のエネルギーとの双方で出力軸（42）を回転させることができ、出力軸（42）で発生する回転動力を増大させることができる。更に、第９の発明によれば、出力軸（42）の回転動力を利用して、発電機（45）で電力を発生させることができ、この電力を冷凍装置の各要素機械の動力源として適宜利用できる。 In the sixth invention, the output shaft (42) can be rotated by the energy of the oil recovered by the recovery mechanism (40), and this rotational power can be used as a predetermined power source. And according to 7th invention, the rotational power of an output shaft (42) can be utilized as a drive power of a compression mechanism (20). Further, according to the eighth invention, the output shaft (42) can be rotated by both the energy of the refrigerant recovered by the expansion mechanism (30) and the energy of the oil recovered by the recovery mechanism (40), The rotational power generated at the output shaft (42) can be increased. Furthermore, according to the ninth aspect, electric power can be generated by the generator (45) using the rotational power of the output shaft (42), and this electric power can be used as a power source for each element machine of the refrigeration apparatus. It can be used as appropriate.
　第１０の発明では、油分離手段（60）で分離した油を油冷却熱交換器（80）で冷却し、冷却後の油を圧縮機構（20）へ供給するので、圧縮機構（20）の圧縮行程中の冷媒を効果的に冷却することができる。 In the tenth invention, the oil separated by the oil separation means (60) is cooled by the oil cooling heat exchanger (80), and the cooled oil is supplied to the compression mechanism (20). The refrigerant in the compression stroke can be effectively cooled.
　特に第１１の発明では、室内の暖房動作中において、油冷却熱交換器（80）内の油の熱を室内へ放出させて該油を冷却するようにしている。これにより、本発明によれば、室内空気を冷媒と油との双方で加熱することができる。その結果、室内の暖房能力を充分に得ることができる。 Particularly in the eleventh aspect of the invention, during the indoor heating operation, the oil in the oil cooling heat exchanger (80) is discharged into the room to cool the oil. Thereby, according to this invention, indoor air can be heated with both a refrigerant | coolant and oil. As a result, the room heating capacity can be sufficiently obtained.
　更に第１２の発明では、室内の暖房動作中において、第１の油冷却熱交換器（80a）内の油の熱を室内へ放出させて該油を冷却するようにし、室内の冷房動作中において、第２の油冷却熱交換器（80b）内の油の熱を室外へ放出させて該油を冷却するようにしている。これにより、本発明によれば、暖房運転中には、室内空気を冷媒と油との双方で加熱することができ、室内の暖房能力を充分に得ることができる。また、冷房運転中には、油の熱が室内空気へ伝わることを回避できるので、室内の冷房能力も充分に得ることができる。 Furthermore, in the twelfth invention, during the indoor heating operation, the heat of the oil in the first oil cooling heat exchanger (80a) is discharged into the room to cool the oil, and during the indoor cooling operation, The heat of the oil in the second oil cooling heat exchanger (80b) is discharged to the outside to cool the oil. Thereby, according to this invention, during heating operation, indoor air can be heated with both a refrigerant | coolant and oil, and indoor heating capability can fully be acquired. Further, during the cooling operation, it is possible to avoid the heat of the oil being transmitted to the room air, so that the room cooling capacity can be sufficiently obtained.
図１は、実施形態１に係る空気調和装置の概略構成を示す配管系統図である。FIG. 1 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Embodiment 1. 図２は、回収機構を拡大した縦断面図である。FIG. 2 is an enlarged longitudinal sectional view of the recovery mechanism. 図３は、回収機構の内部を表した横断面図であり、ピストンの動作を示すものである。FIG. 3 is a cross-sectional view showing the inside of the recovery mechanism, and shows the operation of the piston. 図４は、本実施形態の理想的な冷凍サイクルを示すものであり、図４(Ａ)はＰ－ｈ線図を、図４(Ｂ)は、Ｐ－Ｖ線図を表したものである。FIG. 4 shows an ideal refrigeration cycle of the present embodiment. FIG. 4 (A) shows a Ph diagram and FIG. 4 (B) shows a PV diagram. . 図５は、一般的な冷凍サイクルを示すものであり、図５(Ａ)はＰ－ｈ線図を、図５(Ｂ)は、Ｐ－Ｖ線図を表したものである。FIG. 5 shows a general refrigeration cycle. FIG. 5 (A) shows a Ph diagram and FIG. 5 (B) shows a PV diagram. 図６は、油インジェクション量と、圧縮機構の動力との関係を示すグラフである。FIG. 6 is a graph showing the relationship between the oil injection amount and the power of the compression mechanism. 図７は、油インジェクション量と、ＣＯＰの改善率との関係を示すグラフである。FIG. 7 is a graph showing the relationship between the oil injection amount and the COP improvement rate. 図８は、実施形態１の変形例に係る空気調和装置の概略構成を示す配管系統図である。FIG. 8 is a piping system diagram illustrating a schematic configuration of an air-conditioning apparatus according to a modification of the first embodiment. 図９は、実施形態２に係る空気調和装置の概略構成を示す配管系統図である。FIG. 9 is a piping diagram illustrating a schematic configuration of the air-conditioning apparatus according to Embodiment 2. 図１０は、実施形態３に係る空気調和装置の概略構成を示す配管系統図である。FIG. 10 is a piping diagram illustrating a schematic configuration of the air-conditioning apparatus according to Embodiment 3. 図１１は、実施形態４に係る空気調和装置の概略構成を示す配管系統図である。FIG. 11 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Embodiment 4. 図１２は、実施形態５に係る空気調和装置における圧縮機構の動作中の第１の状態を示す横断面図である。FIG. 12 is a cross-sectional view illustrating a first state during operation of the compression mechanism in the air-conditioning apparatus according to Embodiment 5. 図１３は、実施形態５に係る空気調和装置における圧縮機構の動作中の第２の状態を示す横断面図である。FIG. 13 is a cross-sectional view illustrating a second state during operation of the compression mechanism in the air-conditioning apparatus according to Embodiment 5. 図１４は、コントローラの構成を示すブロック図である。FIG. 14 is a block diagram showing the configuration of the controller. 図１５は、実施形態６に係る空気調和装置のコントローラの構成を示すブロック図である。FIG. 15 is a block diagram illustrating a configuration of a controller of the air-conditioning apparatus according to Embodiment 6. 図１６は、圧縮機構の第１の状態を示す横断面図である。FIG. 16 is a cross-sectional view showing a first state of the compression mechanism. 図１７は、圧縮機構の第２の状態を示す横断面図である。FIG. 17 is a cross-sectional view showing a second state of the compression mechanism. 図１８は、比較例の圧縮機での等温圧縮による動力削減効果を示すグラフである。FIG. 18 is a graph showing the power reduction effect by isothermal compression in the compressor of the comparative example. 図１９は、実施形態６の圧縮機構での等温圧縮による動力削減効果を示すグラフである。FIG. 19 is a graph showing the power reduction effect by isothermal compression in the compression mechanism of the sixth embodiment. 図２０は、実施形態７に係る空気調和装置の概略構成を示す配管系統図である。FIG. 20 is a piping diagram illustrating a schematic configuration of the air-conditioning apparatus according to Embodiment 7. 図２１は、実施形態８に係る空気調和装置（暖房運転中）の概略構成を示す配管系統図である。FIG. 21 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus (during heating operation) according to the eighth embodiment. 図２２は、実施形態８に係る空気調和装置（冷房運転中）の概略構成を示す配管系統図である。FIG. 22 is a piping diagram illustrating a schematic configuration of the air-conditioning apparatus (during cooling operation) according to the eighth embodiment. 図２３は、その他の実施形態の変形例１に係る空気調和装置の概略構成を示す配管系統図である。FIG. 23 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Modification 1 of the other embodiment. 図２４は、その他の実施形態の変形例２に係る空気調和装置の概略構成を示す配管系統図である。FIG. 24 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Modification 2 of the other embodiment. 図２５は、その他の実施形態の変形例３に係る空気調和装置の概略構成を示す配管系統図である。FIG. 25 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Modification 3 of the other embodiment. 図２６は、その他の実施形態の変形例４に係る空気調和装置の概略構成を示す配管系統図である。FIG. 26 is a piping diagram illustrating a schematic configuration of an air-conditioning apparatus according to Modification 4 of the other embodiment. 図２７は、その他の等温圧縮が行われる冷凍サイクルの一例を示すＰ－ｈ線図である。FIG. 27 is a Ph diagram illustrating an example of another refrigeration cycle in which isothermal compression is performed. 図２８は、比較例に係る圧縮機構の横断面図である。FIG. 28 is a cross-sectional view of a compression mechanism according to a comparative example.
符号の説明Explanation of symbols
10　　空気調和装置（冷凍装置）
11　　冷媒回路
12　　室内熱交換器
13　　室内熱交換器
20　　圧縮機構
30　　膨張機構
40　　回収機構
42　　出力軸
45　　発電機
50　　ピストン（可動部）
60　　油分離器（油分離手段）
70　　油導入管（油供給回路）
80　　油クーラ（油冷却熱交換器）
80a　 室内側油クーラ（第１の油冷却熱交換器）
80b　 室外側油クーラ（第２の油冷却熱交換器） 10 Air conditioning equipment (refrigeration equipment)
11 Refrigerant circuit
12 Indoor heat exchanger
13 Indoor heat exchanger
20 Compression mechanism
30 Expansion mechanism
40 Recovery mechanism
42 Output shaft
45 Generator
50 piston (movable part)
60 Oil separator (Oil separation means)
70 Oil introduction pipe (oil supply circuit)
80 Oil cooler (oil cooling heat exchanger)
80a Indoor oil cooler (first oil cooling heat exchanger)
80b Outdoor oil cooler (second oil cooling heat exchanger)
　　以下、本発明の実施形態を図面に基づいて詳細に説明する。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
　　《発明の実施形態１》
　本発明の実施形態１ついて説明する。本発明に係る冷凍装置は、室内の空調を行う空気調和装置（10）を構成している。空気調和装置（10）は、冷房運転と暖房運転とを切り換えて行うように構成されている。 Embodiment 1 of the Invention
Embodiment 1 of the present invention will be described. The refrigeration apparatus according to the present invention constitutes an air conditioner (10) that performs indoor air conditioning. The air conditioner (10) is configured to switch between a cooling operation and a heating operation.
　　〈空気調和装置の全体構成〉
　図１に示すように、空気調和装置（10）は、冷媒回路（11）を備えている。冷媒回路（11）では、冷媒が循環することで冷凍サイクルが行われる。冷媒回路（11）には、冷媒として二酸化炭素（ＣＯ２）が充填されている。そして、冷媒回路（11）では、冷媒が臨界圧力以上まで圧縮される冷凍サイクル（いわゆる超臨界サイクル）が行われる。更に、冷媒回路（11）には、ポリアルキレングリコール（ＰＡＧ）から成る油（冷凍機油）が混在している。 <Overall configuration of air conditioner>
As shown in FIG. 1, the air conditioner (10) includes a refrigerant circuit (11). In the refrigerant circuit (11), a refrigeration cycle is performed by circulating the refrigerant. The refrigerant circuit (11) is filled with carbon dioxide (CO 2 ) as a refrigerant. In the refrigerant circuit (11), a refrigeration cycle (so-called supercritical cycle) in which the refrigerant is compressed to a critical pressure or higher is performed. Furthermore, the refrigerant circuit (11) contains oil (refrigerating machine oil) made of polyalkylene glycol (PAG).
　冷媒回路（11）には、油動力回収型圧縮ユニット（C/O）と、膨張ユニット（E）と、室外熱交換器（12）と、室内熱交換器（13）と、第１四方切換弁（14）と、第２四方切換弁（15）とが設けられている。また、冷媒回路（11）には、油分離器（60）と油導入路（70）と油クーラ（80）とが設けられている。 The refrigerant circuit (11) includes an oil power recovery type compression unit (C / O), an expansion unit (E), an outdoor heat exchanger (12), an indoor heat exchanger (13), and a first four-way switching. A valve (14) and a second four-way switching valve (15) are provided. The refrigerant circuit (11) is provided with an oil separator (60), an oil introduction path (70), and an oil cooler (80).
　油動力回収型圧縮ユニット（C/O）は、圧縮機構（20）と回収機構（40）と電動機（25）とがケーシング（図示省略）の内部に収容されて構成されている。圧縮機構（20）は、ロータリ式の容積型圧縮機を構成している。圧縮機構（20）では、その圧縮室において冷媒が臨界圧力以上まで圧縮される。回収機構（40）は、本体部（41）と出力軸（42）とを有している。回収機構（40）の本体部（41）は、ロータリ式の容積型の流体機械を構成している。出力軸（42）は、圧縮機構（20）と上記本体部（41）とを連結している。電動機（25）は、出力軸（42）を回転駆動させるモータを構成し、出力周波数（即ち、出力軸の回転速度）を可変とするインバータ式に構成されている。 The oil power recovery type compression unit (C / O) includes a compression mechanism (20), a recovery mechanism (40), and an electric motor (25) housed in a casing (not shown). The compression mechanism (20) constitutes a rotary positive displacement compressor. In the compression mechanism (20), the refrigerant is compressed to a critical pressure or higher in the compression chamber. The recovery mechanism (40) has a main body (41) and an output shaft (42). The main body (41) of the recovery mechanism (40) constitutes a rotary positive displacement fluid machine. The output shaft (42) connects the compression mechanism (20) and the main body (41). The electric motor (25) constitutes a motor that rotationally drives the output shaft (42), and is configured as an inverter type in which the output frequency (that is, the rotational speed of the output shaft) is variable.
　油動力回収型圧縮ユニット（C/O）には、圧縮機構（20）へ冷媒を吸入させるための吸入管（22）と、圧縮機構（20）で圧縮された冷媒を吐出させるための吐出管（23）とが設けられている。また、油動力回収型圧縮ユニット（C/O）には、回収機構（40）の本体部（41）へ油（冷凍機油）を流入させるための油流入管（43）と、この本体部（41）の油を流出させるための油流出管（44）とが設けられている。 The oil power recovery type compression unit (C / O) has a suction pipe (22) for sucking refrigerant into the compression mechanism (20) and a discharge pipe for discharging refrigerant compressed by the compression mechanism (20). (23) is provided. The oil power recovery type compression unit (C / O) has an oil inflow pipe (43) through which oil (refrigeration oil) flows into the main body (41) of the recovery mechanism (40), and the main body ( 41) and an oil spill pipe (44) for spilling the oil.
　膨張ユニット（E）は、膨張機構（30）と膨張側出力軸（31）と膨張側発電機（35）とがケーシング（図示省略）の内部に収容されて構成されている。膨張機構（30）は、ロータリ式の容積型膨張機構を構成している。膨張機構（30）では、その膨張室において冷媒が膨張して減圧される。膨張機構（30）では、膨張室で膨張する冷媒によって可動部としてのピストン（図示省略）が回転駆動され、ピストンと連結する膨張側出力軸（31）が更に回転駆動される。これにより、膨張側発電機（35）が駆動されて発電が行われる。つまり、膨張側発電機（35）は、膨張機構（30）の膨張側出力軸（31）と連結して駆動される駆動対象を構成している。膨張ユニット（E）で発電された電力は、油動力回収型圧縮ユニット（C/O）や他の要素機械の動力として利用される。また、膨張ユニット（E）には、膨張機構（30）へ冷媒を流入させるための流入管（33）と、膨張機構（30）から冷媒を流出させるための流出管（34）とが設けられている。 The expansion unit (E) includes an expansion mechanism (30), an expansion side output shaft (31), and an expansion side generator (35) housed in a casing (not shown). The expansion mechanism (30) constitutes a rotary positive displacement expansion mechanism. In the expansion mechanism (30), the refrigerant expands and decompresses in the expansion chamber. In the expansion mechanism (30), a piston (not shown) as a movable portion is rotationally driven by the refrigerant expanding in the expansion chamber, and the expansion-side output shaft (31) connected to the piston is further rotationally driven. Thereby, an expansion side generator (35) is driven and electric power generation is performed. That is, the expansion-side generator (35) constitutes a drive target that is driven by being connected to the expansion-side output shaft (31) of the expansion mechanism (30). The electric power generated by the expansion unit (E) is used as power for the oil power recovery type compression unit (C / O) and other element machines. The expansion unit (E) is provided with an inflow pipe (33) for allowing the refrigerant to flow into the expansion mechanism (30) and an outflow pipe (34) for allowing the refrigerant to flow out from the expansion mechanism (30). ing.
　室外熱交換器（12）は、冷媒を室外空気と熱交換させるための空気熱交換器である。また、室内熱交換器（13）は、冷媒を室内空気と熱交換させるための空気熱交換器である。 The outdoor heat exchanger (12) is an air heat exchanger for exchanging heat between the refrigerant and outdoor air. The indoor heat exchanger (13) is an air heat exchanger for exchanging heat between the refrigerant and room air.
　第１四方切換弁（14）及び第２四方切換弁（15）は、それぞれ第１から第４までのポートを有している。第１四方切換弁（14）では、第１のポートが吐出ライン（18）を介して上記吐出管（23）と接続し、第２のポートが吸入ライン（17）を介して上記吸入管（22）と接続している。また、第１四方切換弁（14）では、第３のポートが室外熱交換器（12）の一端と接続し、第４のポートが室内熱交換器（13）の一端と接続している。第２四方切換弁（15）では、第１のポートが上記流入管（33）と接続し、第２のポートが上記流出管（34）と接続している。また、第２四方切換弁（15）では、第３のポートが室外熱交換器（12）の他端と接続し、第４のポートが室内熱交換器（13）の他端と接続している。 The first four-way switching valve (14) and the second four-way switching valve (15) have first to fourth ports, respectively. In the first four-way switching valve (14), a first port is connected to the discharge pipe (23) via a discharge line (18), and a second port is connected to the suction pipe (17) via a suction line (17). 22) is connected. In the first four-way switching valve (14), the third port is connected to one end of the outdoor heat exchanger (12), and the fourth port is connected to one end of the indoor heat exchanger (13). In the second four-way switching valve (15), the first port is connected to the inflow pipe (33), and the second port is connected to the outflow pipe (34). In the second four-way switching valve (15), the third port is connected to the other end of the outdoor heat exchanger (12), and the fourth port is connected to the other end of the indoor heat exchanger (13). Yes.
　第１四方切換弁（14）と第２四方切換弁（15）とは、それぞれ、第１のポートと第３のポートとが連通し且つ第２のポートと第４のポートとが連通する第１状態（図１の実線で示す状態）と、第１のポートと第４のポートが連通し且つ第２のポートと第３のポートが連通する第２状態（図１の破線で示す状態）とに切り換わるように構成されている。 The first four-way switching valve (14) and the second four-way switching valve (15) are respectively a first port and a third port that communicate with each other and a second port and a fourth port that communicate with each other. 1 state (state indicated by a solid line in FIG. 1), and 2nd state (state indicated by a broken line in FIG. 1) in which the first port and the fourth port communicate with each other and the second port and the third port communicate with each other. It is comprised so that it may switch to.
　油分離器（60）は、上記吐出ライン（18）の途中に設けられている。油分離器（60）は、縦長の略円筒形状の密閉容器から成り、高圧冷媒中から油を分離する油分離手段を構成している。油分離器（60）には、その胴部に冷媒／油流入管（61）が接続され、その頂部に冷媒排出管（62）が接続され、その底部に油排出管（63）が接続されている。油分離器（60）では、冷媒／油流入管（61）から流入した冷媒中から油が分離される。なお、油分離器（60）での油の分離方法としては、旋回流を利用して油を遠心分離する方法や、冷媒と油との比重差を利用して油を沈降分離する方法等が挙げられる。そして、油分離器（60）内では、油が分離された後の冷媒が冷媒排出管（62）を流出し、分離後の油が油排出管（63）を流出する。 The oil separator (60) is provided in the middle of the discharge line (18). The oil separator (60) is composed of a vertically long, substantially cylindrical sealed container, and constitutes an oil separating means for separating oil from the high-pressure refrigerant. The oil separator (60) is connected with a refrigerant / oil inflow pipe (61) at its body, with a refrigerant discharge pipe (62) at its top and with an oil discharge pipe (63) at its bottom. ing. In the oil separator (60), oil is separated from the refrigerant flowing in from the refrigerant / oil inflow pipe (61). In addition, as an oil separation method in the oil separator (60), there are a method of centrifugal separation of oil using a swirl flow, a method of sedimentation separation of oil using a specific gravity difference between refrigerant and oil, and the like. Can be mentioned. In the oil separator (60), the refrigerant after the oil is separated flows out of the refrigerant discharge pipe (62), and the oil after the separation flows out of the oil discharge pipe (63).
　油導入路（70）は、油分離器（60）で分離した油を圧縮機構（20）へ供給する油供給回路を構成している。油導入路（70）は、第１導油管（71）と第２導油管（72）とを含んで構成されている。 The oil introduction path (70) constitutes an oil supply circuit for supplying the oil separated by the oil separator (60) to the compression mechanism (20). The oil introduction path (70) includes a first oil guide pipe (71) and a second oil guide pipe (72).
　第１導油管（71）は、その始端が油分離器（60）の油排出管（63）と接続し、その終端が油流入管（43）と接続している。第１導油管（71）には、上記油クーラ（80）が設けられている。油クーラ（80）は、油分離器（60）で分離した油を冷却する冷却手段であり、油冷却熱交換器を構成している。本実施形態の油クーラ（80）は、空冷式の熱交換器で構成されている。 The first oil guiding pipe (71) has a start end connected to the oil discharge pipe (63) of the oil separator (60) and a terminal end connected to the oil inflow pipe (43). The first oil guide pipe (71) is provided with the oil cooler (80). The oil cooler (80) is a cooling means for cooling the oil separated by the oil separator (60), and constitutes an oil cooling heat exchanger. The oil cooler (80) of the present embodiment is configured by an air-cooled heat exchanger.
　第２導油管（72）は、その始端が油流出管（44）と接続し、その終端が圧縮機構（20）の油インジェクションポート（24）と接続している。圧縮機構（20）の油インジェクションポート（24）は、その圧縮室での圧縮行程の途中箇所に開口している。つまり、本実施形態の油導入路（70）は、油分離器（60）で分離した油を圧縮機構（20）の圧縮行程の途中へ供給するように、圧縮機構（20）に接続されている。 The second oil guide pipe (72) has its start end connected to the oil outflow pipe (44) and its end connected to the oil injection port (24) of the compression mechanism (20). The oil injection port (24) of the compression mechanism (20) opens in the middle of the compression stroke in the compression chamber. That is, the oil introduction path (70) of the present embodiment is connected to the compression mechanism (20) so as to supply the oil separated by the oil separator (60) in the middle of the compression stroke of the compression mechanism (20). Yes.
　以上のような構成の油導入路（70）は、圧縮機構（20）の圧縮行程中の冷媒を冷却するように油分離手段（60）で分離した油を圧縮機構（20）へ供給する油供給回路を構成している。また、油導入路（70）は、圧縮機構（20）の圧縮行程の少なくとも一部の期間で冷媒が等温圧縮されるように圧縮機構（20）へ油を供給するように構成されている。 The oil introduction path (70) configured as described above is an oil that supplies the oil separated by the oil separation means (60) to the compression mechanism (20) so as to cool the refrigerant during the compression stroke of the compression mechanism (20). A supply circuit is configured. The oil introduction path (70) is configured to supply oil to the compression mechanism (20) so that the refrigerant is isothermally compressed during at least a part of the compression stroke of the compression mechanism (20).
　　〈回収機構の構成〉
　上記回収機構（40）の構成について図２及び図３を参照しながら更に説明する。
回収機構（40）は、油の動力（即ち、油の持つエネルギー）を回収するものである。つまり、高圧冷媒と分離された油は、圧縮機構（20）において油を昇圧させるために使われた動力を、運動エネルギー、位置エネルギー、圧力エネルギー等のエネルギーとして保有している。そこで、回収機構（40）は、このような油のエネルギーを動力として回収する。回収機構（40）の本体部（41）は、いわゆる揺動ピストン型のロータリ式流体機械で構成されている。また、出力軸（42）は、その一端が本体部（41）と連結し、その他端部が圧縮機構（20）の可動部（ピストン）と連結している。つまり、圧縮機構（20）は、回収機構（40）の出力軸（42）と連結して駆動される駆動対象を構成している。また、出力軸（42）には、主軸部（42a）と偏心部（42b）とが形成されている。偏心部（42b）は、主軸部（42a）に対して所定量だけ偏心し、且つ主軸部（42a）よりも大径に構成されている。 <Configuration of collection mechanism>
The configuration of the recovery mechanism (40) will be further described with reference to FIGS.
The recovery mechanism (40) recovers the power of the oil (that is, the energy of the oil). In other words, the oil separated from the high-pressure refrigerant has the power used to pressurize the oil in the compression mechanism (20) as energy such as kinetic energy, potential energy, and pressure energy. Therefore, the recovery mechanism (40) recovers such oil energy as power. The main body (41) of the recovery mechanism (40) is constituted by a so-called oscillating piston type rotary fluid machine. The output shaft (42) has one end connected to the main body (41) and the other end connected to the movable part (piston) of the compression mechanism (20). That is, the compression mechanism (20) constitutes a drive target that is driven by being connected to the output shaft (42) of the recovery mechanism (40). The output shaft (42) is formed with a main shaft portion (42a) and an eccentric portion (42b). The eccentric part (42b) is eccentric by a predetermined amount with respect to the main shaft part (42a) and is configured to have a larger diameter than the main shaft part (42a).
　回収機構の本体部（41）には、その下部から上部へ向かって順に、フロントヘッド（46）、シリンダ（47）、及びリアヘッド（48）が設けられている。シリンダ（47）は、上下に出力軸（42）が貫通する筒状に形成されている。シリンダ（47）は、その下端がフロントヘッド（46）に閉塞され、その上端がリアヘッド（48）に閉塞されている。 The main body (41) of the recovery mechanism is provided with a front head (46), a cylinder (47), and a rear head (48) in that order from the bottom to the top. The cylinder (47) is formed in a cylindrical shape through which the output shaft (42) passes vertically. The cylinder (47) has a lower end closed by the front head (46) and an upper end closed by the rear head (48).
　図３にも示すように、シリンダ（47）の内部（シリンダ室）には、可動部としてのピストン（50）が収容されている。ピストン（50）は、円環状あるいは円筒状に形成されている。ピストン（50）の内部には、出力軸（42）の偏心部（42b）が係合して連結している。ピストン（50）は、その外周面がシリンダ（47）の内周面に、一方の端面がフロントヘッド（46）に、他方の端面がリアヘッド（48）にそれぞれ摺接している。シリンダ（47）内には、その内周面とピストン（50）の外周面との間に油室（49）が形成される。油室（49）は、上記油流入管（43）及び油流出管（44）が連通している。 As shown in FIG. 3, a piston (50) as a movable part is accommodated in the cylinder (47) (cylinder chamber). The piston (50) is formed in an annular shape or a cylindrical shape. The eccentric portion (42b) of the output shaft (42) is engaged and connected to the inside of the piston (50). The piston (50) has its outer peripheral surface in sliding contact with the inner peripheral surface of the cylinder (47), one end surface in sliding contact with the front head (46), and the other end surface in contact with the rear head (48). An oil chamber (49) is formed in the cylinder (47) between its inner peripheral surface and the outer peripheral surface of the piston (50). The oil chamber (49) communicates with the oil inflow pipe (43) and the oil outflow pipe (44).
　ピストン（50）には、ブレード（51）が一体に設けられている。ブレード（51）は、ピストン（50）の半径方向へ延びる板状に形成されており、ピストン（50）の外周面から外側へ突出している。このブレード（51）はシリンダ（47）のブレード溝（52）に挿入されている。シリンダ（47）のブレード溝（52）は、シリンダ（47）を厚み方向へ貫通すると共に、シリンダ（47）の内周面に開口している。 The piston (50) is integrally provided with a blade (51). The blade (51) is formed in a plate shape extending in the radial direction of the piston (50), and projects outward from the outer peripheral surface of the piston (50). The blade (51) is inserted into the blade groove (52) of the cylinder (47). The blade groove (52) of the cylinder (47) penetrates the cylinder (47) in the thickness direction, and opens to the inner peripheral surface of the cylinder (47).
　シリンダ（47）には、一対のブッシュ（53）が設けられている。各ブッシュ（53）は、内側面が平面となって外側面が円弧面となるように形成された小片である。シリンダ（47）において、一対のブッシュ（53）は、ブッシュ孔（54）に挿入されてブレード（51）を挟み込んだ状態となる。ブッシュ（53）は、その内側面がブレード（51）と摺接し、その外側面がシリンダ（47）と摺動する。そして、ピストン（50）と一体のブレード（51）は、ブッシュ（53）を介してシリンダ（47）に支持され、シリンダ（47）に対して回動自在で且つ進退自在となっている。 The cylinder (47) is provided with a pair of bushes (53). Each bush (53) is a small piece formed such that the inner surface is a flat surface and the outer surface is a circular arc surface. In the cylinder (47), the pair of bushes (53) are inserted into the bush holes (54) and sandwich the blade (51). The inner surface of the bush (53) is in sliding contact with the blade (51), and the outer surface of the bush (53) slides with the cylinder (47). The blade (51) integrated with the piston (50) is supported by the cylinder (47) via the bush (53), and can rotate and advance and retract with respect to the cylinder (47).
　シリンダ（47）内の油室（49）は、ピストン（50）及びブレード（51）によって仕切られている。そして、図３におけるブレード（51）の左側の部屋が油流入管（43）と連通し、右側の部屋が油流出管（44）と連通している。 The oil chamber (49) in the cylinder (47) is partitioned by the piston (50) and the blade (51). The left chamber of the blade (51) in FIG. 3 communicates with the oil inflow pipe (43), and the right chamber communicates with the oil outflow pipe (44).
　　－運転動作－
　実施形態１に係る空気調和装置（10）の運転動作について説明する。空気調和装置（10）は、第１四方切換弁（14）及び第２四方切換弁（15）の設定に応じて、冷房運転と暖房運転とが可能となっている。まず、空気調和装置（10）の冷房運転時の基本的な動作について説明する。 -Driving operation-
The operation of the air conditioner (10) according to Embodiment 1 will be described. The air conditioner (10) can perform a cooling operation and a heating operation according to the settings of the first four-way switching valve (14) and the second four-way switching valve (15). First, the basic operation during the cooling operation of the air conditioner (10) will be described.
　冷房運転時には、第１四方切換弁（14）及び第２四方切換弁（15）が第１状態（図１に実線で示す状態）に設定され、冷媒回路（11）で冷媒が循環して蒸気圧縮冷凍サイクルが行われる。その結果、冷房運転時には、室外熱交換器（12）が放熱器（凝縮器）となり、室内熱交換器（13）が蒸発器となる冷凍サイクルが行われる。また、冷媒回路（11）では、その高圧が冷媒である二酸化炭素の臨界圧力よりも高い値に設定され、いわゆる超臨界サイクルが行われる。 During the cooling operation, the first four-way switching valve (14) and the second four-way switching valve (15) are set to the first state (the state indicated by the solid line in FIG. 1), and the refrigerant circulates in the refrigerant circuit (11). A compression refrigeration cycle is performed. As a result, during the cooling operation, a refrigeration cycle in which the outdoor heat exchanger (12) serves as a radiator (condenser) and the indoor heat exchanger (13) serves as an evaporator is performed. In the refrigerant circuit (11), the high pressure is set to a value higher than the critical pressure of carbon dioxide, which is a refrigerant, and a so-called supercritical cycle is performed.
　油動力回収型圧縮ユニット（C/O）では、電動機（25）によって圧縮機構（20）が回転駆動される。圧縮機構（20）では、吸入管（22）から圧縮室へ吸入された冷媒が圧縮され、圧縮された冷媒が吐出管（23）より吐出される。圧縮機構（20）から吐出された冷媒は、吐出ライン（18）を流れ、冷媒／油流入管（61）を通じて油分離器（60）内へ流入する。 In the oil power recovery type compression unit (C / O), the compression mechanism (20) is rotationally driven by the electric motor (25). In the compression mechanism (20), the refrigerant sucked into the compression chamber from the suction pipe (22) is compressed, and the compressed refrigerant is discharged from the discharge pipe (23). The refrigerant discharged from the compression mechanism (20) flows through the discharge line (18) and flows into the oil separator (60) through the refrigerant / oil inflow pipe (61).
　油分離器（60）の内部では、冷媒中から油が分離され、油が分離された後の冷媒が上部に溜まり、分離後の油が底部に溜まり込む。分離後の冷媒は、冷媒排出管（62）を流出し、室外熱交換器（12）を流れる。室外熱交換器（12）では、高圧冷媒が室外空気へ放熱する。室外熱交換器（12）を流出した冷媒は、流入管（33）を通じて膨張ユニット（E）の膨張機構（30）へ流入する。 Inside the oil separator (60), the oil is separated from the refrigerant, the refrigerant after the oil is separated accumulates at the top, and the separated oil accumulates at the bottom. The separated refrigerant flows out of the refrigerant discharge pipe (62) and flows through the outdoor heat exchanger (12). In the outdoor heat exchanger (12), the high-pressure refrigerant radiates heat to the outdoor air. The refrigerant that has flowed out of the outdoor heat exchanger (12) flows into the expansion mechanism (30) of the expansion unit (E) through the inflow pipe (33).
　膨張機構（30）では、膨張室で高圧冷媒が膨張し、これによって膨張側出力軸（31）が回転駆動される。その結果、膨張側発電機（35）が駆動されて、膨張側発電機（35）から電力が発生する。この電力は、圧縮機構（20）や他の要素機械へ供給される。膨張機構（30）で膨張した冷媒は、流出管（34）を通じて膨張ユニット（E）から送り出される。 In the expansion mechanism (30), the high-pressure refrigerant expands in the expansion chamber, whereby the expansion-side output shaft (31) is rotationally driven. As a result, the expansion-side generator (35) is driven and electric power is generated from the expansion-side generator (35). This electric power is supplied to the compression mechanism (20) and other element machines. The refrigerant expanded by the expansion mechanism (30) is sent out from the expansion unit (E) through the outflow pipe (34).
　膨張ユニット（E）を流出した冷媒は、室内熱交換器（13）を流れる。室内熱交換器（13）では、冷媒が室内空気から吸熱して蒸発する。その結果、室内空気が冷やされて冷房が行われる。室内熱交換器（13）を流出した冷媒は、吸入管（22）を通じて圧縮機構（20）へ吸入されて再び圧縮される。 The refrigerant that has flowed out of the expansion unit (E) flows through the indoor heat exchanger (13). In the indoor heat exchanger (13), the refrigerant absorbs heat from the indoor air and evaporates. As a result, the room air is cooled and cooling is performed. The refrigerant flowing out of the indoor heat exchanger (13) is sucked into the compression mechanism (20) through the suction pipe (22) and compressed again.
　このような冷房運転時には、空気調和装置（10）の成績係数（ＣＯＰ）を改善するために、油インジェクション動作が行われる。具体的には、油分離器（60）で分離した油は、油排出管（63）を通じて第１導油管（71）を流れる。この冷媒は、油クーラ（80）で所定温度まで冷却される。冷却された油は、油流入管（43）を通じて油動力回収型圧縮ユニット（C/O）の回収機構（40）の本体部（41）へ流入する。 In such cooling operation, an oil injection operation is performed in order to improve the coefficient of performance (COP) of the air conditioner (10). Specifically, the oil separated by the oil separator (60) flows through the first oil guide pipe (71) through the oil discharge pipe (63). This refrigerant is cooled to a predetermined temperature by the oil cooler (80). The cooled oil flows into the main body (41) of the recovery mechanism (40) of the oil power recovery type compression unit (C / O) through the oil inflow pipe (43).
　回収機構（40）の本体部（41）では、油室（49）を流れる油によってピストン（50）が回転駆動され、ピストン（50）がシリンダ（47）内を、図３の(Ａ)→(Ｂ)→(Ｃ)→(Ｄ)→(Ａ)→…という順に偏心回転する。このピストン（50）の偏心回転に伴い、偏心部（42b）、更には主軸部（42a）が回転駆動される。その結果、この回転動力は、圧縮機構（20）を駆動するための駆動動力として利用される。以上のように、油動力回収型圧縮ユニット（C/O）では、回収機構（40）によって回収された油のエネルギーが、圧縮機構（20）の駆動動力として回収され、圧縮機構（20）の動力が軽減される。 In the main body (41) of the recovery mechanism (40), the piston (50) is rotationally driven by the oil flowing through the oil chamber (49), and the piston (50) moves inside the cylinder (47) in FIG. (B) → (C) → (D) → (A) →. With the eccentric rotation of the piston (50), the eccentric portion (42b) and further the main shaft portion (42a) are rotationally driven. As a result, this rotational power is used as driving power for driving the compression mechanism (20). As described above, in the oil power recovery type compression unit (C / O), the energy of the oil recovered by the recovery mechanism (40) is recovered as drive power of the compression mechanism (20), and the compression mechanism (20) Power is reduced.
　油室（49）でエネルギーが回収された油は、所定圧力まで減圧された後、油流出管（44）を通じて回収機構（40）の本体部（41）から流出する。流出後の油は、第２導油管（72）を介して圧縮機構（20）の油インジェクションポート（24）へ流入する。その結果、圧縮機構（20）では、圧縮室での圧縮行程の途中へ低温の油が供給され、油インジェクション動作が行われる。 The oil whose energy has been recovered in the oil chamber (49) is depressurized to a predetermined pressure and then flows out from the main body (41) of the recovery mechanism (40) through the oil outflow pipe (44). The oil after flowing out flows into the oil injection port (24) of the compression mechanism (20) through the second oil guide pipe (72). As a result, in the compression mechanism (20), low temperature oil is supplied during the compression stroke in the compression chamber, and an oil injection operation is performed.
　この油インジェクション動作により、冷房運転時の圧縮機構（20）では、冷媒がＰ－ｈ線図上の等温線に近づくように圧縮され、いわゆる等温圧縮が行われる。この点について、図４(Ａ)及び(Ｂ)を参照しながら説明する。ここで、図４(Ａ)は、理想的な等温圧縮での冷凍サイクルを示すＰ－ｈ線図であり、図４(Ｂ)は、図４(Ａ)の冷凍サイクルに対応するＰ－Ｖ線図である。 By this oil injection operation, in the compression mechanism (20) during the cooling operation, the refrigerant is compressed so as to approach the isotherm on the Ph diagram, and so-called isothermal compression is performed. This point will be described with reference to FIGS. 4 (A) and 4 (B). Here, FIG. 4 (A) is a Ph diagram showing a refrigeration cycle in ideal isothermal compression, and FIG. 4 (B) shows a PV corresponding to the refrigeration cycle in FIG. 4 (A). FIG.
　冷房運転時の冷媒回路（11）では、圧縮機構（20）の吸入側の冷媒が所定温度だけ過熱されるようなスーパーヒート制御が行われる。この吸入冷媒は、図４のＡ点より圧縮機構（20）で圧縮され、所定量だけ昇圧／昇温されてからＢ点で油と混合する。圧縮機構（20）で冷媒と油とが混合されると、上記油クーラ（80）で冷却されて低温となった油により、冷媒が冷却される。つまり、圧縮行程では、Ｂ点以降において冷媒が油によって冷やされながら、更に圧縮される。その結果、冷媒は、図４(Ａ)に示す等温線（例えば約４０℃）に沿うように圧縮されて、目標の高圧圧力（Ｃ点）に至る。このように、Ａ点→Ｂ点→Ｃ点のような挙動で冷媒を圧縮させることで、圧縮機構（20）で冷媒を圧縮するのに要する動力が効果的に低減される。以上のように、本実施形態の圧縮機構（20）では、低圧冷媒が圧縮されてから高圧冷媒に至るまでの圧縮行程（即ち、Ａ点からＣ点に至るまでの行程）において、その一部のＢ点からＣ点の期間で冷媒が等温圧縮される。 In the refrigerant circuit (11) during the cooling operation, superheat control is performed such that the refrigerant on the suction side of the compression mechanism (20) is overheated by a predetermined temperature. The suction refrigerant is compressed by the compression mechanism (20) from the point A in FIG. 4 and is mixed with oil at the point B after the pressure is raised / heated by a predetermined amount. When the refrigerant and oil are mixed by the compression mechanism (20), the refrigerant is cooled by the oil cooled to the low temperature by the oil cooler (80). That is, in the compression stroke, the refrigerant is further compressed while being cooled by oil after point B. As a result, the refrigerant is compressed along an isotherm (for example, about 40 ° C.) shown in FIG. 4A and reaches a target high pressure (point C). In this way, by compressing the refrigerant in the behavior of point A → point B → point C, the power required to compress the refrigerant by the compression mechanism (20) is effectively reduced. As described above, in the compression mechanism (20) of the present embodiment, a part of the compression process from the compression of the low-pressure refrigerant to the high-pressure refrigerant (that is, the process from the point A to the point C). The refrigerant is isothermally compressed during the period from point B to point C.
　ところで、例えば圧縮行程で一般的な断熱圧縮が行われると、冷媒は図４に示すＡ→Ｂ→Ｃ’のような挙動で圧縮される。その結果、この冷凍サイクルでは、冷媒の圧縮動力が大きくなってしまう。これに対し、本実施形態のように、油インジェクション動作により圧縮行程中に冷媒を冷却すると、一般的な断熱圧縮と比して、図４(Ｂ)のＢ点－Ｃ点－Ｃ’点で囲まれる面積ΔＳ分だけ圧縮機構（20）での冷媒の圧縮動力を削減できる。 By the way, for example, when general adiabatic compression is performed in the compression stroke, the refrigerant is compressed in a behavior of A → B → C ′ shown in FIG. 4. As a result, in this refrigeration cycle, the compression power of the refrigerant increases. On the other hand, when the refrigerant is cooled during the compression stroke by the oil injection operation as in the present embodiment, the point B-C-C 'in FIG. The compression power of the refrigerant in the compression mechanism (20) can be reduced by the enclosed area ΔS.
　また、本実施形態のように、冷媒として二酸化炭素を用いて超臨界サイクルを行うもので、上記の油インジェクション動作を行うと、圧縮機構（20）の圧縮動力の削減効果が向上する。この点について以下に説明する。 Further, as in the present embodiment, the supercritical cycle is performed using carbon dioxide as a refrigerant. When the oil injection operation is performed, the compression power reduction effect of the compression mechanism (20) is improved. This will be described below.
　まず、本実施形態の冷媒回路（11）では、上述のように、二酸化炭素を臨界圧力（図４(Ａ）のｃＰ点に示す圧力）以上となるように、圧縮行程で冷媒を圧縮している。このため、圧縮行程ではＢ点→Ｃ点で冷媒を冷却しながら圧縮する際、冷媒が気液二相領域（凝縮領域）に至ることを回避できる。つまり、超臨界サイクルでは、油の冷熱が冷媒の凝縮に利用されることを回避できるので、冷媒を効果的に低温化することができ、冷媒の挙動を等温線に近づけることができる。 First, in the refrigerant circuit (11) of the present embodiment, as described above, the refrigerant is compressed in the compression stroke so that the carbon dioxide becomes equal to or higher than the critical pressure (pressure indicated by the point cP in FIG. 4A). Yes. For this reason, it is possible to avoid the refrigerant reaching the gas-liquid two-phase region (condensation region) when the refrigerant is compressed while being cooled from the point B to the point C in the compression stroke. That is, in the supercritical cycle, it is possible to avoid the cold oil from being used for the condensation of the refrigerant, so that the refrigerant can be effectively lowered in temperature and the behavior of the refrigerant can be brought close to an isotherm.
　これに対し、例えば図５に示す、通常の蒸気圧縮式冷凍サイクル（ここでは、冷媒をＲ４１０Ａとした場合）の圧縮行程では、冷媒が臨界圧力よりも小さい範囲で圧縮される。このため、この冷凍サイクルに上記油インジェクション動作を適用した場合、Ａ１点で冷媒が圧縮されてＢ１点から冷媒が油で冷却される際に、冷媒が気液二相領域（凝縮領域）に至ってしまう。その結果、この冷凍サイクルでは、Ｂ１点→Ｃ１点の範囲でしか等温圧縮を行うことができない。 On the other hand, for example, in the compression stroke of a normal vapor compression refrigeration cycle (here, the refrigerant is R410A) shown in FIG. 5, the refrigerant is compressed in a range smaller than the critical pressure. Therefore, when the oil injection operation is applied to this refrigeration cycle, the refrigerant reaches the gas-liquid two-phase region (condensation region) when the refrigerant is compressed at point A1 and the refrigerant is cooled by oil from point B1. End up. As a result, in this refrigeration cycle, isothermal compression can be performed only in the range of point B1 to point C1.
　以上のような理由により、図５の冷凍サイクルに油インジェクション動作を適用した場合には、圧縮機構の圧縮動力の削減量が図５(Ｂ)のＢ１点－Ｃ１点－Ｃ１’点で囲まれるΔＳ’となってしまう。これに対し、本実施形態の超臨界サイクルに油インジェクション動作を適用した場合には、圧縮機構（20）の圧縮動力の削減量がΔＳとなり、圧縮動力の削減効果が高いものとなる。 For the reasons described above, when the oil injection operation is applied to the refrigeration cycle of FIG. 5, the amount of reduction in the compression power of the compression mechanism is surrounded by the points B1, C1, and C1 ′ in FIG. ΔS ′. On the other hand, when the oil injection operation is applied to the supercritical cycle of the present embodiment, the reduction amount of the compression power of the compression mechanism (20) becomes ΔS, and the reduction effect of the compression power becomes high.
　更に、本実施形態では、上述のように、回収機構（40）によって油の動力を回収している。これにより、油インジェクション動作による冷媒の圧縮動力の低減効果を図りつつ、更に油の昇圧に必要な圧縮動力も低減される。この点について図６を参照しながら説明する。 Furthermore, in this embodiment, as described above, the power of the oil is recovered by the recovery mechanism (40). Thereby, while the effect of reducing the compression power of the refrigerant by the oil injection operation is achieved, the compression power required for boosting the oil is also reduced. This point will be described with reference to FIG.
　上記油インジェクション動作を行うと、圧縮機構（20）では、冷媒の圧縮動力（図６のＷｒ）に加えて、油の昇圧に要する動力（図６のＷｏ）を費やすことになる。ここで、冷媒の圧縮動力Ｗｒは、上述のように、油インジェクション動作による等温圧縮の効果により小さくなる。従って、冷媒の圧縮動力Ｗｒは、圧縮機構（20）へ供給される低温の油の量（油インジェクション量Ｇoil）が多ければ多いほど、小さくなっていく。一方、このように油インジェクション量Ｇoilが多くなると、圧縮機構（20）では、油の昇圧に要する圧縮動力Ｗｏが増大していく。従って、圧縮機構（20）では、その全体としての動力Ｗｔ（即ち、Ｗｒ＋Ｗｏ）と、油インジェクション量Ｇoilとの関係が、図６で示すような関係となり、油インジェクション量Ｇoilが所定値（Ｇｂ）よりも大きくなると、かえって圧縮機構（20）の全体の動力Ｗｔが増大してしまう虞がある。 When the oil injection operation is performed, in the compression mechanism (20), in addition to the compression power of the refrigerant (Wr in FIG. 6), the power required to pressurize the oil (Wo in FIG. 6) is consumed. Here, as described above, the compression power Wr of the refrigerant is reduced by the effect of isothermal compression by the oil injection operation. Accordingly, the compression power Wr of the refrigerant decreases as the amount of low-temperature oil (oil injection amount Goil) supplied to the compression mechanism (20) increases. On the other hand, when the oil injection amount Goil increases as described above, the compression power Wo required for pressurizing the oil increases in the compression mechanism (20). Accordingly, in the compression mechanism (20), the relationship between the overall power Wt (that is, Wr + Wo) and the oil injection amount Goil is as shown in FIG. 6, and the oil injection amount Goil is a predetermined value (Gb). If it is larger than the range, the overall power Wt of the compression mechanism (20) may increase.
　そこで、本実施形態では、油の昇圧に要する圧縮動力Ｗｏを回収するべく、回収機構（40）を用いるようにしている。具体的に、例えば油インジェクション量Ｇoilを所定値より大きいＧｂとして油インジェクション動作を行った場合、油の昇圧に要する圧縮動力Ｗｏも増大するが、油動力回収型圧縮ユニット（C/O）では、昇圧後の油の動力（エネルギー）が、圧縮機構（20）の駆動動力として回収される。その結果、本実施形態では、油インジェクション量Ｇoilを多量としても、この空気調和装置（10）で比較的高いＣＯＰの改善率（等温圧縮による効果）を得ることができる。 Therefore, in the present embodiment, the recovery mechanism (40) is used to recover the compression power Wo required for boosting the oil. Specifically, for example, when the oil injection operation is performed by setting the oil injection amount Goil to Gb larger than a predetermined value, the compression power Wo required for boosting the oil also increases, but in the oil power recovery type compression unit (C / O), The power (energy) of the pressurized oil is recovered as drive power for the compression mechanism (20). As a result, in this embodiment, even if the oil injection amount Goil is increased, a relatively high COP improvement rate (effect by isothermal compression) can be obtained with this air conditioner (10).
　即ち、例えば図７に示すように、回収機構（40）で油の動力を回収しないもの（図７の破線Ｌ-0）では、油インジェクション量が所定値Ｇｂよりも多くなると、等温圧縮の効果に起因する冷媒の圧縮動力Ｗｒの削減量よりも油の昇圧に要する動力Ｗｏの方が大きくなってしまい、ＣＯＰ改善率がかえって低くなってしまう。しかしながら、回収機構（40）で油の動力を回収するようにすると、油の昇圧に要する動力Ｗｏの増大に伴い、圧縮機構（20）へ回収される油の動力が大きくなる。その結果、例えば回収機構（40）の動力回収率が５０％のもの（図７の実線Ｌ-50）では、油インジェクション量を多くしても、高いＣＯＰ改善率を得ることができる。そして、このＣＯＰ改善率は、回収機構（40）の動力回収率が高ければ高いほど（例えば図７の実線L-80（油動力回収率80％）や実線L-100（油動力回収率100%）を参照）、特に油インジェクション量Ｇoilが多い条件下で増大することになる。 That is, for example, as shown in FIG. 7, in the case where the power of the oil is not recovered by the recovery mechanism (40) (broken line L-0 in FIG. 7), the effect of isothermal compression is increased when the oil injection amount exceeds the predetermined value Gb. The power Wo required for boosting the oil becomes larger than the amount of reduction in the compression power Wr of the refrigerant due to the above, and the COP improvement rate is rather lowered. However, when the power of the oil is recovered by the recovery mechanism (40), the power of the oil recovered to the compression mechanism (20) increases as the power Wo required for boosting the oil increases. As a result, for example, when the power recovery rate of the recovery mechanism (40) is 50% (solid line L-50 in FIG. 7), a high COP improvement rate can be obtained even if the amount of oil injection is increased. The higher the power recovery rate of the recovery mechanism (40), the higher the COP improvement rate (for example, solid line L-80 (oil power recovery rate 80%) and solid line L-100 (oil power recovery rate 100 in FIG. 7). %)), Especially under conditions where the oil injection amount Goil is large.
　　－実施形態１の効果－
　上記実施形態１では、油分離器（60）で高圧冷媒中から油を分離し、この油のエネルギーを回収機構（40）で回収して圧縮機構（20）の駆動動力として利用するようにしている。このため、圧縮機構（20）で油の昇圧に要した動力を回収機構（40）で回収でき、空気調和装置（10）の省エネルギーを向上できる。 -Effect of Embodiment 1-
In the first embodiment, oil is separated from the high-pressure refrigerant by the oil separator (60), and the energy of the oil is recovered by the recovery mechanism (40) and used as driving power for the compression mechanism (20). Yes. For this reason, the power required to pressurize the oil by the compression mechanism (20) can be recovered by the recovery mechanism (40), and the energy saving of the air conditioner (10) can be improved.
　また、上記実施形態１では、油分離器（60）で分離した油を油クーラ（80）で冷却し、低温とした油を圧縮機構（20）へ供給している。このため、圧縮機構（20）では、図４に示すような等温圧縮の挙動（即ち、Ａ点→Ｂ点→Ｃ点）に近づくように、冷媒を圧縮することができ、冷媒の圧縮動力を大幅に削減することができる。しかも、油インジェクション量Ｇoilを多くすることで、冷媒の冷却効果が向上して冷媒の圧縮動力が更に低減される一方、回収機構（40）で回収される油のエネルギーも増大する。その結果、空気調和装置（10）のＣＯＰ改善率を大幅に向上でき、省エネ性を更に向上できる。なお、ここで、空気調和装置（10）のＣＯＰ改善率を効果的に向上させるための、油インジェクション量（質量流量）は、圧縮機構（20）への吸入冷媒の量（質量流量）の約０．５倍以上約６．０倍以下の範囲であることが好ましい。 In the first embodiment, the oil separated by the oil separator (60) is cooled by the oil cooler (80), and the low temperature oil is supplied to the compression mechanism (20). For this reason, in the compression mechanism (20), the refrigerant can be compressed so as to approach the isothermal compression behavior as shown in FIG. 4 (that is, the point A → the point B → the point C). It can be greatly reduced. Moreover, by increasing the oil injection amount Goil, the cooling effect of the refrigerant is improved and the compression power of the refrigerant is further reduced, while the energy of the oil recovered by the recovery mechanism (40) is also increased. As a result, the COP improvement rate of the air conditioner (10) can be greatly improved, and the energy saving performance can be further improved. Here, the oil injection amount (mass flow rate) for effectively improving the COP improvement rate of the air conditioner (10) is approximately the amount of refrigerant sucked into the compression mechanism (20) (mass flow rate). The range is preferably 0.5 times or more and about 6.0 times or less.
　加えて、このように油インジェクション量を多くして、圧縮機構（20）へ低温の油を積極的に導入することで以下のような副次的な効果も得られる。具体的には、まず、圧縮機構（20）の吐出冷媒の昇温を防止でき、空気調和装置（10）のシステム異常や、圧縮機構（20）の機械的な損傷を回避できる。また、圧縮機構（20）では、ピストンや軸受け等の摺動部の潤滑が充分図られ、且つ摺動部の放熱効果も向上する。その結果、これらの摺動部での機械損失の増大や焼き付きを防止できる。更に、圧縮機構（20）では、油も比較的低い温度に抑えられるために、油の温度が過剰となって劣化することも回避できる。加えて、圧縮機構（20）では、その周囲温度も比較的低温に抑えられる。その結果、油動力回収型圧縮ユニット（C/O）では、そのケーシング内の温度も比較的低くなる。これにより、電動機（25）の周囲温度も低くなることから、電動機（25）のモータ効率が向上し、圧縮機構（20）の入力が更に低減されることになる。 In addition, by increasing the amount of oil injection in this way and actively introducing low temperature oil into the compression mechanism (20), the following secondary effects can be obtained. Specifically, first, the temperature rise of the refrigerant discharged from the compression mechanism (20) can be prevented, and system abnormality of the air conditioner (10) and mechanical damage to the compression mechanism (20) can be avoided. Further, in the compression mechanism (20), the sliding portions such as pistons and bearings are sufficiently lubricated, and the heat dissipation effect of the sliding portions is improved. As a result, increase in mechanical loss and seizure at these sliding portions can be prevented. Furthermore, in the compression mechanism (20), since the oil can be suppressed to a relatively low temperature, it is possible to avoid deterioration due to excessive oil temperature. In addition, in the compression mechanism (20), the ambient temperature can be suppressed to a relatively low temperature. As a result, in the oil power recovery type compression unit (C / O), the temperature in the casing is also relatively low. Thereby, since the ambient temperature of the electric motor (25) is also lowered, the motor efficiency of the electric motor (25) is improved, and the input of the compression mechanism (20) is further reduced.
　また、上記実施形態１では、高圧冷媒を臨界圧力以上まで圧縮する、超臨界サイクルを行いながら、低温油を圧縮機構（20）へ導入するようにしている。これにより、圧縮機構（20）の圧縮行程では、冷媒を凝縮させることなく等温線に近づくように圧縮でき（例えば図４参照）、通常の冷凍サイクル（例えば図５参照）と比較して、冷媒の圧縮動力を効果的に削減できる。 In the first embodiment, the low-temperature oil is introduced into the compression mechanism (20) while performing a supercritical cycle in which the high-pressure refrigerant is compressed to a critical pressure or higher. Thus, in the compression stroke of the compression mechanism (20), the refrigerant can be compressed so as to approach the isotherm without condensing the refrigerant (see, for example, FIG. 4), and compared with a normal refrigeration cycle (see, for example, FIG. 5). The compression power can be effectively reduced.
　更に、上記実施形態１では、低温とした油を圧縮機構（20）の圧縮途中へ供給するようにしている。これにより、圧縮機構（20）で冷媒を有る程度昇温させてから、昇温後の冷媒を油で冷却することができる。このため、油と混合する冷媒が、油よりも低い温度になるのを回避でき、冷媒が油によって加熱されてしまうのを防止できる。その結果、低温油によって冷媒を確実に冷却することができ、等温圧縮による圧縮動力の低減効果を更に向上させることができる。 Furthermore, in Embodiment 1 described above, low temperature oil is supplied during the compression of the compression mechanism (20). Thereby, after raising the temperature to the extent that the refrigerant is present in the compression mechanism (20), the refrigerant after the temperature rise can be cooled with oil. For this reason, it can avoid that the refrigerant | coolant mixed with oil becomes temperature lower than oil, and it can prevent that a refrigerant | coolant will be heated by oil. As a result, the refrigerant can be reliably cooled by the low-temperature oil, and the effect of reducing the compression power by isothermal compression can be further improved.
　　〈実施形態１の変形例１〉
　上記実施形態１では、冷媒を膨張する膨張機構として、容積型流体機械から成る膨張機構（30）を用いるようにしている。しかしながら、図８に示すように、膨張機構として開度が調節自在な電子式の膨張弁（38）を用いて冷媒を減圧するようにしても良い。 <Modification 1 of Embodiment 1>
In the first embodiment, the expansion mechanism (30) composed of a positive displacement fluid machine is used as the expansion mechanism for expanding the refrigerant. However, as shown in FIG. 8, the refrigerant may be decompressed using an electronic expansion valve (38) whose opening degree is adjustable as an expansion mechanism.
　　《発明の実施形態２》
　本発明の実施形態２について説明する。実施形態２では、冷媒回路（11）の構成が上記実施形態１と異なっている。図９に示すように、実施形態２の冷媒回路（11）では、圧縮機構（20）と膨張機構（30）とが一体となって膨張圧縮ユニット（C/E）に組み込まれ、回収機構（40）が油動力回収ユニット（O）に組み込まれている。 << Embodiment 2 of the Invention >>
A second embodiment of the present invention will be described. In the second embodiment, the configuration of the refrigerant circuit (11) is different from that of the first embodiment. As shown in FIG. 9, in the refrigerant circuit (11) of the second embodiment, the compression mechanism (20) and the expansion mechanism (30) are integrated into the expansion / compression unit (C / E), and the recovery mechanism ( 40) is installed in the oil power recovery unit (O).
　具体的に、膨張圧縮ユニット（C/E）は、圧縮機構（20）と膨張機構（30）と膨張側出力軸（31）と電動機（25）とがケーシング（図示省略）内に収容されて構成されている。圧縮機構（20）と膨張機構（30）とは、膨張側出力軸（31）を介して互いに連結している。つまり、膨張圧縮ユニット（C/E）では、膨張機構（30）で回収された冷媒のエネルギーが、圧縮機構（20）の駆動動力として利用される。換言すると、圧縮機構（20）は、膨張機構（30）の膨張側出力軸（31）と連結して駆動される駆動対象を構成している。 Specifically, the expansion / compression unit (C / E) includes a compression mechanism (20), an expansion mechanism (30), an expansion side output shaft (31), and an electric motor (25) housed in a casing (not shown). It is configured. The compression mechanism (20) and the expansion mechanism (30) are connected to each other via the expansion side output shaft (31). That is, in the expansion / compression unit (C / E), the energy of the refrigerant recovered by the expansion mechanism (30) is used as drive power for the compression mechanism (20). In other words, the compression mechanism (20) constitutes a drive target that is driven by being connected to the expansion-side output shaft (31) of the expansion mechanism (30).
　また、油動力回収ユニット（O）は、回収機構（40）と発電機（45）とがケーシング（図示省略）に収容されて構成されている。回収機構（40）の出力軸（42）は、発電機（45）と連結されている。つまり、油動力回収ユニット（O）では、回収機構（40）で回収された油の動力（即ち、油のエネルギー）によって発電機（45）が駆動され、この発電機（45）で電力が発生する。発電機（45）で発生した電力は、圧縮機構（20）や他の要素機械の駆動動力として利用される。 The oil power recovery unit (O) includes a recovery mechanism (40) and a generator (45) housed in a casing (not shown). The output shaft (42) of the recovery mechanism (40) is connected to the generator (45). In other words, in the oil power recovery unit (O), the generator (45) is driven by the power of the oil recovered by the recovery mechanism (40) (that is, the energy of the oil), and electric power is generated by this generator (45). To do. The electric power generated by the generator (45) is used as driving power for the compression mechanism (20) and other element machines.
　実施形態２の空気調和装置（10）の冷房運転時には、圧縮膨張ユニット（C/E）の圧縮機構（20）で圧縮された冷媒が、油分離器（60）に流入する。油分離器（60）で油が分離された冷媒は、室外熱交換器（12）で放熱した後、圧縮膨張ユニット（C/E）の膨張機構（30）で膨張する。その結果、膨張機構（30）で膨張する冷媒により得られた動力（即ち、膨張動力）が、圧縮機構（20）の駆動動力として利用される。膨張機構（30）で膨張した冷媒は、室内熱交換器（13）で蒸発して室内の冷房に利用された後、圧縮膨張ユニット（C/E）の圧縮機構（20）に吸入される。 During the cooling operation of the air conditioner (10) of Embodiment 2, the refrigerant compressed by the compression mechanism (20) of the compression / expansion unit (C / E) flows into the oil separator (60). The refrigerant from which the oil has been separated by the oil separator (60) is radiated by the outdoor heat exchanger (12) and then expanded by the expansion mechanism (30) of the compression / expansion unit (C / E). As a result, the power (that is, expansion power) obtained by the refrigerant expanding in the expansion mechanism (30) is used as drive power for the compression mechanism (20). The refrigerant expanded by the expansion mechanism (30) is evaporated by the indoor heat exchanger (13) and used for indoor cooling, and then sucked into the compression mechanism (20) of the compression / expansion unit (C / E).
　一方、油分離器（60）で分離された油は、油クーラ（80）で冷却された後、油動力回収ユニット（O）の回収機構（40）へ流入する。回収機構（40）では、油室（49）の油によって出力軸（42）が回転駆動され、発電機（45）が駆動される。その結果、発電機（45）で電力が発生する。 On the other hand, the oil separated by the oil separator (60) is cooled by the oil cooler (80) and then flows into the recovery mechanism (40) of the oil power recovery unit (O). In the recovery mechanism (40), the output shaft (42) is rotationally driven by the oil in the oil chamber (49), and the generator (45) is driven. As a result, electric power is generated by the generator (45).
　回収機構（40）で動力が回収されて減圧した油は、圧縮膨張ユニット（C/E）の圧縮機構（20）の油インジェクションポート（24）へ流入する。圧縮機構（20）では、圧縮途中の冷媒が油によって冷却されることで、冷媒が等温線に近づくように圧縮される。その結果、冷媒の圧縮に要する動力が軽減される。 The oil whose power is recovered by the recovery mechanism (40) and depressurized flows into the oil injection port (24) of the compression mechanism (20) of the compression / expansion unit (C / E). In the compression mechanism (20), the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm. As a result, the power required for refrigerant compression is reduced.
　以上のように、本実施形態においても、油インジェクション量を比較的多めに設定することで、等温圧縮効果により、冷媒の圧縮動力が低減され、且つ昇圧後の油から回収される油の動力（即ち、油のエネルギー）も多くなる。その結果、実施形態２においても、空気調和装置（10）のＣＯＰが効果的に向上する。 As described above, also in the present embodiment, by setting the oil injection amount relatively large, the compression power of the refrigerant is reduced by the isothermal compression effect, and the power of oil recovered from the oil after the pressure increase ( That is, the energy of oil) also increases. As a result, also in the second embodiment, the COP of the air conditioner (10) is effectively improved.
　　《発明の実施形態３》
　本発明の実施形態３について説明する。実施形態３では、冷媒回路（11）の構成が上記各実施形態と異なっている。図１０に示すように、実施形態３の冷媒回路（11）では、圧縮機構（20）が圧縮ユニット（C）に組み込まれ、膨張機構（30）と回収機構（40）とが一体的に油動力回収型膨張ユニット（E/O）に組み込まれている。 << Embodiment 3 of the Invention >>
Embodiment 3 of the present invention will be described. In the third embodiment, the configuration of the refrigerant circuit (11) is different from those in the above embodiments. As shown in FIG. 10, in the refrigerant circuit (11) of the third embodiment, the compression mechanism (20) is incorporated in the compression unit (C), and the expansion mechanism (30) and the recovery mechanism (40) are integrated into oil. Built into the power recovery expansion unit (E / O).
　具体的に、圧縮ユニット（C）は、圧縮機構（20）と駆動軸（21）と電動機（25）とがケーシング（図示省略）に収容されて構成されている。圧縮機構（20）と電動機（25）とは、駆動軸（21）を介して互いに連結している。つまり、圧縮ユニット（C）では、電動機（25）によって圧縮機構（20）が駆動される。 Specifically, the compression unit (C) includes a compression mechanism (20), a drive shaft (21), and an electric motor (25) housed in a casing (not shown). The compression mechanism (20) and the electric motor (25) are connected to each other via the drive shaft (21). That is, in the compression unit (C), the compression mechanism (20) is driven by the electric motor (25).
　また、油動力回収型膨張ユニット（E/O）は、膨張機構（30）と回収機構（40）と発電機（45）とがケーシング（図示省略）に収容されて構成されている。回収機構（40）の出力軸（42）には、その端部に上記膨張機構（30）が連結し、その中間部に発電機（45）が連結している。つまり、油動力回収型膨張ユニット（E/O）では、膨張機構（30）で冷媒のエネルギーが回収され、且つ回収機構（40）で油のエネルギーが回収される。これらのエネルギーは、出力軸（42）を介して発電機（45）の駆動動力として利用される。換言すると、発電機（45）は、回収機構（40）及び膨張機構（30）と出力軸（42）を介して連結して駆動される駆動対象を構成している。その結果、発電機（45）では、上記実施形態１の膨張ユニット（E）よりも多量の電力が発生する。発電機（45）で発生した電力は、圧縮機構（20）や他の要素機械の駆動動力として利用される。 The oil power recovery type expansion unit (E / O) includes an expansion mechanism (30), a recovery mechanism (40), and a generator (45) housed in a casing (not shown). The expansion mechanism (30) is connected to an end portion of the output shaft (42) of the recovery mechanism (40), and a generator (45) is connected to an intermediate portion thereof. That is, in the oil power recovery type expansion unit (E / O), the refrigerant energy is recovered by the expansion mechanism (30), and the oil energy is recovered by the recovery mechanism (40). These energies are used as driving power for the generator (45) via the output shaft (42). In other words, the generator (45) constitutes a drive target that is driven by being connected to the recovery mechanism (40) and the expansion mechanism (30) via the output shaft (42). As a result, the generator (45) generates a larger amount of power than the expansion unit (E) of the first embodiment. The electric power generated by the generator (45) is used as driving power for the compression mechanism (20) and other element machines.
　実施形態３の空気調和装置（10）の冷房運転時には、圧縮ユニット（C）の圧縮機構（20）で圧縮された冷媒が、油分離器（60）に流入する。油分離器（60）で油が分離された冷媒は、室外熱交換器（12）で放熱した後、油動力回収型膨張ユニット（E/O）の膨張機構（30）で膨張する。その結果、膨張機構（30）で膨張する冷媒により得られた動力は、発電機（45）の発電に利用される。膨張機構（30）で膨張した冷媒は、室内熱交換器（13）で蒸発して室内の冷房に利用された後、圧縮ユニット（C）の圧縮機構（20）に吸入される。 During the cooling operation of the air conditioner (10) of Embodiment 3, the refrigerant compressed by the compression mechanism (20) of the compression unit (C) flows into the oil separator (60). The refrigerant from which the oil has been separated by the oil separator (60) is radiated by the outdoor heat exchanger (12) and then expanded by the expansion mechanism (30) of the oil power recovery type expansion unit (E / O). As a result, the power obtained by the refrigerant expanding in the expansion mechanism (30) is used for power generation by the generator (45). The refrigerant expanded in the expansion mechanism (30) evaporates in the indoor heat exchanger (13), is used for indoor cooling, and is then sucked into the compression mechanism (20) of the compression unit (C).
　一方、油分離器（60）で分離された油は、油クーラ（80）で冷却された後、油動力回収型膨張ユニット（E/O）の回収機構（40）へ流入する。回収機構（40）では、油室（49）の油の動力によって出力軸（42）が回転駆動され、発電機（45）が駆動される。その結果、発電機（45）で電力が発生する。 On the other hand, the oil separated by the oil separator (60) is cooled by the oil cooler (80) and then flows into the recovery mechanism (40) of the oil power recovery type expansion unit (E / O). In the recovery mechanism (40), the output shaft (42) is rotated by the power of the oil in the oil chamber (49), and the generator (45) is driven. As a result, electric power is generated by the generator (45).
　回収機構（40）で動力が回収されて減圧した油は、油動力回収型膨張ユニット（E/O）を流出し、圧縮ユニット（C）の圧縮機構（20）の油インジェクションポート（24）へ流入する。圧縮機構（20）では、圧縮途中の冷媒が油によって冷却されることで、冷媒が等温線に近づくように圧縮される。その結果、冷媒の圧縮に要する動力が軽減される。以上のように、本実施形態においても、油インジェクション量を比較的多めに設定することで、等温圧縮効果により、冷媒の圧縮動力が低減され、且つ昇圧後の油から回収される油のエネルギーも多くなる。その結果、実施形態３においても、空気調和装置（10）のＣＯＰが効果的に向上する。 The oil whose power is recovered by the recovery mechanism (40) and depressurized flows out of the oil power recovery type expansion unit (E / O) and flows to the oil injection port (24) of the compression mechanism (20) of the compression unit (C) Inflow. In the compression mechanism (20), the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm. As a result, the power required for refrigerant compression is reduced. As described above, also in this embodiment, by setting the oil injection amount relatively large, the compression power of the refrigerant is reduced by the isothermal compression effect, and the energy of the oil recovered from the oil after the pressure increase is also increased. Become more. As a result, also in Embodiment 3, the COP of the air conditioner (10) is effectively improved.
　　《発明の実施形態４》
　本発明の実施形態４について説明する。実施形態４では、冷媒回路（11）の構成が上記各実施形態と異なっている。図１１に示すように、実施形態４の冷媒回路（11）では、圧縮機構（20）と膨張機構（30）と回収機構（40）とが一体的に油動力回収型膨張圧縮ユニット（C/E/O）に組み込まれている。 << Embodiment 4 of the Invention >>
Embodiment 4 of the present invention will be described. In the fourth embodiment, the configuration of the refrigerant circuit (11) is different from those in the above embodiments. As shown in FIG. 11, in the refrigerant circuit (11) of the fourth embodiment, the compression mechanism (20), the expansion mechanism (30), and the recovery mechanism (40) are integrated into an oil power recovery type expansion / compression unit (C / E / O).
　具体的に、油動力回収型膨張圧縮ユニット（C/E/O）は、圧縮機構（20）と膨張機構（30）と回収機構（40）と電動機（25）とがケーシング（図示省略）に収容されて構成されている。回収機構（40）の出力軸（42）には、その端部に膨張機構（30）が連結し、その中間部に圧縮機構（20）が連結している。また、出力軸（42）には、膨張機構（30）と圧縮機構（20）との間に電動機（25）が連結している。以上のように、油動力回収型膨張圧縮ユニット（C/E/O）では、膨張機構（30）で冷媒のエネルギーが回収され、且つ回収機構（40）で油のエネルギーが回収される。これらの双方のエネルギーは、出力軸（42）を介して圧縮機構（20）を回転駆動する動力として利用される。換言すると、圧縮機構（20）は、回収機構（40）及び膨張機構（30）と出力軸（42）を介して連結して駆動される駆動対象を構成している。その結果、油動力回収型膨張圧縮ユニット（C/E/O）では、上記実施形態１の油動力回収型圧縮ユニット（C/O）と比較して、電動機（25）による圧縮機構（20）の駆動電力が軽減される。 Specifically, the oil power recovery type expansion / compression unit (C / E / O) includes a compression mechanism (20), an expansion mechanism (30), a recovery mechanism (40), and an electric motor (25) in a casing (not shown). Contained and configured. The output mechanism (40) of the recovery mechanism (40) has an expansion mechanism (30) connected to the end thereof and a compression mechanism (20) connected to an intermediate portion thereof. An electric motor (25) is coupled to the output shaft (42) between the expansion mechanism (30) and the compression mechanism (20). As described above, in the oil power recovery type expansion / compression unit (C / E / O), the refrigerant energy is recovered by the expansion mechanism (30), and the oil energy is recovered by the recovery mechanism (40). Both of these energies are used as power for rotationally driving the compression mechanism (20) via the output shaft (42). In other words, the compression mechanism (20) constitutes a drive target that is driven by being connected to the recovery mechanism (40) and the expansion mechanism (30) via the output shaft (42). As a result, in the oil power recovery type expansion / compression unit (C / E / O), compared with the oil power recovery type compression unit (C / O) of the first embodiment, the compression mechanism (20) by the electric motor (25). The driving power is reduced.
　実施形態４の空気調和装置（10）の冷房運転時には、油動力回収型膨張圧縮ユニット（C/E/O）の圧縮機構（20）で圧縮された冷媒が、油分離器（60）に流入する。油分離器（60）で油が分離された冷媒は、室外熱交換器（12）で放熱した後、膨張機構（30）で膨張する。その結果、膨張機構（30）で膨張した冷媒のエネルギーは、出力軸（42）を介して圧縮機構（20）の駆動動力として利用される。膨張機構（30）で膨張した冷媒は、室内熱交換器（13）で蒸発して室内の冷房に利用された後、圧縮ユニット（C）の圧縮機構（20）に吸入される。 During the cooling operation of the air conditioner (10) of the fourth embodiment, the refrigerant compressed by the compression mechanism (20) of the oil power recovery type expansion / compression unit (C / E / O) flows into the oil separator (60). To do. The refrigerant from which the oil has been separated by the oil separator (60) is radiated by the outdoor heat exchanger (12) and then expanded by the expansion mechanism (30). As a result, the energy of the refrigerant expanded by the expansion mechanism (30) is used as driving power for the compression mechanism (20) via the output shaft (42). The refrigerant expanded in the expansion mechanism (30) evaporates in the indoor heat exchanger (13), is used for indoor cooling, and is then sucked into the compression mechanism (20) of the compression unit (C).
　一方、油分離器（60）で分離された油は、油クーラ（80）で冷却された後、回収機構（40）へ流入する。回収機構（40）では、油室（49）の油によって出力軸（42）が回転駆動され、この出力軸（42）の回転動力が圧縮機構（20）の駆動動力として利用される。 On the other hand, the oil separated by the oil separator (60) is cooled by the oil cooler (80) and then flows into the recovery mechanism (40). In the recovery mechanism (40), the output shaft (42) is rotationally driven by the oil in the oil chamber (49), and the rotational power of the output shaft (42) is used as the driving power of the compression mechanism (20).
　回収機構（40）でエネルギーが回収されて減圧した油は、圧縮機構（20）の油インジェクションポート（24）へ流入する。圧縮機構（20）では、圧縮途中の冷媒が油によって冷却されることで、冷媒が等温線に近づくように圧縮される。その結果、冷媒の圧縮に要する動力が軽減される。以上のように、本実施形態においても、油インジェクション量を比較的多めに設定することで、等温圧縮効果により、冷媒の圧縮動力が低減され、且つ昇圧後の油から回収される油のエネルギーも多くなる。その結果、実施形態４においても、空気調和装置（10）のＣＯＰが効果的に向上する。 The oil whose energy is recovered by the recovery mechanism (40) and depressurized flows into the oil injection port (24) of the compression mechanism (20). In the compression mechanism (20), the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm. As a result, the power required for refrigerant compression is reduced. As described above, also in this embodiment, by setting the oil injection amount relatively large, the compression power of the refrigerant is reduced by the isothermal compression effect, and the energy of the oil recovered from the oil after the pressure increase is also increased. Become more. As a result, also in the fourth embodiment, the COP of the air conditioner (10) is effectively improved.
　　《発明の実施形態５》
　本発明の実施形態５について説明する。実施形態５の空気調和装置（10）は、上述した各実施形態について、油インジェクション機構（100）とコントローラ（95）とを付与したものである。 << Embodiment 5 of the Invention >>
Embodiment 5 of the present invention will be described. The air conditioner (10) of the fifth embodiment is provided with an oil injection mechanism (100) and a controller (95) for each of the embodiments described above.
　　〈圧縮機構及び油インジェクション機構の構成〉
　まず、実施形態５における圧縮機構（20）の概略構成と油インジェクション機構（100）の概要について説明する。なお、この例では、上述の実施形態１の空気調和装置（10）において、圧縮機構（20）に油インジェクション機構（100）を設けている。 <Configuration of compression mechanism and oil injection mechanism>
First, a schematic configuration of the compression mechanism (20) and an outline of the oil injection mechanism (100) in the fifth embodiment will be described. In this example, in the air conditioner (10) of the first embodiment, the oil injection mechanism (100) is provided in the compression mechanism (20).
　図１２に示すように、この圧縮機構（20）は、上記回収機構（40）と同様に、揺動ピストン型のロータリ式流体機械で構成されている。圧縮機構（20）は、圧縮室（26）を有し、この圧縮室（26）へ作動流体である冷媒として二酸化炭素を吸入して、圧縮するように構成されている。また、油インジェクション機構（100）は、油インジェクションポート（24）を開閉可能に構成され、所定のタイミングで上記圧縮室（26）へ冷凍機油を供給するように構成されている。この圧縮機構（20）は、上述したように油動力回収型圧縮ユニット（C/O）のケーシング内に収納されている。 As shown in FIG. 12, the compression mechanism (20) is composed of a oscillating piston type rotary fluid machine, similar to the recovery mechanism (40). The compression mechanism (20) has a compression chamber (26), and is configured to suck carbon dioxide as a working fluid into the compression chamber (26) and compress it. The oil injection mechanism (100) is configured to open and close the oil injection port (24), and is configured to supply refrigeration oil to the compression chamber (26) at a predetermined timing. This compression mechanism (20) is housed in the casing of the oil power recovery type compression unit (C / O) as described above.
　この圧縮機構（20）は、圧縮室（26）を有するシリンダ（27）内でのピストン（28）の動作により冷媒を吸入して圧縮するように構成されている。また、この圧縮機構（20）は、圧縮室（26）が断面円形に形成されるとともに、ピストン（28）が該圧縮室（26）内で偏心回転運動をするように構成されている。 The compression mechanism (20) is configured to suck and compress the refrigerant by the operation of the piston (28) in the cylinder (27) having the compression chamber (26). The compression mechanism (20) is configured such that the compression chamber (26) is formed in a circular cross section, and the piston (28) performs an eccentric rotational motion in the compression chamber (26).
　上記ピストン（28）は、出力軸であるクランク軸（42）のクランクピン（42c）に嵌合して偏心回転運動をする環状部（28a）と、この環状部（28a）と一体に形成されたブレード（28b）とを有している。ブレード（28b）は、プレート状であって、環状部（28a）の径方向外側へ延在している。シリンダ（27）は、ブレード（28b）を摺動可能に保持する揺動ブッシュ（29）を有している。揺動ブッシュ（29）は、それぞれほぼ半円形の吸入側ブッシュ（29a）と吐出側ブッシュ（29b）とから構成されている。吸入側ブッシュ（29a）と吐出側ブッシュ（29b）は、一部で連結して一体にしてもよい。 The piston (28) is formed integrally with an annular portion (28a) that engages with a crankpin (42c) of a crankshaft (42) that is an output shaft and performs eccentric rotational motion, and the annular portion (28a). Blade (28b). The blade (28b) has a plate shape and extends outward in the radial direction of the annular portion (28a). The cylinder (27) has a swing bush (29) that slidably holds the blade (28b). The swing bush (29) is composed of a substantially semicircular suction side bush (29a) and a discharge side bush (29b). The suction side bush (29a) and the discharge side bush (29b) may be partly connected and integrated.
　シリンダ（27）には、圧縮室（26）へ冷媒を吸入するように一端が圧縮室（26）に開口した吸入ポート（22a）が形成されている。この吸入ポート（22a）の他端は、上記吸入ライン（17）の吸入管（22）と連通している。また、シリンダ（27）は、上記回収機構（40）と同様に、軸方向の両端面を塞ぐ２枚の端板（27a,27b）（電動機側の端板（27a）をフロントヘッドといい、電動機と反対側の端板（27b）をリヤヘッドという）を有している。フロントヘッド（27a）とリヤヘッド（27b）の一方には、圧縮室（26）で圧縮された冷媒を油動力回収型圧縮ユニット（C/O）のケーシング内の空間へ吐出するための吐出ポート（23a）が形成されている。この吐出ポート（23a）には吐出弁としてリード弁（図示せず）が設けられていて、圧縮室（26）内の圧力と上記油動力回収型圧縮ユニット（C/O）のケーシング内の圧力との圧力差が所定値に達すると吐出ポート（23a）が開くようになっている。この油動力回収型圧縮ユニット（C/O）のケーシングには上記吐出管（23）が直に接続されており、吐出ポート（23a）を流出した冷媒は、吐出管（23）を経て冷媒回路（11）の吐出ライン（18）へ吐出される。 The cylinder (27) is formed with a suction port (22a) having one end opened to the compression chamber (26) so as to suck the refrigerant into the compression chamber (26). The other end of the suction port (22a) communicates with the suction pipe (22) of the suction line (17). In addition, the cylinder (27) has two end plates (27a, 27b) (the end plate (27a) on the motor side) that closes both end surfaces in the axial direction as the front mechanism, similar to the recovery mechanism (40). The end plate (27b) opposite to the electric motor is referred to as a rear head). One of the front head (27a) and the rear head (27b) has a discharge port (for discharging the refrigerant compressed in the compression chamber (26) to the space in the casing of the oil power recovery type compression unit (C / O)). 23a) is formed. This discharge port (23a) is provided with a reed valve (not shown) as a discharge valve, and the pressure in the compression chamber (26) and the pressure in the casing of the oil power recovery type compression unit (C / O) When the pressure difference between and reaches a predetermined value, the discharge port (23a) opens. The discharge pipe (23) is directly connected to the casing of the oil power recovery type compression unit (C / O), and the refrigerant flowing out of the discharge port (23a) passes through the discharge pipe (23) to form a refrigerant circuit. It is discharged to the discharge line (18) of (11).
　上記吸入ポート（22a）は、図１２において縦軸の上方向を０°の位置とすると、そこから横軸の右方向へθｓだけ角度をとった位置に設けられている。また、上記油インジェクション機構（100）は、シリンダ（27）に設けられた噴射ノズル部（101）を有し、この噴射ノズル部（101）は角度がθｉの位置に設けられていて、油インジェクションポート（24）を介して圧縮室（26）に連通している。以上の構成により、上記吸入ポート（22a）と油インジェクションポート（24）は、図１３に示す吸入行程中には圧縮室（26）を介して互いに連通する位置に配置されていることになる。 The suction port (22a) is provided at a position that is angled by θs in the right direction of the horizontal axis when the upward direction of the vertical axis in FIG. Further, the oil injection mechanism (100) has an injection nozzle portion (101) provided in the cylinder (27), and the injection nozzle portion (101) is provided at a position having an angle θi, and the oil injection It communicates with the compression chamber (26) through the port (24). With the above configuration, the suction port (22a) and the oil injection port (24) are arranged at positions that communicate with each other via the compression chamber (26) during the suction stroke shown in FIG.
　上記油インジェクション機構（100）の噴射ノズル部（101）は、円筒状のインジェクションケース（102）と、このインジェクションケース（102）の軸方向へスライド可能なスプール（103）と、このスプール（103）を駆動する駆動機構（104）とを有している。インジェクションケース（102）の一端には、上記油インジェクションポート（24）と連通する油噴射口（105）が形成されている。また、インジェクションケース（102）の他端には、上述の油導入路（70）の第２導油管（72）と繋がる油供給管（106）が接続されている。 The injection nozzle part (101) of the oil injection mechanism (100) includes a cylindrical injection case (102), a spool (103) slidable in the axial direction of the injection case (102), and the spool (103) And a drive mechanism (104) for driving the motor. An oil injection port (105) communicating with the oil injection port (24) is formed at one end of the injection case (102). The other end of the injection case (102) is connected to an oil supply pipe (106) connected to the second oil guide pipe (72) of the oil introduction path (70).
　上記スプール（103）は、油噴射口（105）側の端部がテーパ状の弁部（107）として形成されている。油噴射口（105）は、インジェクションケース（102）の内面側が、スプール（103）の弁部（107）と同じ角度のテーパ面により形成された弁座（108）になっている。この構成において、スプール（103）が後退して弁部（107）の外周面がインジェクションケース（102）の弁座（108）の内周面から離れると（図１２の状態）、油供給管（106）から供給されてきた冷凍機油が弁部（107）と弁座（108）の間の隙間を通って油インジェクションポート（24）から圧縮室（26）内へ噴射される。一方、スプール（103）が前進して弁部（107）の外周面がインジェクションケース（102）の弁座（108）の内周面に圧接すると（図１３の状態）、油供給管（106）から供給されてきた冷凍機油は、インジェクションケース（102）内が密閉空間になるために、圧縮室（26）へは噴射されなくなる。 The spool (103) has an end on the oil injection port (105) side formed as a tapered valve portion (107). The oil injection port (105) is a valve seat (108) formed on the inner surface side of the injection case (102) by a tapered surface having the same angle as the valve portion (107) of the spool (103). In this configuration, when the spool (103) is retracted and the outer peripheral surface of the valve portion (107) is separated from the inner peripheral surface of the valve seat (108) of the injection case (102) (state of FIG. 12), the oil supply pipe ( The refrigerating machine oil supplied from 106) is injected into the compression chamber (26) from the oil injection port (24) through the gap between the valve portion (107) and the valve seat (108). On the other hand, when the spool (103) advances and the outer peripheral surface of the valve portion (107) presses against the inner peripheral surface of the valve seat (108) of the injection case (102) (state of FIG. 13), the oil supply pipe (106) The refrigeration oil supplied from is not injected into the compression chamber (26) because the inside of the injection case (102) becomes a sealed space.
　スプール（103）を軸方向へ進退させる駆動機構（104）としては、ソレノイド機構（109）が用いられている。ソレノイド機構（109）は、スプール（103）に固定された鉄心（110）と、インジェクションケース（102）に固定されたコイル（111）とを有している。インジェクションケース（102）内には、スプール（103）を後退させる方向へバネ力を加えるコイルバネ（112）が設けられ、スプール（103）には、コイルバネ（112）の一端を受けるバネ受け（113）が固定されている。コイルバネ（112）の他端は、インジェクションケース（102）の油噴射口（105）側の端面に接している。 The solenoid mechanism (109) is used as the drive mechanism (104) for moving the spool (103) back and forth in the axial direction. The solenoid mechanism (109) includes an iron core (110) fixed to the spool (103) and a coil (111) fixed to the injection case (102). In the injection case (102), there is provided a coil spring (112) that applies a spring force in a direction to retract the spool (103). The spool (103) receives a spring receiver (113) that receives one end of the coil spring (112). Is fixed. The other end of the coil spring (112) is in contact with the end surface on the oil injection port (105) side of the injection case (102).
　上記ソレノイド機構（109）のコイル（111）に電流を流さない状態では、スプール（103）が可動範囲の後端まで後退する。このとき、鉄心（110）はコイル（111）の中心から外れており、スプール（103）の弁部（107）と油噴射口（105）の弁座（108）との間には隙間が形成されている（図１２）。一方、ソレノイド機構（109）のコイル（111）に電流を流した状態では、コイルバネ（112）のバネ力に抗して鉄心（110）がスプール（103）の前方へに引っ張られ、スプール（103）の弁部（107）と油噴射口（105）の弁座（108）とが圧接する（図１３）。このとき、上記の隙間がなくなり、インジェクションケース（102）の内部が密閉空間となる。 In the state where no current is passed through the coil (111) of the solenoid mechanism (109), the spool (103) moves backward to the rear end of the movable range. At this time, the iron core (110) is off the center of the coil (111), and a gap is formed between the valve portion (107) of the spool (103) and the valve seat (108) of the oil injection port (105). (FIG. 12). On the other hand, in a state where current is passed through the coil (111) of the solenoid mechanism (109), the iron core (110) is pulled forward of the spool (103) against the spring force of the coil spring (112), and the spool (103 ) Is in pressure contact with the valve seat (108) of the oil injection port (105) (FIG. 13). At this time, the gap is eliminated and the inside of the injection case (102) becomes a sealed space.
　　〈コントローラの構成〉
　実施形態５の空気調和装置（10）は、上記油インジェクション機構（100）を制御する制御手段として、コントローラ（95）を有している。 <Configuration of controller>
The air conditioner (10) of Embodiment 5 has a controller (95) as a control means for controlling the oil injection mechanism (100).
　上記圧縮機構（20）を制御するコントローラ（制御手段）（95）は、図１４のブロック図に示すように構成されている。コントローラ（95）は、入力値（諸元）読込部（96）と、測定値（または設定値）読込部（97）と、計算値決定部（98）とを有している。入力値読込部（96）と測定値読込部（97）は、計算値決定部（98）へ信号を送るように、この計算値決定部（98）と接続されている。計算値決定部（98）では、吸入ポート（22a）の位置θｓと、油インジェクションポート（24）の位置θｉと、クランク軸（42）の回転速度ωと、クランク軸（42）の回転角度の現在値θｃとに基づいて、インジェクションタイミングが求められ、コントローラ（95）から油インジェクション機構（100）へ制御信号が送られる。そして、この制御信号に基づいてソレノイド機構（109）のオンとオフが制御され、油の噴射タイミングがコントロールされる。 The controller (control means) (95) for controlling the compression mechanism (20) is configured as shown in the block diagram of FIG. The controller (95) includes an input value (specification) reading unit (96), a measurement value (or set value) reading unit (97), and a calculated value determination unit (98). The input value reading unit (96) and the measured value reading unit (97) are connected to the calculated value determining unit (98) so as to send a signal to the calculated value determining unit (98). In the calculated value determination unit (98), the position θs of the suction port (22a), the position θi of the oil injection port (24), the rotational speed ω of the crankshaft (42), and the rotational angle of the crankshaft (42) The injection timing is obtained based on the current value θc, and a control signal is sent from the controller (95) to the oil injection mechanism (100). Based on this control signal, the solenoid mechanism (109) is turned on and off, and the oil injection timing is controlled.
　具体的には、圧縮機構（20）において吸入行程と圧縮行程と吐出行程とを１サイクルとする動作中に、吸入行程が終了する位置をインジェクション開始点とし、吐出行程が終了する前の位置（この実施形態ではピストン（28）が油インジェクションポート（24）を通過する位置に達した点）をインジェクション終了点として、コントローラ（95）が、インジェクション開始点からインジェクション終了点の範囲の少なくとも一部で油インジェクション動作を行うように上記油インジェクション機構（100）を制御する。特に、コントローラ（95）を、インジェクション開始点からインジェクション終了点の範囲の全体で油インジェクション動作を行うように構成することが、その範囲の全域にわたって等温圧縮を行えるようにするために好ましい。 Specifically, during the operation in which the suction stroke, the compression stroke, and the discharge stroke are performed in one cycle in the compression mechanism (20), the position at which the suction stroke ends is set as the injection start point, and the position before the discharge stroke ends ( In this embodiment, the controller (95) is at least part of the range from the injection start point to the injection end point, with the piston (28 reaching the position where it passes through the oil injection port (24)) as the injection end point. The oil injection mechanism (100) is controlled so as to perform the oil injection operation. In particular, it is preferable that the controller (95) is configured to perform the oil injection operation in the entire range from the injection start point to the injection end point in order to perform isothermal compression over the entire range.
　　〈油インジェクション動作中の噴射ノズル部の開閉タイミング〉
　次に、油インジェクション動作中の噴射ノズル部（101）の開閉タイミングについて説明する。 <Opening / closing timing of injection nozzle during oil injection>
Next, the opening / closing timing of the injection nozzle part (101) during the oil injection operation will be described.
　まず、コントローラ（95）には、入力値読込部（96）に、吸入ポート（22a）の位置θｓと油インジェクション機構（100）の位置θｉとが、予め設定された位置として入力されている。このコントローラ（95）では、運転中のクランク軸（42）の回転速度ωと、クランク軸（42）の回転角度の現在値θｃとが、測定値読込部（97）で測定される。そして、計算値決定部（98）において、これらの値に基づいてインジェクションタイミングが求められる。 First, to the controller (95), the position θs of the suction port (22a) and the position θi of the oil injection mechanism (100) are input to the input value reading unit (96) as preset positions. In this controller (95), the rotational speed ω of the crankshaft (42) during operation and the current value θc of the rotational angle of the crankshaft (42) are measured by the measured value reading unit (97). Then, the calculation value determination unit (98) obtains the injection timing based on these values.
　このインジェクションタイミングは、吸入行程と圧縮行程と吐出行程とを１サイクルとする動作中に、吸入行程が終了する位置をインジェクション開始点θｓとし、吐出行程が終了する前の位置（具体的にはピストン（28）が油インジェクションポート（24）を通過する位置に達した点）をインジェクション終了点θｉとして、インジェクション開始点θｓからインジェクション終了点θいの範囲の少なくとも一部か、またはその範囲の全部で油インジェクション動作を行うように定められる。この範囲の全部で油インジェクション動作を行う場合は、図１２に示すようにピストン（28）がθｓからθｉの範囲に位置しているときに油インジェクション機構（100）の噴射ノズル部（101）のスプール（103）を後退させて油噴射口（105）を開口させ、図１３に示すようにピストン（28）がθｉからθｓの範囲に位置しているときに油インジェクション機構（100）の噴射ノズル部（101）のスプール（103）を前進させて油噴射口（105）を閉塞することになる。 In this injection timing, during the operation in which the suction stroke, the compression stroke, and the discharge stroke are performed in one cycle, the position at which the suction stroke ends is set as the injection start point θs, and the position before the discharge stroke ends (specifically, the piston The point at which (28) reaches the position where it passes through the oil injection port (24)) is set as the injection end point θi, and at least part of the range from the injection start point θs to the injection end point θ, or all of the range It is determined to perform an oil injection operation. When the oil injection operation is performed in the entire range, as shown in FIG. 12, when the piston (28) is located in the range of θs to θi, the injection nozzle portion (101) of the oil injection mechanism (100) The spool (103) is retracted to open the oil injection port (105), and the injection nozzle of the oil injection mechanism (100) when the piston (28) is positioned in the range of θi to θs as shown in FIG. The spool (103) of the portion (101) is advanced to close the oil injection port (105).
　そして、コントローラ（95）は、図１４の計算値決定部（98）で求めたインジェクション時間Δｔの間だけ油噴射口（105）が開口されるようにインジェクションタイミングを決定して、油インジェクション機構（100）の油噴射口（105）を開閉し、圧縮機構（20）への油インジェクション動作を制御する。 Then, the controller (95) determines the injection timing so that the oil injection port (105) is opened only during the injection time Δt determined by the calculated value determination unit (98) in FIG. 100) The oil injection port (105) is opened and closed, and the oil injection operation to the compression mechanism (20) is controlled.
　ここで、従来の油インジェクション機構（100）では、油噴射口（105）が常に開口していたので、図２８に示すようにピストン（28）がθｉからθｓの範囲に位置するときは、吸入ポート（22a）と油インジェクションポート（24）が圧縮室（26）を介して連通してしまい、油インジェクションポート（24）から圧縮室（26）に入った油が吸入ポート（22a）へ逆流してしまうことがあった。 Here, in the conventional oil injection mechanism (100), since the oil injection port (105) is always open, when the piston (28) is located in the range of θi to θs as shown in FIG. The port (22a) and the oil injection port (24) communicate with each other via the compression chamber (26), and the oil that has entered the compression chamber (26) from the oil injection port (24) flows back to the suction port (22a). There was a case.
　これに対して、本実施形態では、図１２に示すように、ピストン（28）がθｓからθｉの範囲に位置しているときは油インジェクション機構（100）のスプール（103）を後退させて油噴射口（105）を開口させるようにしているので、その範囲では正常なインジェクション動作を行うことができるし、図１３に示すようにピストン（28）がθｉからθｓの範囲に位置しているときは油インジェクション機構（100）のスプール（103）を前進させて油噴射口（105）を閉塞するようにしているので、その範囲では無駄な油インジェクション動作が行われない。 On the other hand, in the present embodiment, as shown in FIG. 12, when the piston (28) is located in the range of θs to θi, the spool (103) of the oil injection mechanism (100) is moved backward to make the oil Since the injection port (105) is opened, normal injection operation can be performed in that range, and when the piston (28) is located in the range of θi to θs as shown in FIG. Since the spool (103) of the oil injection mechanism (100) is advanced to close the oil injection port (105), useless oil injection operation is not performed in that range.
　以上のように、実施形態５では、吸入行程と圧縮行程と吐出行程とを１サイクルとするピストン（28）の動作中に、吸入ポート（22a）と油インジェクションポート（24）が連しない間は油インジェクションポート（24）を開くようにしているので、その間は油インジェクション動作をすることによって上述した等温圧縮の効果を充分に得ることができる。また、ピストン（28）の動作中に吸入ポート（22a）と油インジェクションポート（24）が連通する間は油インジェクションポート（24）を閉じるようにしているので、その間は油が圧縮室（26）に流入するのを防止できる。ピストン（28）の動作中に吸入ポート（22a）と油インジェクションポート（24）が連通する間に油インジェクションポート（24）が開いていると、油インジェクションポート（24）から圧縮室（26）に流入した冷凍機油が吸入ポート（22a）へ逆流して冷媒の吸入が妨げられるおそれがあるが、本実施形態では冷凍機油が吸入ポート（22a）へ逆流することはない。したがって、吸入損失が発生してしまうのを防止できる。 As described above, in the fifth embodiment, during the operation of the piston (28) in which the suction stroke, the compression stroke, and the discharge stroke are one cycle, the suction port (22a) and the oil injection port (24) are not connected. Since the oil injection port (24) is opened, the above-described isothermal compression effect can be sufficiently obtained by performing the oil injection operation during that time. Further, the oil injection port (24) is closed while the suction port (22a) and the oil injection port (24) are in communication with each other during the operation of the piston (28). Can be prevented. If the oil injection port (24) is open while the suction port (22a) and the oil injection port (24) are in communication with the piston (28), the oil injection port (24) will move to the compression chamber (26). There is a possibility that the refrigerating machine oil that has flowed back flows into the suction port (22a) and prevents the refrigerant from being sucked, but in this embodiment, the refrigerating machine oil does not flow back to the suction port (22a). Therefore, it is possible to prevent the occurrence of suction loss.
　また、この実施形態では、圧縮機回転速度、吸入圧力、吐出圧力、エンタルピ、冷媒循環量などの多くの値から必要な冷却量を計算して液冷媒噴射装置の開口時間やインジェクション量を算出したり、圧縮機入力を測定してそれが最小値になるようにするための計算ロジックをコントローラ（95）に実装したりする必要はなく、単純に吸入ポート（22a）位置をインジェクション開始点θｓとし、油インジェクションポート（24）の位置をインジェクション終了点θｉとして、その範囲内でタイミングをとって油インジェクション動作を行うようにしているため、油インジェクション機構（100）におけるインジェクションタイミングの算出が非常に容易になり、単純な計算ロジックを実装するだけで効果的な油インジェクションが可能となる。 Further, in this embodiment, the required cooling amount is calculated from many values such as the compressor rotation speed, suction pressure, discharge pressure, enthalpy, and refrigerant circulation amount to calculate the opening time and injection amount of the liquid refrigerant injection device. There is no need to implement the calculation logic to measure the compressor input so that it becomes the minimum value in the controller (95), and simply set the suction port (22a) position as the injection start point θs. Since the oil injection port (24) is set to the injection end point θi, and the oil injection operation is performed within the range, the calculation of the injection timing in the oil injection mechanism (100) is very easy. Therefore, effective oil injection is possible simply by implementing simple calculation logic.
　以上のことから、本実施形態によれば、油インジェクションによる等温圧縮を行う圧縮機において、吸入損失を増加させることなく冷却に必要な大量の油をインジェクションすることができるとともに、複雑な制御をしなくても効果的な等温圧縮の実現が可能となり、大幅なシステム性能の向上が可能となる。 From the above, according to the present embodiment, in a compressor that performs isothermal compression by oil injection, it is possible to inject a large amount of oil necessary for cooling without increasing suction loss and to perform complicated control. Even if not, effective isothermal compression can be realized, and the system performance can be greatly improved.
　　《発明の実施形態６》
　本発明の実施形態６について説明する。実施形態６の空気調和装置（10）は、上記実施形態５と同様の油インジェクション機構（100）を有する一方、実施形態５とコントローラ（95）の構成が異なるものである。 Embodiment 6 of the Invention
Embodiment 6 of the present invention will be described. The air conditioner (10) of the sixth embodiment has the same oil injection mechanism (100) as that of the fifth embodiment, but differs from the fifth embodiment in the configuration of the controller (95).
　　〈コントローラの構成〉
　実施形態６のコントローラ（95）は、図１５のブロック図に示すように構成されている。コントローラ（95）は、入力値（諸元）読込部（96）と、測定値（または設定値）読込部（97）と、計算値決定部（98）とを有している。入力値読込部（96）と測定値読込部（97）は、計算値決定部（98）へ信号を送るため、この計算値決定部（98）と接続されている。計算値決定部（98）では、シリンダ容積Ｖｃと、吸入ポート位置θｓと、油インジェクション位置θｉ（以上、入力値読込部（96）のデータ）と、クランク軸（42）の回転速度ωと、クランク軸（42）の回転角度の現在値θｃと、吸入ガス温度Ｔｓと、冷媒回路（11）の低圧圧力Ｌｐと、冷媒回路（11）の高圧圧力Ｈｐと、インジェクション油温度Ｔｏと、インジェクション油圧力Ｐｏ（以上、測定値読込部（97）のデータ）とに基づいて、油インジェクション動作のタイミングが求められる。つまり、圧縮途中の冷媒ガス温度をＴｒとしたときに、Ｔｒ＝Ｔｏとなるインジェクション開始位置θ１と、圧縮途中の冷媒ガス圧力をＰｒとしたときにＰｒ＝Ｐｏとなるインジェクション終了位置θ２と、θ１からθ２に達するまでのインジェクション時間Δｔとが求められて、これらの値を表す制御信号がコントローラ（95）から油インジェクション機構（100）へ送られる。そして、この制御信号に基づいてソレノイド機構（109）のオンとオフが制御され、油の噴射タイミングがコントロールされる。なお，圧縮途中の冷媒ガス温度Ｔｒと圧縮途中の冷媒ガス圧力Ｐｒは，シリンダ容積Ｖｃや吸入ポート位置θｓなどの圧縮機諸元と、吸入ガス温度Ｔｓや冷媒回路（11）の低圧圧力Ｌｐ、冷媒回路（11）の高圧圧力Ｈｐなどの測定値と、予めコントローラに記録された冷媒物性データとから算出する。図１５中のインジェクション開始位置θ１とインジェクション終了点θ２の計算には、圧縮途中の冷媒ガス温度Ｔｒと圧縮途中の冷媒ガス圧力Ｐｒの算出過程（冷媒温度検出手段と冷媒圧力検出手段）も含まれている。 <Configuration of controller>
The controller (95) of the sixth embodiment is configured as shown in the block diagram of FIG. The controller (95) includes an input value (specification) reading unit (96), a measurement value (or set value) reading unit (97), and a calculated value determination unit (98). The input value reading unit (96) and the measured value reading unit (97) are connected to the calculated value determining unit (98) in order to send a signal to the calculated value determining unit (98). In the calculated value determining unit (98), the cylinder volume Vc, the suction port position θs, the oil injection position θi (hereinafter, the data of the input value reading unit (96)), the rotational speed ω of the crankshaft (42), The current value θc of the rotation angle of the crankshaft (42), the intake gas temperature Ts, the low pressure Lp of the refrigerant circuit (11), the high pressure Hp of the refrigerant circuit (11), the injection oil temperature To, and the injection oil The timing of the oil injection operation is determined based on the pressure Po (the data of the measured value reading unit (97)). That is, when the refrigerant gas temperature in the middle of compression is Tr, the injection start position θ1 where Tr = To, the injection end position θ2 where Pr = Po when the refrigerant gas pressure during compression is Pr, and θ1 The injection time Δt until reaching θ2 is obtained, and a control signal representing these values is sent from the controller (95) to the oil injection mechanism (100). Based on this control signal, the solenoid mechanism (109) is turned on and off, and the oil injection timing is controlled. Note that the refrigerant gas temperature Tr during compression and the refrigerant gas pressure Pr during compression are the compressor specifications such as the cylinder volume Vc and the suction port position θs, the suction gas temperature Ts, the low pressure Lp of the refrigerant circuit (11), It is calculated from measured values such as the high pressure Hp of the refrigerant circuit (11) and refrigerant physical property data recorded in advance in the controller. The calculation of the injection start position θ1 and the injection end point θ2 in FIG. 15 includes a calculation process (refrigerant temperature detection means and refrigerant pressure detection means) of the refrigerant gas temperature Tr during compression and the refrigerant gas pressure Pr during compression. ing.
　具体的には、吸入行程と圧縮行程と吐出行程とを１サイクルとする動作中に、上記圧縮室（26）内の冷媒の温度Ｔｒがインジェクションされる油の温度Ｔｏになる位置をインジェクション開始点θ１とし、圧縮室（26）内の冷媒の圧力Ｔｒが吐出圧力Ｈｐに達する位置をインジェクション終了点θ２として、コントローラ（95）が、インジェクション開始点θ１からインジェクション終了点θ２の範囲の少なくとも一部で油インジェクション動作を行うように上記油インジェクション機構（100）を制御する。特に、コントローラ（95）を、インジェクション開始点θ１からインジェクション終了点θ２の範囲の全体で油インジェクション動作を行うように構成することが、その範囲の全域にわたって等温圧縮を行えるようにするために好ましい。 Specifically, during the operation in which the suction stroke, the compression stroke, and the discharge stroke are performed as one cycle, the position at which the refrigerant temperature Tr in the compression chamber (26) becomes the temperature of the injected oil To is the injection start point. The position at which the refrigerant pressure Tr in the compression chamber (26) reaches the discharge pressure Hp is defined as θ1, and the controller (95) is at least partially in the range from the injection start point θ1 to the injection end point θ2. The oil injection mechanism (100) is controlled so as to perform the oil injection operation. In particular, it is preferable to configure the controller (95) so that the oil injection operation is performed in the entire range from the injection start point θ1 to the injection end point θ2, in order to perform isothermal compression over the entire range.
　　〈油インジェクション動作中の噴射ノズル部の開閉タイミング〉
　次に、油インジェクション動作中の噴射ノズル部（101）の開閉タイミングについて説明する。 <Opening / closing timing of injection nozzle during oil injection>
Next, the opening / closing timing of the injection nozzle part (101) during the oil injection operation will be described.
　まず、コントローラ（95）には、入力値読込部（96）に、シリンダ容積Ｖｃと、吸入ポート位置θｓと、油インジェクション位置θｉとが、予め設定された位置として入力されている。このコントローラ（95）では、クランク軸（42）の回転速度ωと、クランク軸（42）の回転角度の現在値θｃと、吸入ガス温度Ｔｓと、冷媒回路（11）の低圧圧力Ｌｐと、冷媒回路（11）の高圧圧力Ｈｐと、インジェクション油温度Ｔｏと、インジェクション油圧力Ｐｏとが、測定値読込部（97）で測定される。そして、計算値決定部（98）において、これらの値に基づいて、インジェクションタイミングが求められる。具体的には、圧縮途中の冷媒ガス温度をＴｒとしたときにＴｒ＝Ｔｏとなるインジェクション開始位置θ１と、圧縮途中の冷媒ガス圧力をＰｒとしたときにＰｒ＝Ｈｐとなるインジェクション終了位置θ２と、θ１からθ２に達するまでのインジェクション時間Δｔとが求められて、これらの値を表す制御信号がコントローラ（95）から油インジェクション機構（100）へ送られる。そして、この制御信号に基づいてソレノイド機構（109）のオンとオフが制御され、油の噴射タイミングがコントロールされる。 First, the cylinder volume Vc, the suction port position θs, and the oil injection position θi are input to the controller (95) as preset positions in the input value reading unit (96). In this controller (95), the rotational speed ω of the crankshaft (42), the current value θc of the rotational angle of the crankshaft (42), the intake gas temperature Ts, the low pressure Lp of the refrigerant circuit (11), the refrigerant The high pressure Hp of the circuit (11), the injection oil temperature To, and the injection oil pressure Po are measured by the measured value reading unit (97). Then, in the calculated value determining unit (98), the injection timing is obtained based on these values. Specifically, an injection start position θ1 where Tr = To when the refrigerant gas temperature during compression is Tr, and an injection end position θ2 where Pr = Hp when the refrigerant gas pressure during compression is Pr The injection time Δt from θ1 to θ2 is obtained, and a control signal representing these values is sent from the controller (95) to the oil injection mechanism (100). Based on this control signal, the solenoid mechanism (109) is turned on and off, and the oil injection timing is controlled.
　このインジェクションタイミングは、吸入行程と圧縮行程と吐出行程とを１サイクルとする動作中に、上記圧縮室（26）内の冷媒の温度Ｔｒがインジェクションされる油の温度Ｔｏになる位置をインジェクション開始点θ１とし、圧縮室（26）内の冷媒の圧力Ｐｒが吐出圧力Ｈｐに達する位置をインジェクション終了点θ２として、コントローラ（95）が、インジェクション開始点θ１からインジェクション終了点θ２の範囲の少なくとも一部か、またはその範囲の全部で油インジェクション動作を行うように定められる。この範囲の全部で油インジェクション動作を行う場合は、図１６においてθ１のポイントからθ２のポイントまでの範囲の全体で行われ、そのときに油インジェクション機構（100）のスプール（103）を後退させて油噴射口（105）を開口させる。また、図１７に示すようにピストン（28）がθ２からθ１の範囲に位置しているときには、油インジェクション機構（100）のスプール（103）を前進させて油噴射口（105）を閉塞することになる。 In this injection timing, the position at which the refrigerant temperature Tr in the compression chamber (26) becomes the temperature of the injected oil To during the operation in which the suction stroke, the compression stroke, and the discharge stroke are one cycle is the injection start point. The position at which the refrigerant pressure Pr in the compression chamber (26) reaches the discharge pressure Hp is defined as θ1, and the controller (95) is at least part of the range from the injection start point θ1 to the injection end point θ2. Or the entire range of the oil injection operation. When the oil injection operation is performed in the entire range, the entire range from the point θ1 to the point θ2 in FIG. 16 is performed. At that time, the spool (103) of the oil injection mechanism (100) is moved backward. Open the oil injection port (105). Further, as shown in FIG. 17, when the piston (28) is positioned in the range of θ2 to θ1, the spool (103) of the oil injection mechanism (100) is advanced to close the oil injection port (105). become.
　そして、コントローラ（95）は、計算値決定部（98）で求めたインジェクションタイミングに基づいて油インジェクション機構（100）の油噴射口（105）を開閉し、圧縮機構（20）への油インジェクション動作を制御する。 Then, the controller (95) opens and closes the oil injection port (105) of the oil injection mechanism (100) based on the injection timing obtained by the calculated value determination unit (98), and the oil injection operation to the compression mechanism (20) To control.
　ここで、従来の油インジェクション機構（100）では、油インジェクション動作時において、冷凍機油の温度Ｔｏが冷媒の温度Ｔｒよりも高いときは冷媒が過熱されてしまい、過熱圧縮による動力損失が生じてしまうことになる。 Here, in the conventional oil injection mechanism (100), during the oil injection operation, when the temperature To of the refrigerating machine oil is higher than the temperature Tr of the refrigerant, the refrigerant is overheated and power loss due to overheat compression occurs. It will be.
　これに対して、本実施形態では、図１６に示すように、ピストン（28）がθ１からθ２の範囲に位置しているときは油インジェクション機構（100）のスプール（103）を後退させて油噴射口（105）を開口させるようにしているので、その範囲では冷媒の温度Ｔｒが冷凍機油の温度Ｔｏよりも高い領域がなく、等温圧縮により仕事量を十分に削減できる。また、図１７に示すように、ピストン（28）がθ２を過ぎてθ１に至るまでの範囲では、油インジェクション機構（100）のスプール（103）を前進させて油噴射口（105）を閉塞するようにしているので、その範囲では、無駄な油インジェクション動作が行われず、過熱圧縮による動力損失は生じない。 On the other hand, in the present embodiment, as shown in FIG. 16, when the piston (28) is located in the range of θ1 to θ2, the spool (103) of the oil injection mechanism (100) is moved backward to make the oil Since the injection port (105) is opened, there is no region in which the temperature Tr of the refrigerant is higher than the temperature To of the refrigerating machine oil, and the work can be sufficiently reduced by isothermal compression. Further, as shown in FIG. 17, in the range from the piston (28) past θ2 to θ1, the spool (103) of the oil injection mechanism (100) is advanced to close the oil injection port (105). Therefore, in that range, useless oil injection operation is not performed, and power loss due to overheat compression does not occur.
　以上のように、実施形態６では、吸入行程と圧縮行程と吐出行程とを１サイクルとするピストン（28）の動作中に、上記圧縮室（26）内の冷媒の温度Ｔｒがインジェクションされる油の温度Ｔｏになる位置をインジェクション開始点θ１とし、圧縮室（26）内の冷媒の圧力が吐出圧力に達する位置をインジェクション終了点θ２として、インジェクション開始点θ１からインジェクション終了点θ２の範囲の少なくとも一部か、またはその範囲の全部で油インジェクション動作を行うようにしている。θｓからθｉの範囲の全体でインジェクションを行う場合は、図１８に示すように等温圧縮により削減される仕事量を相殺するように作用する仕事量が過熱圧縮により発生していたのに対して、本実施形態によれば、θ１からθ２の範囲内でだけ油インジェクション動作を行うようにしたことにより、図１９に示すように過熱圧縮による仕事量が発生しないようにしているので、等温圧縮による効果を高めることが可能となる。以上のことから、本実施形態によれば、冷却に必要な大量の油をインジェクションすることができるし、過熱圧縮による動力損失も生じないので、効果的な等温圧縮の実現が可能となり、大幅なシステム性能の向上が可能となる。 As described above, in the sixth embodiment, the oil in which the temperature Tr of the refrigerant in the compression chamber (26) is injected during the operation of the piston (28) in which the suction stroke, the compression stroke, and the discharge stroke are one cycle. The position at which the temperature To becomes the injection start point θ1, and the position at which the refrigerant pressure in the compression chamber (26) reaches the discharge pressure is the injection end point θ2, and at least one of the range from the injection start point θ1 to the injection end point θ2. The oil injection operation is performed in the part or all of the range. When the injection is performed in the entire range of θs to θi, the work amount acting to cancel the work amount reduced by the isothermal compression is generated by the overheat compression as shown in FIG. According to this embodiment, since the oil injection operation is performed only within the range of θ1 to θ2, the work amount due to overheat compression is prevented from occurring as shown in FIG. Can be increased. From the above, according to this embodiment, a large amount of oil necessary for cooling can be injected, and power loss due to overheat compression does not occur, so that effective isothermal compression can be realized, System performance can be improved.
　　《発明の実施形態７》
　実施形態７の係る空気調和装置（10）は、室内を暖房のみを行う、暖房専用型の空気調和装置である。図２０に示すように、空気調和装置（10）の冷媒回路（11）には、上記実施形態１と同様にして、油動力回収型圧縮ユニット（C/O）、膨張ユニット（E）、室外熱交換器（12）、室内熱交換器（13）、油分離器（60）等が設けられている。 << Embodiment 7 of the Invention >>
The air conditioner (10) according to Embodiment 7 is a heating-only air conditioner that only heats the room. As shown in FIG. 20, the refrigerant circuit (11) of the air conditioner (10) includes an oil power recovery type compression unit (C / O), an expansion unit (E), an outdoor unit, as in the first embodiment. A heat exchanger (12), an indoor heat exchanger (13), an oil separator (60), and the like are provided.
　実施形態７の冷媒回路（11）は、例えば実施形態１のような２つの四方切換弁（14,15）が省略された構成となっている。つまり、冷媒回路（11）では、油分離器（60）の冷媒排出管（62）が室内熱交換器（13）の流入端と接続し、室内熱交換器（13）の流出端が、膨張ユニット（E）の流入管（33）と接続している。また、膨張ユニット（E）の流出管（34）が室外熱交換器（12）の流入端と接続し、室外熱交換器（12）の流出端が吸入ライン（17）を介して圧縮機構（20）の吸入管（22）と接続している。そして、本実施形態の冷媒回路（11）は、室内熱交換器（13）の冷媒で室内空気を加熱する暖房動作を行うように構成されている。 The refrigerant circuit (11) of Embodiment 7 has a configuration in which, for example, two four-way switching valves (14, 15) as in Embodiment 1 are omitted. That is, in the refrigerant circuit (11), the refrigerant discharge pipe (62) of the oil separator (60) is connected to the inflow end of the indoor heat exchanger (13), and the outflow end of the indoor heat exchanger (13) is expanded. Connected to the inlet pipe (33) of the unit (E). The outflow pipe (34) of the expansion unit (E) is connected to the inflow end of the outdoor heat exchanger (12), and the outflow end of the outdoor heat exchanger (12) is connected to the compression mechanism (17) via the suction line (17). It is connected to the suction pipe (22) of 20). And the refrigerant circuit (11) of this embodiment is comprised so that the heating operation which heats indoor air with the refrigerant | coolant of an indoor heat exchanger (13) may be performed.
　実施形態７の油クーラ（80）は、油分離器（60）で分離した油を冷却するための油冷却熱交換器を構成しており、且つ暖房運転時に油の熱を室内へ放出する補助暖房器を兼ねている。具体的には、油クーラ（80）は、室内熱交換器（13）が設置される室内と同一の室内に設置されている。 The oil cooler (80) of the seventh embodiment constitutes an oil cooling heat exchanger for cooling the oil separated by the oil separator (60), and assists in releasing oil heat into the room during heating operation. Also serves as a heater. Specifically, the oil cooler (80) is installed in the same room as the room in which the indoor heat exchanger (13) is installed.
　実施形態７の空気調和装置（10）の暖房運転時には、圧縮機構（20）で圧縮された冷媒が油分離器（60）内に流入し、油分離器（60）で冷媒中から油が分離される。分離後の冷媒は、室内熱交換器（13）を流れる。室内熱交換器（13）では、高圧冷媒が室内空気へ放熱することで室内空気が加熱され、これにより室内の暖房が行われる。室内熱交換器（13）を流出した冷媒は、膨張ユニット（E）で減圧して室外熱交換器（12）で蒸発した後、圧縮機構（20）へ吸入される。 During the heating operation of the air conditioner (10) of Embodiment 7, the refrigerant compressed by the compression mechanism (20) flows into the oil separator (60), and the oil is separated from the refrigerant by the oil separator (60). Is done. The separated refrigerant flows through the indoor heat exchanger (13). In the indoor heat exchanger (13), the high-pressure refrigerant radiates heat to the room air, thereby heating the room air, thereby heating the room. The refrigerant flowing out of the indoor heat exchanger (13) is decompressed by the expansion unit (E), evaporated by the outdoor heat exchanger (12), and then sucked into the compression mechanism (20).
　実施形態７の暖房運転時にも、上記各実施形態と同様にして、油インジェクション動作が行われる。即ち、油分離器（60）で分離された油は、油クーラ（80）で冷却された後、回収機構（40）へ流入する。回収機構（40）では、油室（49）の油によって出力軸（42）が回転駆動され、この出力軸（42）の回転動力が圧縮機構（20）の駆動動力として利用される。 In the heating operation of the seventh embodiment, the oil injection operation is performed in the same manner as in the above embodiments. That is, the oil separated by the oil separator (60) is cooled by the oil cooler (80) and then flows into the recovery mechanism (40). In the recovery mechanism (40), the output shaft (42) is rotationally driven by the oil in the oil chamber (49), and the rotational power of the output shaft (42) is used as the driving power of the compression mechanism (20).
　回収機構（40）でエネルギーが回収されて減圧した油は、圧縮機構（20）の油インジェクションポート（24）へ流入する。圧縮機構（20）では、圧縮途中の冷媒が油によって冷却されることで、冷媒が等温線に近づくように圧縮される。その結果、冷媒の圧縮に要する動力が軽減される。以上のように、本実施形態においても、油インジェクション量を比較的多めに設定することで、等温圧縮効果により、冷媒の圧縮動力が低減され、且つ昇圧後の油から回収される油のエネルギーも多くなる。 The oil whose energy is recovered by the recovery mechanism (40) and depressurized flows into the oil injection port (24) of the compression mechanism (20). In the compression mechanism (20), the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm. As a result, the power required for refrigerant compression is reduced. As described above, also in this embodiment, by setting the oil injection amount relatively large, the compression power of the refrigerant is reduced by the isothermal compression effect, and the energy of the oil recovered from the oil after the pressure increase is also increased. Become more.
　更に、実施形態７では、油インジェクション動作に伴う暖房能力の低下を補うために、油クーラ（80）を補助暖房器として利用している。この点について詳細に説明する。 Further, in the seventh embodiment, the oil cooler (80) is used as an auxiliary heater in order to compensate for a decrease in heating capacity accompanying the oil injection operation. This point will be described in detail.
　上述の如く、暖房運転時の圧縮機構（20）においても、冷媒が等温線に近づくように圧縮されるため、冷媒の圧縮動力が低減される。一方、このようにして冷媒が等温線に近づくように圧縮されると、圧縮後の冷媒のエンタルピは、いわゆる油インジェクション動作を行わない通常の冷凍サイクルと比較して、小さいものとなる。このため、暖房動作中の冷媒回路（11）の室内熱交換器（13）では、冷媒の放熱量が小さくなり、暖房能力が低下してしまう。 As described above, also in the compression mechanism (20) during the heating operation, the refrigerant is compressed so as to approach the isotherm, so the compression power of the refrigerant is reduced. On the other hand, when the refrigerant is compressed so as to approach the isotherm in this way, the enthalpy of the compressed refrigerant becomes smaller than that of a normal refrigeration cycle that does not perform a so-called oil injection operation. For this reason, in the indoor heat exchanger (13) of the refrigerant circuit (11) during the heating operation, the amount of heat released from the refrigerant is reduced, and the heating capacity is reduced.
　そこで、本実施形態では、油クーラ（80）を室内に設置し、油クーラ（80）を流れる油の熱を室内空気へ放出するようにしている。即ち、暖房運転中の油インジェクション動作において、油分離器（60）で分離された油が油クーラ（80）を流れると、油クーラ（80）では、油と室内空気とが熱交換する。その結果、比較的高温となった油の熱が室内空気へ付与され、室内の暖房が促進される。一方、油クーラ（80）を流れる油は、室内空気によって冷却される。以上のように、暖房運転時には、油クーラ（80）の油が冷却されると同時に、室内空気が油によって加熱されるため、暖房能力の低下を防止しながら油インジェクション動作を行うことができる。 Therefore, in this embodiment, the oil cooler (80) is installed indoors, and the heat of the oil flowing through the oil cooler (80) is released to the indoor air. That is, in the oil injection operation during the heating operation, when the oil separated by the oil separator (60) flows through the oil cooler (80), the oil cooler (80) exchanges heat between the oil and the room air. As a result, the heat of the oil having a relatively high temperature is applied to the indoor air, and indoor heating is promoted. On the other hand, the oil flowing through the oil cooler (80) is cooled by room air. As described above, during the heating operation, the oil in the oil cooler (80) is cooled, and at the same time, the indoor air is heated by the oil, so that the oil injection operation can be performed while preventing the heating capacity from being lowered.
　　《発明の実施形態８》
　実施形態８に係る空気調和装置（10）は、冷房と暖房とを切り換えて行うヒートポンプ式の空気調和装置である。図２１及び図２２に示すように、空気調和装置（10）の冷媒回路（11）には、例えば上記実施形態１と同様、油動力回収型圧縮ユニット（C/O）、第１四方切換弁（14）、室外熱交換器（12）、室内熱交換器（13）、油分離器（60）等が設けられている。また、冷媒回路（11）では、実施形態１の膨張ユニット（E）に代わって減圧機構としての膨張弁（38）が用いられている。 << Embodiment 8 of the Invention >>
The air conditioning apparatus (10) according to Embodiment 8 is a heat pump type air conditioning apparatus that performs switching between cooling and heating. As shown in FIGS. 21 and 22, the refrigerant circuit (11) of the air conditioner (10) includes, for example, an oil power recovery type compression unit (C / O), a first four-way switching valve, as in the first embodiment. (14), an outdoor heat exchanger (12), an indoor heat exchanger (13), an oil separator (60), and the like are provided. In the refrigerant circuit (11), an expansion valve (38) as a pressure reducing mechanism is used instead of the expansion unit (E) of the first embodiment.
　実施形態８の油供給回路（70）は、上述した各実施形態と異なり、冷房運転と暖房運転とで油の流路が切り換わるように構成されている。具体的には、実施形態８の油供給回路（70）には、２つの油クーラ（80,80）と油流路切換機構（81）とが設けられている。 Unlike the above-described embodiments, the oil supply circuit (70) of the eighth embodiment is configured such that the oil flow path is switched between the cooling operation and the heating operation. Specifically, the oil supply circuit (70) of the eighth embodiment is provided with two oil coolers (80, 80) and an oil flow path switching mechanism (81).
　油流路切換機構（81）は、４つのポートを有する四方切換弁で構成されている。油流路切換機構（81）は、第１ポートと第４ポートとが連通して第２ポートと第３ポートとが連通する状態（図２１に示す状態）と、第１ポートと第３ポートとが連通して第２ポートと第４ポートとが連通する状態（図２２に示す状態）とに切り換え可能に構成されている。 The oil flow path switching mechanism (81) is composed of a four-way switching valve having four ports. The oil flow path switching mechanism (81) includes a state in which the first port and the fourth port communicate with each other and a state in which the second port and the third port communicate with each other (state shown in FIG. 21), and the first port and the third port. And the second port and the fourth port communicate with each other (state shown in FIG. 22).
　油流路切換機構（81）の第１ポートは、第１導油管（71）を介して油排出管（63）と接続している。油流路切換機構（81）の第２ポートは、低圧連通管（75）を介して吸入ライン（17）と接続している。油流路切換機構（81）の第３ポートは、室外側油流路（74）を介して油流入管（43）と接続している。油流路切換機構（81）の第４ポートは、室内側油流路（73）を介して油流入管（43）と接続している。 The first port of the oil flow path switching mechanism (81) is connected to the oil discharge pipe (63) via the first oil guide pipe (71). The second port of the oil flow path switching mechanism (81) is connected to the suction line (17) via the low pressure communication pipe (75). The third port of the oil flow path switching mechanism (81) is connected to the oil inflow pipe (43) via the outdoor oil flow path (74). The fourth port of the oil flow path switching mechanism (81) is connected to the oil inflow pipe (43) via the indoor oil flow path (73).
　室内側油流路（73）には、室内熱交換器（13）と同一の室内に設置される室内側油クーラ（80a）が接続されている。室内側油クーラ（80a）は、暖房動作中に油の熱を室内空気へ放出する第１の油冷却熱交換器を構成している。室外側油流路（74）には、室外に設置される室外側油クーラ（80b）が接続されている。室外側油クーラ（80b）は、冷房動作中に油の熱を室外空気へ放出する第２の油冷却熱交換器を構成している。以上のよう構成の油供給回路（70）では、油分離器（60）で分離された油が、室内側油クーラ（80a）と室外側油クーラ（80b）とのいずれか一方に選択的に供給される。 The indoor oil cooler (80a) installed in the same room as the indoor heat exchanger (13) is connected to the indoor oil flow path (73). The indoor oil cooler (80a) constitutes a first oil cooling heat exchanger that releases oil heat to the indoor air during the heating operation. An outdoor oil cooler (80b) installed outside the room is connected to the outdoor oil flow path (74). The outdoor oil cooler (80b) constitutes a second oil cooling heat exchanger that releases oil heat to the outdoor air during the cooling operation. In the oil supply circuit (70) configured as described above, the oil separated by the oil separator (60) is selectively supplied to either the indoor oil cooler (80a) or the outdoor oil cooler (80b). Supplied.
　実施形態８の空気調和装置（10）の暖房運転時には、第１四方切換弁（14）及び油流路切換機構（81）が図２１に示す状態に設定される。圧縮機構（20）で圧縮された冷媒は、油分離器（60）内に流入し、油分離器（60）で油が分離される。分離後の冷媒は、室内熱交換器（13）を流れる。室内熱交換器（13）では、高圧冷媒が室内空気へ放熱することで室内空気が加熱され、これにより室内の暖房が行われる。室内熱交換器（13）で凝縮した冷媒は、膨張弁（38）で減圧されてから室外熱交換器（12）で蒸発した後、圧縮機構（20）へ吸入される。 During the heating operation of the air conditioner (10) of the eighth embodiment, the first four-way switching valve (14) and the oil flow path switching mechanism (81) are set to the state shown in FIG. The refrigerant compressed by the compression mechanism (20) flows into the oil separator (60), and the oil is separated by the oil separator (60). The separated refrigerant flows through the indoor heat exchanger (13). In the indoor heat exchanger (13), the high-pressure refrigerant radiates heat to the room air, thereby heating the room air, thereby heating the room. The refrigerant condensed in the indoor heat exchanger (13) is decompressed by the expansion valve (38), evaporated by the outdoor heat exchanger (12), and then sucked into the compression mechanism (20).
　暖房運転時において、油分離器（60）で分離した油は、室内側油流路（73）を通じて室内側油クーラ（80a）を流れる。室内側油クーラ（80a）では、油の熱が室内空気へ放出される。これにより、上記実施形態７と同様、室内側油クーラ（80a）が補助暖房器として機能し、暖房能力の低下が防止される。以上のようにして室内側油クーラ（80a）で冷却された油は、回収機構（40）へ流入する。回収機構（40）では、油室（49）の油によって出力軸（42）が回転駆動され、この出力軸（42）の回転動力が圧縮機構（20）の駆動動力として利用される。 During the heating operation, the oil separated by the oil separator (60) flows through the indoor oil cooler (80a) through the indoor oil passage (73). In the indoor oil cooler (80a), the heat of oil is released to the indoor air. Thereby, like the said Embodiment 7, an indoor side oil cooler (80a) functions as an auxiliary | assistant heater, and the fall of a heating capability is prevented. The oil cooled by the indoor oil cooler (80a) as described above flows into the recovery mechanism (40). In the recovery mechanism (40), the output shaft (42) is rotationally driven by the oil in the oil chamber (49), and the rotational power of the output shaft (42) is used as the driving power of the compression mechanism (20).
　回収機構（40）でエネルギーが回収されて減圧した油は、圧縮機構（20）の油インジェクションポート（24）へ流入する。圧縮機構（20）では、圧縮途中の冷媒が油によって冷却されることで、冷媒が等温線に近づくように圧縮される。その結果、冷媒の圧縮に要する動力が軽減される。以上のように、本実施形態においても、油インジェクション量を比較的多めに設定することで、等温圧縮効果により、冷媒の圧縮動力が低減され、且つ昇圧後の油から回収される油のエネルギーも多くなる。しかも、室内側油クーラ（80a）を流れる油の熱が暖房に利用される。その結果、実施形態８においても、空気調和装置（10）のＣＯＰが効果的に向上する。 The oil whose energy is recovered by the recovery mechanism (40) and depressurized flows into the oil injection port (24) of the compression mechanism (20). In the compression mechanism (20), the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm. As a result, the power required for refrigerant compression is reduced. As described above, also in this embodiment, by setting the oil injection amount relatively large, the compression power of the refrigerant is reduced by the isothermal compression effect, and the energy of the oil recovered from the oil after the pressure increase is also increased. Become more. Moreover, the heat of the oil flowing through the indoor oil cooler (80a) is used for heating. As a result, also in Embodiment 8, the COP of the air conditioner (10) is effectively improved.
　実施形態８の空気調和装置（10）の冷房運転時には、第１四方切換弁（14）及び油流路切換機構（81）が図２２に示す状態に設定される。圧縮機構（20）で圧縮された冷媒は、油分離器（60）内に流入し、油分離器（60）で油が分離される。分離後の冷媒は、室外熱交換器（12）で凝縮し、膨張弁（38）で減圧されてから室内熱交換器（13）を流れる。室内熱交換器（13）では、冷媒が室内空気から吸熱して蒸発する。これにより、室内空気が冷却されて冷房が行われる。室内熱交換器（13）で蒸発した冷媒は、圧縮機構（20）へ吸入される。 During the cooling operation of the air conditioner (10) of the eighth embodiment, the first four-way switching valve (14) and the oil flow path switching mechanism (81) are set to the state shown in FIG. The refrigerant compressed by the compression mechanism (20) flows into the oil separator (60), and the oil is separated by the oil separator (60). The separated refrigerant is condensed in the outdoor heat exchanger (12), depressurized by the expansion valve (38), and then flows through the indoor heat exchanger (13). In the indoor heat exchanger (13), the refrigerant absorbs heat from the indoor air and evaporates. Thereby, indoor air is cooled and air_conditioning | cooling is performed. The refrigerant evaporated in the indoor heat exchanger (13) is sucked into the compression mechanism (20).
　冷房運転時において、油分離器（60）で分離した油は、室外側油流路（74）を通じて室外側油クーラ（80b）を流れる。室外側油クーラ（80b）では、油の熱が室外空気へ放出される。これにより、室外側油クーラ（80b）を流れる油が室外空気によって冷却される。以上のように、冷房運転では、油分離器（60）で分離した油が室内側油クーラ（80a）を流れない。従って、室内側油クーラ（80a）から油の熱が室内へ放出されることがないので、室内の冷房負荷が増大してしまうことが防止される。 During cooling operation, the oil separated by the oil separator (60) flows through the outdoor oil cooler (80b) through the outdoor oil passage (74). In the outdoor oil cooler (80b), the heat of oil is released to the outdoor air. Thereby, the oil flowing through the outdoor oil cooler (80b) is cooled by the outdoor air. As described above, in the cooling operation, the oil separated by the oil separator (60) does not flow through the indoor oil cooler (80a). Therefore, the heat of the oil is not released into the room from the indoor side oil cooler (80a), thereby preventing the indoor cooling load from increasing.
　以上のようにして、室外側油クーラ（80b）で冷却された油は、回収機構（40）へ流入する。回収機構（40）では、油室（49）の油によって出力軸（42）が回転駆動され、この出力軸（42）の回転動力が圧縮機構（20）の駆動動力として利用される。 Thus, the oil cooled by the outdoor oil cooler (80b) flows into the recovery mechanism (40). In the recovery mechanism (40), the output shaft (42) is rotationally driven by the oil in the oil chamber (49), and the rotational power of the output shaft (42) is used as the driving power of the compression mechanism (20).
　回収機構（40）でエネルギーが回収されて減圧した油は、圧縮機構（20）の油インジェクションポート（24）へ流入する。圧縮機構（20）では、圧縮途中の冷媒が油によって冷却されることで、冷媒が等温線に近づくように圧縮される。その結果、冷媒の圧縮に要する動力が軽減される。 The oil whose energy is recovered by the recovery mechanism (40) and depressurized flows into the oil injection port (24) of the compression mechanism (20). In the compression mechanism (20), the refrigerant in the middle of compression is cooled by oil, so that the refrigerant is compressed so as to approach the isotherm. As a result, the power required for refrigerant compression is reduced.
　なお、上記実施形態７や実施形態８の空気調和装置（10）において、上述した油動力回収ユニット（O）や油動力回収型膨張圧縮ユニット（C/E/O）を用いる構成を採用しても良いのは勿論のことである。 In the air conditioner (10) of the seventh embodiment or the eighth embodiment, a configuration using the oil power recovery unit (O) or the oil power recovery type expansion / compression unit (C / E / O) described above is adopted. Of course it is also good.
　　《その他の実施形態》
　上記の各実施形態については、上述した各構成以外にも以下のような変形例の構成とすることができる。 << Other Embodiments >>
About each said embodiment, it can be set as the structure of the following modifications other than each structure mentioned above.
　　〈変形例１〉
　上述した各実施形態において、油分離器（60）で冷媒中から分離した油を圧縮機構（20）の圧縮途中ではなく、圧縮機構（20）の吸入側（低圧側）へ供給するようにしても良い。即ち、例えば図２３に示すように、上記各実施形態の油導入路（70）は、分離後の油を圧縮機構（20）の吸入側へ供給するように構成しても良い。なお、図２３の例では、上述の実施形態１について、油導入路（70）の第２導油管（72）の終端を吸入ライン（17）に接続したものである。この変形例においても、油クーラ（80）で冷却した油により、圧縮機構（20）で圧縮される冷媒を同時に冷却することができ、上述のような等温圧縮の効果を得ることができる。 <Modification 1>
In each of the embodiments described above, the oil separated from the refrigerant by the oil separator (60) is supplied to the suction side (low pressure side) of the compression mechanism (20), not during the compression of the compression mechanism (20). Also good. That is, for example, as shown in FIG. 23, the oil introduction path (70) of each of the above embodiments may be configured to supply the separated oil to the suction side of the compression mechanism (20). In the example of FIG. 23, the end of the second oil guide pipe (72) of the oil introduction path (70) is connected to the suction line (17) in the first embodiment. Also in this modification, the refrigerant cooled by the compression mechanism (20) can be simultaneously cooled by the oil cooled by the oil cooler (80), and the isothermal compression effect as described above can be obtained.
　　〈変形例２〉
　上述した各実施形態において、油クーラ（80）で冷却した油を回収機構（40）へ供給するのではなく、回収機構（40）でエネルギーを回収した油を油クーラ（80）で冷却しても良い。即ち、例えば図２４に示すように、上記各実施形態について、油導入路（70）において油クーラ（80）を回収機構（40）の下流側に配置しても良い。なお、図２４の例では、上述の実施形態１について、回収機構（40）の下流側に油クーラ（80）を配置している。この変形例においても、回収機構（40）で油のエネルギーを回収でき、且つ油クーラ（80）で冷却した油を圧縮機構（20）へ供給することで、上述のような等温圧縮の効果を得ることができる。また、図２４の変形例のようにすると、圧縮機構（20）へ供給される直前の油を油クーラ（80）で冷却することができるので、圧縮機構（20）へ安定して低温の油を供給できる。その結果、上記の等温圧縮の効果を更に向上させることができる。 <Modification 2>
In each embodiment described above, the oil cooled by the oil cooler (80) is not supplied to the recovery mechanism (40), but the oil recovered by the recovery mechanism (40) is cooled by the oil cooler (80). Also good. That is, for example, as shown in FIG. 24, in each of the above embodiments, the oil cooler (80) may be arranged on the downstream side of the recovery mechanism (40) in the oil introduction path (70). In the example of FIG. 24, the oil cooler (80) is disposed on the downstream side of the recovery mechanism (40) in the first embodiment. Also in this modification, the energy of the oil can be recovered by the recovery mechanism (40) and the oil cooled by the oil cooler (80) is supplied to the compression mechanism (20), so that the effect of isothermal compression as described above can be achieved. Obtainable. 24, the oil immediately before being supplied to the compression mechanism (20) can be cooled by the oil cooler (80), so that the oil can be stably supplied to the compression mechanism (20). Can supply. As a result, the above-mentioned isothermal compression effect can be further improved.
　　〈変形例３〉
　上述した各実施形態において、例えば図２５に示すように、冷媒回路（11）に内部熱交換器（90）を付与するようにしても良い。なお、図２５の例では、上述の変形例２（図２４の例）について、冷媒回路（11）に内部熱交換器（90）を接続している。 <Modification 3>
In each of the embodiments described above, for example, as shown in FIG. 25, an internal heat exchanger (90) may be added to the refrigerant circuit (11). In the example of FIG. 25, the internal heat exchanger (90) is connected to the refrigerant circuit (11) in the above-described modification 2 (example of FIG. 24).
　具体的に、内部熱交換器（90）は、第１流路（91）と第２流路（92）とを有し、両者の流路（91,92）を流れる冷媒同士を熱交換させるものである。第１流路（91）は、冷媒回路（11）で放熱器（例えば冷房運転時の室外熱交換器（12））で放熱した後、膨張機構（30）へ流入する前の冷媒が流れる高圧ライン（19）に接続されている。また、第２流路（92）は、吸入ライン（17）に接続されている。従って、内部熱交換器（90）では、第１流路（91）を高圧冷媒が、第２流路（92）を流れる低圧冷媒によって冷却される。その結果、この変形例の冷房運転時には、高圧側の冷媒の過冷却度が大きくなり、室内熱交換器（13）での冷房能力が向上する。また、第２流路（92）を流れる低圧冷媒は、第１流路（91）を流れる高圧冷媒によって過熱されるので、吸入過熱度が大きくなる。その結果、図２５に示すように、低温の油を圧縮機構（20）の吸入側へ供給した場合にも、吸入冷媒を油よりも高温とすることができ、油による冷媒の冷却効果を充分に得ることができる。 Specifically, the internal heat exchanger (90) has a first flow path (91) and a second flow path (92), and exchanges heat between the refrigerants flowing through both flow paths (91, 92). Is. The first flow path (91) is a high pressure through which the refrigerant before flowing into the expansion mechanism (30) flows after the heat is radiated by the radiator (for example, the outdoor heat exchanger (12) during cooling operation) in the refrigerant circuit (11). Connected to line (19). The second channel (92) is connected to the suction line (17). Therefore, in the internal heat exchanger (90), the first flow path (91) is cooled by the high pressure refrigerant and the low pressure refrigerant flowing in the second flow path (92). As a result, during the cooling operation of this modification, the degree of supercooling of the high-pressure side refrigerant increases, and the cooling capacity in the indoor heat exchanger (13) is improved. Moreover, since the low pressure refrigerant | coolant which flows through a 2nd flow path (92) is overheated by the high pressure refrigerant | coolant which flows through a 1st flow path (91), suction superheat degree becomes large. As a result, as shown in FIG. 25, even when low-temperature oil is supplied to the suction side of the compression mechanism (20), the suction refrigerant can be heated to a higher temperature than the oil, and the cooling effect of the refrigerant by the oil is sufficient. Can get to.
　　〈変形例４〉
　上述した各実施形態において、例えば図２６に示すように、油分離器（60）を他の箇所に設けるようにしても良い。なお、図２６の例は、上述の実施形態１について、変形例３で述べた高圧ライン（19）に油分離器（60）を配置している。この変形例においても、油分離器（60）には、圧縮機構（20）で昇圧された油が溜まり込むので、この油を回収機構（40）へ送ることで、この油のエネルギーを回収することができる。また、この変形例では、冷房運転時の油分離器（60）に溜まる油は、室外熱交換器（12）で放熱後の油となる。つまり、この変形例の油分離器（60）には、上記の各実施形態と比較して低温の油が溜まり込む。従って、この変形例の油インジェクション動作では、一層低温とした油を圧縮機構（20）へ供給でき、上述の等温圧縮の効果を更に向上させることができる。 <Modification 4>
In each of the embodiments described above, for example, as shown in FIG. 26, the oil separator (60) may be provided at another location. In the example of FIG. 26, the oil separator (60) is arranged in the high-pressure line (19) described in the modification 3 in the first embodiment. Also in this modified example, since the oil pressurized by the compression mechanism (20) accumulates in the oil separator (60), the oil energy is recovered by sending the oil to the recovery mechanism (40). be able to. Moreover, in this modification, the oil which accumulates in the oil separator (60) during the cooling operation becomes oil after heat dissipation in the outdoor heat exchanger (12). That is, low-temperature oil accumulates in the oil separator (60) of this modification as compared with the above embodiments. Therefore, in the oil injection operation of this modified example, oil having a lower temperature can be supplied to the compression mechanism (20), and the above-described isothermal compression effect can be further improved.
　　〈その他の変形例〉
　上述した各実施形態では、油分離器（60）で分離した油を圧縮機構（20）へ供給することで、圧縮機構（20）の圧縮行程で冷媒を等温圧縮させるようにしている（図４を参照）。ここで、図４に示す例では、圧縮行程の一部の期間（即ち、Ｂ点からＣ点に至るまでの間）において、冷媒を等温圧縮させているが、圧縮行程の全期間において、冷媒を等温圧縮させても良い。また、圧縮行程の一部の期間は、図４の例に限られるものではなく、異なるタイミングであっても良い。 <Other variations>
In each of the embodiments described above, the refrigerant separated by the oil separator (60) is supplied to the compression mechanism (20) so that the refrigerant is isothermally compressed in the compression stroke of the compression mechanism (20) (FIG. 4). See). Here, in the example shown in FIG. 4, the refrigerant is isothermally compressed during a part of the compression stroke (that is, from the point B to the point C). May be compressed isothermally. Further, the partial period of the compression stroke is not limited to the example of FIG. 4 and may be at different timing.
　また、図４に示す等温圧縮は、圧縮行程中に冷媒がほぼ等温線に沿うように圧縮されている。しかしながら、図４は、上述のように理想的な等温圧縮を例示したものに過ぎず、本発明の等温圧縮は、必ずしも図４に示すような挙動でなくても良い。具体的には、例えば図２７に示すように、本発明の等温圧縮は、油によって冷却される冷媒が等温線に対して少しずつ離れてしまうような挙動で圧縮されるものであっても良い。つまり、本発明の「等温圧縮」とは、圧縮行程中の冷媒が油によって冷却されることで、圧縮行程において、一般的な断熱圧縮と比較して冷媒が等温線に近づくように圧縮されること（つまり、いわゆる擬似的な等温圧縮）を含むものである。 In the isothermal compression shown in FIG. 4, the refrigerant is compressed so as to substantially follow the isothermal line during the compression stroke. However, FIG. 4 merely illustrates ideal isothermal compression as described above, and the isothermal compression of the present invention does not necessarily have the behavior shown in FIG. Specifically, for example, as shown in FIG. 27, the isothermal compression of the present invention may be performed in such a manner that the refrigerant cooled by the oil is gradually separated from the isotherm. . In other words, the “isothermal compression” of the present invention is that the refrigerant in the compression stroke is cooled by the oil, and in the compression stroke, the refrigerant is compressed so as to approach the isotherm as compared with general adiabatic compression. (That is, so-called pseudo-isothermal compression).
　上述した各実施形態では、油分離器（60）で分離した油を積極的に圧縮機構（20）へ供給し、いわゆる等温圧縮を行うものについて、本発明の回収機構（40）を適用するようにしている。しかしながら、例えば圧縮機構（20）から流出した油を、油戻し管を介して圧縮機構（20）の吸入側へ返送し、圧縮機構（20）の潤滑不良を防止するような冷媒回路について、この油戻し管に本発明の回収機構（40）を適用しても良い。このようにしても、高圧の油のエネルギーを回収機構（40）によって回収することができ、冷凍装置のＣＯＰを改善することができる。 In each of the above-described embodiments, the recovery mechanism (40) of the present invention is applied to what performs so-called isothermal compression by actively supplying the oil separated by the oil separator (60) to the compression mechanism (20). I have to. However, for example, a refrigerant circuit that returns oil that has flowed out of the compression mechanism (20) to the suction side of the compression mechanism (20) via an oil return pipe to prevent poor lubrication of the compression mechanism (20). The recovery mechanism (40) of the present invention may be applied to the oil return pipe. Even in this case, the energy of the high-pressure oil can be recovered by the recovery mechanism (40), and the COP of the refrigeration apparatus can be improved.
　また、上述した各実施形態の回収機構（40）の本体部（41）は、ロータリ式の容積型流体機械で構成されている。しかしながら、上記本体部（41）を例えばスクロール式の容積型流体機械で構成しても良いし、例えば非容積型の流体機械（例えばタービン式の非容積型の流体機械）で構成するようにしても良い。また、上述の圧縮機構（20）や膨張機構（30）を他の形式の流体機械で構成しても良いのは勿論のことである。 Further, the main body (41) of the recovery mechanism (40) of each embodiment described above is composed of a rotary positive displacement fluid machine. However, the main body portion (41) may be constituted by, for example, a scroll type positive displacement fluid machine, or may be constituted by, for example, a non positive displacement type fluid machine (eg, a turbine type non positive displacement type fluid machine). Also good. Needless to say, the compression mechanism (20) and the expansion mechanism (30) may be formed of other types of fluid machines.
　また、上述した各実施形態において、冷媒回路（11）に充填される冷媒として、他の冷媒を用いるようにしても良い。また、冷媒回路（11）の冷媒中に混在する油（冷凍機油）として他の油を用いるようにしても良い。 In each of the above-described embodiments, another refrigerant may be used as the refrigerant charged in the refrigerant circuit (11). Moreover, you may make it use other oil as oil (refrigeration machine oil) mixed in the refrigerant | coolant of a refrigerant circuit (11).
　また、上述した各実施形態では、室内の空調を行う空気調和装置（10）について本発明を適用しているが、例えば冷蔵庫や冷凍庫内を冷却する冷凍装置や、他の冷凍装置に本発明を適用しても良い。 Moreover, in each embodiment mentioned above, although this invention is applied about the air conditioning apparatus (10) which air-conditions a room | chamber interior, this invention is applied to the freezing apparatus which cools the inside of a refrigerator or a freezer, for example, and another freezing apparatus. It may be applied.
　なお、以上の実施形態は、本質的に好ましい例示であって、本発明、その適用物、あるいはその用途の範囲を制限することを意図するものではない。 In addition, the above embodiment is an essentially preferable example, and is not intended to limit the scope of the present invention, its application, or its use.
　以上説明したように、本発明は、冷媒が循環して冷凍サイクルを行う冷媒回路を備えた冷凍装置について有用である。 As described above, the present invention is useful for a refrigeration apparatus including a refrigerant circuit that performs a refrigeration cycle by circulating refrigerant.

Claims (12)

  1. 　圧縮機構が接続されて冷凍サイクルを行う冷媒回路を備えた冷凍装置であって、
    　上記冷媒回路には、上記圧縮機構で圧縮した高圧冷媒中から油を分離する油分離手段と、上記圧縮機構の圧縮行程中の冷媒を冷却するように上記油分離手段で分離した油を圧縮機構へ供給する油供給回路とが設けられ、
    　上記油供給回路には、該油供給回路を流れる油のエネルギーを回収する回収機構が設けられていることを特徴とする冷凍装置。     A refrigeration apparatus including a refrigerant circuit connected to a compression mechanism to perform a refrigeration cycle,
    The refrigerant circuit includes an oil separation unit that separates oil from the high-pressure refrigerant compressed by the compression mechanism, and a compression mechanism that separates the oil separated by the oil separation unit so as to cool the refrigerant during the compression stroke of the compression mechanism. And an oil supply circuit for supplying to
    The oil supply circuit is provided with a recovery mechanism for recovering energy of oil flowing through the oil supply circuit.
  2. 　請求項１において、
    　上記油供給回路は、上記圧縮機構の圧縮行程の少なくとも一部の期間で冷媒が等温圧縮されるように圧縮機構へ油を供給することを特徴とする冷凍装置。     In claim 1,
    The refrigeration apparatus, wherein the oil supply circuit supplies oil to the compression mechanism so that the refrigerant is isothermally compressed during at least a part of the compression stroke of the compression mechanism.
  3. 　請求項１又は２において、
    　上記冷媒回路は、上記圧縮機構によって冷媒を臨界圧力まで圧縮する冷凍サイクルを行うように構成されていることを特徴とする冷凍装置。     In claim 1 or 2,
    The refrigerant circuit is configured to perform a refrigeration cycle in which the refrigerant is compressed to a critical pressure by the compression mechanism.
  4. 　請求項１又は２において、
    　上記油供給回路は、上記圧縮機構の圧縮行程の途中に油を供給するように構成されていることを特徴とする冷凍装置。     In claim 1 or 2,
    The refrigeration apparatus, wherein the oil supply circuit is configured to supply oil during a compression stroke of the compression mechanism.
  5. 　請求項１又は２において、
    　上記油供給回路は、上記圧縮機構の吸入側に油を供給するように構成されていることを特徴とする冷凍装置。     In claim 1 or 2,
    The refrigeration apparatus, wherein the oil supply circuit is configured to supply oil to a suction side of the compression mechanism.
  6. 　請求項１又は２において、
    　上記回収機構は、油によって回転駆動される可動部と、該可動部に連結する出力軸とを有することを特徴とする冷凍装置。     In claim 1 or 2,
    The recovery mechanism includes a movable part that is rotationally driven by oil, and an output shaft that is coupled to the movable part.
  7. 　請求項６において、
    　上記圧縮機構は、上記回収機構の出力軸と連結して駆動されるように構成されていることを特徴とする冷凍装置。     In claim 6,
    The refrigeration apparatus, wherein the compression mechanism is configured to be connected to and driven by an output shaft of the recovery mechanism.
  8. 　請求項６において、
    　上記冷媒回路には、冷媒によって回転駆動されると共に上記回収機構の出力軸と連結する可動部を有する膨張機構が設けられていることを特徴とする冷凍装置。     In claim 6,
    The refrigerating apparatus, wherein the refrigerant circuit is provided with an expansion mechanism having a movable portion that is rotationally driven by the refrigerant and coupled to the output shaft of the recovery mechanism.
  9. 　請求項６において、
    　上記回収機構の出力軸と連結して駆動される発電機を備えていることを特徴とする冷凍装置。     In claim 6,
    A refrigerating apparatus comprising a generator driven in connection with an output shaft of the recovery mechanism.
  10. 　請求項１又は２において、
    　上記油供給回路には、油分離手段で分離した油を冷却するための油冷却熱交換器が接続されていることを特徴とする冷凍装置。     In claim 1 or 2,
    An oil cooling heat exchanger for cooling the oil separated by the oil separation means is connected to the oil supply circuit.
  11. 　請求項１０において、
    　上記冷媒回路は、室内に設置される室内熱交換器を有して該室内熱交換器を流れる冷媒で室内空気を加熱する暖房動作を行うように構成され、
    　上記油冷却熱交換器は、室内に設置されて上記暖房動作中に油の熱を室内空気へ放出するように構成されていることを特徴とする冷凍装置。     In claim 10,
    The refrigerant circuit has an indoor heat exchanger installed indoors, and is configured to perform a heating operation of heating indoor air with a refrigerant flowing through the indoor heat exchanger,
    The oil cooling heat exchanger is installed in a room and is configured to release heat of oil to room air during the heating operation.
  12. 　請求項１０において、
    　上記冷媒回路は、室内に設置される室内熱交換器を有して該室内熱交換器を流れる冷媒で室内空気を加熱する暖房動作と、該室内熱交換器を流れる冷媒で室内空気を冷却する冷房動作とを切り換えて行うように構成され、
    　上記油供給回路には、室内に設置されて上記暖房動作中に油の熱を室内空気へ放出する第１の油冷却熱交換器と、室外に設置されて上記冷房動作中に油の熱を室内空気へ放出する第２の油冷却熱交換器とが接続されていることを特徴とする冷凍装置。     In claim 10,
    The refrigerant circuit has an indoor heat exchanger installed indoors and heats indoor air with refrigerant flowing through the indoor heat exchanger, and cools indoor air with refrigerant flowing through the indoor heat exchanger It is configured to switch between cooling operations,
    The oil supply circuit includes a first oil cooling heat exchanger that is installed indoors and releases oil heat to the indoor air during the heating operation, and an oil supply circuit that is installed outside and heats the oil during the cooling operation. A refrigeration apparatus comprising a second oil-cooling heat exchanger that discharges to indoor air.
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JP5380987B2 (en) 2014-01-08
CN101939599A (en) 2011-01-05
AU2009210984A1 (en) 2009-08-13
EP2251621A1 (en) 2010-11-17
EP2251621A4 (en) 2014-05-14
KR20100114122A (en) 2010-10-22
US20100275634A1 (en) 2010-11-04
AU2009210984B2 (en) 2011-11-24
JP2010032195A (en) 2010-02-12
KR101185307B1 (en) 2012-09-26

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