WO2017098567A1 - 圧縮機及び冷凍サイクル装置 - Google Patents
圧縮機及び冷凍サイクル装置 Download PDFInfo
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- WO2017098567A1 WO2017098567A1 PCT/JP2015/084314 JP2015084314W WO2017098567A1 WO 2017098567 A1 WO2017098567 A1 WO 2017098567A1 JP 2015084314 W JP2015084314 W JP 2015084314W WO 2017098567 A1 WO2017098567 A1 WO 2017098567A1
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- WIPO (PCT)
- Prior art keywords
- bearing
- crankshaft
- end portion
- peripheral surface
- inner peripheral
- 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
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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
- F04C29/02—Lubrication; Lubricant separation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
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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
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
Definitions
- the present invention relates to a compressor and a refrigeration cycle apparatus.
- a hermetic compressor includes a hermetic container, a compression mechanism that compresses a refrigerant, and an electric motor that drives the compression mechanism.
- the compression mechanism and the electric motor are both housed in a sealed container and are connected to each other by a crankshaft.
- the crankshaft is composed of an eccentric shaft portion, a main shaft portion, and a subshaft portion.
- the compression mechanism includes a cylinder, a rolling piston fitted to the eccentric shaft portion, a main bearing that is a bearing that supports the main shaft portion, and a sub bearing that is a bearing that supports the sub shaft portion.
- An eccentric shaft portion and a rolling piston are accommodated in a cylinder chamber that is an internal space of the cylinder.
- a working chamber is formed between the outer peripheral surface of the rolling piston and the inner peripheral surface of the cylinder.
- Refrigerator oil is stored at the bottom of the sealed container. This refrigeration oil is sucked up through an oil supply passage formed in the crankshaft and filled in a gap between the crankshaft and the bearing, whereby an oil film is formed between the crankshaft and the bearing.
- the bearing supports the crankshaft without contacting the crankshaft by fluid lubrication of the oil film.
- the electric motor is provided below the compression mechanism, but some hermetic compressors are provided with the electric motor above the compression mechanism.
- the crankshaft bends with the upper end portion of the main shaft portion as a fulcrum as the rotor swings.
- Increasing the motor core width while maintaining the diameter of the crankshaft does not change the rigidity of the crankshaft. Therefore, the greater the whirling of the rotor, the greater the deflection of the crankshaft with the upper end of the main shaft as a fulcrum. .
- fluid lubrication of the oil film is hindered, and the upper end of the main bearing may come into contact with the main shaft and scuffing may occur at the upper end of the main bearing or the main shaft.
- An object of the present invention is to prevent the upper end portion of the bearing on the electric motor side from coming into contact with the crankshaft even when the crankshaft is increased in the compressor.
- a compressor according to an aspect of the present invention is provided.
- a compression mechanism disposed below the electric motor inside the container and driven by the rotational force of the electric motor transmitted through the crankshaft, wherein the crankshaft is fitted and the crankshaft is used to
- a compression mechanism having a bearing on the inner side of the motor, on which an oil film is formed by supplying the refrigerating machine oil from the bottom of the container, Since the inner peripheral surface of the upper end portion of the bearing is curved, the inner diameter of the upper end portion of the bearing is gradually increased upward.
- the inner peripheral surface of the upper end portion of the bearing on the motor side is curved, the inner diameter of the upper end portion of the bearing is gradually increased upward. For this reason, according to this invention, even if the bending of a crankshaft increases, the upper end part of the said bearing becomes difficult to contact a crankshaft.
- FIG. 1 is a circuit diagram of a refrigeration cycle apparatus according to Embodiment 1.
- FIG. 1 is a circuit diagram of a refrigeration cycle apparatus according to Embodiment 1.
- FIG. 1 is a longitudinal sectional view of a compressor according to Embodiment 1.
- FIG. 3 is a cross-sectional view of the compression mechanism of the compressor according to the first embodiment, taken along line AA.
- FIG. 3 is a longitudinal sectional view of a part of the compression mechanism and the crankshaft of the compressor according to the first embodiment.
- 6 is a graph showing the relationship between the axial position of the crankshaft of the compressor according to Embodiment 1 and the oil film load capacity.
- Embodiment 1 FIG. The configuration of the apparatus and device according to this embodiment, the operation of the device according to this embodiment, the detailed configuration of the components of the device according to this embodiment, and the effects of this embodiment will be described in order.
- FIG. 1 shows the refrigerant circuit 11 during the cooling operation.
- FIG. 2 shows the refrigerant circuit 11 during heating operation.
- the refrigeration cycle apparatus 10 is an air conditioner in the present embodiment, but may be an apparatus other than an air conditioner such as a refrigerator or a heat pump cycle apparatus.
- the refrigeration cycle apparatus 10 includes a refrigerant circuit 11 in which a refrigerant circulates.
- the refrigeration cycle apparatus 10 further includes a compressor 12, a four-way valve 13, a first heat exchanger 14 that is an outdoor heat exchanger, an expansion mechanism 15 that is an expansion valve, and a second heat that is an indoor heat exchanger. And an exchanger 16.
- the compressor 12, the four-way valve 13, the first heat exchanger 14, the expansion mechanism 15, and the second heat exchanger 16 are connected to the refrigerant circuit 11.
- Compressor 12 compresses the refrigerant.
- the four-way valve 13 switches the direction in which the refrigerant flows between the cooling operation and the heating operation.
- the first heat exchanger 14 operates as a condenser during the cooling operation, and dissipates the refrigerant compressed by the compressor 12. That is, the first heat exchanger 14 performs heat exchange using the refrigerant compressed by the compressor 12.
- the first heat exchanger 14 operates as an evaporator during the heating operation, and heats the refrigerant by exchanging heat between the outdoor air and the refrigerant expanded by the expansion mechanism 15.
- the expansion mechanism 15 expands the refrigerant radiated by the condenser.
- the second heat exchanger 16 operates as a condenser during the heating operation, and dissipates heat from the refrigerant compressed by the compressor 12. That is, the second heat exchanger 16 performs heat exchange using the refrigerant compressed by the compressor 12.
- the second heat exchanger 16 operates as an evaporator during the cooling operation, and heats the refrigerant by exchanging heat between the indoor air and the refrigerant expanded by the expansion mechanism 15.
- the refrigeration cycle apparatus 10 further includes a control device 17.
- the control device 17 is specifically a microcomputer. 1 and 2 show only the connection between the control device 17 and the compressor 12, the control device 17 is connected not only to the compressor 12 but also to each element connected to the refrigerant circuit 11. The control device 17 monitors and controls the state of each element.
- any refrigerant such as R32 refrigerant, R290 (propane) refrigerant, R407C refrigerant, R410A refrigerant, R744 (CO 2 ) refrigerant, R1234yf refrigerant, or the like can be used.
- FIG. 3 shows a longitudinal section of the compressor 12. In FIG. 3, hatching representing a cross section is omitted.
- the compressor 12 is a hermetic compressor in the present embodiment.
- the compressor 12 is specifically a one-cylinder rotary compressor, but may be a two-cylinder or more rotary compressor, a scroll compressor, or a reciprocating compressor.
- the compressor 12 includes a container 20, a compression mechanism 30, an electric motor 40, and a crankshaft 50.
- the container 20 is specifically a sealed container. Refrigerating machine oil 25 is stored at the bottom of the container 20. A suction pipe 21 for sucking the refrigerant and a discharge pipe 22 for discharging the refrigerant are attached to the container 20.
- the electric motor 40 is accommodated in the container 20. Specifically, the electric motor 40 is installed in the upper part inside the container 20. In this embodiment, the electric motor 40 is a concentrated winding motor, but may be a distributed winding motor.
- the compression mechanism 30 is accommodated in the container 20. Specifically, the compression mechanism 30 is installed in the lower part inside the container 20. That is, the compression mechanism 30 is disposed below the electric motor 40 inside the container 20.
- the electric motor 40 and the compression mechanism 30 are connected by a crankshaft 50.
- the crankshaft 50 forms an oil supply passage for the refrigerating machine oil 25 and a rotating shaft of the electric motor 40.
- the refrigerating machine oil 25 is pumped up by an oil pump provided at the lower part of the crankshaft 50, supplied to each sliding portion of the compression mechanism 30, and lubricates each sliding portion of the compression mechanism 30.
- an oil pump provided at the lower part of the crankshaft 50, supplied to each sliding portion of the compression mechanism 30, and lubricates each sliding portion of the compression mechanism 30.
- the refrigerating machine oil 25 POE (polyol ester), PVE (polyvinyl ether), AB (alkylbenzene) or the like which is a synthetic oil is used.
- the compression mechanism 30 compresses the refrigerant by being driven by the rotational force of the electric motor 40 transmitted through the crankshaft 50. Specifically, this refrigerant is a low-pressure gas refrigerant sucked into the suction pipe 21. The high-temperature and high-pressure gas refrigerant compressed by the compression mechanism 30 is discharged from the compression mechanism 30 into the container 20.
- the crankshaft 50 includes an eccentric shaft portion 51, a main shaft portion 52, and a subshaft portion 53. These are provided in the order of the main shaft portion 52, the eccentric shaft portion 51, and the auxiliary shaft portion 53 in the axial direction. That is, the main shaft portion 52 is provided on one end side in the axial direction of the eccentric shaft portion 51, and the auxiliary shaft portion 53 is provided on the other end side in the axial direction of the eccentric shaft portion 51.
- the eccentric shaft part 51, the main shaft part 52, and the auxiliary shaft part 53 are each cylindrical.
- the main shaft portion 52 and the sub shaft portion 53 are provided so that their center axes coincide with each other, that is, coaxially.
- the eccentric shaft portion 51 is provided such that the central axis is deviated from the central axes of the main shaft portion 52 and the sub shaft portion 53.
- the eccentric shaft portion 51 rotates eccentrically.
- the electric motor 40 is a brushless DC (Direct Current) motor, but may be a motor other than a brushless DC motor, such as an induction motor.
- DC Direct Current
- the electric motor 40 includes a stator 41 and a rotor 42.
- the stator 41 has a cylindrical shape and is fixed so as to be in contact with the inner peripheral surface of the container 20.
- the rotor 42 has a columnar shape, and is installed inside the stator 41 via a gap having a width of 0.3 mm or more and 1.0 mm or less.
- the stator 41 includes a stator core 43 and a winding 44.
- the stator core 43 is formed by punching a plurality of electromagnetic steel sheets having iron as a main component and having a thickness of 0.1 mm or more and 1.5 mm or less into a certain shape, laminating in an axial direction, caulking, welding, or the like. Made fixed.
- the stator core 43 has an outer diameter larger than the inner diameter of the intermediate portion of the container 20 and is fixed by being shrink-fitted inside the container 20.
- the winding 44 is wound around the stator core 43. Specifically, the winding 44 is wound around the stator core 43 by concentrated winding via an insulating member.
- the winding 44 is composed of a core wire and at least one layer of a coating covering the core wire.
- the material of the core wire is copper.
- the material of the coating is AI (amidoimide) / EI (ester imide).
- the material of the insulating member is PET (polyethylene terephthalate).
- the material of the core wire may be aluminum.
- the insulating member is made of PBT (polybutylene terephthalate), FEP (tetrafluoroethylene / hexafluoropropylene copolymer), PFA (tetrafluoroethylene / perfluoroalkyl vinyl ether copolymer), PTFE (polytetrafluoroethylene), LCP (liquid crystal polymer), PPS (polyphenylene sulfide), or phenol resin may be used.
- One end of a lead wire (not shown) is connected to the winding 44.
- the rotor 42 includes a rotor core 45 and a permanent magnet (not shown).
- the rotor core 45 is formed by punching a plurality of electrical steel sheets mainly composed of iron and having a thickness of 0.1 mm or more and 1.5 mm or less into a certain shape and axially. And are fixed by caulking or welding.
- the permanent magnet is inserted into a plurality of insertion holes formed in the rotor core 45.
- the permanent magnet forms a magnetic pole.
- a ferrite magnet or a rare earth magnet is used as the permanent magnet.
- a shaft hole in which the main shaft portion 52 of the crankshaft 50 is shrink-fitted or press-fitted is formed at the center of the rotor core 45 in plan view.
- a plurality of through holes penetrating in the axial direction are formed around the shaft hole of the rotor core 45.
- Each through hole serves as one of the passages of the gas refrigerant that is discharged from the discharge muffler 35 described later into the space in the container 20.
- the motor 40 when configured as an induction motor, a plurality of slots formed in the rotor core 45 are filled or inserted with a conductor formed of aluminum, copper, or the like. A squirrel-cage winding in which both ends of the conductor are short-circuited by end rings is formed.
- a terminal 24 connected to an external power source such as an inverter device is attached to the top of the container 20.
- the terminal 24 is specifically a glass terminal.
- the terminal 24 is fixed to the container 20 by welding.
- the terminal 24 is connected to the other end of the above-described lead wire. Thereby, the terminal 24 and the winding 44 of the electric motor 40 are electrically connected.
- a discharge pipe 22 having openings at both axial ends is attached to the top of the container 20.
- the gas refrigerant discharged from the compression mechanism 30 is discharged from the space in the container 20 to the external refrigerant circuit 11 through the discharge pipe 22.
- FIG. 4 shows a cut surface when the compression mechanism 30 is cut along a plane AA in FIG. 1, that is, a plane perpendicular to the axial direction of the crankshaft 50.
- hatching representing a cross section is omitted.
- the compression mechanism 30 includes a cylinder 31, a rolling piston 32, a main bearing 33, a sub bearing 34, and a discharge muffler 35.
- the inner circumference of the cylinder 31 is circular in plan view.
- a cylinder chamber 61 that is a circular space in plan view is formed inside the cylinder 31.
- a suction port for sucking gas refrigerant from the refrigerant circuit 11 is provided on the outer peripheral surface of the cylinder 31. The refrigerant sucked from the suction port is compressed in the cylinder chamber 61.
- the cylinder 31 is open at both axial ends.
- the rolling piston 32 has a ring shape. Therefore, the inner periphery and outer periphery of the rolling piston 32 are circular in plan view.
- the rolling piston 32 rotates eccentrically in the cylinder chamber 61.
- the rolling piston 32 is slidably fitted to an eccentric shaft portion 51 of a crankshaft 50 that serves as a rotating shaft of the rolling piston 32.
- the cylinder 31 is provided with a vane groove 62 connected to the cylinder chamber 61 and extending in the radial direction.
- a back pressure chamber 63 that is a circular space in plan view connected to the vane groove 62 is formed outside the vane groove 62.
- the vane 64 has a plate shape with a rounded tip. The vane 64 reciprocates while sliding in the vane groove 62.
- the vane 64 is always pressed against the rolling piston 32 by a vane spring provided in the back pressure chamber 63.
- the vane spring is mainly used for the purpose of pressing the vane 64 against the rolling piston 32 when the compressor 12 is started so that there is no difference in pressure between the container 20 and the cylinder chamber 61.
- the main bearing 33 has an inverted T shape when viewed from the side.
- the main bearing 33 is slidably fitted to a main shaft portion 52 that is a portion above the eccentric shaft portion 51 of the crankshaft 50.
- a through hole 54 serving as an oil supply passage is provided in the crankshaft 50 along the axial direction, and the refrigeration sucked up through the through hole 54 between the main bearing 33 and the main shaft portion 52.
- An oil film is formed by supplying machine oil 25.
- the main bearing 33 closes the upper side of the cylinder chamber 61 and the vane groove 62 of the cylinder 31. That is, the main bearing 33 closes the upper side of the two working chambers in the cylinder 31.
- the auxiliary bearing 34 has a T shape when viewed from the side.
- the auxiliary bearing 34 is slidably fitted to an auxiliary shaft portion 53 that is a portion below the eccentric shaft portion 51 of the crankshaft 50.
- An oil film is formed between the auxiliary bearing 34 and the auxiliary shaft portion 53 by supplying the refrigerating machine oil 25 sucked up through the through hole 54 of the crankshaft 50.
- the auxiliary bearing 34 closes the lower side of the cylinder chamber 61 and the vane groove 62 of the cylinder 31. That is, the auxiliary bearing 34 closes the lower side of the two working chambers in the cylinder 31.
- the main bearing 33 and the sub bearing 34 are fixed to the cylinder 31 by fasteners 36 such as bolts, respectively, and support a crankshaft 50 that is a rotating shaft of the rolling piston 32.
- the main bearing 33 supports the main shaft portion 52 without contacting the main shaft portion 52 by fluid lubrication of an oil film between the main bearing 33 and the main shaft portion 52.
- the auxiliary bearing 34 supports the auxiliary shaft portion 53 without contacting the auxiliary shaft portion 53 by fluid lubrication of an oil film between the auxiliary bearing 34 and the auxiliary shaft portion 53.
- the main bearing 33 is provided with a discharge port for discharging the refrigerant compressed in the cylinder chamber 61 to the refrigerant circuit 11.
- the discharge port is at a position connected to the compression chamber when the cylinder chamber 61 is partitioned into the suction chamber and the compression chamber by the vane 64.
- the main bearing 33 is provided with a discharge valve that closes and opens the discharge port. The discharge valve is closed until the gas refrigerant in the compression chamber reaches a desired pressure, and opens when the gas refrigerant in the compression chamber reaches a desired pressure. Thereby, the discharge timing of the gas refrigerant from the cylinder 31 is controlled.
- the discharge muffler 35 is attached to the outside of the main bearing 33.
- the high-temperature and high-pressure gas refrigerant discharged when the discharge valve is opened once enters the discharge muffler 35 and then is discharged from the discharge muffler 35 into the space in the container 20.
- the discharge port and the discharge valve may be provided in the auxiliary bearing 34 or both the main bearing 33 and the auxiliary bearing 34.
- the discharge muffler 35 is attached to the outside of the bearing provided with the discharge port and the discharge valve.
- a suction muffler 23 is provided beside the container 20.
- the suction muffler 23 sucks low-pressure gas refrigerant from the refrigerant circuit 11.
- the suction muffler 23 prevents the liquid refrigerant from directly entering the cylinder chamber 61 of the cylinder 31 when the liquid refrigerant returns.
- the suction muffler 23 is connected to a suction port provided on the outer peripheral surface of the cylinder 31 via a suction pipe 21.
- the suction port is located at a position connected to the suction chamber when the cylinder chamber 61 is partitioned by the vane 64 into the suction chamber and the compression chamber.
- the main body of the suction muffler 23 is fixed to the side surface of the container 20 by welding or the like.
- the material of the cylinder 31, the main bearing 33, and the auxiliary bearing 34 is sintered steel, but may be gray cast iron or carbon steel.
- the material of the rolling piston 32 is alloy steel containing chromium or the like.
- the material of the vane 64 is high-speed tool steel.
- the vane 64 is provided integrally with the rolling piston 32.
- the vane 64 reciprocates along the groove of the support that is rotatably attached to the rolling piston 32.
- the vane 64 moves back and forth in the radial direction while swinging according to the rotation of the rolling piston 32, thereby partitioning the inside of the cylinder chamber 61 into a compression chamber and a suction chamber.
- the support is composed of two columnar members having a semicircular cross section.
- the support body is rotatably fitted in a circular holding hole formed in an intermediate portion between the suction port and the discharge port of the cylinder 31.
- Electric power is supplied from the terminal 24 to the stator 41 of the electric motor 40 via the lead wire.
- a current flows through the winding 44 of the stator 41 and a magnetic flux is generated from the winding 44.
- the rotor 42 of the electric motor 40 rotates by the action of the magnetic flux generated from the winding 44 and the magnetic flux generated from the permanent magnet of the rotor 42.
- the crankshaft 50 fixed to the rotor 42 rotates.
- the rolling piston 32 of the compression mechanism 30 rotates eccentrically in the cylinder chamber 61 of the cylinder 31 of the compression mechanism 30.
- a cylinder chamber 61 that is a space between the cylinder 31 and the rolling piston 32 is divided into a suction chamber and a compression chamber by a vane 64.
- the crankshaft 50 rotates, the volume of the suction chamber and the volume of the compression chamber change.
- the volume gradually increases, whereby low-pressure gas refrigerant is sucked from the suction muffler 23.
- the compression chamber the gas refrigerant therein is compressed by gradually reducing the volume. The compressed, high-pressure and high-temperature gas refrigerant is discharged from the discharge muffler 35 into the space in the container 20.
- the discharged gas refrigerant further passes through the electric motor 40 and is discharged out of the container 20 from the discharge pipe 22 at the top of the container 20.
- the refrigerant discharged to the outside of the container 20 returns to the suction muffler 23 again through the refrigerant circuit 11.
- FIG. 5 shows a longitudinal section of a part of the compression mechanism 30 and the crankshaft 50.
- hatching representing a cross section is omitted.
- the compression mechanism 30 has the main bearing 33 on the electric motor 40 side and the auxiliary bearing 34 on the opposite side to the electric motor 40 side.
- a crankshaft 50 is fitted in each of the main bearing 33 and the sub bearing 34.
- the main shaft portion 52 is slidably fitted to the main bearing 33
- the subshaft portion 53 is slidably fitted to the sub bearing 34.
- An oil film is formed on the inner peripheral surfaces of the main bearing 33 and the sub bearing 34 by supplying the refrigerating machine oil 25 from the bottom of the container 20 via the crankshaft 50.
- the main bearing 33 and the sub bearing 34 support the crankshaft 50 without contacting the crankshaft 50 by fluid lubrication of the oil film.
- the main bearing 33 has a flat plate-like fixing portion 71 and a cylindrical bearing portion 72.
- the fixing portion 71 is fixed to the upper side of the cylinder 31 by the fastener 36 described above.
- the bearing portion 72 rises from the fixed portion 71 in the direction opposite to the cylinder 31, that is, in the direction of the rotor 42. Openings are provided at both axial ends of the bearing portion 72.
- a main shaft portion 52 is inserted into a space connecting these openings so as to penetrate from one opening to the other.
- the sub-bearing 34 has a flat plate-like fixed portion 73 and a cylindrical bearing portion 74, similarly to the main bearing 33.
- the fixing portion 73 is fixed to the lower side of the cylinder 31 with the fastener 36 described above.
- the bearing portion 74 rises from the fixed portion 73 in the direction opposite to the cylinder 31, that is, in the direction of the bottom portion of the container 20. Openings are provided at both axial ends of the bearing portion 74. In the space connecting these openings, a sub-shaft portion 53 is inserted so as to penetrate from one opening to the other opening.
- the electric motor 40 is provided above the compression mechanism 30. Therefore, the deflection of the crankshaft 50 with the upper end portion of the main shaft portion 52 as a fulcrum increases as the swirl of the rotor 42 increases.
- the upper end portion 81 of the main bearing 33 comes into contact with the main shaft portion 52 and the upper end portion 81 of the main bearing 33. Or there is a possibility that scuffing may occur in the main shaft portion 52. Therefore, at least one of the main bearing 33 and the main shaft portion 52 needs to be configured so that fluid lubrication of the oil film can be appropriately maintained even when the whirling of the rotor 42 increases.
- the fluid lubrication of the oil film is maintained by devising the configuration of the main bearing 33.
- the main bearing 33 provided at a position closer to the electric motor 40 than the auxiliary bearing 34 is greatly affected by the bending of the crankshaft 50 associated with the swing of the rotor 42.
- the fluid lubrication of the oil film can be appropriately maintained.
- the inner peripheral surface 82 of the upper end portion 81 of the main bearing 33 is curved, so that the inner diameter of the upper end portion 81 of the main bearing 33 gradually increases upward. According to this configuration, the effect of preventing the occurrence of burrs at the upper end portion 81 of the main bearing 33 is also obtained.
- the inner peripheral surface 84 of the lower end 83 of the main bearing 33 is inclined, so that the inner diameter of the lower end 83 of the main bearing 33 gradually increases downward. That is, the inner peripheral portion of the lower end portion 83 of the main bearing 33 is chamfered. According to this configuration, the effect of preventing the occurrence of burrs at the lower end 83 of the main bearing 33 is obtained.
- the vertical distance D1 of the curved portion 85 which is a portion where the inner peripheral surface 82 of the upper end portion 81 of the main bearing 33 is curved, is preferably 0.1 mm or more and 2.0 mm or less.
- the vertical distance of the curved portion 85 is extended to 3 millimeters or more, the gap 55 between the curved portion 85 and the crankshaft 50 is reduced when the crankshaft 50 is less bent, such as when the compressor 12 is operating at a low rotational speed. Since it is wide, the range where the oil film does not work effectively is expanded. As a result, the substantial bearing length decreases, and scuffing may occur at the upper end portion 81 or the main shaft portion 52 of the main bearing 33.
- the vertical distance D2 of the inclined portion 86 which is the portion where the inner peripheral surface 84 of the lower end portion 83 of the main bearing 33 is inclined, is preferably 0.1 mm or more and 2.0 mm or less.
- the vertical distance D1 of the curved portion 85 is the same as the vertical distance D2 of the inclined portion 86.
- the shape of the inner peripheral surface 82 of the curved portion 85 in the longitudinal section of the upper end portion 81 of the main bearing 33 is an arc having a radius having the same length as the vertical distance D2 of the inclined portion 86.
- the substantial bearing length can be ensured by setting the vertical distance D1 of the curved portion 85 adopting the arc shape to 0.1 mm or more and 2.0 mm or less. Therefore, fluid lubrication of the oil film can be maintained even when the crankshaft 50 is not bent.
- the gap 56 between the inclined portion 86 and the crankshaft 50 be as narrow as possible in order to easily maintain fluid lubrication of the oil film.
- the gap 55 between the curved portion 85 and the crankshaft 50 needs to be wide enough to avoid metal contact when the crankshaft 50 is greatly bent. Therefore, it is desirable that the maximum width W1 of the gap 55 between the curved portion 85 and the crankshaft 50 is wider than the maximum width W2 of the gap 56 between the inclined portion 86 and the crankshaft 50.
- the inner peripheral surface 82 of the upper end portion 81 of the main bearing 33 is curved, so that the inner diameter of the upper end portion 81 of the main bearing 33 gradually increases upward. For this reason, according to the present embodiment, even if the bending of the crankshaft 50 with the upper end portion of the main shaft portion 52 as a fulcrum increases, the upper end portion 81 of the main bearing 33 is less likely to contact the main shaft portion 52. Therefore, the occurrence of scuffing at the upper end portion 81 or the main shaft portion 52 of the main bearing 33 can be prevented.
- the compressor 12 In order to manufacture a small and high output air conditioner, the compressor 12 needs a compression mechanism 30 that is small and has a large excluded volume.
- the refrigerant that is used under the low compression condition can obtain the same potential as the conventional refrigerant unless the circulation amount in the refrigerant circuit 11 is increased. Absent. Therefore, in order to use such a refrigerant, the compression mechanism 30 having a large excluded volume is required.
- the eccentric shaft portion of the crankshaft 50 is maintained while maintaining the inner diameter of the cylinder chamber 61 of the compression mechanism 30 and the diameter of the crankshaft 50. It is optimal to increase the amount of eccentricity 51. In order to improve the output of the electric motor 40 according to the excluded volume, it is effective to increase the electric motor core width.
- the swirl of the rotor 42 increases due to the increase in the weight of the rotor 42 and the rise in the position of the center of gravity. Since the rigidity of the crankshaft 50 does not change, the deflection of the crankshaft 50 with the upper end portion of the main shaft portion 52 as a fulcrum increases as the swirl of the rotor 42 increases. If the fluid lubrication of the oil film is inhibited by this bending, the upper end portion 81 of the main bearing 33 may come into contact with the main shaft portion 52 and scuffing may occur at the upper end portion 81 of the main bearing 33 or the main shaft portion 52.
- an arc-shaped curved portion 85 is provided only at the upper end of the main bearing 33 close to the rotor 42.
- the radius of the arc is the same length as the chamfer at the lower end far from the rotor 42 of the main bearing 33, and preferably 0.1 mm or more and 2.0 mm or less. Therefore, when the crankshaft 50 is greatly bent, the oil film load capacity can be secured rather than the chamfering. Further, a substantial bearing length can be secured even when the crankshaft 50 is not bent. Therefore, according to the present embodiment, scuffing of the upper end portion 81 of the main bearing 33 or the main shaft portion 52 can be prevented.
- a bearing is provided only on one side of the rotor 42. Therefore, the amount of bending of the crankshaft 50 is large on the side close to the rotor 42 of the bearing, and the amount of bending of the crankshaft 50 is small on the side far from the rotor 42 of the bearing. Accordingly, an arc shape is adopted only for the end closer to the rotor 42 of the main bearing 33 provided closer to the electric motor 40 than the auxiliary bearing 34, and the end far from the rotor 42 is chamfered. Thus, a suitable main bearing 33 can be realized.
- the oil film load capacity can be secured even if the deflection of the crankshaft 50 with the upper end portion of the main shaft portion 52 as a fulcrum increases, and the substantial bearing length is reduced. Can be secured. Therefore, the lubricity of any of the front end portion and the substantial length portion of the main bearing 33 is not deteriorated, and scuffing can be prevented. Thereby, the compressor 12 with high performance and high reliability can be obtained.
- the inclined portion 86 is provided at the lower end portion 83 of the main bearing 33, but the inclined portion 86 may not be provided. That is, the inner peripheral portion of the lower end portion 83 of the main bearing 33 may not be chamfered.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressor (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
底部に冷凍機油が貯留された容器と、
前記容器に収納された電動機と、
前記容器の内部で前記電動機の下方に配置され、前記クランク軸を介して伝達される前記電動機の回転力によって駆動される圧縮機構であり、前記クランク軸が嵌められ、前記クランク軸を介して前記容器の底部から前記冷凍機油が供給されることで内周面に油膜が形成される軸受を、前記電動機側に有する圧縮機構とを備え、
前記軸受の上端部の内周面が湾曲していることで前記軸受の上端部の内径が上方に向かって徐々に大きくなっている。
本実施の形態に係る装置及び機器の構成、本実施の形態に係る機器の動作、本実施の形態に係る機器の構成要素の詳細な構成、本実施の形態の効果を順番に説明する。
図1及び図2を参照して、本実施の形態に係る装置である冷凍サイクル装置10の構成を説明する。
図3及び図4を参照して、本実施の形態に係る機器である圧縮機12の動作を説明する。圧縮機12の動作は、本実施の形態に係る冷媒圧縮方法に相当する。
図5を参照して、本実施の形態に係る機器の構成要素である主軸受33の詳細な構成を説明する。
本実施の形態では、主軸受33の上端部81の内周面82が湾曲していることで主軸受33の上端部81の内径が上方に向かって徐々に大きくなっている。このため、本実施の形態によれば、主軸部52の上端部を支点としたクランク軸50の撓みが増大しても、主軸受33の上端部81が主軸部52に接触しにくくなる。よって、主軸受33の上端部81又は主軸部52におけるスカッフの発生を防止することができる。
本実施の形態では、主軸受33の下端部83に傾斜部86が設けられているが、傾斜部86はなくてもよい。即ち、主軸受33の下端部83の内周部は、面取りされていなくてもよい。
Claims (7)
- 底部に冷凍機油が貯留された容器と、
前記容器に収納された電動機と、
前記冷凍機油の給油路と前記電動機の回転軸とを形成するクランク軸と、
前記容器の内部で前記電動機の下方に配置され、前記クランク軸を介して伝達される前記電動機の回転力によって駆動される圧縮機構であり、前記クランク軸が嵌められ、前記クランク軸を介して前記容器の底部から前記冷凍機油が供給されることで内周面に油膜が形成される軸受を、前記電動機側に有する圧縮機構と
を備え、
前記軸受の上端部の内周面が湾曲していることで前記軸受の上端部の内径が上方に向かって徐々に大きくなっている圧縮機。 - 前記軸受の下端部の内周面が傾斜していることで前記軸受の下端部の内径が下方に向かって徐々に大きくなっている請求項1に記載の圧縮機。
- 前記軸受の上端部の内周面が湾曲している部分である湾曲部の垂直距離が、前記軸受の下端部の内周面が傾斜している部分である傾斜部の垂直距離と同じであり、前記軸受の上端部の縦断面における前記湾曲部の内周面の形状が、前記傾斜部の垂直距離と同じ長さの半径を持つ円弧である請求項2に記載の圧縮機。
- 前記軸受の上端部の内周面が湾曲している部分である湾曲部と前記クランク軸との隙間の最大幅が、前記軸受の下端部の内周面が傾斜している部分である傾斜部と前記クランク軸との隙間の最大幅よりも広い請求項2に記載の圧縮機。
- 前記軸受の上端部の内周面が湾曲している部分である湾曲部の垂直距離が0.1ミリメートル以上2.0ミリメートル以下である請求項1又は2に記載の圧縮機。
- 前記圧縮機構は、前記軸受である主軸受を、前記電動機側に有し、前記クランク軸が嵌められ、前記クランク軸を介して前記容器の底部から前記冷凍機油が供給されることで内周面に油膜が形成される副軸受を、前記電動機側と逆側に有する請求項1から5のいずれか1項に記載の圧縮機。
- 請求項1から6のいずれか1項に記載の圧縮機を備える冷凍サイクル装置。
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CN201580085012.1A CN108368849A (zh) | 2015-12-07 | 2015-12-07 | 压缩机以及制冷循环装置 |
PCT/JP2015/084314 WO2017098567A1 (ja) | 2015-12-07 | 2015-12-07 | 圧縮機及び冷凍サイクル装置 |
KR1020187009262A KR101992586B1 (ko) | 2015-12-07 | 2015-12-07 | 압축기 및 냉동 사이클 장치 |
JP2017554686A JPWO2017098567A1 (ja) | 2015-12-07 | 2015-12-07 | 圧縮機及び冷凍サイクル装置 |
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Citations (4)
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JP2001182741A (ja) * | 1999-12-27 | 2001-07-06 | Sankyo Seiki Mfg Co Ltd | スラスト動圧軸受装置及びその製造方法 |
JP2010255448A (ja) * | 2009-04-22 | 2010-11-11 | Panasonic Corp | ロータリー圧縮機 |
JP2013245767A (ja) * | 2012-05-25 | 2013-12-09 | Taiho Kogyo Co Ltd | すべり軸受 |
JP2014139443A (ja) * | 2012-10-23 | 2014-07-31 | Panasonic Corp | ロータリ圧縮機 |
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KR20000009656U (ko) * | 1998-11-09 | 2000-06-05 | 구자홍 | 밀폐형 회전식 압축기의 마찰손실 저감구조 |
JP2001289169A (ja) | 2000-04-05 | 2001-10-19 | Matsushita Electric Ind Co Ltd | 圧縮機 |
JP2003003959A (ja) * | 2001-06-20 | 2003-01-08 | Matsushita Electric Ind Co Ltd | 圧縮機 |
CN101749247B (zh) * | 2008-12-05 | 2014-03-19 | 童夏民 | 冷缸压缩循环的全封闭转子式制冷压缩机 |
CN104514722B (zh) * | 2014-12-22 | 2017-01-18 | 重庆凌达压缩机有限公司 | 压缩组件及具有其的旋转式压缩机 |
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Publication number | Priority date | Publication date | Assignee | Title |
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JP2001182741A (ja) * | 1999-12-27 | 2001-07-06 | Sankyo Seiki Mfg Co Ltd | スラスト動圧軸受装置及びその製造方法 |
JP2010255448A (ja) * | 2009-04-22 | 2010-11-11 | Panasonic Corp | ロータリー圧縮機 |
JP2013245767A (ja) * | 2012-05-25 | 2013-12-09 | Taiho Kogyo Co Ltd | すべり軸受 |
JP2014139443A (ja) * | 2012-10-23 | 2014-07-31 | Panasonic Corp | ロータリ圧縮機 |
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KR20180050351A (ko) | 2018-05-14 |
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