EP0941405B1 - Verdichter für flüssige medien - Google Patents

Verdichter für flüssige medien Download PDF

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Publication number
EP0941405B1
EP0941405B1 EP98941784A EP98941784A EP0941405B1 EP 0941405 B1 EP0941405 B1 EP 0941405B1 EP 98941784 A EP98941784 A EP 98941784A EP 98941784 A EP98941784 A EP 98941784A EP 0941405 B1 EP0941405 B1 EP 0941405B1
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EP
European Patent Office
Prior art keywords
blade
plating layer
roller
cylinder
fluid compressor
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
EP98941784A
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English (en)
French (fr)
Other versions
EP0941405A2 (de
Inventor
Takayoshi Fujiwara
Masayuki Okuda
Takashi Honjo
Takuya Hirayama
Tetsuo Fukuda
Shinobu Sato
Yoshinori Sone
Moriaki Shimoda
Shigeo Kida
Satoshi Oyama
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Toshiba Corp
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Toshiba Corp
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Publication date
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Publication of EP0941405A2 publication Critical patent/EP0941405A2/de
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Publication of EP0941405B1 publication Critical patent/EP0941405B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/10Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member
    • F04C18/107Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member with helical teeth
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00Metals
    • F05C2201/90Alloys not otherwise provided for
    • F05C2201/903Aluminium alloy, e.g. AlCuMgPb F34,37
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00Non-metallic inorganic materials
    • F05C2203/08Ceramics; Oxides
    • F05C2203/0804Non-oxide ceramics
    • F05C2203/0813Carbides
    • F05C2203/0817Carbides of silicon
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00Non-metallic inorganic materials
    • F05C2203/08Ceramics; Oxides
    • F05C2203/0804Non-oxide ceramics
    • F05C2203/083Nitrides
    • F05C2203/0843Nitrides of silicon
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00Non-metallic inorganic materials
    • F05C2203/08Ceramics; Oxides
    • F05C2203/0804Non-oxide ceramics
    • F05C2203/0856Sulfides
    • F05C2203/086Sulfides of molybdenum
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/08Thermoplastics
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/10Polyimides, e.g. Aurum
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/12Polyetheretherketones, e.g. PEEK
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00Material properties
    • F05C2251/04Thermal properties
    • F05C2251/042Expansivity
    • F05C2251/046Expansivity dissimilar
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00Other material characteristics; Treatment of material
    • F05C2253/12Coating

Definitions

  • the present invention relates to a fluid compressor employed in a refrigeration cycle apparatus, having a helical blade type compression mechanism, and designed for compressing a refrigerant gas (i.e., a gas to be compressed).
  • a refrigerant gas i.e., a gas to be compressed
  • helical blade type compressors In recent years, fluid compressors that are referred to as helical blade type compressors are proposed.
  • a cylinder is arranged in a sealed case, and a roller serving as a rotating member is eccentrically arranged inside the cylinder. Inside the cylinder, the roller rotates on its own axis or revolves around a given axis.
  • a blade is interposed between the circumferential surface of the roller and the inner circumferential surface of the cylinders, and a plurality of compression chambers are defined by the blade.
  • a refrigerant gas i.e., a gas to be compressed in a refrigeration cycle
  • the refrigerant gas is compressed while gradually moving closer to the other-end region.
  • this type of compressor is very reliable in sealing characteristics in spite of its simple structure. In addition, it enables efficient compression and can be easily assembled by use of easily-manufactured parts.
  • the parts constituting the compression section are formed of iron-based materials. Since the parts of the compression section slide with reference to each other, they are required to have reliable abrasion resistance. Normally, therefore, they are made of cast iron or sintered metal.
  • the parts jointly define a compression chamber and therefore has a function of sealing the gas. If they are formed of the same iron-based material, they have the same coefficient of thermal expansion, and the clearance between them remains unchanged without reference to changes in temperature. Therefore, the use of the same iron-based material enables the clearance to be as narrow as possible and contributes to improvement of the compression performance.
  • the roller is mainly formed of an abrasion-resistant material which has a comparatively large specific gravity, just like cast iron. The use of such a material ensures enhanced reliability (improved abrasion resistant characteristics) even under the boundary lubrication condition.
  • the cast iron roller having a large specific gravity has a large inertia weight when the compressor is driven and is disadvantageous in light of the vibration suppression. It is therefore desirable that the roller be as light in weight as possible, so as to suppress both vibration and noise and therefore to improve the performance.
  • the blade described above is made of a fluoroplastic material, such as tetraethylene fluoride resin (hereinafter referred to as PTFE resin) or perfluoroalkoxy resin (hereinafter referred to as PFA resin), since the use of such a material is advantageous in light of the plasticity, the sealing characteristics, the sliding characteristics, and the environmental resistance (temperature, oil, and refrigerant).
  • PTFE resin tetraethylene fluoride resin
  • PFA resin perfluoroalkoxy resin
  • a composite material is normally used for forming the blade. That is, inorganic fibers (e.g., glass fibers and carbon fibers), a solid lubricant and an organic filler are contained in the material of the blade.
  • clearances a and b defined between the blade D and the wall of the helical groove H, which is formed in the piston P arranged inside the cylinder C, are set to be minimum values when the temperature is highest (during operation of the compressor), in consideration of the compression efficiency and the size variation of the blade D due to the thermal expansion.
  • the clearances are set or determined in this manner, they may be too large when a compression operation has just be started or in the other low-temperature situations. If this occurs, the sealing characteristics between the components are degraded, and an intended compression performance may not be attained.
  • the fluoroplastic blade D is soft and may easily bend due to the differential pressure. As shown in FIG. 14, moreover, the blade D may be rubbed at one side with the edge portion Z of the helical blade H. It should be also noted that the elastic modulus may decrease due to the thermal expansion, and the blade may be permanently deformed under an extremely high state of pressure.
  • EP 0 464 683 A1 relates to a fluid compressor.
  • a fluid compressor which comprises a closed case having an inlet for a fluid at one end thereof and an outlet for a fluid at the other, a cylinder fixed in the case, and a rotary member which orbits in and relatively to the cylinder, wherein the rotary member has a compression unit for compressing a fluid supplied into the closed case from the inlet thereof on the orbital movement of the rotary member, then discharging it to the outside from the outlet of the closed case.
  • US 5 368 457 A discloses a fluid compressor having a moulded helical blade.
  • a fluid compressor is described having a cylinder, a rotary rod, and a helical blade that defines work chambers between the cylinder and the rod.
  • the compressor successively compresses and conveys a fluid from a suction end to a discharge end through the work chambers according the rotation of the rod.
  • the continuous helical blade is formed by pressurizing and injecting synthetic resin material into a mould through two gates, so that a weld line of the blade is located in an intermediate region between a suction pressure region and a discharge pressure region of the blade.
  • US 4 560 332 A discloses a rotary vane-type compressor with vanes of more thermally expansible material than the rotor for maintaining separation of the rotor from the housing side blade during high temperate operation.
  • the rotor, the housing and the side plates are made of the same kind of material as one another.
  • a plurality of vane grooves is provided on the rotor.
  • a set of vanes which is made of a different material than the rotor, more particularly of a material with a coefficient of thermal expansion which is larger than that of the rotor, is received in the vane grooves in such manner that the end faces thereof face against the side plate.
  • the width of the vanes longitudinally of the rotor is slightly less than the thickness of the rotor when the temperature thereof is less than normal, but when the temperature becomes high the vane width becomes slightly greater than the thickness of the rotor because of the difference of the coefficients of thermal expansion.
  • JP 09242681 A discloses a helical blade type compressor used in e. g. a refrigerating cycle apparatus, having two crank units rotated around a crank shaft inside a cylinder to rotate a roller movably that is arranged inside the cylinder and on which the helical groove is provided on the roller peripheral surface.
  • the disclosed compressor has a roller movably arranged inside a cylinder and a helical groove is provided on the peripheral surface of the roller.
  • a compression space is divided by a helical blade that pops in and out of the helical grooves.
  • a pair of crank units is rotated around a crank shaft inside the cylinder to rotate the roller. Therefore, the rotation vibration of the roller is decreased and the compression efficiency is improved. Further, the weight of the roller is reduced since the roller is made of a material with a specific gravity lower than the specific gravity of iron. Further, the rotation inside the cylinder is ensured and a smooth oil supply is enabled.
  • JP 01182592 A describes a vane-type compressor.
  • components such as a cylinder block, both side blocks, a rotor and vanes, etc. with an aluminum material and coating them with Ni electroless composite platings in which polytetraflouroethylene is dispersed.
  • a rotor is inserted into a cylinder block partitioning a plurality of operating spaces.
  • a driving shaft is fixed to the center of the rotor while vanes are inserted in grooves formed in the radial direction thereof.
  • Front and rear both side blocks are provided on both sides of the cylinder block and the rotor and vanes are brought into contact with these blocks.
  • the components such as the cylinder block, the front and the rear both side blocks, the rotor and the vanes are formed with an aluminum material. At least one or more of the components are coated with Ni electroless composite platings in which polytetraflouroethylene is dispersed.
  • JP 02291491 A discloses a compressor. To reduce the number of parts and to improve intensity by inserting a helical blade composed of a fluorine resinous material of a specified composition in a groove of a roller piston pivotally supported in a sleeve-shaped cylinder, for free rising and setting, so as to construct a compressor part.
  • a compressor an electric motor part and a compressor part are stored in a concentric circle in a closed casing.
  • a rod-like roller piston is supported for free rotation, and a helical blade is inserted into a helical groove of the roller piston for free rising and setting.
  • the helical blade is formed out with a fluorine resinous material filled with at least one species out of a heat-resistant polymeric material, a liquid crystal polymer as a reinforcing material or as an abrasion resistant material.
  • the first object of the present invention is to provide a fluid compressor which enables pressure release to be easily done if the liquid flows back in the compressor or under a low-pressure condition as in the initial stage of operation, and which therefore enhances the compression performance under a high-temperature condition during operation.
  • the second object of the present invention is to provide a fluid compressor wherein the roller (a rotating member) is formed of a pre-selected material such that it is light in weight and highly improved in abrasion resistance and such that the vibration and noise are suppressed, and which is improved in compression performance.
  • the third object of the present invention is to provide a fluid compressor which suppresses the effects the thermal expansion and the pressure conditions may have on the helical blade by using a pre-selected material for forming the helical blade, and which is improved in compression performance.
  • the fluid compressor recited in claim 1 comprises a helical blade type compression mechanism made up of a cylinder, a rotating member arranged inside the cylinder, and a helical blade interposed between the rotating member and the cylinder.
  • the feature of the fluid compressor is that the cylinder, the rotating member and the cylinder are formed of materials such that their coefficients of thermal expansion satisfy the relationships: Blade > Rotating Member > Cylinder.
  • the fluid compressor recited therein is based on the fluid compressor described above, and is featured in that the blade is formed of a material selected from the group of a PEEK (polyether ether ketone) resin material, a PES (polyether sulfone) resin material, a PEI (polyether imide) resin material, a PAI (polyamide imide) resin material, a TPI (thermoplastic polyimide) resin material, an LCP (a liquid crystal polymer such as every kind of aromatic polyester) resin material, and a PPS (polyphenylene sulfide) resin material.
  • a PEEK polyether ether ketone
  • PES polyether sulfone
  • PEI polyether imide
  • PAI polyamide imide
  • TPI thermoplastic polyimide
  • LCP liquid crystal polymer such as every kind of aromatic polyester
  • PPS polyphenylene sulfide
  • pressure release can be easily performed in this case where the liquid flows back or under a low-temperature condition as at the time of actuation.
  • the compression performance can be improved under a high-temperature condition during operation.
  • the roller i.e., a rotating member
  • the roller is formed of a pre-selected material, so that it is light in weight and highly improved in abrasion resistance.
  • the third object of the present invention is to provide a fluid compressor which suppresses the effects the thermal expansion and the pressure conditions may have on the helical blade by using a pre-selected material for forming the helical blade, and which is improved in compression performance.
  • the helical blade compressor disclosed herein is used, for example, in the refrigeration cycle of an air conditioner.
  • the fluid to be compressed is a refrigerant gas.
  • a sealed case 1 is made up of: a main case body 1a which is installed, with its axis extending in the vertical direction, and which has two open ends; an upper lid 1b for closing the upper open end of the main case body 1a; and a lower lid 1c for closing the lower open end thereof.
  • a helical blade type compressor mechanism section 3 and an electric motor section 4 are arranged inside the sealed case 1.
  • the compressor mechanism section 3 and the electric motor section 4 are located in the lower and upper regions of the sealed case 1, and the border between them is substantially at the axial center of the case 1.
  • the compression mechanism section 3 comprises a cylinder 5 which is a hollow cylinder and which has a pair of flanges 5a and 5b on the outer circumferential wall at the respective ends.
  • the cylinder 5 is formed of an iron-based material.
  • the flanges 5a and 5b are forcibly inserted into the main case body 1a of the case 1, so as to position the cylinder 5.
  • a main bearing 6 is secured to the upper end face of the cylinder 5 by means of a fixing tool 7, thereby closing the upper open end of the cylinder.
  • An auxiliary bearing 8 is secured to the lower end face of the cylinder 5 by means of a fixing tool 7, thereby closing the lower open end of the cylinder.
  • a crankshaft 9 is inserted between the main and auxiliary bearings 6 and 8 such that it extends along the axes of the bearings 6 and 8.
  • the crankshaft 9 is ratably supported.
  • the crankshaft 9 not only penetrates the cylinder 5 between the main and auxiliary bearings 6 and 8 but also protrudes from the main bearing in the upward direction, as viewed in FIG. 1. That portion of the crankshaft 9 protruding from the main bearing constitutes the rotating shaft 9Z of the electric motor section 4.
  • crank 9a is integrally provided for the crankshaft 9.
  • the axis of the crank 9a is shifted from that of the crankshaft 9 by a predetermined distance.
  • a first counter balancer 9b and a second counter balancer 9c are integrally provided for the crankshaft 9 on the upper and lower sides of the crank 9a.
  • the axes of these counter balancers 9b and 9c are shifted in the opposite direction to that of the crank 9a.
  • a roller 11 (rotating member) formed of an aluminium alloy (i.e., an aluminium-based material) is interposed between the crankshaft 9 and the cylinder 5.
  • the roller 11 is made of a cylindrical body which is open at both ends. The axial length of the roller 11 is equal to that of the cylinder 5.
  • the inner circumferential wall portion of the roller 11 which opposes the crank 9a of the crankshaft 9 defines an eccentric hole section 11a.
  • the eccentric hole section 11a has the same width as the crank 9a and is rotatable or in sliding contact with the outer circumferential wall of the crank 9a.
  • a thin sleeve 12 formed of an iron-based material is forcibly inserted such that it is in contact with the inner circumferential wall of the eccentric hole section 11a.
  • the sleeve 12 is supported such that it is in sliding contact with the crank 9a of the crankshaft 9.
  • the roller 11 is coaxial with the crank 9a, and the axis of the roller 11 is shifted from that of the cylinder 5 by the same distance as the axis of the crank 9a is.
  • the outer circumferential wall of the roller 11 is in rolling contact with part of the inner circumferential wall of the cylinder 5, such that the contact portion extends in the axial direction.
  • the lower portion of the roller 11 is supported by the auxiliary bearing 8, and the lower end face of the roller 11 serves as a thrust face.
  • An Oldham's mechanism 13 for restricting the axial rotation of the roller 11 is interposed between the auxiliary bearing 8 and the lower end of the roller.
  • a helical groove 14 is formed in the outer circumferential wall of the roller 11 such that the pitch of the groove gradually decreases from the end cured to the auxiliary bearing 8 to the end secured to the main bearing 6.
  • a helical blade 15 is arranged along the groove in such a manner that it can be moved into or away from the groove.
  • the blade 15 is formed of a fluoroplastic material, and has an inner diameter greater than the outer diameter of the roller 11. To be more specific, the blade 15 is inserted in the helical groove 14, with its diameter forcibly reduced. Therefore, when the roller 11 is assembled within the cylinder 5, the blade 15 expands and the outer circumferential face of the blade 15 is kept in contact with the inner circumferential surface of the cylinder at all times.
  • the rolling contact position of the roller 11 with reference to the cylinder 5 moves in accordance with the revolution of the roller 11.
  • the blade 15 gradually enters the helical groove 14 when the rolling contact position comes closer to the blade 15.
  • the rolling contact position is on the blade 15, its outer circumferential surface is completely flush with the outer circumferential wall of the roller.
  • the blade 15 protrudes from the helical groove 14 in accordance with the distance by which the blade 15 is away from the rolling contact position.
  • the protrusion length of the blade 15 becomes a maximum when the blade 15 is 180° away from the rolling contact position. Thereafter, the blade 15 moves closer to the rolling contact position again, and the operation described above is repeated.
  • this space is viewed in the axial direction, it can be understood that the region between the roller 11 and the cylinder 5 is divided into a plurality of spaces by the blade 15, since the blade 15 is arranged along the helical groove 14 of the roller 11 and the outer circumference of that blade 15 is in rolling contact with the inner circumferential surface of the cylinder 5.
  • the divided spaces will be referred to as compression chambers 16. Because of the manner in which the helical groove 14 is formed, the volumes of the compression chambers 16 gradually decrease from the end secured to the auxiliary bearing 8 to the end secured to the main bearing 6. In addition, because of the manner in which the pitch of the helical groove 14 is varied, the compression chamber 16 at the lower end serves as an inlet port A, while the compression chamber 16 at the upper end serves as an outlet port B.
  • the accumulator Q communicates with an evaporator (not shown), which constitutes part of a refrigeration cycle.
  • the gas suction port 18 is an opening extending to the inner circumferential surface of the cylinder 5, and is open in opposition to the outer circumferential surface of the roller 11.
  • the gas suction port 18 sucks a refrigerant gas and guides it into the compression chambers 16 defined between the roller 11 and the cylinder 5.
  • the gas suction port 18 is located at the lower end of the cylinder 5, and communicates with one end of the compression chambers 16.
  • the main bearing 6 is provided with a discharge hole 20 extending in parallel to the axial direction, and the highly-pressurized gas, which is compressed in the compression chambers 16, is discharged and guided into the interior of the sealed case 1.
  • a discharge pipe 21 is connected to the upper lid 1b of the sealed case 1, and this discharge pipe 21 communicates with a condenser (not shown), which constitutes part of the refrigeration cycle.
  • the electric motor section 4 comprises: a rotor 30 into which the rotating shaft 9Z of the crankshaft 9 protruding from the main bearing 6 is inserted; and a stator 31 attached to the inner circumferential surface of the main case body 1a, with a predetermined gap maintained between the stator and the outer circumferential surface of the rotor 30.
  • crankshaft 9 In the helical blade type fluid compressor designed as above, power is applied to the electric motor section 4, so as to rotate the crankshaft 9 together with the rotor 30. The torque of the crankshaft 9 is transmitted to the roller 11 through the crankshaft 9a.
  • crankshaft 9a Since the crankshaft 9a is eccentric and the eccentric hole section 11a of the roller 11 rotatably engages therewith, the roller is pushed by the crankshaft 9a.
  • the Oldham's mechanism 13 interposed between the roller 11 and the auxiliary bearing 8 restrains the roller 11 from rotating on its own axis. As a result, the roller revolves around the given axis.
  • a low-pressure refrigerant gas is sucked from the suction pipe 17 through the accumulator Q.
  • the sucked gas is guided from the gas suction port 18 to the compression chamber 16 serving as the inlet port A. Since the roller revolves around the given axis, the rolling contact position at which the roller contacts the inner circumferential surface of the cylinder 5 gradually moves in the circumferential direction.
  • the blade 15 goes into or comes out of the helical groove 14. In other words, the blade 15 is inserted into the groove 14 and then protrudes therefrom, both in the radial direction of the roller.
  • the refrigerant gas guided to the compression chamber 16 serving as an inlet port gradually flows toward the compression chamber serving as an output port in accordance with the revolution of the roller 11.
  • the pitch of the blade 15 gradually decreases from the inlet port A to the outlet port B, and the volumes of the compression chambers 16 partitioned by the blade 15 also decrease in the same direction. Therefore, the refrigerant gas is compressed when it sequentially flows through the compression chambers. When the refrigerant gas reaches the compression chamber serving as output port 10, it is in the pressurized state; its pressure takes a predetermined large value.
  • the high-pressure gas is discharged from the compression chamber 16 of the outlet port B, and is guided into the electric motor section 4, i.e., the upper region of the space of the sealed case 1, by way of the discharge hole 20 of the main bearing 6. Thereafter, the high-pressure gas is led to the condenser by way of the discharge pipe 21 provided for the upper end of the sealed case 1.
  • the cylinder 5 is formed of an iron-based material
  • the roller 11 is formed of an aluminium alloy
  • the helical blade 15 is formed of a fluoroplastic material.
  • the coefficients of thermal expansion of these materials satisfy the following relationships: (blade 15) > (roller 11) > (cylinder 5)
  • the materials of the blade 15, roller 11 and cylinder 5 must be so selected as to satisfy the above relationship.
  • the compression chambers 16 are defined by the cylinder 5, the roller 11 and the blade 15, and the clearances between these structural components have much effect on the compression performance and the gas behavior.
  • FIGS. 2A and 2B show how a clearance is formed.
  • clearance d formed therebetween is large under a low-temperature condition, and is small under a high-temperature condition.
  • the clearances should be as small as possible so as to enhance the compression performance.
  • the pressures in the compression chambers 16 may increase rapidly as a result of the compression of liquid.
  • a certain amount of refrigerant should be made to leak from the compression chambers 16.
  • the coefficient of thermal expansion of the material of the blade 15 is larger than that of the material of the roller 11. Therefore, the clearance between the blade 15 and the helical groove 14 of the roller is small when the temperature is high, and is large when the temperature is low. Accordingly, the operating condition described above is attained.
  • the coefficient of thermal expansion of the material of the roller 11 is larger than that of the material of the cylinder 5. Therefore, the clearance between the roller 11 and the cylinder 5 is small when the temperature is high, and is large when the temperature is low. Accordingly, the operation condition described above is attained. Moreover, since the roller 11 is formed of an aluminium alloy, it is lighter in weight than a conventional roller formed of cast iron. Hence, the vibration and noise during operation can be suppressed.
  • the sliding portion between the roller 11 and the crankshaft 9 has nothing to do with the compression performance of the compression chambers 16. It is therefore ideal to maintain the same clearance between the roller 11 and the crankshaft 9 without reference to the temperature. Since the roller 11 and the crankshaft 9 are such components as are exerted with a large force which is due to the gas load, the clearance between them is of special importance.
  • roller 11 is formed of an aluminium alloy
  • crankshaft 9 is formed of an iron-based material. Since they are formed of completely-different kinds of materials, there is a large difference in the coefficients of thermal expansion between them. Since the clearance varies greatly, it is very likely that galling will occur.
  • the present invention has solved this problem by employing the sleeve 12 formed of the same material as the crankshaft 9 and arranging that sleeve 12 only at the region where the roller and the crankshaft 9 are in sliding contact.
  • the sleeve 12 is formed of the same iron-based material as the crankshaft 9 and is forcibly inserted such that it is in contact with the inner circumferential wall of the Eccentric hole section 11a. Accordingly, the clearance between the roller 11 and the crankshaft 9 is constant without reference to the temperature.
  • the roller 11, formed of an aluminium alloy, may be overlaid with an electroless plating layer formed of Ni, so as to improve the abrasion resistant characteristic.
  • the aluminium alloy of the roller 11 is an Al-Si alloy containing 3% of Si (silicon) by mass or more, the precipitation area ratio of initial crystallized Si is 20% or less, the average particle diameter of initially crystallized Si particles is 30 ⁇ m or less (the average particle diameter being measured as the diameter of a corresponding circle), and the hardness of the compound is HRB60 or more.
  • the electroless plating layer M on the surface of the roller 11 made of the aluminium alloy is formed on a displacement plating layer t. It has a film hardness of Hmv 500 or more and is formed at least inside the helical groove 14 and on that portion which opposes the Oldham's mechanism 13, in such a manner that the thickness of the layer is within the range of 5 to 30 ⁇ m.
  • the film thickness deviation is within ⁇ 20% of the average thickness.
  • the electroless plating layer is either an alloy plating layer or a dispersion (composite) plating layer 1 which is formed on the displacement plating layer t provided on the surface of the roller 11 and which contains 80% of Ni by mass or more.
  • a two-layered electroless plating layer MA made up of a base plating layer ma and an upper plating layer mb may be provided.
  • the base plating layer ma is formed on the displacement plating layer t provided on the surface of the aluminium alloy base material 11 and contains 80% of Ni by mass or more.
  • the electroless plating layer may be formed of a three-alloy material based on (Ni-P), (Ni-B) or (Ni-P-B).
  • the electroless plating layer may be made up of a matrix formed of a three-alloy material of (Ni-P), (Ni-B) or (Ni-P-B), and either a plating layer in which rigid particles of SiN, SiC and BN are dispersed in an amount of 20% by mass or less, or a plating layer in which rigid particles, self-lubrication materials such as C, PTFE, mica, and MoS 2 are dispersed in an amount of 20% by mass or less.
  • the two-layered electroless plating layer MA mentioned above may be modified such that it comprises a base plating layer formed of Ni-P and an upper plating layer which is formed continuously with the base plating layer and which is one of: a layer formed of an alloy material of either Ni-B or Ni-P-B; a layer in which rigid particles of SiN, SiC and BN are dispersed in an amount of 20% by mass or less; and a layer in which self-lubrication materials such as C, PTFE, mica, and MoS 2 are dispersed in an amount of 20% by mass or less.
  • the thickness ratio of the upper layer mb to the lower layer may be within the range of 9/1 to 2/1.
  • FIGS. 4 and 5 are graphs showing how the amount of abrasion in the helical groove 14 is associated with the operating time.
  • the data in the graphs were obtained in a durability test in which rollers of different materials were tested.
  • the characteristics of Embodiment 1, those of Embodiment 2 and those of Control 1 are shown in TABLE 1.
  • PTFE (10% GF) represents a tetraethylene fluoride to which glass fibers are added for reinforcement in an amount of 10%.
  • a Casting corresponds to JIS ACSC
  • Tintered Alloy corresponds to JIS SMF4.
  • Embodiments 1 and 2 wherein the surface of the roller 11 was covered with a plating layer formed in the electroless plating method, the amount of abrasion in the roller 11 and the Oldham's ring 13 did not significantly increase after the initial running abrasion occurred at the start of operation. In the Embodiments, therefore, a stable operation could be performed for a long period of time.
  • the blade 15 is formed of so-called a super engineering plastic material (hereinafter referred to as SEP material), which is a thermoplastic resin material improved in heat resistance, oil resistance and refrigeration, the adverse effects caused by the thermal expansion and the pressure condition can be suppressed to a minimum, thus improving the compression characteristics and the reliability.
  • SEP material super engineering plastic material
  • a blade was actually formed by injection molding by use of a PEEK resin material (Victrex 450G [trade name] commercially available from Sumitomo Chemical Co., Ltd.), and the compression performance was measured by use of the blade.
  • a PEEK resin material Victrex 450G [trade name] commercially available from Sumitomo Chemical Co., Ltd.
  • another blade was formed by use of a PTFE resin material (7-J commercially available from DuPont-Mitsui Fluorochemicals Co., Ltd.) having a density of 2.1 g/cm 3 , and the compression performance was measured under the same condition.
  • Table 2 shows test results of the embodiment, the test results being indicated such that the coefficient of performance measured immediately after the assembly of the compressor of the embodiment and when the temperature was 80°C is expressed as 100%.
  • the amounts of abrasion of the blade, which were measured after 100 hours' operation, are also indicated in the Table.
  • the blade 15 formed of the PEEK resin material according to the embodiment did not show any significant difference between the coefficient of performance measured immediately after the assembly and that measured after 100 hours' operation. An improvement in performance, which was attributable to the fit between the sliding surfaces, was observed after the elapse of time. In addition, the temperatures of the cases did not give rise to a large difference in performance.
  • the coefficient of thermal expansion is large.
  • the clearance may be unnecessarily large when the temperature of the compressor is comparatively low.
  • the compression performance becomes poor.
  • the blade deformation shown in FIG. 14 may easily occur, and the amount of abrasion is considered to have increased.
  • the blade is formed of the PEEK resin material and is made by injection molding in such a manner as to have unequal pitches conforming with that of the helical groove 14, the movement of the blade with reference to the helical groove is not prevented or restricted.
  • the PEEK resin material does not greatly expand by heat. Therefore, even if the initial clearance is determined in consideration of the clearance exhibited at the upper limit of the temperature range in which the compressor is used, the clearance at a low temperature is appropriate nevertheless. Hence, the performance of the compressor does not significantly decrease.
  • the modulus of elasticity is large at high temperature, satisfactory compression performance can be maintained in a wide temperature range.
  • the use of the SEP material for the blade 15 satisfies the environmental conditions under which the compressor can be used (such as the heat resistance, oil resistance and refrigerant resistance).
  • the SEP material has a modulus of elasticity that is 4 to 10 times larger than that of a fluoplastic material and a coefficient of linear expansion that is 1/3 or less of that of the fluoplastic material. Accordingly, the use of either material produces the same advantages.
  • the helical blade type compressor is a type wherein the roller 11A is arranged at an eccentric position inside the cylinder 5A and is rotated together with the cylinder 5A.
  • the hollow region 15x in the blade 15A is formed such that it extends from the inlet port A (i.e., a low-pressure end) to the outlet port B (i.e., a high-pressure end).
  • the hollow region 15x is closed at the outlet port so that it does not communicate with the compression chamber.
  • a PEEK resin (Victrex 450G [trade name] commercially available from Sumitomo Chemical Co., Ltd.) is used as the material of the blade 15A.
  • Victrex 450G trade name
  • a blade having no hollow region was fabricated by use of the same material, and the compression performance was measured under the same conditions.
  • the blade according to the control which was formed of the PEEK resin material and had no hollow region, had a poor compression performance and the amount of blade abrasion was large (25 ⁇ m). Probably, this was because the load exerted on the blade increased due to the liquid compression of the refrigerant.
  • the blade 15A according to the embodiment was also formed of the PEEK resin material but had a hollow region 15x extending from the low-pressure end to the high-pressure end. In spite of the use of the same material, however, the compressor employing that blade exhibited compression performance that was as high as 115%. In addition, the amount of blade abrasion was small (3 ⁇ m). Probably, this was because the hollow region 15x served as a liquid reservoir for temporarily storing a liquefied refrigerant and therefore suppressed the liquid compression.
  • a hollow region 15x is applied to a blade made of a soft fluoroplastic material as measures for coping with the liquid compression (excessive compression)
  • a low-pressure refrigerant enters the hollow region 15x, and a large pressure difference is produced at the high-pressure end of the blade 15A. Due to this pressure difference, the blade 15A is deformed. Since, therefore, the sealing characteristic becomes poor, the compression performance is low under steady-state operating conditions.
  • the blade 15A is formed of a SEP material having a small coefficient of thermal expansion and having a large modulus of elasticity at high temperature, and the hollow region 15x is provided in the blade 15A.
  • the compressor can maintain high compression performance and high reliability under a variety of operation conditions, even under the transient situation where the liquid-state refrigerant is sucked.
  • the hollow region 15x in the blade 15A can be easily formed by gas assist formation.
  • FIGS. 8A-8C show an example of a manner in which a blade is formed by a gas assist formation method (Asahi Chemical Industry Co., Ltd.: AGI method).
  • FIG. 8A shows a two-gate type mold 35, and a gas is injected from a nozzle 36 of an injection molding machine.
  • Reference numeral 37 denotes a core
  • numeral 38 denotes a cylinder
  • numeral 39 denotes a screw
  • numeral 40 indicates gas injection
  • numeral 15A denotes a blade.
  • FIG. 8B shows a formation method which uses a one-gate mold 35A and in which gas is injected from an end of the blade at the fixed mold, as indicated by numeral 40.
  • the other portions of the injection molding machine are similar to those of the machine described above.
  • FIG. 8C shows a formation method which uses a one-gate mold 35B and in which gas is injected from an intermediate inner circumferential portion of the blade at the movable mold, as indicated by numeral 40.
  • the other portions of the injection molding machine are similar to those of the machine described above.
  • a unit is connected to an ordinary type of injection molding machine.
  • a high-pressure nitrogen gas is injected, in the pressurized state, into the interior of the formation nozzles 38 and molds 35-35B such as those shown in FIGS. 8A-8C.
  • a blade 15A was actually manufactured in the gas assist method explained with reference to FIG. 8B, wherein resin for filling is supplied from an end of the blade.
  • a PEI resin material (Ultem 1000 commercially available from GE Plastics Co., Ltd.) was used as the material, and a fluoloplastic material (PFA340-J commercially available from DuPont-Mitsui Fluorochemicals Co., Ltd.) was used as a control.
  • PFA340-J commercially available from DuPont-Mitsui Fluorochemicals Co., Ltd.
  • the blade shrink mark (i.e., the dimensional difference at the center portion of a cross section of the blade) is shown in FIG. 9.
  • the blade shrink mark was hardly observed with respect to the case where the PEI resin material was used, whereas it was observed at the end portion of the blade with respect to the case where PFA resin material was used.
  • FIG. 10A How the blade shrink mark occurs is shown in FIG. 10A. As shown, the surface layer 41 of the blade 51 cools and hardens a predetermined time after the formation of the blade 15. At the time, however, the interior 42 of the blade 51 is still in the molten state.
  • the blade shrink mark is marked in the case of the fluoroplastic material since it has a large mold shrinkage factor. All surfaces of the blade 15 are sealing surfaces.
  • the gate from which resin is injected should not be provided at an intermediate position of the helical structure since the gate provided at such a position adversely affects the smoothness of the surfaces. This being so, the gate must be located at an end of the blade. This structure, however, has problems in that the resin has to flow for a long distance and the pressure with which the resin is injected is not much transmitted to the terminating end. Accordingly, the blade shrink mark occurs markedly at the position which is opposite to the gate.
  • a high-pressure gas is injected into the interior of the blade 15A. Since the blade 15A is cooled and held by the pressurized gas in the interior of the blade, the blade shrink mark is remarkably suppressed. In addition, the pressure applied to the helical structure is uniform at any position, and low-pressure formation is enabled.
  • the hollow region 15n at measurement position No. 9 located at the blade end (hollow region 15n shown in FIG. 11B) is smaller than the hollow region 15m at measurement position No. 1 located at the gas inlet port (hollow region 15m shown in FIG. 11A).
  • the shrink mark at the end portion of the blade 15 is more marked.
  • the shrink mark is very marked at the blade end portion where the hollow region is small.
  • the hollow region 15x does not show a large dimensional difference even when it is measured at different positions, as shown in FIGS. 12A and 12B.
  • the PEI resin material is only an example, and any kind of SEP material is improved in fluidity.
  • the mold shrinkage factor of the SEP materials is less than 1/2 of that of the fluororesin material, and the SEP materials therefore serve to increase the dimensional accuracy when they are selected as the material of the blade 15A fabricated in gas assist formation method.
  • the use of the SEP materials ensures improves sealing characteristics and thus realizes high compression performance.
  • the hollow region 15x can be formed in such a manner as to extend from the low-pressure inlet end to the high-pressure outlet end.
  • the gas assist formation method also increases the cooling rate, as measured in a cross section, and shortens the formation cycle. Hence, the manufacturing yield is enhanced and the productivity is increased.
  • an SEP material can be blended with other kinds of SEP materials as long as the original characteristics are not adversely affected thereby.
  • a composite material is also known, which contains a filler that is added to improve the sliding characteristics. Examples of fillers include inorganic fibers and a solid lubricant.
  • examples of the inorganic fibers include glass fibers, carbon fibers (PAN, pitch), graphite fibers, aluminum fibers, wollastonite, potassiam titanate whisker, carbon whisker, silicon carbide whisker, etc.
  • examples of the solid lubricant include molybdenum disulfide, graphite, carbon, boron nitride, bronze, fluororesin, etc.
  • the tip seal employed in a scroll type compressor and the tip seal employed in a recently-proposed 3D scroll type compressor have a similar function to the blade of the helical blade type compressor described above.
  • these structural members do not move into or out of a helical groove.
  • they are sealing members and made to slide, and thus require a great seal length. They are similar to the helical blade described above in that high dimensional precision is required. Therefore, if they are formed of an SEP material and fabricated in the gas assist method, the same advantages as pointed out above are attained.

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

Claims (14)

  1. Fluidkompressor, umfassend einen Kompressionsmechanismus vom helikalen Klingentyp, der einschließt: einen Zylinder; ein Drehelement, das innerhalb des Zylinders angeordnet ist; und eine helikale Klinge, die zwischen dem Drehelement und dem Zylinder angeordnet ist,
    wobei die Klinge, das Drehelement und der Zylinder aus Materialien gebildet sind, deren thermische Ausdehnungskoeffizienten die Beziehungen erfüllen:
    Klinge > Drehelement > Zylinder
  2. Fluidkompressor nach Anspruch 1, wobei die Klinge aus einem Komposit-Harzmaterial gebildet ist, das Drehelement aus einem Aluminium-basierten Material gebildet ist, und der Zylinder aus einem Eisen-basierten Material gebildet ist.
  3. Fluidkompressor nach Anspruch 1, wobei das Drehelement aus einem Aluminiumlegierungsmaterial gebildet ist.
  4. Fluidkompressor nach Anspruch 3, wobei das Drehelement eine Walze ist, die einen exzentrischen Lochabschnitt aufweist, und eine Manschette, die aus einem Eisen-basierten Material gebildet ist, für eine innere Umfangswand des exzentrischen Lochabschnitts bereit gestellt ist.
  5. Fluidkompressor nach Anspruch 3, wobei das Aluminiumlegierungsmaterial des Drehelements eine Al-Si-Legierung ist, die 3 Massen-% Silikon oder mehr enthält, ein Ausfällungsflächenverhältnis von anfänglich kristallisiertem Silizium 20% oder weniger ist, ein mittlerer Teilchendurchmesser des anfänglich kristallisierten Siliziums 30 µm oder weniger ist, und eine Härte einer Verbindung HRB60 oder mehr ist.
  6. Fluidkompressor nach Anspruch 3, wobei das Drehelement eine Walze ist, dessen Oberfläche mit einer elektrodenlosen Plattierungsschicht beschichtet ist, die hauptsächlich aus Nickel gebildet ist.
  7. Fluidkompressor nach Anspruch 6, wobei die elektrodenlose Plattierungsschicht auf einer Versetzungs-Plattierungsschicht gebildet ist, eine Filmhärte von Hmv 500 oder mehr aufweist, zumindest innerhalb der helikalen Nut und auf jenem Gleitabschnitt angeordnet ist, der einem Mechanismus von Oldham gegenübersteht, und eine Dicke innerhalb eines Bereichs von 5 bis 30 µm aufweist, wobei die elektrodenlose Plattierungsschicht eine Filmdickenabweichung aufweist, die innerhalb ±20% einer mittleren Dicke ist.
  8. Fluidkompressor nach Anspruch 6, wobei die elektrodenlose Plattierungsschicht, die um die Umfangsfläche des Drehelements angeordnet und hauptsächlich aus Nickel gebildet ist, eine eines Einschichtaufbaus oder eines Zweischichtaufbaus ist,
    wobei die elektrodenlose Plattierungsschicht aus einem Legierungsmaterial gebildet ist, das entweder Ni-P, Ni-B oder Ni-P-B ist, und das 80 Massen-% von Ni oder mehr enthält.
  9. Fluidkompressor nach Anspruch 8, wobei eine elektrodenlose Plattierungsschicht auf der Umfangsfläche des Drehelements bereit gestellt ist, die elektrodenlose Plattierungsbeschichtung die elektrodenlose Plattierungsschicht als eine Matrix einsetzt und einschließt:
    entweder eine Plattierungsschicht, in welcher feste Partikel SiN, SiC und BN in einer Menge von 20 Massen-% oder weniger dispergiert sind; oder eine Plattierungsschicht, in welcher selbstschmierende Materialien, wie etwa C, PTFE, Mika und MoS2 in einer Menge von 20 Massen-% oder weniger dispergiert sind.
  10. Fluidkompressor nach Anspruch 8, wobei die elektrodenlose Plattierungsschicht des Zweischichtaufbaus eine Klingenplattierungsschicht, die auf Ni-P gebildet ist, und eine obere Plattierungsschicht umfasst, die fortlaufend mit der Basisplattierungsschicht gebildet ist, und die ist:
    entweder eine Schicht, die aus einem Legierungsmaterial von entweder Ni-B oder NB-P-B gebildet ist; oder eine Schicht, in welcher feste Partikel von SiN, SiC und BN in einer Menge von 20 Massen-% oder weniger dispergiert sind; oder eine Schicht, in welcher selbstschmierende Materialien, wie etwa C, PTFE, Mika und MoS2 in einer Menge von 20 Massen-% oder weniger dispergiert sind.
  11. Fluidkompressor nach Anspruch 8, wobei die elektrodenlose Plattierungsschicht des Zweischichtaufbaus, die um die Umfangsfläche des Drehelements herum bereit gestellt ist, derart gebildet ist, dass ein Dickenverhältnis der oberen Plattierungsschicht zu der Basisplattierungsschicht innerhalb eines Bereichs von 9/1 bis 2/1 liegt.
  12. Fluidkompressor nach Anspruch 1, wobei die Klinge aus einem Material gebildet ist, das aus der Gruppe eines Polyether-Etherketon-Harzmaterials, eines Polyether-Sulfon-Harzmaterials, eines Polyether-Imid-Harzmaterials, eines Polyamid-Imid-Harzmaterials, eines thermoplastischen Polyimid-Harzmaterials, eines Flüssigkristall-Polymer-Harzmaterials und eines Polyphenylen-Sulfid-Harzmaterials gewählt ist.
  13. Fluidkompressor nach Anspruch 12, wobei die Klinge einen hohlen Bereich innen aufweist.
  14. Fluidkompressor nach Anspruch 13, wobei die Klinge, die einen hohlen Bereich innen aufweist, durch Spritzguss gebildet ist, und der Spritzguss in einem gasunterstütztes Erzeugungsverfahren ausgeführt wird,
    wobei ein Hochdruck-Stickstoffgas von einer Düse oder einer Gussform eingeblasen wird.
EP98941784A 1997-09-30 1998-09-09 Verdichter für flüssige medien Expired - Lifetime EP0941405B1 (de)

Applications Claiming Priority (3)

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JP26587697A JP3517098B2 (ja) 1997-09-30 1997-09-30 流体圧縮機
JP26587697 1997-09-30
PCT/JP1998/004046 WO1999017023A2 (en) 1997-09-30 1998-09-09 Fluid compressor

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EP0941405A2 EP0941405A2 (de) 1999-09-15
EP0941405B1 true EP0941405B1 (de) 2004-11-24

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JP4836336B2 (ja) * 2001-02-07 2011-12-14 上野製薬株式会社 ハーメチックモーター用ステーターコア
JP2003003979A (ja) 2001-06-25 2003-01-08 Toshiba Kyaria Kk 流体機械
DE10212940A1 (de) * 2002-03-22 2003-10-02 Leybold Vakuum Gmbh Exzenterpumpe und Verfahren zum Betrieb dieser Pumpe
JP4583731B2 (ja) * 2003-06-24 2010-11-17 トヨタ自動車株式会社 真空ポンプ
WO2009115854A1 (zh) 2008-02-21 2009-09-24 Ulvac Inc 叶片的制造方法
CN103486036B (zh) * 2012-06-12 2016-06-29 广东美芝制冷设备有限公司 旋转式压缩机
US9885347B2 (en) 2013-10-30 2018-02-06 Emerson Climate Technologies, Inc. Components for compressors having electroless coatings on wear surfaces
CN107160117A (zh) * 2017-07-21 2017-09-15 上海宇盛压缩机械有限公司 一种无油活塞及其加工工艺以及活塞压缩机
CN109251532B (zh) * 2018-09-14 2021-01-12 江苏新孚达复合材料有限公司 一种塑料叶轮用复合材料及其制备方法和应用
JP2021055560A (ja) * 2019-09-27 2021-04-08 株式会社ミクニ ベーンポンプ
KR102562912B1 (ko) 2021-02-25 2023-08-04 (주)코리아테크 측면 고정부와 누름부를 포함하는 uv 차단 마스크

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US2527536A (en) 1945-05-15 1950-10-31 Ralph E Engberg Rotary screw pump
JPS59229080A (ja) * 1983-06-08 1984-12-22 Nippon Denso Co Ltd ベ−ン型コンプレツサ
JPH01182592A (ja) * 1988-01-14 1989-07-20 Diesel Kiki Co Ltd ベーン形圧縮機
JP2918951B2 (ja) * 1989-01-31 1999-07-12 株式会社東芝 コンプレッサ
JPH03145592A (ja) * 1989-10-31 1991-06-20 Toshiba Corp コンプレッサー
JP2888936B2 (ja) * 1990-06-28 1999-05-10 株式会社東芝 流体圧縮機
JPH062675A (ja) * 1992-06-18 1994-01-11 Toshiba Corp 流体圧縮機
JP3350336B2 (ja) * 1996-03-05 2002-11-25 株式会社東芝 ヘリカルブレード式圧縮機

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TW430723B (en) 2001-04-21
KR20000069162A (ko) 2000-11-25
WO1999017023A3 (en) 1999-06-17
JP3517098B2 (ja) 2004-04-05
WO1999017023A2 (en) 1999-04-08
BR9806255A (pt) 2000-01-25
EP0941405A2 (de) 1999-09-15
JPH11107953A (ja) 1999-04-20
CN1087401C (zh) 2002-07-10
CN1241247A (zh) 2000-01-12
DE69827763D1 (de) 2004-12-30

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