WO2018154716A1 - Compresseur rotatif et procédé de fabrication de compresseur rotatif - Google Patents

Compresseur rotatif et procédé de fabrication de compresseur rotatif Download PDF

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Publication number
WO2018154716A1
WO2018154716A1 PCT/JP2017/007128 JP2017007128W WO2018154716A1 WO 2018154716 A1 WO2018154716 A1 WO 2018154716A1 JP 2017007128 W JP2017007128 W JP 2017007128W WO 2018154716 A1 WO2018154716 A1 WO 2018154716A1
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WO
WIPO (PCT)
Prior art keywords
vane
mounting groove
rotary compressor
vane mounting
cylinder
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PCT/JP2017/007128
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English (en)
Japanese (ja)
Inventor
政明 檜田
朴木　継雄
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 CN201780086739.0A priority Critical patent/CN110312870A/zh
Priority to JP2019500957A priority patent/JP6896056B2/ja
Priority to PCT/JP2017/007128 priority patent/WO2018154716A1/fr
Publication of WO2018154716A1 publication Critical patent/WO2018154716A1/fr

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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
    • F04C18/30—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

Definitions

  • the present invention relates to a rotary compressor and a method for manufacturing the rotary compressor, and more particularly to surface properties of vanes and vane mounting grooves.
  • a rolling piston fitted to an eccentric shaft portion of a crankshaft is movably disposed in a central space portion in the cylinder, and includes an outer peripheral surface, an inner wall surface of the cylinder, and an outer peripheral surface.
  • a vane extending from the inner surface of the cylinder is in contact.
  • a space formed in the gap between the cylinder and the rolling piston is partitioned into a compression chamber and a suction chamber by a vane.
  • the rolling piston rotates eccentrically by the rotation of the crankshaft, and sequentially repeats the suction process of sucking the refrigerant gas into the space between the cylinder and the rolling piston and the compression process of compressing the sucked refrigerant gas.
  • the refrigerant gas compressed in the gap between the cylinder and the rolling piston passes through a series of steps of an intake process and a compression process, and then is discharged into the sealed container and sent from the sealed container to the refrigeration circuit through the discharge pipe.
  • the vane moves to the bottom dead center following the rolling piston that rotates eccentrically by the pressing load from the back pressure chamber at the base of the vane mounting groove until the phase reaches 180 °.
  • the vane receives a load from the eccentric rotating rolling piston and moves to the top dead center.
  • the vane is guided to the vane mounting groove formed on the inner peripheral surface of the cylinder by the high-speed rotation of the rolling piston, and reciprocates while contacting the inner surface of the vane mounting groove at the side surface of the vane. Therefore, a clearance is provided between the vane and the vane mounting groove, and sliding and reciprocation between the vane and the inside of the vane mounting groove are enabled by interposing lubricating oil. It has also been proposed to suppress the clearance between the vane and the vane mounting groove in order to reduce leakage loss of the compressed refrigerant gas in the cylinder.
  • Patent Document 1 describes that when the sliding surface of the vane is converted into a surface roughness Ra of 0.1 ⁇ m or less and a ten-point average maximum height roughness, it is 0.4 ⁇ m or less.
  • the surface roughness in the rotor rotation direction on the surface of the vane that contacts the rotor is 10 point average maximum height roughness of 1 ⁇ m or less, and the surface roughness in the direction perpendicular to the rotor rotation direction is 10 point average. It has been proposed that the maximum height Rz be 0.6 ⁇ m or less.
  • the side surface of the vane that contacts the inner surface of the vane mounting groove is ground to suppress the clearance.
  • the present invention has been made to solve the above-described problems, and has a surface property that can smoothly reciprocate the vane mounting groove and reduce noise, sliding loss, and sliding resistance due to the reciprocating motion. It aims at providing the manufacturing method of a rotary type compressor provided with vane which has, and a rotary type compressor.
  • a rotary compressor according to the present invention includes: a vane mounting groove formed in a cylinder; and a vane that reciprocates with a side surface in contact with an inner side surface of the vane mounting groove. It has a super-smooth surface texture with a roughness value of 10-point average roughness of less than 0.1 ⁇ m.
  • the side surface of the vane in contact with the inner surface of the vane mounting groove has an ultra-smooth surface shape with a ten-point average roughness of less than 0.1 ⁇ m. Improves. Thereby, the pressure loss from the gap between the vane and the vane mounting groove can be reduced, and a rotary compressor having high performance with reduced sliding resistance can be obtained.
  • FIG. 3 is a side view of the vane of FIG. 2. It is a cross-sectional curve which shows the surface property of the vane which concerns on Embodiment 1 of this invention. It is a cross-sectional curve which shows the surface property of the conventional vane. It is a graph which shows the relationship between the test time and friction coefficient in the vane side part which concerns on Embodiment 1 of this invention, and the conventional vane side part.
  • Embodiment 1 FIG.
  • the rotary type compressor according to the present embodiment is, for example, a rotary type compressor such as a multistage cylinder type or a single cylinder type.
  • the refrigerant is compressed, and the compressed refrigerant is used as a refrigeration circuit. Used for sending in.
  • a multi-stage cylinder type rotary compressor will be described as an example.
  • FIG. 1 is a schematic diagram of a rotary compressor 1 according to the present embodiment.
  • the rotary compressor 1 includes a cylindrical sealed container 2 made of a steel plate, an electric element 12 disposed at an upper portion in the sealed container 2, and a rotation disposed below the electric element 12. And a compression mechanism unit 4.
  • the electric element 12 has a crankshaft 3 and is connected to the rotary compression mechanism portion 4 disposed below the electric element 12 by the crankshaft 3.
  • the electric element 12 serves as a drive source for rotating the rotary compression mechanism unit 4 including the rotary compression element.
  • the rotary compression mechanism 4 is composed of a cylinder 5, an eccentric shaft 8 provided on the crankshaft 3, and a rolling piston 6 fitted to the eccentric shaft 8.
  • the cylinder 5 has a space in the center, and a rolling piston 6 is arranged in the center space.
  • the rolling piston 6 is movably provided in the central space of the cylinder 5, and rotates eccentrically while contacting the inner surface of the cylinder 5 by driving the eccentric shaft portion 8.
  • a vane mounting groove 11 that guides the vane 9 is formed in the inner peripheral surface of the cylinder 5 and is formed from the inner peripheral surface toward the outer peripheral surface.
  • the vane 9 is inserted into the vane mounting groove 11, moves in the vane mounting groove 11 by the guide of the vane mounting groove 11, and maintains a state in line contact with the outer peripheral surface of the rolling piston 6.
  • An upper cover 10 and a lower cover 7 having a function as a bearing for the crankshaft 3 are attached to the upper and lower portions of the cylinder 5, and the axial opening is blocked by the upper cover 10 and the lower cover 7. Yes.
  • the eccentric shaft portion 8 is rotated by the rotation of the crankshaft 3, and accordingly, the rolling piston 6 inside the cylinder 5 rotates eccentrically.
  • FIG. 2 is a schematic view of the end face of the cylinder 5 of the rotary compressor 1 according to the present embodiment.
  • the vane mounting groove 11 formed in the cylinder 5 opens in the axial direction on the inner peripheral surface of the cylinder 5.
  • a vane 9 is inserted into the vane mounting groove 11 via a spring 14 to partition a space formed between the cylinder 5 and the rolling piston 6.
  • the vane 9 is maintained in contact with the rolling piston 6 that rotates eccentrically by the restoring force of the spring 14 that acts in the direction of the opening from the back of the vane mounting groove 11.
  • FIG. 3 is a side view of the vane 9 of FIG.
  • the vane 9 is a rectangular flat plate
  • the vane side surface portion 13 has an ultra-smooth surface property with a surface roughness value of 10-point average roughness of less than 0.1 ⁇ m.
  • the ten-point average roughness is a scale of surface roughness unique to Japan, also abbreviated as Rzjis.
  • Rzjis a scale of surface roughness unique to Japan
  • the value of the surface roughness of the vane side surface portion 13 is desirably as small as possible, and is set to 0.05 ⁇ m, for example.
  • One end 9a of the vane 9 is inserted into the vane mounting groove 11, is in contact with a spring 14 disposed at the back of the vane mounting groove 11, and the other end 9b is eccentrically rotated on the outer surface of the rolling piston 6. Is in line contact.
  • the vane side surface portion 13 is in surface contact with the inner side surface of the vane mounting groove 11.
  • the vane side surface portion 13 slides along the inner side surface of the vane mounting groove 11 by the reciprocating motion of the vane 9 accompanying the eccentric rotation of the rolling piston 6.
  • the vane side surface portion 13 that moves along the vane mounting groove 11 has an ultra-smooth surface property, and a convex portion is excluded. Therefore, even if the inner surface of the vane mounting groove 11 has a convex shape, the convex shape is suppressed from being caught by the vane mounting groove 11. Accordingly, the vane 9 can smoothly reciprocate without being subjected to sliding resistance due to the convex hook when moving in the vane mounting groove 11.
  • the rotary compressor 1 includes a suction process for sucking refrigerant gas in a space formed between a cylinder 5 and a rolling piston 6 partitioned by a vane 9 into a suction chamber and a compression chamber, and the sucked refrigerant gas A compression step of compressing. While repeatedly performing the suction process and the compression process, the refrigerant gas compressed by the suction process and the compression process is discharged into the sealed container 2 and sent to the refrigeration circuit.
  • the refrigerant gas is compressed by reducing the space formed by the cylinder 5, the rolling piston 6, and the vanes 9 with the eccentric rotation of the rolling piston 6. At this time, if the gap between the vane 9 and the vane mounting groove 11 is large, the compressed refrigerant gas leaks. However, by eliminating the convex portion of the vane side surface portion 13, the vane 9 and the vane mounting groove 11 can be brought closer to each other, and the gap is suppressed to be small. As a result, the compressed refrigerant gas is less likely to leak from the gap between the vane 9 and the vane mounting groove 11, and the pressure loss is reduced.
  • FIG. 4 is a cross-sectional curve showing the surface properties of the vane 9 according to the present embodiment.
  • FIG. 5 is a cross-sectional curve showing the surface properties of a conventional vane. 4 and 5, the horizontal axis represents the dimension in the longitudinal direction of the vane 9, and the vertical axis represents the surface property in a cross section orthogonal to the side surface of the vane 9. Further, the reference position S1 representing the surface position is set to 0.00 ⁇ m.
  • the vane side surface portion 13 of the vane 9 according to the present embodiment is processed to be ultra-smooth and the surface roughness value is less than 0.1 ⁇ m in terms of 10-point average roughness.
  • the conventional vane is formed in the surface shape whose surface roughness is 0.8-micrometer or less by 10-point average roughness.
  • the vane side surface portion 13 according to the present embodiment has very small irregularities and protrudes from the reference position S1. It can be observed that the surface is super smooth. On the other hand, on the surface of the conventional vane side surface part, it can be observed that the unevenness is large, the convex part reaches a position away from the reference position S1, and the convex part with a large peak height remains. The convex portion remaining on the vane side surface portion 13 is caught by the convex shape of the inner side surface of the vane mounting groove 11 when the vane 9 is slid, and the sliding resistance is increased. In the conventional vane, when the convex part of the vane side surface part and the convex shape of the vane mounting groove 11 come into contact with each other, the gap becomes large, and the compressed refrigerant gas leaks to cause pressure loss.
  • the vane 9 has an ultra-smooth surface property, the convex portion of the vane side surface portion 13 is eliminated, and it is difficult for the vane 9 to be caught on the convex portion on the inner surface of the vane mounting groove 11, and the sliding resistance is suppressed. Further, since the vane side surface portion 13 and the inner side surface of the vane mounting groove 11 are in close contact with each other, leakage from the gap is prevented and pressure loss is reduced. Therefore, friction between the vane mounting groove 11 and the vane 9 and pressure loss can be suppressed.
  • the vane 9 mounted on the rotary compressor 1 is manufactured through a processing step for processing the vane 9.
  • the processing process includes a grinding process and a polishing process.
  • a member to be the vane 9 is cut out from the sheet metal.
  • a material of the sheet metal for example, SUS440 can be used as stainless steel, or SKH51 can be used as high speed steel.
  • the grinding process which grinds the surface of the side part of the cut-out member is carried out.
  • a polishing process is performed in which the abrasive grains are polished using a polishing liquid in which the liquid is dissolved.
  • diamond is used as the material of the abrasive grains.
  • a polishing process may be performed by applying a polishing liquid in which abrasive grains having a particle size of 3 ⁇ m or the like are dissolved in a liquid on the surface of the side surface portion.
  • a lapping process in which a polishing sheet is pressed and processed.
  • the vane 9 is polished in a processing step and processed so that the surface roughness value is less than 0.1 ⁇ m in terms of 10-point average roughness.
  • the vane 9 mounted on the rotary compressor 1 formed in this way is polished with a polishing liquid using diamond abrasive grains and the like, and the side surface portion of the vane 9 is compared with the vane produced by the conventional manufacturing method. Is super smooth. As a result, sliding resistance generated between the vane 9 and the vane mounting groove 11 is reduced, and noise, sliding loss, and pressure loss are suppressed, and the refrigerant gas is smoothly compressed. It is possible to manufacture a rotary compressor 1 capable of
  • FIG. 6 is a graph showing the relationship between the test time and the friction coefficient in the vane side surface portion 13 according to the present embodiment and the conventional vane side surface portion.
  • the vertical axis indicates the friction coefficient
  • the horizontal axis indicates the test time.
  • the vane 9 according to the present embodiment was subjected to an experiment using a surface roughness value of 0.06 ⁇ m with a 10-point average roughness, and the experimental result is indicated by a mark “ ⁇ ”.
  • a diamond having a surface roughness value of 0.8 ⁇ m with a 10-point average roughness is indicated by diamonds, and a surface roughness value of 0.2 ⁇ m with a 10-point average roughness is used. The case where it was used is indicated by a cross.
  • the conventional vane side surface portion had a surface texture with a surface roughness value of 0.8 ⁇ m in terms of 10-point average roughness.
  • the average value of the sliding friction coefficient with the inner surface of the vane mounting groove 11 is 0.109, and the surface roughness value is 0.099 when the surface roughness is 10-point average roughness of 0.2 ⁇ m. It was.
  • the average value of the sliding friction coefficient with the inner surface of the vane mounting groove 11 was 0.045. From the above experimental results, it was found that by making the vane side surface portion 13 an ultra-smooth surface property, a friction resistance is reduced and a compressor in which the vane 9 slides smoothly can be obtained.
  • the rotary compressor 1 is processed into an ultra-smooth surface property in which the value of the surface roughness of the vane side surface portion 13 is a ten-point average roughness of less than 0.1 ⁇ m, It has a surface texture from which convex portions are excluded. Thereby, the flatness of the surface of the vane side surface portion 13 is improved, and sliding resistance due to friction between the vane 9 and the vane mounting groove 11 and pressure loss due to leakage from the gap can be suppressed.
  • the vane side surface portion 13 is polished with a polishing solution in which abrasive grains are dissolved in a liquid, the surface property is ultra-smooth with an average roughness of 10 points of less than 0.1 ⁇ m.
  • a polishing step of polishing the vane 9 with an abrasive in which abrasive grains are dissolved in a liquid is performed, and the surface roughness is an ultra-smooth surface property having a ten-point average roughness of less than 0.1 ⁇ m It is said.
  • the rotary compressor 1 with reduced sliding resistance, pressure loss, noise, and the like can be manufactured.
  • the use of diamond as the abrasive material makes it possible to realize the vane 9 having an ultra-smooth surface property.
  • FIG. A rotary compressor 1 according to Embodiment 2 will be described.
  • the rotary compressor 1 according to the present embodiment is different from the first embodiment in that a concave shape R is formed on the inner surface of the vane mounting groove 11.
  • differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.
  • FIG. 7 is a cross-sectional curve of the side surface portion of the vane mounting groove 11 of the rotary compressor 1 according to the present embodiment.
  • FIG. 8 is a cross-sectional curve of a side surface portion of a conventional vane mounting groove. 7 and 8, similarly to FIGS. 4 and 5, the horizontal axis indicates the longitudinal dimension of the vane mounting groove 11, and the vertical axis indicates the surface property in a cross section orthogonal to the side surface of the vane mounting groove 11. .
  • a dotted line indicates a sliding position P on which the vane side surface portion 13 slides, and a reference position S2 is set to 0.00 ⁇ m.
  • the vane mounting groove 11 has a concave shape R formed on the inner side surface, and has a surface property of 0.1 ⁇ m with a protruding mountain height Rpk on the inner side surface.
  • the protruding peak height Rpk is one of the parameters for evaluating the lubricity of the surface of the plateau structure, and indicates the average height of the protruding peak portions above the reference height.
  • the inner surface of the vane mounting groove 11 has a surface texture with a protruding peak height Rpk of less than 0.1 ⁇ m, the convex shape protruding from the inner surface is eliminated, and the sliding position P is close to the reference position S2 of the vane mounting groove 11. is doing. Due to the surface properties of the inner side surface of the vane mounting groove 11, the reference position S2 of the vane mounting groove 11 and the sliding position P of the vane side surface portion 13 are in close contact with each other. And the gap between them is suppressed.
  • the concave shape R provided on the inner surface of the vane mounting groove 11 is a groove that is recessed in the in-plane direction from the reference position S2 of the vane mounting groove 11, and is supplied to the vane 9 and the vane mounting groove 11 and the gap. 9 holds lubricating oil for improving the slidability.
  • the maximum depth of the concave shape R is, for example, 0.3 ⁇ m to 1.5 ⁇ m. For this reason, the reference position S2 of the vane mounting groove 11 and the sliding position P of the vane side surface portion 13 processed to be ultra-smooth are in close contact with each other, and the oil stored in the recessed shape R is successively supplied even if the gap is kept small. Thus, an increase in sliding resistance due to running out of oil is prevented.
  • the inner surface is a surface property having a protruding peak height Rpk of 0.3 ⁇ m or less, and the concave shape R is not formed.
  • the convex shape remains on the inner surface of the vane mounting groove in FIG. 8, and the gap between the reference position S2 of the vane mounting groove and the sliding position P becomes larger. ing.
  • the vane mounting groove 11 having an ultra-smooth surface property is inserted into the vane mounting groove 11 having an ultra-smooth surface property that eliminates the convex shape of the inner side surface.
  • the gap between the reference position S2 and the sliding position P can be further suppressed. Accordingly, the gap is suppressed by being in close contact with the ultra-smooth vane side surface portion 13, and the compressed refrigerant gas is prevented from leaking and causing pressure loss. Thereby, an increase in sliding resistance due to running out of oil is reduced, and pressure loss due to leakage of the refrigerant gas is prevented.
  • the vane mounting groove 11 is, for example, a member having a surface property of 3 ⁇ m or less at the protruding mountain height Rpk as a member constituting the inner surface of the vane mounting groove 11, and has a surface property of 0.1 ⁇ m at the protruding mountain height Rpk. What is necessary is just to grind and produce so that it may become.
  • a polishing method for example, it can be produced by plastic working by pressing a cemented carbide round bar having higher hardness than the vane mounting groove against the vane mounting groove and plastically deforming and crushing the convex shape.
  • the vane mounting groove 11 having a concave shape R having a protruding peak height Rpk of 0.1 ⁇ m and a maximum depth of 0.3 ⁇ m to 1.5 ⁇ m is formed.
  • the polishing method is not limited to the above, and it is sufficient that the convex shape can be eliminated.
  • the concave shape R is formed in the vane mounting groove 11
  • the concave shape R may be formed in the vane side surface portion 13, and the vane mounting groove 11 and the vane It may be formed on both sides 13.
  • the configuration of the vane side surface portion 13 and the configuration of the vane mounting groove 11 described in the present embodiment are reversed to form the concave shape R in the vane side surface portion 13 and the protruding mountain height Rpk is 0.1 ⁇ m. It is good also as surface property and it is good also considering the vane attachment groove
  • FIG. 9 is a graph showing the relationship between the operation time and the input value of the rotary compressor 1 provided with the vane attachment groove 11 according to the present embodiment and the conventional rotary compressor provided with the vane attachment groove.
  • the vertical axis indicates the primary input ratio
  • the horizontal axis indicates the operation time.
  • the thick line indicates the experimental result of the rotary compressor 1 of the present embodiment
  • the thin line indicates the experimental result of the conventional rotary compressor.
  • the primary input ratio decreases until the operation time exceeds 160 minutes, and thereafter, the constant 100 It showed a tendency to change around%.
  • the primary input ratio of the rotary compressor provided with the vane mounting groove of the conventional specification tended to continue to decrease even after the operation time exceeded 260 minutes and thereafter remained constant. That is, the slidability of the vane 9 was deteriorated in the vane mounting groove of the conventional specification.
  • the concave shape R is formed on the inner surface of the vane mounting groove 11, and the lubricating oil held in the concave shape R is the vane 9 and the vane. Supplied to the gap with the mounting groove. Thereby, running out of oil is prevented and the vane 9 can smoothly slide in the vane mounting groove 11.
  • the concave shape R is formed on the side surface of the vane, the lubricating oil is held in the concave shape R, preventing oil shortage, and the vane 9 can smoothly slide in the vane mounting groove 11.
  • the inner surface of the vane mounting groove 11 has a surface roughness with a surface roughness value of less than 0.1 ⁇ m in terms of the protruding ridge height, the convex shape of the side surface of the vane mounting groove 11 is eliminated, and the vane 9 And the vane mounting groove 11 can suppress frictional resistance and pressure loss.
  • a plastic working step of plastically deforming and crushing the convex shape is applied to the vane mounting groove 11, and the surface property of the inner side surface of the vane mounting groove 11 is 0.1 ⁇ m at the protruding peak height. Less than.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un compresseur rotatif pourvu d'un organe obturateur qui effectue un mouvement alternatif sans à-coups, et un procédé de fabrication du compresseur rotatif. Le compresseur rotatif est pourvu d'une rainure de montage d'organe obturateur formée sur un cylindre et d'un organe obturateur qui effectue un mouvement alternatif, sa surface latérale étant en contact avec la surface latérale interne de la rainure de montage d'organe obturateur. La section de surface latérale de l'organe obturateur est pourvue d'une propriété de surface extrêmement lisse indiquée par une valeur de rugosité de surface inférieure à 0,1 µm en termes de rugosité moyenne de dix points.
PCT/JP2017/007128 2017-02-24 2017-02-24 Compresseur rotatif et procédé de fabrication de compresseur rotatif WO2018154716A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201780086739.0A CN110312870A (zh) 2017-02-24 2017-02-24 回转型压缩机以及回转型压缩机的制造方法
JP2019500957A JP6896056B2 (ja) 2017-02-24 2017-02-24 ロータリー型圧縮機、及び、ロータリー型圧縮機の製造方法
PCT/JP2017/007128 WO2018154716A1 (fr) 2017-02-24 2017-02-24 Compresseur rotatif et procédé de fabrication de compresseur rotatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/007128 WO2018154716A1 (fr) 2017-02-24 2017-02-24 Compresseur rotatif et procédé de fabrication de compresseur rotatif

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Cited By (1)

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Publication number Priority date Publication date Assignee Title
WO2021193107A1 (fr) * 2020-03-27 2021-09-30 日立Astemo株式会社 Dispositif de cylindre et procédé de fabrication de tige de piston

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JPS6146486A (ja) * 1984-08-13 1986-03-06 Atsugi Motor Parts Co Ltd ベ−ン型回転圧縮機
US4895501A (en) * 1988-12-22 1990-01-23 General Electric Company Rotary compressor with vane positioned to reduce noise
JPH06299981A (ja) * 1993-04-14 1994-10-25 Matsushita Refrig Co Ltd 横型回転式圧縮機
JPH08261185A (ja) * 1995-03-23 1996-10-08 Matsushita Electric Ind Co Ltd 密閉型回転式圧縮機
JP2000249088A (ja) * 1999-02-26 2000-09-12 Nippon Piston Ring Co Ltd 回転圧縮機及び同用ベーン

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JP5030439B2 (ja) * 2006-02-28 2012-09-19 株式会社リケン 摺動部材
ES2660014T3 (es) * 2010-12-22 2018-03-20 Daikin Industries, Ltd. Compresor
CZ307900B6 (cs) * 2015-03-02 2019-08-07 Mitsubishi Electric Corporation Rotační kompresor a způsob jeho výroby

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Publication number Priority date Publication date Assignee Title
JPS6146486A (ja) * 1984-08-13 1986-03-06 Atsugi Motor Parts Co Ltd ベ−ン型回転圧縮機
US4895501A (en) * 1988-12-22 1990-01-23 General Electric Company Rotary compressor with vane positioned to reduce noise
JPH06299981A (ja) * 1993-04-14 1994-10-25 Matsushita Refrig Co Ltd 横型回転式圧縮機
JPH08261185A (ja) * 1995-03-23 1996-10-08 Matsushita Electric Ind Co Ltd 密閉型回転式圧縮機
JP2000249088A (ja) * 1999-02-26 2000-09-12 Nippon Piston Ring Co Ltd 回転圧縮機及び同用ベーン

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021193107A1 (fr) * 2020-03-27 2021-09-30 日立Astemo株式会社 Dispositif de cylindre et procédé de fabrication de tige de piston
JPWO2021193107A1 (fr) * 2020-03-27 2021-09-30
JP7407908B2 (ja) 2020-03-27 2024-01-04 日立Astemo株式会社 自動車用サスペンション装置のピストンロッドの製造方法

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