WO2016079805A1 - スクロール圧縮機及び冷凍サイクル装置 - Google Patents
スクロール圧縮機及び冷凍サイクル装置 Download PDFInfo
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- WO2016079805A1 WO2016079805A1 PCT/JP2014/080498 JP2014080498W WO2016079805A1 WO 2016079805 A1 WO2016079805 A1 WO 2016079805A1 JP 2014080498 W JP2014080498 W JP 2014080498W WO 2016079805 A1 WO2016079805 A1 WO 2016079805A1
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- WIPO (PCT)
- Prior art keywords
- scroll compressor
- scroll
- spiral tooth
- base plate
- refrigerant
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0253—Details concerning the base
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/28—Safety arrangements; Monitoring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/0085—Prime movers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F25B31/02—Compressor arrangements of motor-compressor units
- F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/30—Casings or housings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/19—Temperature
Definitions
- the present invention relates to a scroll compressor and a refrigeration cycle apparatus.
- thermal expansion of the compression mechanism portion occurs, for example, a tooth tip that contacts the base plate (for example, the base plate of the fixed scroll) with which the tip of the scroll teeth (for example, the spiral teeth of the orbiting scroll) of the compression mechanism portion faces Invite contact.
- the operable range of the scroll compressor for example, the frequency of the scroll compressor
- the present invention has been made in order to solve the above-described problems, and avoids the thermal expansion of the compression mechanism by suppressing the increase in the discharge temperature of the scroll compressor, and the operable range of the scroll compressor.
- the purpose is to expand.
- the scroll compressor according to the present invention includes a pressure vessel, a frame in which a hollow cylindrical portion and a bottom portion as side portions are integrally formed, and an outer peripheral surface of the hollow cylindrical portion is fixed to an inner peripheral surface of the pressure vessel; , And a first spiral tooth formed on one surface of the first base plate, wherein the first base plate includes the first spiral tooth and the bottom surface portion.
- a refrigeration cycle apparatus includes the scroll compressor, a radiator, a decompressor, and an evaporator.
- the second suction pipe directly flows in the suction refrigerant from the refrigerant circuit constituting the refrigeration cycle into the frame housing the compression mechanism in the scroll compressor, that is, into the hollow cylindrical portion of the frame. Therefore, the refrigerant temperature at the start of compression can be lowered to suppress an increase in discharge temperature.
- the increase in the discharge temperature of the scroll compressor it is possible to avoid the thermal expansion of the compression mechanism, so the operating range of the scroll compressor that was limited due to the thermal expansion due to the increase in the discharge temperature is expanded. can do.
- FIG. 1 is a schematic diagram showing a configuration of a refrigeration cycle apparatus 1 according to Embodiment 1 of the present invention.
- FIG. 1 is a schematic diagram showing a configuration of a refrigeration cycle apparatus 1 according to Embodiment 1 of the present invention.
- the dimensional relationship and shape of each component may be different.
- symbol is attached
- symbol is abbreviate
- the refrigeration cycle apparatus 1 includes a scroll compressor 10, a radiator 20, a decompressor 30, and an evaporator 40.
- the scroll compressor 10, the radiator 20, the decompressor 30, and the evaporator 40 constitute a refrigeration cycle 2 that is communicated through the refrigerant flow path to circulate the refrigerant.
- the scroll compressor 10 is a fluid machine that compresses sucked low-pressure refrigerant and discharges it as high-pressure refrigerant using a pair of scroll wraps (spiral teeth) having the same shape.
- the structure and operation of the scroll compressor 10 according to Embodiment 1 of the present invention will be described later.
- the heat radiator 20 is a heat exchanger, and heat is released from the refrigerant circulating in the heat radiator 20.
- the decompression device 30 is a device that decompresses the high-pressure refrigerant into a low-pressure refrigerant.
- an expansion valve such as an electronic expansion valve whose opening degree can be adjusted is used.
- the evaporator 40 is a heat exchanger. In the evaporator 40, the refrigerant circulating inside absorbs heat from the outside.
- the high-temperature and high-pressure gas-phase refrigerant discharged from the scroll compressor 10 flows into the radiator 20.
- the radiator 20 heat exchange is performed between the refrigerant flowing inside the radiator 20 and the outside (for example, external air in the case of cooling operation of the air conditioner), and the heat of condensation of the refrigerant is radiated to the outside. Is done.
- the high-temperature and high-pressure gas-phase refrigerant that has flowed into the radiator 20 passes through the two-phase refrigerant and becomes a high-pressure liquid-phase refrigerant.
- the high-pressure liquid-phase refrigerant flows into the decompression device 30, is decompressed, becomes a low-pressure two-phase refrigerant, and flows into the evaporator 40.
- the evaporator 40 heat is exchanged between the refrigerant flowing inside the evaporator 40 and the outside (for example, indoor air in the case of the cooling operation of the air conditioner), and the evaporation heat of the refrigerant absorbs heat from the outside. Is done.
- the low-pressure two-phase refrigerant flowing into the evaporator 40 becomes a low-pressure gas-phase refrigerant or a low-pressure two-phase refrigerant having a high dryness.
- the low-pressure gas-phase refrigerant or the low-pressure two-phase refrigerant having a high dryness is sucked into the scroll compressor 10.
- the low-pressure gas-phase refrigerant sucked into the scroll compressor 10 is compressed into a high-temperature and high-pressure gas-phase refrigerant. In the refrigeration cycle 2, the above operation is performed.
- a bypass flow path 3 for lowering the temperature of the refrigerant sucked into the scroll compressor 10 is provided.
- the bypass flow path 3 connects the refrigerant flow path of the refrigeration cycle 2 between the radiator 20 and the decompression device 30 and the refrigerant flow path of the refrigeration cycle 2 between the evaporator 40 and the scroll compressor 10.
- the bypass flow path 3 allows a part of the refrigerant flowing out of the radiator 20 to pass through the refrigerant flow path of the refrigeration cycle 2 on the outlet side of the evaporator 40 (that is, the refrigeration cycle 2 on the suction side of the scroll compressor 10). Bypass to refrigerant flow path).
- the bypass flow path 3 includes the first flow rate regulator 50a, and adjusts the flow rate of the refrigerant flowing through the bypass flow path 3 by opening degree control.
- the refrigeration cycle apparatus 1 includes the control unit 60, and the opening degree control of the first flow rate regulator 50a can be performed by the control unit 60.
- the control unit 60 includes a microcomputer having a CPU, a memory (for example, ROM, RAM, etc.), an I / O port, and the like.
- the first refrigeration cycle apparatus 1 is disposed downstream of the junction of the refrigerant flow path and the bypass flow path 3 of the refrigeration cycle 2 between the evaporator 40 and the scroll compressor 10.
- a branch channel 4 is provided.
- FIG. 2 is a schematic longitudinal sectional view showing the configuration of the scroll compressor 10 according to Embodiment 1 of the present invention.
- the configuration example of the vertical scroll compressor 10 will be described.
- the scroll compressor 10 is a fluid machine that compresses sucked low-pressure refrigerant and discharges it as high-pressure refrigerant.
- the scroll compressor 10 includes a pressure vessel 100 that is a cylindrical housing. Inside the pressure vessel 100 is housed a frame 110 having a hollow cylindrical portion 110a and a bottom surface portion 110b as side portions, and the hollow cylindrical portion 110a and the bottom surface portion 110b are integrally formed.
- the outer peripheral surface of the hollow cylindrical portion 110a of the frame 110 is fixed to the inner peripheral surface of the pressure vessel 100 by welding or the like.
- the frame 110 accommodates a compression mechanism 120 having a turning scroll 121 and a fixed scroll 122.
- the orbiting scroll 121 has a first base plate 121a and a first spiral tooth 121b that is a spiral protrusion having an involute curve shape formed on one surface of the first base plate 121a.
- the orbiting scroll 121 is rotatably accommodated in the hollow portion of the hollow cylindrical portion 110a of the frame 110 so that the first base plate 121a is positioned between the first spiral tooth 121b and the bottom surface portion 110b of the frame 110. Yes.
- the orbiting scroll 121 is housed in the hollow portion of the hollow cylindrical portion 110a of the frame 110 so that the first spiral tooth 121b has the tooth tip portion facing upward.
- a boss portion 121d having a turning bearing 121c for eccentrically turning the orbiting scroll 121 is formed at the center of the other surface of the first base plate 121a of the orbiting scroll 121.
- a concave orbiting support portion 110c that accommodates the boss portion 121d of the orbiting scroll 121 so as to be eccentrically rotatable, and a main shaft that rotatably supports a main shaft 132 of the electric mechanism portion 130 described later.
- a support portion 110d is formed.
- the fixed scroll 122 has a second base plate 122a and a second spiral tooth 122b which is a spiral protrusion having an involute curve shape formed on one surface of the second base plate 122a.
- the second spiral teeth 122 b of the fixed scroll 122 are arranged so as to mesh with the first spiral teeth 121 b of the orbiting scroll 121.
- the second spiral tooth 122b of the fixed scroll 122 is meshed with the first spiral tooth 121b of the orbiting scroll 121 so that the tip of the tooth faces downward.
- the second base plate 122a of the fixed scroll 122 is fixed to the annular surface 110e of the hollow cylindrical portion 110a of the frame 110 by a fixing member (for example, a bolt). Further, the fixed scroll 122 (for example, the central portion of the fixed scroll 122) is formed with a discharge port 122c that discharges the compressed refrigerant gas that has become high temperature and high pressure.
- the orbiting scroll 121 and the fixed scroll 122 are attached to the frame 110 in a state where the first spiral teeth 121b and the second spiral teeth 122b are engaged with each other.
- a compression chamber 123 whose volume changes relatively is formed between the first spiral tooth 121b and the second spiral tooth 122b.
- the electric mechanism unit 130 is configured to rotate the orbiting scroll 121 eccentrically and compress the refrigerant by the compression mechanism unit 120.
- the electric mechanism unit 130 is disposed below the frame 110.
- the electric mechanism unit 130 includes a rotor 131, a main shaft 132 fixed to the center of the rotor 131, a turning shaft 133 formed at the tip of the main shaft 132, and a stator disposed around the rotor 131. 134.
- the orbiting shaft 133 is supported by the orbiting bearing 121 c of the orbiting scroll 121.
- the stator 134 is fixed inside the pressure vessel 100.
- the rotor 131 is rotated by energizing the stator 134. Due to the rotation of the main shaft 132 fixed to the rotor 131, the turning shaft 133 turns eccentrically, and the turning scroll 121 turns eccentrically.
- the motion that the orbiting scroll 121 rotates eccentrically is a revolving motion that revolves around the center of the second spiral tooth 122b of the fixed scroll 122.
- the frame 110 accommodates an Oldham ring 124 for allowing the orbiting scroll 121 to revolve and preventing the orbiting scroll 121 from rotating during eccentric rotation.
- Refrigerator oil 140 for operating the compression mechanism 120 to lubricate is accommodated in the bottom (oil reservoir) of the pressure vessel 100. As the main shaft 132 rotates, the refrigerating machine oil 140 is sucked up through an oil supply passage (not shown) inside the main shaft 132 and supplied to the compression mechanism unit 120.
- the scroll compressor 10 includes a discharge pipe 150 communicating with the discharge port 122c of the fixed scroll 122.
- the discharge pipe 150 guides the high-temperature and high-pressure gas-phase refrigerant discharged from the scroll compressor 10 into the refrigerant flow path of the refrigeration cycle 2 between the scroll compressor 10 and the radiator 20 in FIG.
- the discharge pipe 150 is disposed above the fixed scroll 122.
- the scroll compressor 10 includes a first suction pipe 160 that communicates with the low-pressure space inside the pressure vessel 100 outside the frame 110.
- the first suction pipe 160 communicates with the refrigerant flow path of the refrigeration cycle 2 between the evaporator 40 and the scroll compressor 10 of FIG. 1, and allows the refrigerant flowing in from the evaporator 40 and the bypass flow path 3 to pass through the pressure vessel 100.
- the first suction pipe 160 is disposed on the side surface of the body portion of the pressure vessel 100 and communicates with the low-pressure space inside the pressure vessel 100 below the frame 110.
- the scroll compressor 10 includes a second suction pipe 170 that passes through the pressure vessel 100 and the hollow cylindrical portion 110a of the frame 110 and communicates with the hollow portion of the hollow cylindrical portion 110a.
- the second suction pipe 170 communicates with the first branch flow path 4 of FIG. 1 and compresses a part of the refrigerant that flows from the evaporator 40 and the bypass flow path 3 and is divided into the first branch flow path 4. It is guided directly to the mechanism unit 120.
- the rotor 131 rotates by receiving a rotational force from a rotating magnetic field generated by the stator 134. Accordingly, the main shaft 132 fixed to the rotor 131 rotates. The rotation of the main shaft 132 is transmitted to the orbiting scroll 121 via the orbiting shaft 133 formed at the tip of the main shaft 132. The rotation of the orbiting scroll 121 is restricted by the Oldham ring 124 and revolves.
- the refrigerant flowing in through the first suction pipe 160 and the refrigerant flowing in through the second suction pipe 170 are on the outer peripheral side formed by the orbiting scroll 121 and the fixed scroll 122. It is taken into the compression chamber 123.
- the refrigerant flowing in through the first suction pipe 160 flows into the low-pressure space inside the pressure vessel 100 outside the frame 110 from the refrigerant flow path of the refrigeration cycle 2 between the evaporator 40 and the scroll compressor 10. .
- the refrigerant flowing in via the second suction pipe 170 flows directly from the first branch flow path 4 into the hollow cylindrical portion 110a of the frame 110.
- the refrigerant taken into the compression chamber 123 moves toward the center while being gradually compressed by the eccentric turning of the orbiting scroll 121. Then, the refrigerant compressed in the compression chamber 123 becomes a high-temperature and high-pressure gas-phase refrigerant and is discharged from the discharge port 122 c formed in the second base plate 122 a of the fixed scroll 122.
- the high-temperature and high-pressure gas-phase refrigerant discharged from the discharge port 122 c is guided to the refrigerant flow path of the refrigeration cycle 2 between the scroll compressor 10 and the radiator 20 through the discharge pipe 150.
- the refrigerant that has flowed in through the suction pipe (corresponding to the first suction pipe 160 according to the first embodiment) is heat generated in the low-pressure space inside the scroll compressor (for example, The temperature rises by absorbing heat generated in the electric mechanism section or refrigerating machine oil. For this reason, the effect of suppressing the increase in discharge temperature is reduced, and the operable range of the scroll compressor is limited.
- the scroll compressor 10 has a second suction that communicates with the refrigerant flow path between the evaporator 40 and the scroll compressor 10 (that is, the suction side circuit of the scroll compressor 10).
- a tube 170 is provided.
- the second suction pipe 170 is configured to directly flow a part of the refrigerant circulating in the refrigerant flow path into the hollow portion of the hollow cylindrical portion 110 a of the frame 110. Therefore, the temperature rise of the refrigerant flowing in via the first suction pipe 160 is alleviated by joining the refrigerant flowing in via the second suction pipe 170 and the hollow portion of the hollow cylindrical portion 110a.
- the scroll compressor 10 of the first embodiment a part of the refrigerant flowing out from the radiator 20 is bypassed to the outlet side of the evaporator 40 via the bypass flow path 3. Therefore, in the scroll compressor 10 according to the first embodiment, the refrigerant temperature at the start of compression in the compression mechanism unit 120 can be kept low, and thus an increase in the discharge temperature of the scroll compressor 10 can be suppressed.
- the thermal expansion of the orbiting scroll 121 and the fixed scroll 122 during the operation of the scroll compressor 10 can be suppressed by suppressing the increase in the discharge temperature.
- the operable range of the scroll compressor 10 that is limited due to the thermal expansion of the orbiting scroll 121 and the fixed scroll 122 can be expanded.
- the gap between the orbiting scroll 121 and the fixed scroll 122 can be designed to be small.
- the gap (tooth gap) between the first spiral tooth 121b of the orbiting scroll 121 and the second base plate 122a of the fixed scroll 122 can be designed to be small, in the compression stroke Refrigerant leakage from the tooth gap can be reduced. Therefore, in the first embodiment, by reducing the gap between the orbiting scroll 121 and the fixed scroll 122, the performance of the scroll compressor 10 can be improved and the energy consumption can be reduced.
- the suction refrigerant can be caused to flow into the hollow portion of the hollow cylindrical portion 110a of the frame 110, the temperature rise of the orbiting scroll 121 can be suppressed.
- the temperature rises due to friction between the first base plate 121a of the orbiting scroll 121 and the frame 110 for example, the temperature rise due to eccentric orbiting in the vicinity of the orbiting bearing 121c and the spindle support portion 110d). Can be suppressed.
- FIG. 3 is a schematic cross-sectional view showing the configuration of the compression mechanism 120 of the scroll compressor 10 according to Embodiment 2 of the present invention.
- the second suction pipe 170 has a center 122d of the second spiral tooth 122b (for example, the center of the spiral basic circle), It arrange
- the other configurations of the scroll compressor 10 and the refrigeration cycle apparatus 1 are the same as the configurations of the scroll compressor 10 and the refrigeration cycle apparatus 1 in Embodiment 1 described above, and thus the description thereof is omitted.
- the second suction pipe 170 is disposed so as to be orthogonal to a straight line connecting the center 122d of the second spiral tooth 122b and the winding end portion 122e, thereby providing the second suction pipe.
- the refrigerant flowing in from the pipe can be distributed substantially evenly to the two compression chambers that form a pair.
- FIG. 4 is a schematic diagram showing the configuration of the refrigeration cycle apparatus 1 according to Embodiment 3 of the present invention.
- FIG. 5 is a schematic longitudinal sectional view showing the configuration of the scroll compressor 10 according to Embodiment 3 of the present invention.
- the bypass flow path 3 has the first flow rate regulator 50a, and the first branch flow path 4 has the third flow rate regulator 50c. .
- the rest of the configuration of the refrigeration cycle apparatus 1 is the same as the configuration of the refrigeration cycle apparatus 1 in Embodiment 1 described above, and a description thereof will be omitted.
- the oil temperature sensor 141 provided at a position where the oil temperature can be estimated, and the discharge pipe 150 side A discharge temperature sensor 151 for detecting the temperature (discharge temperature) of the refrigerant.
- the rest of the configuration of the scroll compressor 10 is the same as the configuration of the scroll compressor 10 in the above-described first embodiment, and thus description thereof is omitted.
- the control unit 60 receives the electrical signals transmitted from the oil temperature sensor 141 and the discharge temperature sensor 151, and controls the opening of the third flow rate regulator 50c according to the received signals. Configured to do.
- the oil temperature sensor 141 is provided outside the pressure vessel 100. Further, the discharge temperature sensor 151 is provided inside the discharge pipe 150.
- the oil temperature sensor 141 and the discharge temperature sensor 151 are configured using a thermocouple or a resistance temperature detector (for example, a thermistor).
- control unit 60 detects the oil temperature and the discharge temperature from the oil temperature sensor 141 and the discharge temperature sensor 151, thereby performing the opening degree control of the third flow rate regulator 50c.
- the amount of refrigerant flowing into the suction pipe 170 can be adjusted.
- the control unit 60 determines whether or not the operable range of the scroll compressor 10 (for example, the frequency of the scroll compressor 10) is limited by the increase in the oil temperature. When it is determined that the operable range is limited, the control unit 60 controls the opening of the third flow rate regulator 50c to reduce the amount of refrigerant flowing into the second suction pipe 170. Accordingly, the flow rate of the refrigerant flowing into the first suction pipe 160 can be increased, and the cooling of the low-pressure space (for example, the electric mechanism unit 130, the refrigerating machine oil 140, etc.) inside the scroll compressor 10 can be promoted.
- the low-pressure space for example, the electric mechanism unit 130, the refrigerating machine oil 140, etc.
- control unit 60 determines whether or not the operable range of the scroll compressor 10 is limited by the increase in the discharge temperature. When it is determined that the operable range is limited, the control unit 60 controls the opening degree of the third flow rate regulator 50c and increases the amount of refrigerant flowing into the second suction pipe 170. Thereby, since the refrigerant temperature at the time of the compression start in the compression mechanism part 120 can be suppressed low, an increase in the discharge temperature of the scroll compressor 10 can be suppressed.
- FIG. 6 is a schematic diagram showing the configuration of the refrigeration cycle apparatus 1 according to Embodiment 4 of the present invention.
- FIG. 7 is a schematic longitudinal sectional view showing the configuration of the scroll compressor 10 according to the fourth embodiment of the present invention.
- the refrigeration cycle apparatus 1 branches from the bypass flow path 3 between the first flow rate regulator 50a and the second flow rate regulator 50b and communicates with the intermediate pressure portion of the scroll compressor 10.
- the second branch flow path 5 is provided. Further, in the refrigeration cycle apparatus 1 according to Embodiment 4, the first branch flow path 4 has the third flow rate regulator 50c, and the second branch flow path 5 has the fourth flow rate regulator 50d. have.
- the rest of the configuration of the refrigeration cycle apparatus 1 is the same as the configuration of the refrigeration cycle apparatus 1 in Embodiment 1 described above, and a description thereof will be omitted.
- the scroll compressor 10 includes an intermediate injection mechanism 180 that communicates with the second branch flow path 5 and injects into the compression chamber 123 in the middle of the compression stroke.
- the rest of the configuration of the scroll compressor 10 is the same as the configuration of the scroll compressor 10 in the above-described first embodiment, and thus description thereof is omitted.
- the control unit 60 according to the fourth embodiment is configured to control the opening degree of the fourth flow rate regulator 50d.
- the scroll compressor 10 according to the fourth embodiment can further suppress the increase in the discharge temperature by injecting the refrigerant into the scroll compressor 10 by the intermediate injection mechanism 180.
- the scroll compressor 10 is the vertical scroll compressor 10, but is not limited thereto, and may be a horizontal type.
- the scroll compressor 10 of the above-described embodiment includes a refrigerator, a freezer, a vending machine, an air conditioner (air conditioner), a refrigeration apparatus (refrigerator), and a refrigeration cycle apparatus (heat pump device) such as a water heater. Can be used.
- air conditioner air conditioner
- refrigeration apparatus refrigerator
- refrigeration cycle apparatus heat pump device
- the refrigeration cycle apparatus 1 of the above-described embodiment may include components other than those shown in the above-described embodiment.
- a refrigerant flow switching device for example, a four-way valve
- control unit 60 detects the temperature detected by the scroll compressor 10 (for example, the discharge temperature), and the first flow rate regulator 50a, the second flow rate regulator 50b, Or it is good also as a structure which performs the opening degree control of the 4th flow regulator 50d.
- another flow regulator (not shown) is provided so that the flow rate of the first suction pipe 160 of the scroll compressor 10 can be adjusted, and the control unit 60 adjusts the flow rate.
- the opening degree of the container may be controlled.
- the opening degree of the third flow rate regulator 50c may be controlled by the control unit 60 detecting the temperature of the electric mechanism unit 130.
Abstract
Description
本発明の実施の形態1に係る冷凍サイクル装置1について説明する。図1は、本発明の実施の形態1に係る冷凍サイクル装置1の構成を示す概略図である。なお、図1を含む以下の図面では各構成部材の寸法の関係や形状が異なることがある。また、以下の図面では、同一の又は類似する部材又は部分には、同一の符号を付すか、又は、符号を付すことを省略している。
以下に、本発明の実施の形態2に係るスクロール圧縮機10の圧縮機構部120について説明する。図3は、本発明の実施の形態2に係るスクロール圧縮機10の圧縮機構部120の構成を示す概略的な断面図である。
以下に、本発明の実施の形態3に係る冷凍サイクル装置1及びスクロール圧縮機10について説明する。図4は、本発明の実施の形態3に係る冷凍サイクル装置1の構成を示す概略図である。図5は、本発明の実施の形態3に係るスクロール圧縮機10の構成を示す概略的な縦断面図である。
以下に、本発明の実施の形態4に係る冷凍サイクル装置1及びスクロール圧縮機10について説明する。図6は、本発明の実施の形態4に係る冷凍サイクル装置1の構成を示す概略図である。図7は、本発明の実施の形態4に係るスクロール圧縮機10の構成を示す概略的な縦断面図である。
上述の実施の形態に限らず種々の変形が可能である。例えば、上述の実施の形態においては、スクロール圧縮機10は縦置型のスクロール圧縮機10としたがこれに限定されず、横置型のものであってもよい。
Claims (5)
- 圧力容器と、
側面部としての中空円筒部と底面部とが一体形成され、前記中空円筒部の外周面が前記圧力容器の内周面に固定されたフレームと、
第1の台板と前記第1の台板の一方の面上に形成された第1の渦巻歯とを有し、前記第1の台板が前記第1の渦巻歯と前記底面部との間に位置するように前記中空円筒部の中空部分に旋回可能に収容される旋回スクロールと、
第2の台板と前記第2の台板の一方の面上に形成された第2の渦巻歯とを有し、前記第2の渦巻歯が前記第1の渦巻歯と噛み合うように配置され、前記フレームに対して固定される固定スクロールと、
前記第1の台板に形成された吐出口と連通する吐出管と、
前記フレームの外側で前記圧力容器の内部の低圧空間と連通する第1の吸入管と、
前記圧力容器と前記中空円筒部とを貫通して、前記中空円筒部の中空部分と連通する第2の吸入管と
を備えるスクロール圧縮機。 - 前記第2の吸入管は、前記第2の渦巻歯の中心と、前記第2の渦巻歯の巻き終り部分とを結ぶ直線に対し直交するように配置される請求項1に記載のスクロール圧縮機。
- 前記旋回スクロールと前記固定スクロールとの間に形成される圧縮室内に圧縮行程の途中でインジェクションを行う中間インジェクション機構を更に備える請求項1又は請求項2に記載のスクロール圧縮機。
- 前記吐出管側の冷媒の温度を検知する吐出温度センサと、
前記圧力容器の底部に貯留される冷凍機油の温度を検知する油温センサと
を更に備える請求項1~請求項3のいずれか一項に記載のスクロール圧縮機。 - 請求項1~請求項4のいずれか一項に記載のスクロール圧縮機と、放熱器と、減圧装置と、蒸発器とを備える冷凍サイクル装置。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2014/080498 WO2016079805A1 (ja) | 2014-11-18 | 2014-11-18 | スクロール圧縮機及び冷凍サイクル装置 |
US15/500,712 US10436202B2 (en) | 2014-11-18 | 2014-11-18 | Scroll compressor and refrigeration cycle apparatus |
JP2016559723A JPWO2016079805A1 (ja) | 2014-11-18 | 2014-11-18 | スクロール圧縮機及び冷凍サイクル装置 |
Applications Claiming Priority (1)
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PCT/JP2014/080498 WO2016079805A1 (ja) | 2014-11-18 | 2014-11-18 | スクロール圧縮機及び冷凍サイクル装置 |
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WO2016079805A1 true WO2016079805A1 (ja) | 2016-05-26 |
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PCT/JP2014/080498 WO2016079805A1 (ja) | 2014-11-18 | 2014-11-18 | スクロール圧縮機及び冷凍サイクル装置 |
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US (1) | US10436202B2 (ja) |
JP (1) | JPWO2016079805A1 (ja) |
WO (1) | WO2016079805A1 (ja) |
Cited By (1)
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WO2023079667A1 (ja) * | 2021-11-05 | 2023-05-11 | 三菱電機株式会社 | スクロール圧縮機およびこのスクロール圧縮機を備えた冷凍サイクル装置 |
Families Citing this family (1)
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JP7206506B2 (ja) * | 2020-10-30 | 2023-01-18 | ダイキン工業株式会社 | 回転式圧縮機 |
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US20170218957A1 (en) | 2017-08-03 |
JPWO2016079805A1 (ja) | 2017-04-27 |
US10436202B2 (en) | 2019-10-08 |
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