EP1193396B1 - Flügelzellenvakuumpumpe für Automobile - Google Patents

Flügelzellenvakuumpumpe für Automobile Download PDF

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Publication number
EP1193396B1
EP1193396B1 EP01107401.0A EP01107401A EP1193396B1 EP 1193396 B1 EP1193396 B1 EP 1193396B1 EP 01107401 A EP01107401 A EP 01107401A EP 1193396 B1 EP1193396 B1 EP 1193396B1
Authority
EP
European Patent Office
Prior art keywords
rotor
shaft
vane
case
vacuum pump
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
EP01107401.0A
Other languages
English (en)
French (fr)
Other versions
EP1193396A3 (de
EP1193396A2 (de
Inventor
Tadayoshi Mitsubishi Electric Nishikawa
Takashi Mitsubishi Electric Kinoshita
Ryuichi Mitsubishi Electric Komurasaki
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP1193396A2 publication Critical patent/EP1193396A2/de
Publication of EP1193396A3 publication Critical patent/EP1193396A3/de
Application granted granted Critical
Publication of EP1193396B1 publication Critical patent/EP1193396B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • 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
    • 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
    • F01C21/08—Rotary pistons
    • 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

Definitions

  • the present invention relates to an improvement of an automotive vane-type vacuum pump.
  • Fig. 11 is a side view, which is partly a sectional view, showing a part of a conventional automotive vane-type vacuum pump disclosed in, for example, International Publication No. WO00/36303 .
  • Fig. 12 is a sectional view taken along the line E-E of Fig. 11 .
  • the conventional automotive vane-type vacuum pump has an inlet 1, an outlet 2, and a sealed space formed by a substantially cylindrical housing 4 with a bottom and a bracket 5 that are coupled by a bolt 3, the housing 4 and the bracket 5 being made of aluminum.
  • the bracket 5 rotatably supports a shaft 21 by a bearing portion 8.
  • the shaft 21 is provided with a rotor 24 that is eccentrically accommodated in the housing 4 and allowed to rotate in the housing 4.
  • the rotor 24 formed of aluminum is provided with vane slots 10 radially formed, and a vane 11 is retractably disposed in the vane slots 10.
  • the vane 11 rotates together with the rotor 24 with the outer edge thereof slidably in contact with the inner peripheral surface of the housing 4 in an attempt to jut out radially outward from the vane slots 10 due to a centrifugal force.
  • the rotor 24 and the vane 11 together draw in a fluid through the inlet 1 and forcibly feed the fluid to discharge it through the outlet 2.
  • the shaft 21 is equipped with a coupling 13 so as to enable torque to be input from a vehicle.
  • the rotor 24 has two axial grooves 25 in which the two fin-like protuberances 23 fit so that torque can be transmitted via the fin-like protuberances 23 and the axial grooves 25.
  • the rotor 24 is integrally formed on the shaft 21 by one-piece casting, so that there is no play between the shaft main body 22 of the shaft 21 and the rotor 24.
  • the rotor is integrally formed by one-piece molding by, for example, aluminum die casting or plastic molding.
  • the movement of the rotor 24 and the shaft 21 in an axial direction has been restricted by the contact between the side surfaces of the rotor 24 and the housing 4 and the bracket 5. More specifically, the side surfaces of the rotor 24 slidably contact the housing 4 and the bracket 5 thereby to restrict the movement of the rotor 24 and the shaft 21 in the axial direction.
  • the rotor 24, the housing 4, and the bracket 5 are all formed of the same metal, namely, aluminum. This has been presenting a problem of seizure.
  • EP 1 055 823 describes the features of the preamble of claim 1.
  • the present invention has been made with a view toward solving the problem mentioned above, and it is an object of the present invention to provide an automotive vane-type vacuum pump free of the problem of seizure between an axial end surface of a rotor and a case, thus permitting higher quality and reliability, and improved durability.
  • an automotive vane-type vacuum pump for forcibly feeding a fluid from an inlet to an outlet, including a bottomed cylindrical case having an inlet and an outlet, a rotor eccentrically accommodated in the case, a shaft that is secured to the rotor, having both ends thereof rotatably supported by both bottom surfaces of the case, and rotates the rotor by an external driving force, and a vane that rotates slidably in contact with the inner peripheral surface of the case while moving radially in and out of the rotor as the rotor rotates, wherein the axial movement of the shaft is restricted by slidable contact between axial movement restricting stepped portions provided on both ends of the shaft and the case, and a very small gap is formed between an axial end surface of the rotor and the case.
  • the shaft and the case are formed of different metals.
  • an oil reservoir is provided on the axial end surface of the rotor.
  • the oil reservoir is formed at the same time when the rotor is formed by one-piece molding.
  • the rotor is cast integrally with the shaft by insert molding, and the shaft is provided with a slippage-proof groove in its peripheral direction.
  • a lubricant groove is formed in a bearing portion of the case.
  • a drive transmitting means is provided outside the bearing portion of the shaft, and the bearing portion has a length that has been set so that the drive transmitting means does not contact the case even if the bearing portion expands or contracts due to heat.
  • a portion of an axial restriction flange provided on the shaft that is associated with a vane slot is cut so that it is smaller than the innermost diameter of the vane slot in a radial direction and larger than the width of the vane slot in the peripheral direction.
  • Fig. 1 is a side view, which is partly a sectional view, showing a first embodiment of an automotive vane-type vacuum pump in accordance with the present invention.
  • Fig. 2 is a front view of the embodiment viewed from A of Fig. 1 , partly showing the sections of a rotor and a shaft.
  • Fig. 3 is a sectional view taken along the line B-B of Fig. 2 .
  • the automotive vane-type vacuum pump according to the first embodiment includes a substantially cylindrical bottomed housing 4, which has an inlet 1 and an outlet 2, and a bracket 5 that covers an opening of the housing 4, the housing 4 and the bracket 5 being coupled by a bolt 3.
  • the housing 4 and the bracket 5 form a sealed space of a cylindrical case 30 having bottom surfaces at its both ends.
  • the housing 4 and the bracket 5 are made of aluminum.
  • a shaft 21 is disposed such that it penetrates the case 30, and its both ends are rotatably supported by both bottom surfaces of the case 30.
  • the shaft 21 is composed of carbon steel or alloy steel or the like.
  • a side surface of the housing 4 includes a lubricating port 27.
  • a lubricant is supplied through the lubricating port 27.
  • the lubricating port 27 is in communication with an inner surface of the housing 4 via a shaft end of the shaft 21.
  • One end of the shaft 21 that is close to the lubricating port 27 is provided with a stepped portion 28 serving as a stepped portion for restricting axial movement.
  • the other end of the shaft 21 is provided with a flange 29 also serving as the stepped portion for restricting axial movement.
  • the stepped portion 28 slidably contacts the inner surface of the housing 4 so that its movement to the left in Fig. 1 is restricted, while the flange 29 slidably contacts the inner surface of the bracket 5 so that its movement to the right in Fig. 1 is restricted.
  • a spiral lubricant groove 21b is formed in a bearing portion of the bracket 5.
  • a rotor 24 that is eccentrically accommodated in the housing 4 and able to rotate in the housing 4 is secured to the shaft 21, the rotor 24 being made of aluminum.
  • a very small gap is formed between an axial end surface of the rotor 24 and the inner surface of the housing 4, and another very small gap is formed between the axial end surface of the rotor 24 and the inner surface of the bracket 5. This means that both axial end surfaces of the rotor 24 are not in contact with the housing 4 and the bracket 5 constituting the case 30.
  • the rotor 24 has vane slots 10 radially arranged, and a vane 11 retractably disposed in the vane slots 10.
  • the shaft 21 is equipped with a coupling 13 serving as a drive transmitting means so as to enable torque to be input from a vehicle.
  • the drive transmitting means may be a gear, a sprocket, a pulley, or the like in place of the coupling 13.
  • the rotor 24 is integrally formed and installed on the shaft 21 by one-piece casting, so that there is no play between a shaft main body 22 of the shaft 21 and the rotor 24.
  • the rotor 24 is integrally formed by one-piece molding by, for example, casting, forging, aluminum die casting or plastic molding.
  • an oil reservoir 24a is provided on an axial end surface of the rotor 24.
  • the other end surface of the rotor 24 at the rear side is also provided with the oil reservoir 24a.
  • the oil reservoirs 24a are formed at the same time when the rotor 24 is integrally formed as mentioned above.
  • a lubricant is supplied through the lubricating port 27 to lubricate the shaft ends of the shaft 21, then the lubricant reaches the inner surface of the housing 4.
  • the lubricant then gathers in the oil reservoir 24a to perform lubrication between the rotor 24 and the housing 4.
  • the lubricant passes through a hollow portion of the rotor 24 to reach the other side, and gathers in the oil reservoir 24a on the other side to perform lubrication between the rotor 24 and the bracket 5.
  • the lubricant gathers in the lubricant groove 21b formed in the bearing portion of to perform lubrication between the shaft 21 and the bracket 5.
  • An automotive vane-type vacuum pump constructed as described above includes the bottomed cylindrical case 30 having the inlet 1 and the outlet 2, the rotor 24 eccentrically accommodated in the case 30, the shaft 21 that is secured to the rotor 24, having both ends thereof rotatably supported by both bottom surfaces of the case 30, and rotates the rotor 24 by an external driving force, and the vane 11 that rotates slidably in contact with the inner peripheral surface of the case 30 while moving in and out of the rotor 24 as the rotor 24 rotates.
  • the axial movement of the shaft 21 is restricted by the slidable contact between axial movement restricting stepped portions, namely, the stepped portion 28 and the flange 29, which are provided on both ends of the shaft, and the case 30.
  • a very small gap is formed between the axial end surface of the rotor 24 and the case 30. This arrangement restrains seizure from taking place between the axial end surface of the rotor 24 and the case 30, thus leading to higher quality and reliability, and improved durability.
  • the shaft 21 and the case 30 are made of different metals.
  • the shaft 21 is composed of carbon steel, alloy steel, or the like, while the case 30 is composed of aluminum. Hence, seizure between the axial end surface of the rotor 24 and the case 30 can be further restrained, resulting in higher quality and improved durability.
  • the oil reservoirs 24a are provided on the axial end surfaces of the rotor 24. Therefore, seizure between the axial end surface of the rotor and the case can be further restrained, permitting higher quality and improved durability to be achieved. Moreover, there will be less friction, allowing rotational load to be reduced.
  • the oil reservoirs 24a are formed at the same time when the rotor 24 is fabricated by one-piece molding. Hence, the oil reservoirs 24a can be easily formed, permitting a reduction in cost.
  • the lubricant groove formed in the bearing portion of the case restrains wear on the shaft, so that durability can be improved, and friction can be reduced with resultant reduced rotational load.
  • Fig. 4 is a rear view of a rotor and a shaft of a second embodiment of the automotive vane-type vacuum pump in accordance with the present invention.
  • Fig. 5 is a side view showing the section of the rotor, taken along the line C-C of Fig. 4 .
  • Fig. 6 is a front view of the rotor and the shaft.
  • a rotor 24 is integrally cast with a shaft 21 by insert molding, as in the case of the first embodiment.
  • the shaft 21 is, however, provided with a slippage-proof groove 24c formed along the full periphery thereof to prevent slipping off. This arrangement securely prevents the shaft 21 from coming off the rotor 24, leading to higher reliability.
  • the slippage-proof groove 24c may not necessarily be formed over the full periphery.
  • the same advantage can be obtained by, for example, intermittently forming the slippage-proof groove 24c in the peripheral direction.
  • Fig. 7 is a rear view showing a rotor and a shaft of a third embodiment of the automotive vane-type vacuum pump in accordance with the present invention.
  • Fig. 8 is a side view showing the section of the rotor, taken along the line D-D of Fig. 7 .
  • Fig. 9 is a front view of the rotor and the shaft.
  • a shaft 21 in this embodiment is provided with an axial restriction flange 29 for restricting the lateral movement (in Fig. 8 ) of the shaft 21, as in the case of the first embodiment. Furthermore, in the third embodiment, the portion of the axial movement restriction flange 29 that is associated with a vane slot 10 is provided with a cutout 29a that is smaller than the innermost diameter of the vane slot 10 in a radial direction and larger than the width of the vane slot 10 in the peripheral direction.
  • a vane slot is integrally cast with the shaft 21 by insert molding, then finished by machining.
  • the provision of the cutout 29a permits easy insertion and removal of a cutting tool in an axial direction. This allows easier machining of the vane slot 10, allowing reduced cost to be achieved.
  • Fig. 10 is a side view, which is partly a sectional view, showing an essential section of a fourth embodiment of the automotive vane-type vacuum pump in accordance with the present invention.
  • a gear 31 serving as a drive transmitting means is secured, by shrink fitting, outside a bearing portion 21a of a shaft 21.
  • the length of the bearing portion 21a is set so that the gear 31 will not contact a bracket 5 even if the bearing portion 21a expands or contracts due to heat.
  • an axial length Y of the bearing portion 21a is set such that a difference in thermal expansion coefficient between the bracket 5 and the shaft 21 does not cause the length Y to relatively become smaller than a thickness X of the bracket 5.
  • the automotive vane-type vacuum pump for forcibly feeding a fluid from an inlet to an outlet includes a bottomed cylindrical case having an inlet and an outlet, a rotor eccentrically accommodated in the case, a shaft that is secured to the rotor, having both ends thereof rotatably supported by both bottom surfaces of the case, and rotates the rotor by an external driving force, and a vane that rotates slidably in contact with the inner peripheral surface of the case while moving in and out of the rotor as the rotor rotates, wherein the axial movement of the shaft is restricted by slidable contact between axial movement restricting stepped portions provided on both ends of the shaft and the case, and a very small gap is formed between an axial end surface of the rotor and the case.
  • This arrangement restrains seizure from taking place between the axial end surfaces of the rotor and the case, leading to higher quality and reliability, and improved durability.
  • the shaft and the case are formed of different metals. This will further restrains seizure from taking place between the axial end surfaces of the rotor and the case, resulting in higher quality and improved durability.
  • An oil reservoir is provided on the axial end surface of the rotor. This will further restrain the seizure from taking place between the axial end surface of the rotor and the case, permitting higher quality and improved durability to be achieved. Moreover, there will be less friction, allowing rotational load to be reduced.
  • the oil reservoir is formed at the same time when the rotor is fabricated by casting or forging. Hence, the oil reservoir can be easily formed, permitting a reduction in cost.
  • the lubricant groove formed in the bearing portion of the case restrains wear on the shaft, so that durability can be improved, and friction can be reduced, with resultant reduced rotational load.
  • a drive transmitting means is provided outside the bearing portion of the shaft, and the bearing portion has a length that has been set so that the drive transmitting means does not contact the case even if the bearing portion expands or contracts due to heat. Therefore, the rotation of the bearing portion will not be restricted by being caught between a shaft main body and a drive transmitting means, allowing higher reliability to be achieved.
  • a portion of an axial restriction flange provided on the shaft that is associated with a vane slot is cut so that it is smaller than the innermost diameter of the vane slot in a radial direction and larger than the width of the vane slot in the peripheral direction.

Claims (8)

  1. Automobil-Flügelzellenvakuumpumpe zum erzwungenen Zuführen eines Fluids von einem Einlass (1) zu einem Auslass (2), mit:
    einem zylindrischen Gehäuse mit Boden (30), mit dem Einlass (1) und dem Auslass (2);
    einem Rotor (24), der in dem Gehäuse (30) exzentrisch aufgenommen ist;
    einer Welle (21), die an dem Rotor (24) gesichert ist, bei welcher beide Enden durch beide Bodenflächen des Gehäuses (30) drehbar gelagert sind, und die den Rotor (24) durch eine externe Antriebskraft dreht; und
    einem Flügelrad (11), das sich gleitbar in Kontakt mit der Innenumfangsfläche des Gehäuses (30) dreht, während es sich radial in und aus dem Rotor (24) bewegt, wenn sich der Rotor (24) dreht,
    dadurch gekennzeichnet, dass die Axialbewegung der Welle durch Gleitkontakt zwischen Axialbewegungs-begrenzenden Stufenabschnitten (28, 29), die an beiden Enden der Welle (21) vorgesehen sind, und dem Gehäuse (30) begrenzt ist, und ein sehr kleiner Spalt zwischen einer axialen Endfläche des Rotors (24) und dem Gehäuse (30) ausgebildet ist.
  2. Automobil-Flügelzellenvakuumpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Welle (21) und das Gehäuse (30) aus unterschiedlichen Metallen ausgebildet sind.
  3. Automobil-Flügelzellenvakuumpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass ein Ölreservoir (24a) auf der axialen Endfläche des Rotors (24) vorgesehen ist.
  4. Automobil-Flügelzellenvakuumpumpe nach Anspruch 3, dadurch gekennzeichnet, dass das Ölreservoir (24a) zur gleichen Zeit ausgebildet wird, wenn der Rotor (24) durch einstückiges Formen gebildet wird.
  5. Automobil-Flügelzellenvakuumpumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Rotor (24) integral mit der Welle (21) durch Einsatzformen gegossen wird und die Welle (21) mit einer Schlupf-sicheren Vertiefung (24c) in ihrer peripheren Richtung versehen ist.
  6. Automobil-Flügelzellenvakuumpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass eine Schmiermittelvertiefung (21b) in einem Lagerabschnitt des Gehäuses (30) ausgebildet ist.
  7. Automobil-Flügelzellenvakuumpumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass ein Antriebsübertragungsmittel außerhalb des Lagerabschnitts der Welle (21) vorgesehen ist und der Lagerabschnitt eine Länge aufweist, die so festgelegt worden ist, dass das Antriebsübertragungsmittel nicht mit dem Gehäuse (30) in Kontakt gelangt, selbst wenn sich der Lagerabschnitt in Folge von Wärme ausdehnt oder zusammenzieht.
  8. Automobil-Flügelzellenvakuumpumpe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass ein Abschnitt eines Axialbewegungsrestriktionsflanschs (29), der an der Welle (21) vorgesehen ist, der einer Flügelnut (10) zugeordnet ist, so geschnitten ist, dass er kleiner als der innerste Durchmesser der Flügelnut (10) in einer Radialrichtung ist und größer als die Breite der Flügelnut (10) in der peripheren Richtung ist.
EP01107401.0A 2000-10-02 2001-03-26 Flügelzellenvakuumpumpe für Automobile Expired - Lifetime EP1193396B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000301962 2000-10-02
JP2000301962A JP3672237B2 (ja) 2000-10-02 2000-10-02 自動車用ベーン式真空ポンプ

Publications (3)

Publication Number Publication Date
EP1193396A2 EP1193396A2 (de) 2002-04-03
EP1193396A3 EP1193396A3 (de) 2003-07-30
EP1193396B1 true EP1193396B1 (de) 2015-03-11

Family

ID=18783409

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01107401.0A Expired - Lifetime EP1193396B1 (de) 2000-10-02 2001-03-26 Flügelzellenvakuumpumpe für Automobile

Country Status (3)

Country Link
EP (1) EP1193396B1 (de)
JP (1) JP3672237B2 (de)
KR (1) KR100385682B1 (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE423908T1 (de) * 2004-10-22 2009-03-15 Ixetic Hueckeswagen Gmbh Pumpe
JP5366884B2 (ja) * 2010-05-21 2013-12-11 三菱電機株式会社 ベーンロータリー型圧縮機
WO2012167780A2 (de) * 2011-06-07 2012-12-13 Ixetic Bad Homburg Gmbh Rotor für eine flügelzellenpumpe
DE102015216104B3 (de) * 2015-08-24 2016-12-29 Magna Powertrain Bad Homburg GmbH Vakuumpumpe in Leichtbauweise
JPWO2017094639A1 (ja) * 2015-11-30 2018-09-13 株式会社ヴァレオジャパン ベーン型圧縮機

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2312655A (en) * 1941-05-22 1943-03-02 Pump Engineering Service Corp Pump
US3819309A (en) * 1972-10-11 1974-06-25 Gen Motors Corp Means for altering the effective displacement of an axial vane compressor
US5265457A (en) * 1990-02-16 1993-11-30 Sumitomo Electric Industries, Ltd. Method of forming an oil groove on the end surface of a rotor of an aluminum alloy
KR960002186U (ko) * 1994-06-02 1996-01-19 로타리 압축기
JPH1054382A (ja) * 1996-08-14 1998-02-24 Mitsubishi Electric Corp ベーン式真空ポンプ
KR100385683B1 (ko) * 1998-12-14 2003-05-27 미쓰비시덴키 가부시키가이샤 자동차용 베인식 진공펌프

Also Published As

Publication number Publication date
KR20020026790A (ko) 2002-04-12
EP1193396A3 (de) 2003-07-30
JP3672237B2 (ja) 2005-07-20
KR100385682B1 (ko) 2003-05-27
EP1193396A2 (de) 2002-04-03
JP2002106486A (ja) 2002-04-10

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