EP0264749B1 - Pompe à vide à palettes - Google Patents

Pompe à vide à palettes Download PDF

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Publication number
EP0264749B1
EP0264749B1 EP87114808A EP87114808A EP0264749B1 EP 0264749 B1 EP0264749 B1 EP 0264749B1 EP 87114808 A EP87114808 A EP 87114808A EP 87114808 A EP87114808 A EP 87114808A EP 0264749 B1 EP0264749 B1 EP 0264749B1
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.)
Expired - Lifetime
Application number
EP87114808A
Other languages
German (de)
English (en)
Other versions
EP0264749A2 (fr
EP0264749A3 (en
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
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(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Barmag 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 mounted on the fly and is made in one piece with the bearing attachment attached on one side, the rotor and bearing attachment having the same outer diameter.
  • Such a vane vacuum pump is known from DE-A 2 354 039.
  • the disadvantage is that the rotor with the bearing shoulder must be fitted exactly between the front cover.
  • the diameter of the rotor is larger than the diameter of the bearing shoulder.
  • the rotor must therefore be fitted exactly between the housing covers.
  • the object of the invention is to avoid this disadvantage.
  • the seal is made by the bearing shoulder and the bearing located there, preferably designed as a plain bearing,
  • a vane pump is known from DE-A 3 510 681, 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 overdetermination 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, e.g. To use aluminum for the housing and steel for the rotors, without too large gaps 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 so cool gert that it is in circumferential contact with the housing at one point, the so-called bottom dead center.
  • 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.
  • Vent holes 10 which connect the bottom of the grooves 9 with the - seen in the direction of rotation - front of the wing, ensure that the highest pressure in the pump is always present in the grooves 9, so that the sealing strips 8 are pressed outwards.
  • the wing 9 - as sketched in Fig. 3 - consists of only one piece, the wing is possibly including the sealing strip so long that - thanks to the cross-sectional shape of the housing, which will be described later - it seals the circumference of the housing in every rotational position Housing 4 abuts.
  • 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 that 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 wing length L.
  • This requirement applies if the wing is designed with pointed ends.
  • the circumferential wall of the pump housing circumscribes in cross-section an equidistant to a self-contained curve which meets the geometrical requirement that all secants through the center of the rotor have the same length have 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 circumferential wall of the pump housing is found by the distance from the previously determined curve that 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 the outlet opening in the outlet chamber 25 covered.
  • 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 supply 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, which on the one hand is dynamically load-bearing 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 for 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 from getting caught on the longitudinal edges of the rotor slot when the wing is moved in with the sealing strip into the rotor slot.
  • 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 01 first gets into the inner bore of the rotor 5, specifically in the area 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 annular 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 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 especially available for lubrication and sealing of the gaps between the guide slot 6 and wing.

Landscapes

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

Claims (4)

1. Pompe à vide à palettes, dont le rotor pour le guidage des palettes est monté unilatéralement en porte-à-faux et est réalisé d'une seule pièce avec le tourillon unilatéral, de telle manière que le rotor et le tourillon possèdent le même diamètre extérieur, caractérisée par le fait que le rotor est monté de façon axialement mobile et est couplé de façon axialement mobile à un arbre d'entraînement (3) et est sous pression atmosphérique côté entraînement.
2. Pompe à vide à palettes selon la revendication 1, caractérisée par un montage du rotor sur palier à glissement.
3. Pompe à vide à palettes selon revendication 1 ou 2, caractérisée par le fait que le rotor et le tourillon possèdent le même diamètre intérieur.
4. Pompe à vide à palettes selon la revendication 3, caractérisée par le fait que le diamètre intérieur est muni d'un rebord (22) qui se trouve entre une embouchure (28) de la chambre de sortie (25) dans l'alésage intérieur (21) du rotor et l'extrémité libre du rotor.
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 EP0264749A2 (fr) 1988-04-27
EP0264749A3 EP0264749A3 (en) 1988-11-17
EP0264749B1 true 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)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3906823B4 (de) * 1988-12-08 2004-01-08 Barmag Ag Flügel-Vakuumpumpe
JP2882696B2 (ja) * 1990-03-10 1999-04-12 ルーク アウトモービルテヒニーク ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディトゲゼルシャフト ベーンポンプ
US6923628B1 (en) * 1998-09-30 2005-08-02 Luk, Automobitechnik Gmbh Vacuum pump
WO2002033263A2 (fr) * 2000-10-18 2002-04-25 Luk Automobiltechnik Gmbh & Co.Kg Pompe
ES2307417B2 (es) * 2000-10-18 2009-09-22 LUK AUTOMOBILTECHNIK GMBH & CO .KG Bomba.
FR2869958B1 (fr) * 2004-05-07 2008-08-08 Peugeot Citroen Automobiles Sa Pompe a vide a palette(s) perfectionnee
WO2010031504A2 (fr) * 2008-09-16 2010-03-25 Ixetic Hückeswagen Gmbh Pompe à vide
IT1402417B1 (it) * 2010-10-26 2013-09-04 O M P Officine Mazzocco Pagnoni S R L Pompa monopaletta
CN107429695B (zh) 2015-03-25 2020-10-16 皮尔伯格泵技术有限责任公司 真空泵

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3525578A (en) * 1968-11-29 1970-08-25 Precision Scient Co Vacuum pump
DE2354039A1 (de) * 1973-10-29 1975-05-07 Leybold Heraeus Gmbh & Co Kg Drehschieberpumpe
DE2631152C2 (de) * 1976-07-10 1985-08-08 Volkswagenwerk Ag, 3180 Wolfsburg Flügelzellen-Vakuumpumpe

Also Published As

Publication number Publication date
EP0264749A2 (fr) 1988-04-27
DE3762651D1 (de) 1990-06-13
EP0264749A3 (en) 1988-11-17

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