WO2018042507A1 - 圧縮機および冷凍サイクル装置 - Google Patents

圧縮機および冷凍サイクル装置 Download PDF

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Publication number
WO2018042507A1
WO2018042507A1 PCT/JP2016/075276 JP2016075276W WO2018042507A1 WO 2018042507 A1 WO2018042507 A1 WO 2018042507A1 JP 2016075276 W JP2016075276 W JP 2016075276W WO 2018042507 A1 WO2018042507 A1 WO 2018042507A1
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WO
WIPO (PCT)
Prior art keywords
crankshaft
solid lubricant
shaft portion
bearing
compressor
Prior art date
Application number
PCT/JP2016/075276
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
尚久 五前
聡経 新井
谷　真男
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to KR1020197001759A priority Critical patent/KR20190020092A/ko
Priority to CZ201997A priority patent/CZ309090B6/cs
Priority to PCT/JP2016/075276 priority patent/WO2018042507A1/ja
Priority to CN201680088680.4A priority patent/CN109642561B9/zh
Priority to JP2018536547A priority patent/JP6878443B2/ja
Publication of WO2018042507A1 publication Critical patent/WO2018042507A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • 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
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • 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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/14—Features relating to lubrication
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10N—INDEXING SCHEME ASSOCIATED WITH SUBCLASS C10M RELATING TO LUBRICATING COMPOSITIONS
    • C10N2050/00—Form in which the lubricant is applied to the material being lubricated
    • C10N2050/08—Solids
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/91—Coating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2230/00—Manufacture
    • F05B2230/90—Coating; Surface treatment

Definitions

  • the present invention relates to a compressor and a refrigeration cycle apparatus.
  • the rotary compressor described in Patent Document 1 includes a crankshaft made of mechanical structural steel.
  • a manganese phosphate coating and a molybdenum disulfide coating are provided on the surface of the portion of the crankshaft that slides with the bearing.
  • crankshaft which is made of a cast material such as FCD (Ferrum Casting Ductile) 550 or FCD700 and whose coating is only a manganese phosphate coating.
  • FCD Fluorrum Casting Ductile
  • FCD700 The Young's modulus of a cast material such as FCD550 or FCD700 is about 164 gigapascal. That is, the rigidity of the cast material is not high. Therefore, when the diameter of the crankshaft made of the cast material is reduced, the amount of bending of the crankshaft due to the gas load in the compression chamber increases. When the amount of bending of the crankshaft increases, the crankshaft tends to seize on the bearing, and the reliability of the compressor is impaired.
  • the crankshaft material is changed to a material with high rigidity, it is possible to suppress an increase in the amount of bending of the crankshaft.
  • the Young's modulus of the forging material such as S45C is about 205 gigapascal or higher. That is, the forging material has high rigidity.
  • the seizure strength of the crankshaft made of the forged material and the coating only of the manganese phosphate coating is inferior to the seizure resistance of the crankshaft made of the cast material and the coating only of the manganese phosphate coating by about 10%. Therefore, when the material of the crankshaft is changed from the cast material to the forged material, the crankshaft is easily seized on the bearing even if the amount of bending of the crankshaft does not increase, and the reliability of the compressor is impaired.
  • a compressor according to an aspect of the present invention is provided.
  • a crankshaft partially covered with a solid lubricant film containing molybdenum disulfide and a resin;
  • a compression mechanism that has a bearing slidably fitted to a portion of the crankshaft covered with the solid lubricant film and that is driven by rotation of the crankshaft.
  • a coating containing not only molybdenum disulfide but also resin is employed on the crankshaft of the compressor. For this reason, the seizure resistance of the crankshaft is sufficiently improved.
  • 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. AA sectional view of FIG. Sectional drawing which shows the structure of the film in the solid lubricant application part of the crankshaft of the compressor which concerns on Embodiment 1.
  • FIG. The graph which shows the relationship between the ratio of the film thickness with respect to a crankshaft diameter in the compressor which concerns on Embodiment 1, and the ratio of the seizing load with respect to the conventional product.
  • the graph which shows the relationship between the ratio of the film thickness fluctuation
  • Embodiment 1 FIG. This embodiment will be described with reference to FIGS.
  • 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 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 exchanger that is an indoor heat 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 elements other than the compressor 12 connected to the refrigerant circuit 11. May be.
  • the control device 17 monitors and controls the state of elements connected to the control device 17.
  • HFC HydroFluoroCarbon refrigerants
  • R32, R125, R134a, R407C, and R410A HFC refrigerants
  • HFO HydroFluoroOlefin refrigerants
  • R1123, R1132 (E), R1132 (Z), R1132a, R1141, R1234yf, R1234ze (E), R1234ze (Z) are used.
  • natural refrigerants such as R290 (propane), R600a (isobutane), R744 (carbon dioxide), R717 (ammonia) are used.
  • other refrigerants are used.
  • a mixture of two or more of these refrigerants is used.
  • FIG. 3 shows a longitudinal section of the compressor 12.
  • the compressor 12 is a hermetic compressor in the present embodiment. Specifically, the compressor 12 is a single-cylinder rotary compressor, but may be a multi-cylinder rotary compressor, a scroll compressor, or a reciprocating compressor.
  • the compressor 12 includes an airtight container 20, a compression mechanism 30, an electric motor 40, and a crankshaft 50.
  • Refrigerator oil 25 is stored at the bottom of the sealed container 20.
  • a suction pipe 21 for sucking the refrigerant and a discharge pipe 22 for discharging the refrigerant are attached to the sealed container 20.
  • the electric motor 40 is stored in the sealed container 20. Specifically, the electric motor 40 is installed on the inner upper part of the sealed container 20.
  • the electric motor 40 is a concentrated winding motor in the present embodiment, but may be a distributed winding motor.
  • the compression mechanism 30 is accommodated in the sealed container 20. Specifically, the compression mechanism 30 is installed in the lower part inside the sealed container 20. That is, the compression mechanism 30 is disposed below the electric motor 40 inside the sealed 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 electric motor 40 rotates the crankshaft 50.
  • the compression mechanism 30 compresses the refrigerant by being driven by the rotation of the crankshaft 50. That is, the compression mechanism 30 compresses the refrigerant by being driven by the rotational force of the electric motor 40 transmitted via the crankshaft 50.
  • 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 sealed container 20.
  • the crankshaft 50 has 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.
  • a part of the crankshaft 50 is coated with a solid lubricant to form a film.
  • the part of the crankshaft 50 to which the solid lubricant is applied that is, the structure of the coating film in the solid lubricant application part 37 will be described later.
  • the electric motor 40 has 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 sealed 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 has a stator core 43 and a winding 44.
  • the stator core 43 is formed by punching a plurality of electromagnetic 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, stacking them in an axial direction, and fixing them by caulking. Produced.
  • the stator core 43 has an outer diameter larger than the inner diameter of the intermediate portion of the sealed container 20 and is fixed by being shrink-fitted inside the sealed 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. One end of a lead wire (not shown) is connected to the winding 44.
  • winding 44 consists of a core wire and the at least 1 layer of film which covers a 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 method of fixing the electromagnetic steel plates of the stator core 43 is not limited to caulking, and other methods such as welding may be used.
  • the method for fixing the stator core 43 to the inside of the sealed container 20 is not limited to shrink fitting, and may be press-fitting.
  • the material of the core wire of the winding 44 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.
  • PBT polybutylene terephthalate
  • FEP tetrafluoroethylene / hexafluoropropylene copolymer
  • PFA tetrafluoroethylene / perfluoroalkyl vinyl ether copolymer
  • PTFE polytetrafluoroethylene
  • LCP liquid crystal polymer
  • PPS polyphenylene sulfide
  • phenol resin may be used.
  • the rotor 42 has 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. It is manufactured by laminating and fixing with caulking.
  • 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.
  • the method of fixing the electromagnetic steel plates of the rotor core 45 is not limited to caulking, and other methods such as welding may be used.
  • 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. That is, the inner diameter of the rotor core 45 is smaller than the outer diameter of the main shaft portion 52.
  • a plurality of through holes penetrating in the axial direction are formed around the shaft hole of the rotor core 45.
  • Each through-hole becomes one of the passages of the gas refrigerant discharged from the discharge muffler 35 described later to the space in the sealed container 20.
  • Each through hole also serves as one of passages for dropping the refrigerating machine oil 25 guided to the upper part of the sealed container 20 to the lower part of the sealed 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 or copper. Then, 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 sealed container 20.
  • the terminal 24 is specifically a glass terminal.
  • the terminal 24 is fixed to the sealed 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 both ends opened in the axial direction is attached to the top of the sealed container 20.
  • the gas refrigerant discharged from the compression mechanism 30 is discharged from the space in the sealed container 20 through the discharge pipe 22 to the external refrigerant circuit 11.
  • FIG. 4 shows a cut surface when the compression mechanism 30 is cut along a plane AA in FIG. 3, 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 roller 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 roller 32 has a ring shape. Therefore, the inner periphery and the outer periphery of the roller 32 are circular in plan view.
  • the roller 32 rotates eccentrically in the cylinder chamber 61.
  • the roller 32 is slidably fitted to an eccentric shaft portion 51 of the crankshaft 50 that serves as a rotation shaft of the roller 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 roller 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 roller 32 when the compressor 12 is started so that there is no difference in pressure between the sealed container 20 and the cylinder chamber 61.
  • the main bearing 33 is a reverse T-shaped bearing in side view.
  • 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 secondary bearing 34 is a T-shaped bearing 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, and support a crankshaft 50 that is a rotating shaft of the roller 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 is then discharged from the discharge muffler 35 into the space in the sealed container 20.
  • the discharge port and the discharge valve may be provided in the auxiliary bearing 34 or in 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 sealed 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 sealed container 20 by welding or the like.
  • the material of the eccentric shaft portion 51, the main shaft portion 52, and the subshaft portion 53 of the crankshaft 50 may be a cast material, but in this embodiment is a forging material such as S45C.
  • the material of the main bearing 33 and the auxiliary bearing 34 is either a cast material or a sintered material, and specifically, sintered steel, gray cast iron, or carbon steel.
  • the material of the cylinder 31 is also sintered steel, gray cast iron, or carbon steel.
  • the material of the roller 32 is a cast material, specifically, an alloy steel containing molybdenum, nickel, and chromium, or an iron-based cast material.
  • the material of the vane 64 is high-speed tool steel.
  • the vane 64 is provided integrally with the roller 32.
  • the crankshaft 50 is driven, the vane 64 reciprocates along a groove of a support that is rotatably attached to the roller 32.
  • the vane 64 moves back and forth in the radial direction while swinging according to the rotation of the roller 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 rotor 42 rotates due to the attractive repulsion action between the rotating magnetic field generated by the current flowing through the winding 44 of the stator 41 and the magnetic field of the permanent magnet of the rotor 42.
  • the crankshaft 50 fixed to the rotor 42 rotates.
  • the roller 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 roller 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 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 sealed container 20.
  • the discharged gas refrigerant further passes through the electric motor 40 and is discharged out of the sealed container 20 from the discharge pipe 22 at the top of the sealed container 20.
  • the refrigerant discharged to the outside of the sealed container 20 returns to the suction muffler 23 again through the refrigerant circuit 11.
  • FIG. 5 shows a part of a cross section of the three layers of the solid lubricant film 70, the manganese phosphate film 80, and the base material 55 of the crankshaft 50.
  • the solid lubricant film 70 includes molybdenum disulfide 71 and a resin 72.
  • the resin 72 is PAI (polyamideimide).
  • solid lubricant film 70 further includes graphite 73.
  • the resin 72 is preferably PAI, but may be PTFE, PPS, PES (polyethersulfone), PI (polyimide), or PEEK (polyetheretherketone).
  • a part of the crankshaft 50 is covered with the solid lubricant film 70 having the above configuration.
  • the main bearing 33 and the sub bearing 34 of the compression mechanism 30 are slidably fitted to the portion of the crankshaft 50 covered with the solid lubricant film 70. That is, in the present embodiment, the portion where the main bearing 33 of the main shaft portion 52 is fitted and the portion where the sub bearing 34 of the sub shaft portion 53 is fitted are the solid lubricant film having the above-described configuration. 70.
  • the seizure resistance of crankshaft 50 can be sufficiently increased. Therefore, the main shaft portion 52 is difficult to seize on the main bearing 33.
  • the auxiliary shaft portion 53 is also less likely to seize on the auxiliary bearing 34.
  • the material of the main shaft portion 52 and the sub shaft portion 53 is a forged material, whereas the material of the main bearing 33 and the sub bearing 34 is either a cast material or a sintered material.
  • the material of the main shaft portion 52 and the sub shaft portion 53 and the material of the main bearing 33 and the sub bearing 34 may be the same type of metal.
  • both the material of the main shaft portion 52 and the sub shaft portion 53 and the material of the main bearing 33 and the sub bearing 34 may be iron-based materials.
  • the seizure resistance is reduced due to “co-metal”.
  • the solid lubricant film 70 can suppress a decrease in the seizure resistance of the main shaft portion 52 and the sub shaft portion 53 due to “common gold”.
  • the portion of the eccentric shaft portion 51 where the roller 32 is fitted is also covered with the solid lubricant film 70 having the above-described configuration. Therefore, the eccentric shaft portion 51 is difficult to seize on the roller 32.
  • the material of the eccentric shaft portion 51 is a forged material, whereas the material of the roller 32 is a cast material.
  • the material of the eccentric shaft portion 51 and the material of the roller 32 are The same kind of metal may be used.
  • both the material of the eccentric shaft portion 51 and the material of the roller 32 may be an iron-based material.
  • the solid lubricant film 70 can also suppress the seizure resistance of the eccentric shaft portion 51 due to “common gold”.
  • the portion of the main shaft portion 52 that is shrink-fitted or press-fitted into the rotor core 45 is not covered with the solid lubricant film 70. Therefore, it becomes easy to shrink-fit or press-fit the main shaft portion 52 into the shaft hole of the rotor core 45.
  • the graphite 73 is not essential, but by including the graphite 73 in the solid lubricant film 70, the seizure resistance of the crankshaft 50 can be further increased.
  • the solid lubricant film 70 is overlaid on the manganese phosphate film 80.
  • a surface 81 in contact with the solid lubricant film 70 of the manganese phosphate film 80 is an uneven surface. That is, a large number of concave portions 82 and convex portions 83 are formed on the surface 81 of the manganese phosphate coating 80. Since the surface 81 of the manganese phosphate coating 80 is not flat, the solid lubricant coating 70 tends to adhere to the surface 81 of the manganese phosphate coating 80 and is difficult to peel off. Therefore, the seizure resistance of the crankshaft 50 is further improved.
  • the roughness of the surface 81 of the manganese phosphate coating 80 in contact with the solid lubricant coating 70 is 1.5 z or more, the effect that the solid lubricant coating 70 can easily adhere to the surface 81 of the manganese phosphate coating 80 is obtained. It is done.
  • the roughness of the surface 81 of the manganese phosphate coating 80 is desirably 2.0 z or more, and more desirably 3.0 z or more.
  • the parameter values such as 1.5z, 2.0z, and 2.0z are values that represent the roughness of the surface 81 of the manganese phosphate coating 80 in terms of a ten-point average height.
  • the manganese phosphate coating 80 is formed by subjecting the base material 55 of the crankshaft 50 to a manganese phosphate base treatment. After the manganese phosphate base treatment, when buffing is performed as in the prior art, the concave portions 82 and the convex portions 83 of the manganese phosphate coating 80 are removed, and the surface 81 of the manganese phosphate coating 80 becomes smooth. End up. Therefore, in this embodiment, buff processing is omitted. As a result, the roughness of the surface 81 of the manganese phosphate coating 80 as described above is obtained. Further, the seizure resistance of the crankshaft 50 is improved by about 70% as compared with the case where the buffing is performed after the manganese phosphate base treatment.
  • the solid lubricant film 70 is formed by performing a deflick coating process on the manganese phosphate film 80 after the manganese phosphate base treatment.
  • the molybdenum disulfide 71 may penetrate into the manganese phosphate coating 80. Therefore, in the present embodiment, the fixed lubricant is applied to the surface 81 of the manganese phosphate coating 80 by spraying during the deflick coating process. As a result, molybdenum disulfide 71 does not penetrate the manganese phosphate coating 80, and a solid lubricant coating 70 having the structure shown in FIG. 5 is obtained. Then, the seizure resistance of the crankshaft 50 is sufficiently improved.
  • FIG. 6 shows the relationship between the ratio of the film thickness to the crankshaft diameter and the ratio of the seizure load to the conventional product.
  • crankshaft diameter is the diameter of the portion of the crankshaft 50 where the bearing is fitted.
  • the diameter of the portion of the main shaft portion 52 where the main bearing 33 is fitted corresponds to the “crank shaft diameter”.
  • the diameter of the portion of the auxiliary shaft portion 53 where the auxiliary bearing 34 is fitted also corresponds to the “crankshaft diameter”.
  • the “film thickness” is the minimum thickness of the solid lubricant film 70.
  • the main bearing 33 of the solid lubricant film 70 is opposed to the main bearing 33 from the apex of the projection 83 having the highest height of the manganese phosphate coating 80 in the portion where the main bearing 33 of the main shaft portion 52 is fitted.
  • the distance up to the sliding surface 74 corresponds to the “film thickness”.
  • the ratio of the film thickness to the crankshaft diameter is a value obtained by dividing the film thickness by the crankshaft diameter.
  • the ratio of the seizure load to the conventional product is the ratio of the seizure strength of the crankshaft 50 according to the present embodiment to the seizure strength of the conventional product having only the manganese phosphate coating. It is assumed that the total thickness of the solid lubricant film 70 and the manganese phosphate film 80 is the same as the thickness of the conventional film.
  • the ratio of the film thickness to the crankshaft diameter exceeds 0.8 ⁇ 10 ⁇ 3 , the ratio of the seizure load to the conventional product is less than 100%. This is because when the ratio of the film thickness to the crankshaft diameter exceeds 0.8 ⁇ 10 ⁇ 3 , the solid lubricant film 70 is easily peeled off. Therefore, the ratio of the film thickness to the crankshaft diameter is desirably 0.8 ⁇ 10 ⁇ 3 or less.
  • the ratio of the film thickness to the crankshaft diameter is less than 0.3 ⁇ 10 ⁇ 3 , the film thickness after the compressor 12 has been operated for a long period of time such as 10 years. Is not enough. This is because the amount of wear of the solid lubricant film 70 increases as the period of operation of the compressor 12 increases. Therefore, the ratio of the film thickness to the crankshaft diameter is preferably 0.3 ⁇ 10 ⁇ 3 or more.
  • the solid lubricant film 70 with respect to the diameter of the main shaft portion 52 in the portion where the main bearing 33 of the main shaft portion 52 is fitted, in order to prevent the seizure strength from being lowered due to peeling and abrasion of the solid lubricant film 70.
  • the minimum thickness ratio is preferably 0.0003 or more and 0.0008 or less.
  • the ratio of the minimum thickness of the solid lubricant film 70 to the diameter of the auxiliary shaft portion 53 is preferably 0.0003 or more and 0.0008 or less. .
  • FIG. 7 shows the relationship between the ratio of film thickness variation to the clearance between the coating and the bearing and the ratio of oil film thickness to the conventional product.
  • the “clearance between the coating and the bearing” is the distance between the solid lubricant coating 70 and the bearing.
  • the maximum value of the distance between the solid lubricant film 70 and the main bearing 33 corresponds to the “clearance between the film and the bearing”.
  • the maximum value of the distance between the solid lubricant film 70 and the auxiliary bearing 34 also corresponds to the “clearance between the film and the bearing”.
  • the “film thickness variation” is a difference in height of the sliding surface 74 facing the bearing of the solid lubricant film 70.
  • the difference between the maximum value and the minimum value of the distance corresponds to the “film thickness variation”.
  • the difference between the value and the minimum value corresponds to “film thickness variation”.
  • the ratio of film thickness fluctuation to the clearance between the film and the bearing is a value obtained by dividing the film thickness fluctuation by the clearance between the film and the bearing.
  • the ratio of the oil film thickness to the conventional product refers to the distance between the main bearing 33 and the main shaft portion 52 in the crankshaft 50 according to the present embodiment with respect to the thickness of the oil film in the conventional product having only the manganese phosphate coating. Or the ratio of the thickness of the oil film between the auxiliary bearing 34 and the auxiliary shaft portion 53.
  • the ratio of the film thickness variation to the clearance between the coating and the bearing exceeds 0.15
  • the ratio of the oil film thickness to the conventional product is less than 1.0. This is because if the ratio of the variation in film thickness to the clearance between the coating and the bearing exceeds 0.15, the gap between the solid lubricant coating 70 and the bearing is too wide to form an oil film. is there. Therefore, it is desirable that the ratio of film thickness variation to the clearance between the coating and the bearing is 0.15 or less.
  • the portion of the main shaft portion 52 where the main bearing 33 is fitted is formed between the solid lubricant film 70 and the main bearing 33.
  • the ratio of the height difference of the sliding surface 74 facing the main bearing 33 of the solid lubricant film 70 with respect to the clearance between them is preferably 0.15 or less. Even in the portion where the auxiliary bearing 34 of the auxiliary shaft portion 53 is fitted, the height of the sliding surface 74 of the solid lubricant film 70 facing the auxiliary bearing 34 with respect to the clearance between the solid lubricant film 70 and the auxiliary bearing 34 is high.
  • the difference ratio is desirably 0.15 or less.
  • a coating including not only molybdenum disulfide 71 but also resin 72 is employed on the crankshaft 50 of the compressor 12.
  • the seizure resistance of the crankshaft 50 is sufficiently improved.
  • the seizure resistance of the crankshaft 50 is improved by about 10% to 20% over the conventional product. Therefore, even if a forged material is used as the material of the crankshaft 50, the crankshaft 50 is difficult to seize on the bearing. Therefore, the diameter of the crankshaft 50 can be reduced without impairing the reliability of the compressor 12, and the highly efficient compressor 12 can be obtained.
  • the oil film thickness may be significantly reduced. In the present embodiment, even in such a case, the crankshaft 50 is not seized, and the highly reliable compressor 12 can be obtained.
  • the solid lubricant film 70 may further include a different type of resin from the resin 72.
  • the solid lubricant film 70 may contain two or more kinds of resins among PAI, PTFE, PPS, PES, PI, and PEEK.
  • the compressor 12 may be a multi-cylinder rotary compressor.
  • the compressor 12 is configured as a multi-cylinder rotary compressor will be described as a modification of the present embodiment.
  • the compression mechanism 30 includes a plurality of cylinders 31, a plurality of rollers 32, and a number of partition plates that is one less than the number of cylinders 31. If the number of cylinders 31 is two, the number of rollers 32 is two and the number of partition plates is one.
  • the crankshaft 50 has the same number of eccentric shaft portions 51 as the number of rollers 32.
  • a corresponding roller 32 is slidably fitted to each eccentric shaft portion 51.
  • the shaft diameter of the portion between the plurality of eccentric shaft portions 51 is approximately the same as the diameter of the main shaft portion 52.
  • a cylinder chamber 61 that is a circular space in plan view is formed inside each cylinder 31.
  • Each roller 32 rotates eccentrically in the corresponding cylinder chamber 61. That is, the compression mechanism 30 is formed with a plurality of cylinder chambers 61 that are spaces for compressing the refrigerant.
  • the plurality of cylinder chambers 61 are partitioned in the axial direction of the crankshaft 50 by a partition plate. That is, the partition plate closes the cylinder chamber 61 directly above the partition plate and the cylinder chamber 61 directly below the partition plate.
  • the partition plate may be composed of a single plate through which the crankshaft 50 passes.
  • the partition plate extends from one end in the axial direction of the crankshaft 50 to a portion between the plurality of eccentric shaft portions 51. If it does not pass through the through hole, the partition plate cannot be installed at a desired position.
  • the partition plate must be formed with a through hole having a size that allows the eccentric shaft portion 51 on the side close to one end of the crankshaft 50 in the axial direction to pass therethrough.
  • the partition plate is composed of a plurality of divided plates arranged around the crankshaft 50.
  • the partition plate can be installed at a desired position. That is, it is only necessary that the partition plate be formed with a through-hole having a size capable of passing a portion between the plurality of eccentric shaft portions 51.
  • Each divided plate is provided with a notch corresponding to a part of a through hole formed when all divided plates are combined. If the number of divided plates is two, a donut-shaped partition plate in which circular through-holes are formed by combining semi-circular divided plates each having a small semi-circular cutout in a straight portion. Will be configured.
  • a film including not only molybdenum disulfide 71 but also resin 72 is employed on the crankshaft 50 of the compressor 12. Therefore, as described above, the diameter of the crankshaft 50 can be reduced without impairing the reliability of the compressor 12, and the highly efficient compressor 12 can be obtained.
  • reducing the diameter of the crankshaft 50 means reducing the diameter of the main shaft portion 52 without changing the diameter of the eccentric shaft portion 51, that is, increasing the amount of eccentricity. Even if the diameter of the eccentric shaft portion 51 is increased without changing the diameter of the main shaft portion 52, the amount of eccentricity increases.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Press Drives And Press Lines (AREA)
PCT/JP2016/075276 2016-08-30 2016-08-30 圧縮機および冷凍サイクル装置 WO2018042507A1 (ja)

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KR1020197001759A KR20190020092A (ko) 2016-08-30 2016-08-30 압축기 및 냉동 사이클 장치
CZ201997A CZ309090B6 (cs) 2016-08-30 2016-08-30 Kompresor a zařízení chladicího cyklu
PCT/JP2016/075276 WO2018042507A1 (ja) 2016-08-30 2016-08-30 圧縮機および冷凍サイクル装置
CN201680088680.4A CN109642561B9 (zh) 2016-08-30 2016-08-30 压缩机和制冷循环装置
JP2018536547A JP6878443B2 (ja) 2016-08-30 2016-08-30 ロータリ圧縮機および冷凍サイクル装置

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JPH07259768A (ja) * 1994-03-28 1995-10-09 Hitachi Ltd 回転式圧縮機
JP2005336577A (ja) * 2004-05-28 2005-12-08 Matsushita Electric Ind Co Ltd リン酸マンガン系化成処理液および密閉型圧縮機
JP2009287523A (ja) * 2008-05-30 2009-12-10 Daikin Ind Ltd 圧縮機
JP2013237065A (ja) * 2012-05-15 2013-11-28 Yoshimura Company:Kk クランクシャフトの製造方法およびクランクシャフト
JP2015169252A (ja) * 2014-03-06 2015-09-28 大豊工業株式会社 軸受およびスクロール式流体機械

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JPH06173877A (ja) * 1992-10-09 1994-06-21 Hitachi Ltd 回転機器の軸受とそれを用いたスクロール圧縮機
JPH0783169A (ja) * 1993-09-20 1995-03-28 Hitachi Ltd 密閉形電動圧縮機およびその製造方法
JP4023872B2 (ja) * 1997-06-26 2007-12-19 大豊工業株式会社 斜板式コンプレッサー用斜板
JP4324305B2 (ja) * 2000-03-14 2009-09-02 東芝キヤリア株式会社 冷媒用の密閉型圧縮機または密閉容器の製造方法
CN100378332C (zh) * 2002-12-16 2008-04-02 松下冷机株式会社 冷媒压缩机和使用该冷媒压缩机的冷冻机
JP5199728B2 (ja) 2008-05-16 2013-05-15 三菱電機株式会社 ロータリ圧縮機
EP2933488B1 (en) * 2012-12-11 2020-09-30 Panasonic Intellectual Property Management Co., Ltd. Method for manufacturing a compressor

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JPH05195974A (ja) * 1992-01-16 1993-08-06 Hitachi Ltd 密閉型横形回転式圧縮機
JPH07259768A (ja) * 1994-03-28 1995-10-09 Hitachi Ltd 回転式圧縮機
JP2005336577A (ja) * 2004-05-28 2005-12-08 Matsushita Electric Ind Co Ltd リン酸マンガン系化成処理液および密閉型圧縮機
JP2009287523A (ja) * 2008-05-30 2009-12-10 Daikin Ind Ltd 圧縮機
JP2013237065A (ja) * 2012-05-15 2013-11-28 Yoshimura Company:Kk クランクシャフトの製造方法およびクランクシャフト
JP2015169252A (ja) * 2014-03-06 2015-09-28 大豊工業株式会社 軸受およびスクロール式流体機械

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CZ309090B6 (cs) 2022-01-26
CN109642561A (zh) 2019-04-16
CN109642561B (zh) 2020-11-27
CZ201997A3 (cs) 2019-05-15
KR20190020092A (ko) 2019-02-27
JPWO2018042507A1 (ja) 2018-10-25
CN109642561B9 (zh) 2021-01-01
JP6878443B2 (ja) 2021-05-26

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