EP0264749A2 - Pompe à vide à palettes - Google Patents

Pompe à vide à palettes Download PDF

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Publication number
EP0264749A2
EP0264749A2 EP87114808A EP87114808A EP0264749A2 EP 0264749 A2 EP0264749 A2 EP 0264749A2 EP 87114808 A EP87114808 A EP 87114808A EP 87114808 A EP87114808 A EP 87114808A EP 0264749 A2 EP0264749 A2 EP 0264749A2
Authority
EP
European Patent Office
Prior art keywords
rotor
wing
housing
bearing
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.)
Granted
Application number
EP87114808A
Other languages
German (de)
English (en)
Other versions
EP0264749A3 (en
EP0264749B1 (fr
Inventor
Siegfried Hertell
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.)
Oerlikon Barmag AG
Original Assignee
Barmag AG
Barmag Barmer Maschinenfabrik AG
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6311978&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0264749(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Barmag AG, Barmag Barmer Maschinenfabrik AG filed Critical Barmag AG
Publication of EP0264749A2 publication Critical patent/EP0264749A2/fr
Publication of EP0264749A3 publication Critical patent/EP0264749A3/de
Application granted granted Critical
Publication of EP0264749B1 publication Critical patent/EP0264749B1/fr
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
    • 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
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
    • 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
    • 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

Definitions

  • the invention relates to a vane vacuum pump according to the preamble of claim 1.
  • Vane pumps of this type are used to generate a negative pressure for the brake booster in diesel motor vehicles and motor vehicles with fuel injection.
  • the vane vacuum pump according to the invention is characterized in that its rotor, which serves to guide the vane, is overhung and is made in one piece with the bearing attachment attached on one side.
  • the object of the invention is to avoid this disadvantage.
  • the bearing shoulder and rotor having the same outside diameter. This creates a sealing problem only at the free end of the rotor.
  • the seal is formed by the bearing shoulder and the bearing located there, preferably designed as a plain bearing.
  • a vane pump is known from DE-A 35 10 681, in which the rotor is sealed on both sides on its circumference by sealing rings and is additionally mounted on both sides in ball bearings.
  • the bearings mean a static over-determination of the seal, so that the function of the seal can only be obtained at the price of a very strong compression of the seal and high wear.
  • an automatic, axial alignment of the rotor occurs in the housing.
  • the rotor is preferably produced as a tube, preferably as a tube with an internal diameter that remains the same from front to back.
  • the invention makes it possible to use materials with different coefficients of thermal expansion, such as aluminum for the housing and steel for the rotors, without the gaps being too large due to the differences in thermal expansion.
  • the gap in the area of the plain bearing is independent of the differences in the temperature behavior of the paired materials with regard to its tightness insofar as this gap is sufficiently long so that a sufficiently good seal is provided even with a relatively large gap width.
  • the axial fixing of the rotor which must at the same time result in a sealing contact of the rotor on the housing cover facing away from the bearing side, can be done by guides which are arranged outside the housing. This holding force can e.g. be exercised by the drive shaft.
  • the vane pump also serves as a spare part that can be replaced without the engine having to be dismantled.
  • a mechanical guide for axially fixing the rotor also results in corresponding wear of the guide.
  • the rotor be axially movably mounted and coupled axially movably to the drive shaft, the bearing-side rotor end, however, being at atmospheric pressure with its drive end face and e.g. protrudes from the pump housing. This ensures that the rotor is pressed by the external pressure with its free end face against the housing cover. The pressure is stronger, the stronger the vacuum generated.
  • the vane pump 1 shown in Figures 1 to 3 is flanged to the crankcase 2 of a motor vehicle engine by flange 13 and sealed with seal 14.
  • the circular cylindrical rotor 5 is rotatably mounted in the pump housing 4.
  • the pump housing the cross-sectional shape of which will be explained later, has an eccentric projection, which forms the bearing housing 37.
  • the bearing housing 37 projects into the crankcase and is centered therein.
  • the rotor is mounted so that it is in circumferential contact with the housing at one point, the so-called bottom dead center. It should be mentioned that the bearing housing 37 forms a sliding bearing for the free end of the rotor 5. An axial groove is therefore indicated, which serves to lubricate this plain bearing.
  • the rotor 5 is a tube that has the same outer diameter between its two ends.
  • An inner bore 21 extends over the entire length of the tube.
  • the tube In the area of the housing, the tube has a single guide slot 6, which lies in an axial plane, which penetrates the inner bore and whose axial length corresponds exactly to the axial length of the pump housing 4.
  • a single wing 7 is slidably guided in the guide slot 6.
  • the width of the wing corresponds to the axial length of the pump housing.
  • the wing 4 can be made in one piece. However, it can also have sealing strips at its ends, which are guided in grooves 9 of the wing 7 in a radial but sliding manner in the radial direction.
  • the wing may be so long, including the sealing strip, that it - thanks to the cross-sectional shape of the housing to be described later - in each Rotating position sealingly abuts the circumference of the housing 4.
  • the wing ends are rounded with a radius r in each case. This radius is chosen to be as large as possible and is in any case greater than half the thickness of the wing 7.
  • the wing is provided with sealing strips, these have a head outside the guide grooves, which is considerably wider than the guide grooves 9, but somewhat narrower than the wing 7.
  • the peripheral wall of the pump housing 4 is determined so that it represents an equidistant cross-section to a Pascal spiral with the radius of curvature of the wing tips r as a distance, provided the wing tips are circularly curved. If the wing ends are not circularly curved in cross section, the distance between the housing cross section and the Pascal spiral is equal to the distance of the contact edge from the center plane of the wing with the respective surface lines of the housing, this distance being measured on the normal in the contact edge.
  • the peripheral wall of the pump housing can be determined so that it is a self-contained curve that meets the geometric requirement that all secants through the rotor center have the same length, this length being substantially equal to the length of the wing L.
  • This requirement applies if the wing is designed with pointed ends. If, however, as shown in FIG. 2, the wing has a large radius of curvature, then describes it the circumferential wall of the pump housing in cross section an equidistant to a self-contained curve, which meets the geometric requirement that all secants through the rotor center have the same length and are as long as the wing length L - 2r.
  • the equidistant has a distance from this curve which is substantially equal to the radius of curvature r of the wing heads. If the wing ends are not curved in a circle, the peripheral wall of the pump housing is found by the distance from the previously determined curve, which the current contact edges have on their normal to the wing center plane.
  • the vane length and the outer diameter of the rotor 5 are first determined.
  • the difference between the length of the wing and the outside diameter determines the delivery volume of the pump. The difference is limited by strength and other considerations. Since the rotor is mounted in the housing so that it is in circumferential contact with the housing in its place, the so-called bottom dead center, the wing 7 is completely immersed in the bottom dead center - as shown in FIG. 2 - in the guide slot 6 of the Rotor 5 a.
  • the pump housing 4 has the suction inlet 11 with a check valve 31 arranged therein and an outlet 12 with a check valve 24 arranged therein.
  • the inlet 11 is offset by approximately 90 ° from the dead center position and the inlet 12 is in the region before bottom dead center - seen in direction of rotation 35.
  • the inlet valve 31 is designed as a mushroom valve. It is a mushroom-shaped rubber body, which is inserted with its style into a perforated valve plate and which rests with the edges of its head on the valve plate, sealingly enclosing the holes in the valve plate.
  • the head turns over in the suction direction in such a way that the suction opening is opened. The head locks in the opposite direction.
  • the outlet initially has a groove 36 in the end face of the pump housing, which extends over a larger outlet area. From this groove, the outlet channel 12 penetrates the housing cover. The outlet channel 12 opens into an outlet chamber 25.
  • the valve 24 is designed as a spring leaf valve which is clamped on one side and covers the outlet opening in the outlet chamber 25.
  • the outlet chamber is designed so that it encloses the valve 24 and that it adjoins the bearing housing 37 of the pump housing.
  • the outlet chamber 25 is closed by a cover 32.
  • the bearing housing 37 has a radial tap bore 27 which starts from the outlet comb 25 and opens into an annular groove 26.
  • the annular groove 26 lies in the inner circumference of the bearing housing 37 and is delimited by the outer circumference of the rotor.
  • the annular groove 26 can also be formed on the outer circumference of the rotor and delimited by the inner circumference of the bearing housing 37.
  • the rotor has a radial bore 28 which lies in the same normal plane as the annular groove 26 and which therefore connects the inner bore 21 of the rotor with the annular groove.
  • the radial bore 28 rotates and is located only by chance in the plane of the drawing in FIG. 1.
  • the rotor At its end of the bearing, which protrudes into the crankcase 2, the rotor has a somewhat enlarged turn, into which a drive shaft of the motor projects with its clutch disc 15.
  • the drive shaft 3 can e.g. are the drive shaft for the injection pump.
  • the clutch disc 15 is fastened with screw 18 on the drive shaft.
  • the clutch disc 15 has at one point on its circumference a clutch tab 16 which engages in an incision 17 (see FIG. 3) of the rotor 5 without preventing the axial mobility of the rotor.
  • the drive shaft 3 and the screw 18 have a central oil feed bore 19. In the screw, this axial bore bifurcates into two or more oil injection bores 20, the oil injection bores 20 being directed into the inner bore 21 of the rotor 5 in such a way that they do not hit the wing 7 .
  • the rotor has in its inner bore 21 a circumferential collar 22 which is attached between the radial channel 28 and the rotor end. It should be noted that the rotor is open at its free end; This means that the inner circumference of the collar 22 forms with the head of the screw 18 and the clutch disc 15 forms an annular gap with the recess 23, which connects the inner bore 21 of the rotor with the clutch housing.
  • the rotor 5 is driven by the drive shaft 3 with the direction of rotation 35.
  • the vane 7 executes a relative movement in the guide slot 6 and lies with its two ends in a sealing and sliding manner on the housing periphery of the pump housing 4.
  • the large radius of curvature of the wing ends has the advantage that the surface pressure of the wing on the housing periphery is low, but that on the other hand a relatively wide gap is created between each wing head and the housing periphery.
  • An oil cushion can form in this gap on the one hand is dynamically stable and on the other hand has a good sealing effect. Due to the large radius of curvature, the contact line of the wing head on the circumference of the housing changes constantly. On the one hand, this results in good cooling, so that there is no local overheating of the wing as a result of the friction. On the other hand, this also reduces wear and, moreover, causes an even distribution of wear, so that a long service life of the wing can be expected.
  • the invention allows the use of a wing with large head radii and still ensures a snug fit of the wing heads on the housing circumference in any rotational position, namely in that the pump housing is designed in cross section as an equidistant to a Pascal spiral, which is the center of the curvature circle of the wing heads is constructed.
  • the sealing strips can serve to compensate for tolerances and to compensate for wear on the pump housing and the vanes.
  • the sealing strips it is of particular importance that the sealing strips outside the guide groove 9 are significantly widened to approximately the wing width. This enables the sealing strips to be manufactured with a large radius of curvature, so that the contact lines of the heads of the sealing strips 8 change over a wide range during a rotor revolution. If the head ends of the sealing strips are approximately as thick as the wing, this has the advantage that in the bottom dead center position, as shown in FIG. 2, only a small amount of oil is enclosed in the guide slot 6 of the rotor and is carried along. On the other hand, the fact that the head end of the sealing strip is somewhat narrower than the wing prevents the Sealing strips get stuck in the rotor slot on the longitudinal edges of the rotor slot when the wing is inserted with the sealing strip.
  • the rotor is a tube which has the same outer diameter over its entire length. Compared to the usual design, in which the rotor shaft has a smaller diameter than the rotor, the rotor gains stability. Because of this improved stability, it is possible to make the rotor thin-walled and therefore low-mass.
  • the wall thickness is limited in that the rotor wall in the guide slot 6 has a good, i.e. good sealing and low surface pressure causing guide for the wing must represent.
  • a relatively small outer diameter of the rotor is also made possible, it being necessary to know that the difference between the wing lengths and the outer diameter of the rotor - apart from the wing thickness - essentially determines the delivery volume of the pump.
  • the design of the rotor also has other advantages: As can be seen from FIG. 1, the bearing area in the bearing housing 37 is in the immediate vicinity of the vane chambers formed in the pump housing. As a result of this direct connection between the vane chambers and the slide bearing, the slide bearing area is subject to constantly changing pressure gradients. This results in a good distribution of the lubricating oil in the bearing area.
  • a rotor of this type can be sealed particularly well in the housing.
  • the critical sealing points of the rotor of vane pumps are Usually the gaps that are formed between the end faces of the rotor on the one hand and the pump housing on the other. If, in the known vane pumps, the rotor of which has a larger diameter than the rotor shaft, an end face of the rotor is pressed close to the end face of the pump housing, a gap that is all the greater is created on the other side. This is not the case here, where the rotor shaft and rotor have the same outside diameter.
  • the gap 33 is sealed between the rotor end face and the adjacent housing wall in that the vacuum prevailing in the pump housing continues in the gap 33.
  • a central pressure gradient field is thus formed in this gap.
  • the rotor face is exposed to atmospheric pressure. There is therefore a resulting compressive force which presses the rotor with its end face facing away from the bearing in a sealing manner against the corresponding end face of the pump housing.
  • the negative pressure in the pump housing 4 is reduced only over a relatively large radial length of the gap, so that the annular area which is subjected to negative pressure is large and thus also the difference in the compressive forces which act on the two opposite end faces of the rotor is large .
  • This large difference works in the sense of a reduction in the gap and thus a better seal. It therefore automatically adjusts the contact pressure to a value that represents an optimal compromise between sealing on the one hand and wear on the other.
  • the air outlet is initially returned with its entire cross section to the inside of the rotor and opens into the crankcase of the engine via the inside of the rotor.
  • This measure is used to create an oil circuit.
  • the lubricating oil is supplied to the pump through oil supply bore 19 and oil injection bores 20.
  • the oil first gets into the inner bore of the rotor 5, specifically in the region of the guide slot 6.
  • the oil is distributed as a film or jacket on the inner circumference of the rotor. This jacket also surrounds the gaps which the guide slot 6 forms with the wing 7.
  • the entire pump housing 4 is under negative pressure outside the rotor, not only on the suction side, but - initially after a short period of operation - also on the so-called outlet side in the area of the outlet 12. that the pump housing can only flow through the check valves 31 and 24 in the suction direction.
  • the oil which lies on the inner circumference of the rotor 5 is now in the sealing gap of the guide slot 6 and in the sealing gap 33 which the end face of the rotor forms with the end face of the pump housing 4. drawn in and conveyed into the wing cells.
  • the lubricating oil In the wing cells, the lubricating oil is entrained by the surrounding wing and forms a lubricating and sealing film in the lubricating gaps between the wing heads and the housing circumference. At the same time, however, the lubricating oil is also conveyed back into the outlet chamber 25 through the outlet groove 36 and the outlet channel 12 with the outlet air. From there, the lubricating oil passes through the tap hole 27 into the annular groove 26. This Ring groove 26 is under atmospheric pressure. Therefore, the lubricating oil can spread from here into the bearing gaps and the lubrication groove of the bearing. It is partly sucked back through the bearing gaps into the pump chamber of the pump housing 4; another part seeps into the crankcase.
  • the amount of oil in the circuit determines not only the lubricating, but also the sealing effect in the areas of the gaps.
  • the outlet 12 can also be arranged on the other end of the pump housing.
  • a valve chamber with a check valve is also provided on the outside of this other end face. This valve chamber is led back through a radially inward channel and an axially parallel branch channel back into the space formed by the inner bore 21.
  • the collar 22 is in any case provided somewhere between the opening of the outlet in the inner bore 21 of the rotor and the free rotor end.
  • the collar is preferably located between the free end of the rotor and the beginning of the wing slot, so that the returned and accumulated amounts of lubricating oil are available especially for lubrication and sealing of the gaps between the guide slot 6 and wing.

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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)
EP87114808A 1986-10-18 1987-10-10 Pompe à vide à palettes Expired - Lifetime EP0264749B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3635493 1986-10-18
DE3635493 1986-10-18

Publications (3)

Publication Number Publication Date
EP0264749A2 true EP0264749A2 (fr) 1988-04-27
EP0264749A3 EP0264749A3 (en) 1988-11-17
EP0264749B1 EP0264749B1 (fr) 1990-05-09

Family

ID=6311978

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87114808A Expired - Lifetime EP0264749B1 (fr) 1986-10-18 1987-10-10 Pompe à vide à palettes

Country Status (2)

Country Link
EP (1) EP0264749B1 (fr)
DE (1) DE3762651D1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2640699A1 (fr) * 1988-12-21 1990-06-22 Bar Ag Ag Pompe a vide a ailettes
DE4107720A1 (de) * 1990-03-10 1991-10-10 Barmag Luk Automobiltech Fluegelzellenpumpe
FR2815384A1 (fr) * 2000-10-18 2002-04-19 Luk Automobiltech Gmbh & Co Kg Pompe
US6743004B2 (en) 1998-09-30 2004-06-01 Luk. Automobiltechnik Gmbh & Co. Kg. Vacuum pump
FR2869958A1 (fr) * 2004-05-07 2005-11-11 Peugeot Citroen Automobiles Sa Pompe a vide a palette(s) perfectionnee
ES2307417A1 (es) * 2000-10-18 2008-11-16 LUK AUTOMOBILTECHNIK GMBH & CO .KG Bomba.
WO2010031504A2 (fr) * 2008-09-16 2010-03-25 Ixetic Hückeswagen Gmbh Pompe à vide
ITMI20101984A1 (it) * 2010-10-26 2012-04-27 O M P Officine Mazzocco Pagnoni S R L Pompa monopaletta
US10696280B2 (en) 2015-03-25 2020-06-30 Pierburg Pump Technology Gmbh Vacuum pump with rotor shaft supported by friction bearings

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1948804A1 (de) * 1968-11-29 1970-07-02 Prec Scient Company Vakuumpumpe
DE2354039A1 (de) * 1973-10-29 1975-05-07 Leybold Heraeus Gmbh & Co Kg Drehschieberpumpe
US4231727A (en) * 1976-07-10 1980-11-04 Volkswagenwerk Aktiengesellschaft Vacuum producing rotary vane pump with shaft lubrication

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1948804A1 (de) * 1968-11-29 1970-07-02 Prec Scient Company Vakuumpumpe
DE2354039A1 (de) * 1973-10-29 1975-05-07 Leybold Heraeus Gmbh & Co Kg Drehschieberpumpe
US4231727A (en) * 1976-07-10 1980-11-04 Volkswagenwerk Aktiengesellschaft Vacuum producing rotary vane pump with shaft lubrication

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2640699A1 (fr) * 1988-12-21 1990-06-22 Bar Ag Ag Pompe a vide a ailettes
DE4107720A1 (de) * 1990-03-10 1991-10-10 Barmag Luk Automobiltech Fluegelzellenpumpe
DE4107720C2 (de) * 1990-03-10 2002-10-24 Luk Automobiltech Gmbh & Co Kg Flügelzellenpumpe
DE19964598B4 (de) * 1998-09-30 2013-12-12 Ixetic Hückeswagen Gmbh Vakuumpumpe
US6743004B2 (en) 1998-09-30 2004-06-01 Luk. Automobiltechnik Gmbh & Co. Kg. Vacuum pump
US6923628B1 (en) * 1998-09-30 2005-08-02 Luk, Automobitechnik Gmbh Vacuum pump
DE19981942B4 (de) * 1998-09-30 2009-07-23 Ixetic Hückeswagen Gmbh Vakuumpumpe
FR2815384A1 (fr) * 2000-10-18 2002-04-19 Luk Automobiltech Gmbh & Co Kg Pompe
WO2002033263A2 (fr) * 2000-10-18 2002-04-25 Luk Automobiltechnik Gmbh & Co.Kg Pompe
WO2002033263A3 (fr) * 2000-10-18 2002-11-28 Luk Automobiltech Gmbh & Co Kg Pompe
ES2264306A1 (es) * 2000-10-18 2006-12-16 LUK AUTOMOBILTECHNIK GMBH & CO.KG. Bomba.
ES2307417A1 (es) * 2000-10-18 2008-11-16 LUK AUTOMOBILTECHNIK GMBH & CO .KG Bomba.
FR2869958A1 (fr) * 2004-05-07 2005-11-11 Peugeot Citroen Automobiles Sa Pompe a vide a palette(s) perfectionnee
WO2010031504A3 (fr) * 2008-09-16 2010-09-02 Ixetic Hückeswagen Gmbh Pompe à vide
WO2010031504A2 (fr) * 2008-09-16 2010-03-25 Ixetic Hückeswagen Gmbh Pompe à vide
ITMI20101984A1 (it) * 2010-10-26 2012-04-27 O M P Officine Mazzocco Pagnoni S R L Pompa monopaletta
US10696280B2 (en) 2015-03-25 2020-06-30 Pierburg Pump Technology Gmbh Vacuum pump with rotor shaft supported by friction bearings

Also Published As

Publication number Publication date
EP0264749A3 (en) 1988-11-17
EP0264749B1 (fr) 1990-05-09
DE3762651D1 (de) 1990-06-13

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