EP0933532A2 - Machine rotative à fluide du type à pallettes - Google Patents

Machine rotative à fluide du type à pallettes Download PDF

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Publication number
EP0933532A2
EP0933532A2 EP99101550A EP99101550A EP0933532A2 EP 0933532 A2 EP0933532 A2 EP 0933532A2 EP 99101550 A EP99101550 A EP 99101550A EP 99101550 A EP99101550 A EP 99101550A EP 0933532 A2 EP0933532 A2 EP 0933532A2
Authority
EP
European Patent Office
Prior art keywords
rotor
vane
casing
inner periphery
edge
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.)
Withdrawn
Application number
EP99101550A
Other languages
German (de)
English (en)
Other versions
EP0933532A3 (fr
Inventor
Mitsuo c/o Asuka Japan Co. Ltd Nakamura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Asuka Japan Co Ltd
Original Assignee
Asuka Japan Co Ltd
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
Priority claimed from JP5877398A external-priority patent/JPH11218086A/ja
Priority claimed from JP10225130A external-priority patent/JP2000018183A/ja
Priority claimed from JP10263889A external-priority patent/JP2000064974A/ja
Priority claimed from JP10295990A external-priority patent/JP2000087887A/ja
Priority claimed from JP10340959A external-priority patent/JP2000130374A/ja
Application filed by Asuka Japan Co Ltd filed Critical Asuka Japan Co Ltd
Publication of EP0933532A2 publication Critical patent/EP0933532A2/fr
Publication of EP0933532A3 publication Critical patent/EP0933532A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • F04C18/344—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 inner member
    • F04C18/3441—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 inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C2250/00—Geometry
    • F04C2250/30—Geometry of the stator
    • F04C2250/301—Geometry of the stator compression chamber profile defined by a mathematical expression or by parameters

Definitions

  • the present invention generally relates to a vane-type fluid machine such as a vacuum pump or a blower and more particularly, to a vane-type fluid machine which is capable of mechanically moving a vane and of producing a high compression ratio.
  • vanes are freely inserted in vane grooves formed on a rotor and slidingly move along a casing inner periphery due to centrifugal force by rotation of the rotor so as to suck in fluid between vanes and to discharge the fluid after compression thereof.
  • the vane needs early replacement because of wear caused by strong friction with the casing inner periphery.
  • a high compression ratio can not be obtained with the above conventional vane-type fluid machine in a compression process.
  • the casing inner periphery is a circle with a diameter 2Q, if a vane edge-to-edge span 2L is constant, a clearance 2S arises between a vane edge and the casing inner periphery along whole the inner periphery, and practical mechanical performance can not be obtained.
  • the fluid machine with a oil lubricating vane would have a structure of circulating the lubricating oil, which makes the fluid machine complex, thereby increasing a trouble, and needs a much manufacturing cost. Further, this structure needs exchange of a lubricating oil every one or two years, which needs much maintenance cost.
  • the free vane structure has various of problems, the structure with mechanically moving the vane has a great effect of preventing the wear of the vane.
  • this structure is not also capable of solving a big problem of producing a high compression ratio with only one rotation of the rotor.
  • a vane-type fluid machine with oil lubricating eight free vanes has been used or serial connection of a plurality of vane-type fluid machines has been applied.
  • a discharge pressure of 2kgf/ C m 2 or a suction vacuum of 50 Toll has been the maximum, and especially getting a high compression ratio has been the most difficult thing to be solved for an oil free vane-type fluid machine.
  • an object of the present invention is to provide a vane-type fluid machine of an oil free type, wherein even a self-lubricative vane is not worn and, further, a high compression ratio can be got with one rotation of a the rotor, and to provide a casing applied to the vane-type fluid machine.
  • a vane-type fluid machine includes: a casing with a sidecover, the casing having a contacting-surface circular arc on an inner periphery thereof; a rotor eccentrically fitted in the casing with a predetermined eccentricity, the rotor having a diameter to form a sealing surface with respect to the contacting-surface circular arc formed on the inner periphery of the casing for keeping seal between a suction side and a discharge side and the rotor having a rotor discharging groove on an outer surface thereof; a vane slidably inserted in a rotor groove formed on the rotor so that an edge of the vane proceeds along the inner periphery of the casing on rotation of the rotor; and a drive shaft inserted in a boss portion of the rotor concentrically with the rotor for rotating the rotor, wherein, with rotation of the rotor, fluid is sucked into
  • the sealing surface between the rotor and the contacting-surface circular arc on the inner periphery of the casing makes sufficient seal between the suction side and the discharge side.
  • the discharge hole on the contacting-surface circular arc and the rotor discharging groove on the rotor enables to produce any high compression ratio surely and easily.
  • the vane since the vane is not slidably but mechanically set on the rotor, a clearance between the vane edge and the casing inner periphery can be freely set to almost zero or very small one at any rotation angle of the rotor by adjusting length of the vane according to material of the vane or temperature of the fluid. Consequently, even if the vane is made a self-lubricating material such as carbon, wear of the vane caused by centrifugal force does not occur, thereby achieving long life of the vane and simultaneously producing clean compressed fluid not containing wear powder.
  • the vane-type fluid machine with the first aspect further includes: an orbiting shaft fitting rotor accommodated in the sidecover on the undriven-side rotatably around an axis positioned in the middle of axes of the casing and of the rotor; and a partition provided on a bottom portion of the rotor groove, wherein the vane slidably inserted in the rotor groove formed on the rotor is made up of a pair of vane members connected by a connecting member keeping a fixed edge-to-edge span of the pair of vane members and having an orbiting shaft outwardly in the center of the edge-to-edge span of vane members, the orbiting shaft being rotatably fitted into the orbiting shaft fitting rotor with half of the predetermined eccentricity and orbiting the axis of the orbiting shaft fitting rotor.
  • a vane-type fluid machine includes: a casing with an undriven-side sidecover; a rotor eccentrically fitted in the casing with a predetermined eccentricity; a vane slidably inserted in a rotor groove formed on the rotor so that an edge of the vane proceeds along an inner periphery of the casing on rotation of the rotor; a drive shaft inserted in a boss portion of the rotor concentrically with the rotor for rotating the rotor; and a pin-crank shaft having an eccentricity of half of the predetermined eccentricity and set between an undriven-side end of the vane and the undriven-side sidecover, wherein one end of the pin-crank shaft is rotatably fitted into the vane in its edge-to-edge span center and the other end is fitted into the undriven-side sidecover also rotatably around an axis positioned in the middle of axes of the casing and of the rotor so that an axi
  • a clearance between the vane edge and the casing inner periphery can be freely set to almost zero or very small one at any rotation angle of the rotor by adjusting length of the vane according to material of the vane or temperature of the fluid. Consequently, even if the vane is made a self-lubricating material such as carbon, wear of the vane caused by centrifugal force does not occur, thereby achieving long life of the vane and simultaneously producing clean compressed fluid not containing wear powder.
  • a vane-type fluid machine includes: a casing with sidecovers; a rotor eccentrically fitted in the casing with a predetermined eccentricity; a vane slidably inserted in a rotor groove formed on the rotor so that an edge of the vane proceeds along an inner periphery of the casing on rotation of the rotor; a drive shaft inserted in a boss portion of the rotor concentrically with the rotor for rotating the rotor; and an undriven-side rotor flange concentrically assembled with the rotor on an undriven-side thereof so that both sides of the rotor are rotatably supported by the respective sidecovers through bearings, wherein, with rotation of the rotor, fluid is sucked into a space formed in the casing with an inner surface thereof, the outer surface of the rotor, and the vane, and simultaneously fluid in another space formed in the casing is compressed, while being discharged from a discharge hole.
  • the vane since the vane is not slidably but mechanically set on the rotor, a clearance between the vane edge and the casing inner periphery can be freely set to almost zero or very small one at any rotation angle of the rotor by adjusting length of the vane according to material of the vane or temperature of the fluid. Consequently, even if the vane is made a self-lubricating material such as carbon, wear of the vane caused by centrifugal force does not occur, thereby achieving long life of the vane and simultaneously producing clean compressed fluid not containing wear powder. Further, since the rotor can have rotor flanges on the respective sides thereof and the rotor flanges can be supported by the respective sidecovers, a big capacity vane-type fluid machine with a long casing can be obtained.
  • a vane-type fluid machine includes: a casing with an undriven-side sidecover; a rotor eccentrically fitted in the casing with a predetermined eccentricity; a vane slidably inserted in a rotor groove formed on the rotor so that an edge of the vane proceeds along an inner periphery of the casing on rotation of the rotor; a drive shaft inserted in a boss portion of the rotor concentrically with the rotor for rotating the rotor; an orbiting shaft fitting rotor accommodated in the undriven-side sidecover rotatably around an axis positioned in the middle of axes of the casing and of the rotor; and an orbiting shaft set between an undriven-side end of the vane and the orbiting shaft fitting rotor, wherein one end of the orbiting shaft is fixedly inserted into the vane in its edge-to-edge span center and the other end is fitted into the orbiting shaft fitting rotor with half of the
  • a clearance between the vane edge and the casing inner periphery can be freely set to almost zero or very small one at any rotation angle of the rotor by adjusting length of the vane according to material of the vane or temperature of the fluid. Consequently, even if the vane is made a self-lubricating material such as carbon, wear of the vane caused by centrifugal force does not occur, thereby achieving long life of the vane and simultaneously producing clean compressed fluid not containing wear powder.
  • the vane can be thin, thereby increasing a capacity of the casing and reducing a material cost, and this fixed insertion of the orbiting shaft allows easier machining of its hole on the vane, not requiring a severe machining tolerance. Still further, since the orbiting shaft is a straight one, a machining cost can be low.
  • the above-described vane-type fluid machine includes: a grease reservoir and a grease hole connecting the grease reservoir with the vane are formed inside the rotor so as to lubricate the vane through the grease hole.
  • the grease reservoir can have a big capacity, thereby not requiring supply of the grease for a long period, and a structure of pressuring the grease with use of centrifugal force can maintain reliable grease supply, which enables a vane-type fluid machine not to have a oil supply system and not to raise the wear powder.
  • a clearance between the vane edge and the casing inner periphery can be freely set to almost zero or very small one at any rotation angle of the rotor by adjusting length of the vane according to material of the vane or temperature of the fluid. Consequently, wear of the vane caused by centrifugal force does not occur, thereby achieving long life of the vane, which can reduce a maintenance cost, and simultaneously producing clean compressed fluid not containing wear powder.
  • FIGS.1-3 show a first embodiment of the vane-type fluid machine in accordance with the present invention.
  • FIG. 1 is a longitudinal sectional view showing the first embodiment of a vane-type fluid machine in accordance with the present invention
  • FIG. 2 is a cross-sectional view of the vane-type fluid machine of FIG. 1.
  • a rotor-boss 9 with a bearing 14 is provided in a casing 1 in connection with a rotor 4 which has an eccentricity m with respect to the casing 1 through a drive-side sidecover 2.
  • 6A is a connecting member having a pair of connecting member shafts 6B specifying a vane edge-to-edge span of a pair of vanes 7 to 2L(FIG.3) by inserting the connecting member shafts 6B in insertion holes of the respective vanes 7, and an orbiting shaft 6 is provided on the connecting member 6A in the center thereof.
  • 6C is a rotation preventing key for the connecting member shaft 6B.
  • the orbiting shaft 6 having a bearing 10, with the Y-axis orbits around the A-line, i.e. the center of an orbiting shaft fitting rotor 10, with an eccentricity m/2.
  • the orbiting shaft fitting rotor 10 rotates with the A-line through a bearing 11 accommodated in an undriven-side sidecover 3.
  • the vane 7 is slidably inserted in a rotor groove 4B.
  • 4A is a rotor groove bottom partition.
  • FIGS.3A to 3D are schematic views showing operation of the vane-type fluid machine of FIG. 1.
  • the center of the orbiting shaft 6, i.e. the vane edge-to-edge span center G is on an intersection point of X-axis and the Y1-axis.
  • An orbital circle h of the vane edge-to-edge span center G has the center of the intersection point T of the A-line and the X-axis and a radius m/2.
  • the orbiting shaft fitting rotor 10 rotates around the intersection point T with twice a rotation speed of the rotor 4.
  • a space F on the left of the vane 7 is in a state of completion of suction, and a space E on the right side of a lower vane 7 is in a state of discharging a highly compressed fluid.
  • a contacting-surface circular arc between a casing inner periphery and the rotor 4 has a radius r and a diameter U in order to make a contacting surface distance W (FIG.3).
  • a rotor discharging groove 5 is formed on the compressing side of the vane 7, wherein a long rotor discharging groove 5 produces a low compression ratio and a short rotor discharging groove 5 produces a high compression ratio, and the diameter U and the contacting surface distance W are decided also taking account of a compression ratio.
  • Reference character K indicates a suction hole and D indicates a discharge hole.
  • FIG.3B shows a state that both the rotor 4 and the vane 7 have rotated by 45° in a counterclockwise sense, the orbiting shaft fitting rotor 10 has rotated by 90° in the same direction, and the vane edge-to-edge span center G of the vanes 7 has arrived at an intersection point between the A-line and the X-axis on the orbital circle h, wherein a space E is in a compression process.
  • the lower vane 7 has just discharged the compressed fluid from the discharge hole D.
  • both the rotor 4 and the vane 7 have rotated by 90° in a counterclockwise sense, the vane edge-to-edge span center G of the vanes 7 has arrived at an intersection point between the X-axis and the Y-axis on the orbital circle h, and the vane edges are on the X-axis.
  • the discharge hole D is completely closed by the rotor 4, and fluid in a space E is compressed to a compression ratio of approximately 1.9.
  • the orbiting shaft fitting rotor 10 has rotated by 180° .
  • FIG.3D shows a state that the vane 7 has rotated by 150° in a counterclockwise sense, and the vane edge-to-edge span center G of the vanes 7 has arrived at an intersection point between the vane centerline C and the orbital circle h.
  • fluid in the space E is compressed to a compression ratio of approximately 6, and the rotor discharging groove 5 is about to open to the discharge hole D.
  • the space F is just before completion of suction.
  • both of the vane edges move along the casing inner periphery R, the vane edge-to-edge span center G orbits on the orbital circle h, and the space F gradually decreases, thereby raising compression ratio of the fluid therein.
  • the vanes 7 are slidably inserted in respective rotor grooves 4B, and a rotor groove bottom partition 4A is formed between the rotor grooves 4B so as to prevent leakage of fluid.
  • the orbiting shaft fitting rotor 10 rotates with twice a rotation speed of the rotor 4 simultaneously with keeping the eccentricity m/2 of the orbiting shaft 6, and clearance, i.e. little clearance or very small one, between the vane edge and the casing inner periphery R does not change at any rotation angle.
  • a grease reservoir (not shown) along with a grease hole (not shown) may be provided inside the rotor 4 for lubricating the vane 7 in case of grease lubrication.
  • the above-mentioned first embodiment of the vane-type fluid machine consisting of the casing 1, the rotor 4, the rotor discharging groove 5, and the contacting-surface circular arc and the discharge hole D and capable of producing a high compression ratio is applicable to a conventional vane-type fluid machine wherein a vane slides freely in a rotor groove by centrifugal force.
  • FIGS.4 and 5 show a second embodiment of the vane-type fluid machine in accordance with the present invention.
  • FIG.4 is a cross-sectional view showing a second embodiment of a vane-type fluid machine with a single vane in accordance with the present invention.
  • FIG.5 is a longitudinal sectional view showing the vane-type fluid machine having the single vane structure of FIG. 4 and additionally having a drive-side pin-crank shaft structure and a bearing structure of a undriven-side rotor flange.
  • a rotor 4 concentrically having a drive-side rotor flange 4a is eccentrically assembled in a casing 1 through a drive-side sidecover 2 and rotatably supported by a bearing 16 accommodated in a boss portion of the drive-side sidecover 2.
  • a main shaft 6d, having the B-axis with an eccentricity 2/m from the rotor center Y1-axis, of a drive-side pin-crank shaft is supported by a pin-crank rotor 8 with a bearing 11.
  • the pin-crank rotor 8 is accommodated in a drive-side end portion of the rotor 4 and is rotatable around the Y1-axis.
  • An auxiliary shaft 6a of the drive-side pin-crank shaft is inserted in a vane drive-side edge-to-edge span center along with a bearing 13 and an oil-seal 14 for a vane-inside grease reservoir 5a.
  • the vane 7 is slidably inserted in a rotor groove 4B.
  • An undriven-side rotor flange 4d is concentrically assembled with the rotor 4 and rotatably supported by an undriven-side sidecover 3 through a bearing 20b.
  • a main shaft 19 of an undriven-side pin-crank shaft is rotatably supported by a housing 15 through a bearing 20a on the A-axis which is positioned in the middle between the Y-axis of the casing and the Y1-axis of the rotor, that is, the A-axis has the eccentricity of m/2 from the Y1-axis.
  • An auxiliary shaft 19a of the undriven-side pin-crank shaft is inserted in the vane 7 through a bearing 21 in the vane edge-to-edge span center on the undriven-side.
  • a reference character 4f indicates a grease reservoir which, along with a grease hole (not shown), is utilized to lubricate the vane 7 in case of grease lubrication.
  • FIG.6 shows a modified embodiment of a second embodiment of the vane-type fluid machine in accordance with the present invention.
  • FIG.6 is a longitudinal sectional view showing the modified embodiment having a straight orbiting shaft, wherein a vane is in a horizontal state.
  • one end of a rotor 4 eccentrically accommodated in a casing 1 is rotatably inserted along with a bearing 14 in a boss portion of a drive-side sidecover 2 assembled to the casing 1.
  • One side of an orbiting shaft 6 is fixedly inserted axially in a vane 7 in the vane edge-to-edge span center.
  • a reference character 6a indicates a rotation preventing key of an orbiting shaft 6a against the vane 7.
  • a bearing portion 6b of the orbiting shaft 6 is rotatably supported by an orbiting shaft fitting rotor 10 through a bearing 8 on the Y1-axis having the eccentricity of m/2 from the A-axis being the center of the orbiting shaft fitting rotor 10.
  • the orbiting shaft fitting rotor 10 with a bearing 11 is accommodated in an undriven-side sidecover 3 rotatably on the A-axis having the eccentricity of m/2 from the Y-axis being the casing center.
  • the vane 7 is slidably inserted in a rotor groove 4B.
  • the drive shaft 5 is inserted in a boss portion of the rotor 4.
  • a dimension L i.e. 2L on both sides of point G, is fundamental for deciding the casing inner periphery.
  • the orbital circle h is formed with the radius m/2 based on the eccentricity m of the rotor with respect to the casing.
  • a length G-Z is calculated as (m sin ⁇ +L) and also a length G-V is calculated as (L-m sin ⁇ ).
  • the casing inner periphery R can be obtained by getting the points Z and V according to the angle ⁇ as a variable.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP99101550A 1998-02-02 1999-02-01 Machine rotative à fluide du type à pallettes Withdrawn EP0933532A3 (fr)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
JP5877398 1998-02-02
JP5877398A JPH11218086A (ja) 1998-02-02 1998-02-02 ベーン形流体機械
JP10225130A JP2000018183A (ja) 1998-07-02 1998-07-02 ベーン式流体機械
JP22513098 1998-07-02
JP26388998 1998-08-12
JP10263889A JP2000064974A (ja) 1998-08-12 1998-08-12 ベーン式流体機械
JP29599098 1998-09-09
JP10295990A JP2000087887A (ja) 1998-09-09 1998-09-09 ベーン式流体機械
JP10340959A JP2000130374A (ja) 1998-10-23 1998-10-23 ベーン式流体機械
JP34095998 1998-10-23

Publications (2)

Publication Number Publication Date
EP0933532A2 true EP0933532A2 (fr) 1999-08-04
EP0933532A3 EP0933532A3 (fr) 2000-09-20

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP99101550A Withdrawn EP0933532A3 (fr) 1998-02-02 1999-02-01 Machine rotative à fluide du type à pallettes

Country Status (2)

Country Link
EP (1) EP0933532A3 (fr)
KR (1) KR19990072320A (fr)

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DE102004034920B3 (de) * 2004-07-09 2005-12-01 Joma-Hydromechanic Gmbh Einflügelvakuumpumpe
DE102004034922A1 (de) * 2004-07-09 2006-02-02 Joma-Hydromechanic Gmbh Einflügelvakuumpumpe
DE102005015721B3 (de) * 2005-03-31 2006-12-21 Joma-Hydromechanic Gmbh Vakuumpumpe
CN100396928C (zh) * 2004-03-23 2008-06-25 兄弟工业株式会社 泵和安装该泵的喷墨打印机
US7393090B2 (en) * 2003-10-31 2008-07-01 Brother Kogyo Kabushiki Kaisha Inkjet printer and method of controlling the inkjet printer
WO2009109282A1 (fr) * 2008-03-01 2009-09-11 Ixetic Hückeswagen Gmbh Couvercle de corps de pompe à vide
US7588432B2 (en) * 2003-03-05 2009-09-15 Brother Kogyo Kabushiki Kaisha Pump and inkjet printer
EP2587064A1 (fr) * 2011-10-27 2013-05-01 Pierburg Pump Technology GmbH Pompe à vide à palettes
CN103422981A (zh) * 2012-05-21 2013-12-04 北京星旋世纪科技有限公司 星旋式流体机械及其应用的发动机和流体马达
CN105090019A (zh) * 2014-05-17 2015-11-25 王映辉 轴中轴定心滑板转子泵
DE102015213099B3 (de) * 2015-07-13 2016-08-04 Joma-Polytec Gmbh Kunststoffrotor für Vakuumpumpe
CN106536855A (zh) * 2014-08-22 2017-03-22 威伯科欧洲有限责任公司 带有偏心驱动叶片的真空泵（偏心泵设计）
CN106640648A (zh) * 2017-01-13 2017-05-10 南通荣恒环保设备有限公司 一种滑片根部滚轮限位的回转式风机
CN110159589A (zh) * 2019-07-05 2019-08-23 张银量 斜置式三维同步流体机械

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US7588432B2 (en) * 2003-03-05 2009-09-15 Brother Kogyo Kabushiki Kaisha Pump and inkjet printer
US7393090B2 (en) * 2003-10-31 2008-07-01 Brother Kogyo Kabushiki Kaisha Inkjet printer and method of controlling the inkjet printer
US7192263B2 (en) 2004-03-23 2007-03-20 Brother Kogyo Kabushiki Kaisha Pump and ink jet printer mounting the pump
EP1582745A3 (fr) * 2004-03-23 2005-10-12 Brother Kogyo Kabushiki Kaisha Pompe et imprimante à jet d' encre associée
CN100376796C (zh) * 2004-03-23 2008-03-26 兄弟工业株式会社 泵和安装该泵的喷墨打印机
CN100396928C (zh) * 2004-03-23 2008-06-25 兄弟工业株式会社 泵和安装该泵的喷墨打印机
DE102004034922B4 (de) * 2004-07-09 2006-05-11 Joma-Hydromechanic Gmbh Einflügelvakuumpumpe
DE102004034922A1 (de) * 2004-07-09 2006-02-02 Joma-Hydromechanic Gmbh Einflügelvakuumpumpe
DE102004034920B3 (de) * 2004-07-09 2005-12-01 Joma-Hydromechanic Gmbh Einflügelvakuumpumpe
DE102005015721B3 (de) * 2005-03-31 2006-12-21 Joma-Hydromechanic Gmbh Vakuumpumpe
WO2009109282A1 (fr) * 2008-03-01 2009-09-11 Ixetic Hückeswagen Gmbh Couvercle de corps de pompe à vide
EP2587064A1 (fr) * 2011-10-27 2013-05-01 Pierburg Pump Technology GmbH Pompe à vide à palettes
CN103422981A (zh) * 2012-05-21 2013-12-04 北京星旋世纪科技有限公司 星旋式流体机械及其应用的发动机和流体马达
CN103422981B (zh) * 2012-05-21 2016-03-23 北京星旋世纪科技有限公司 星旋式流体机械及其应用的发动机和流体马达
CN105090019A (zh) * 2014-05-17 2015-11-25 王映辉 轴中轴定心滑板转子泵
CN106536855A (zh) * 2014-08-22 2017-03-22 威伯科欧洲有限责任公司 带有偏心驱动叶片的真空泵（偏心泵设计）
CN106536855B (zh) * 2014-08-22 2019-06-04 威伯科欧洲有限责任公司 带有偏心驱动叶片的真空泵
DE102015213099B3 (de) * 2015-07-13 2016-08-04 Joma-Polytec Gmbh Kunststoffrotor für Vakuumpumpe
US10138888B2 (en) 2015-07-13 2018-11-27 Joma-Polytec Gmbh Plastic Rotor for a vacuum pump
CN106640648A (zh) * 2017-01-13 2017-05-10 南通荣恒环保设备有限公司 一种滑片根部滚轮限位的回转式风机
CN110159589A (zh) * 2019-07-05 2019-08-23 张银量 斜置式三维同步流体机械
CN110159589B (zh) * 2019-07-05 2024-03-22 张银量 斜置式三维同步流体机械

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