EP0199984B1 - Rotary vane vacuum pump - Google Patents

Rotary vane vacuum pump Download PDF

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Publication number
EP0199984B1
EP0199984B1 EP19860103981 EP86103981A EP0199984B1 EP 0199984 B1 EP0199984 B1 EP 0199984B1 EP 19860103981 EP19860103981 EP 19860103981 EP 86103981 A EP86103981 A EP 86103981A EP 0199984 B1 EP0199984 B1 EP 0199984B1
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EP
European Patent Office
Prior art keywords
rotor
connecting piece
vacuum pump
shaft
bore
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
Application number
EP19860103981
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German (de)
French (fr)
Other versions
EP0199984A3 (en
EP0199984A2 (en
Inventor
Robert Lange
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
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Filing date
Publication date
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Publication of EP0199984A2 publication Critical patent/EP0199984A2/en
Publication of EP0199984A3 publication Critical patent/EP0199984A3/en
Application granted granted Critical
Publication of EP0199984B1 publication Critical patent/EP0199984B1/en
Expired 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
    • F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft

Definitions

  • the invention relates to a vane vacuum pump according to the preamble of claim 1.
  • a vane vacuum pump is known from DE-OS 29 52 401.
  • Vane vacuum pumps of this type are used in the use of diesel engines and injection gasoline engines in motor vehicles to create pneumatic brake boosters, the negative pressure generated by the pump being used to boost the brake force. Since the pneumatic system is not particularly susceptible to malfunctions, other servo drives are actuated by means of the negative pressure, such as in particular the gear adjustment, the headlight adjustment, the seat adjustment, etc.
  • the known vacuum pumps are usually flanged directly to the housing of the drive motor and the drive shaft of the pump is connected directly to a shaft of the drive motor, for example the camshaft, by a coupling.
  • the bearing points of the vacuum pump are lubricated, for example, by an axial bore in the drive shaft of the motor and the shaft of the vacuum pump coupled therewith.
  • the lubricating oil entering the hollow shaft of the pump is also conveyed through radial bores into the wing root spaces and used to seal the gaps on the guide surfaces of the wings and to reduce the friction on the wing heads.
  • the coupling between the drive shaft of the internal combustion engine and the hollow shaft of the vane pump is carried out in known units as a compensating coupling, which ensures safe driving of the pump rotor and compensates for misalignments. It is used as a loose adapter with coupling teeth or drivers with play between the driving shaft on the motor side and the pump shaft.
  • a vane pump for generating compressed air in which the clutch is held by a cup-shaped element on the rotor shaft, the cup-shaped element being put over the coupling intermediate piece and flanged over a flange of the rotor shaft.
  • This element is disadvantageous because it has a large diameter, because it has to be deformed during assembly and disassembly and because it also projects into the gap between the coupling intermediate piece and the drive shaft and therefore in frictional contact with at least one of the two is coming.
  • the object of the present invention is to avoid these disadvantages and to provide a vane vacuum pump, in which on the one hand the pump rotor and the coupling form a unit for assembly and disassembly, so that it is ensured that the components required for torque transmission without special inspection with the necessary movement play for their function are built in, on the other hand, however, the elements for connecting the pump rotor and the coupling can be installed and detached without any particular deformation and can be installed in the pump without requiring particular space and without wear.
  • the captive coupling is captively attached to the shaft journal of the rotor by means of a pin which is coaxial with the compensating coupling and the rotor shaft and which can be clamped in the rotor shaft.
  • the attachment can also be accomplished by a pipe which serves to supply the lubricating oil from the lubricating oil supply of the drive motor into the vane vacuum pump and additionally has the function of clamping the coupling to the rotor shaft. Details relating to the structural design of this connecting and fastening pin or pipe are given in claims 4 and 5 to 7 and the following description.
  • the vane vacuum pump shown in Fig. 1 in a partial longitudinal section consists of the pump housing 1, which is tightly closed by a flat turned cover 2, in which an intake port 3 is formed and which is fastened to the housing 1 by screws 4 distributed around the circumference.
  • the pump housing 1 has a cylindrical recess 5 and has, in the housing base 6, an eccentrically arranged bearing eye 7 for one-sided mounting of the shaft journal 8 fixedly attached to the rotor 9.
  • the rotor 9 for example, four vanes 10 are arranged so as to be radially movable in radial guide slots.
  • the blades 10 are evenly distributed on the circumference of the rotor 9, two guide slots in each case being diametrically opposed and adjacent blades 10 enclosing a rotor segment of 90 °.
  • material recesses for example axial bores 11, are preferably provided between adjacent wing slots and extend from one end face of the rotor 9 to the other.
  • the circumference of the housing base is designed as a centering flange 12 in order to be able to fasten the vane vacuum pump to the housing 13 of an internal combustion engine, in particular coaxially to the camshaft 14.
  • the shaft journal 8 which is mounted in a floating manner in the bearing eye of the housing base 6, has an axial bore 18 which extends to the front end of the rotor 9. Radial bores 15 emanate from this and communicate with the wing root spaces 16 of the wing slots and dip into the axial bore 18 through the coupling pins 17 fastened to the wing feet. If a wing 10 gets stuck or jammed in its retracted position (bottom dead center), this wing 10 is pushed radially outward by the coupling pin 17 of the opposite wing 10 as the rotor 9 continues to rotate.
  • vane cell vacuum pumps of a different design for example those with two hook-shaped vanes according to DE-OS 35 07 176, are known for which the subject matter of the invention can be applied in an analogous manner.
  • the axial bore 18 has a central recess or extension 25 in the outer region of the shaft journal 8, into which a compensating coupling 19 with radial play is inserted.
  • 4 is designed as a ring element 26, on the circumference of which two diametrically opposed, radial coupling teeth or drivers 30 are fastened, which engage in a radial slot or correspondingly shaped recesses in the shaft journal 8 in a form-fitting manner.
  • the radial slot or the correspondingly shaped recesses of the shaft journal have such an axial depth that the compensating coupling 19 used in the extension 25 with its ring element 26 and the drivers 30 with the end face of the bearing eye 7 in the plane of the centering flange 12 is essentially flush.
  • the compensating coupling and its radial and axial mobility permitted within certain limits can be used to compensate for displacements, in particular axial and / or angular displacement of the two shafts 8, 14 in a simple manner.
  • the lubricating oil for bearing lubrication and sealing of the vacuum pump is supplied by the oil pump through an axial bore 21 in the drive shaft 14 or is sucked in by the negative pressure generated in the vacuum pump.
  • a connecting tube 23 is provided which is leak-free sealed on the circumference by elastic radial sealing rings 22 and projects into the drive shaft 14 and the shaft journal 9. This connecting tube is inserted with such radial play through the center of the compensating coupling 19 that the compensating movements of the shafts are not hindered.
  • the oil flow supplied in the shaft journal 8 is injected in the area of the bearing eye 7 through a nozzle 24 into the axial bore 18 of the rotor 9.
  • the nozzle 24 is not absolutely necessary for the supply of lubricating oil to the vacuum pump. Further details relating to the connecting pipe 23 and the compensating coupling 19 will be explained later with reference to FIGS. 3 and 4.
  • a relief bore 29 is also provided in the housing base. This is angularly offset from the outlet kidney and is in terms of its level in the highest area of the pump, but its distance from the bearing eye 7 is smaller than the rotor radius, so that it is covered by the rotor end face.
  • the distance of the relief bore 29 from the bearing eye 7 and the radius on which the axial bores 11 of the rotor 9 lie correspond to one another in such a way that the lubricating oil received by the axial bores 11 from the rotor end face flows back without pressure via the relief bore 29 into the oil sump of the drive machine can.
  • the relief opening 29 can of course also be designed as an elongated hole on the corresponding radius of the axial recesses of the rotor 9.
  • FIG. 3a shows in a partial longitudinal section a detail of the shaft connection on an enlarged scale compared to FIG. 1.
  • the shaft journal 8 has at its end facing away from the rotor 9 the central extension 25 of the axial bore 18 with its diameter, into which the ring element 26 of the compensating clutch 19 is inserted with its drivers 30 which engage in the radial slot of the shaft journal 8.
  • the axially opposite drivers 31 engage positively in the slot 20 on the end face of the drive shaft 14.
  • the differential coupling 19 has a bore 32 in the axial direction, which has a radial step 33 in the ring element 26.
  • the connecting tube 23 is inserted through the bore 32 of the compensating coupling 19 into the central axial bore 18 of the shaft journal 8 or 21 of the drive shaft 14 in a sealing manner (radial sealing rings 22), the insertion length being limited by the radial step of the axial bore 18.
  • the connecting tube 23 has, on the one hand, approximately in its longitudinal center an annular shoulder (collar) 34, the outer diameter of which is somewhat larger than the smaller diameter of the bore 32 on the radial step 33.
  • a groove is inserted at the end of the connecting tube 23 into which a spring ring 35 is loosely inserted, which can be clipped into the radial groove 36 of the axial bore 18 of the shaft journal 8.
  • 3b shows a modified constructive solution in which the lubricating oil is injected as a free jet into the longitudinal bore 18 in the shaft journal 8.
  • a short tube 23.1 which is funnel-shaped at the inlet in order to catch the oil jet emerging from the nozzle 37 at an axial distance, is firmly pressed into the shaft journal 8 (press fit).
  • the annular shoulder 34.1 at the inlet of the tube 23.1 also has the previously described function to cooperate with the step 33 of the bore 32 in the compensating coupling 19 and to fix it captively, but with a definable axial play on the shaft journal 8.
  • this can be made of, in particular, thermoplastic and can be clipped into the radial groove 36 of the axial bore 18 in the shaft journal.
  • the solution according to FIG. 3b is preferred if the lubricating oil is supplied in excess from the bore 21 of the drive shaft 14, since the oil not taken up by the tube 23.1 can freely flow off and flow back into the oil sump of the engine.
  • the air entrained by the oil jet into the funnel-shaped extension of the tube 23.1 by means of an injector action ensures that a pressure of approx. 1 is always in the axial bore 18 of the rotor 9 and thus also in the wing root spaces 16 of the pump bar prevails.
  • Figures 4a to 4c show the compensating coupling 19 in the top and side view and in axial section according to the preceding description.

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

Description

Die Erfindung bezieht sich auf eine Flügelzellenvakuumpumpe nach dem Oberbegriff des Anspruchs 1. Eine derartige Flügelzellenvakuumpumpe ist aus der DE-OS 29 52 401 bekannt.The invention relates to a vane vacuum pump according to the preamble of claim 1. Such a vane vacuum pump is known from DE-OS 29 52 401.

Derartige Flügelzellenvakuumpumpen werden bei der Verwendung von Dieselmotoren und Einspritz-Otto-Motoren in Kraftfahrzeugen zur Schaffung pneumatischer Bremskraftverstärker verwandt, wobei der durch die Pumpe erzeugte Unterdruck zur Bremskraftverstärkung benutzt wird. Da das Pneumatiksystem besonders wenig anfällig gegen Störungen ist, werden mittels des Unterdrucks auch sonstige Servoantriebe betätigt, wie insbesondere die Getriebeverstellung, die Scheinwerferverstellung, die Sitzverstellung u.a.Vane vacuum pumps of this type are used in the use of diesel engines and injection gasoline engines in motor vehicles to create pneumatic brake boosters, the negative pressure generated by the pump being used to boost the brake force. Since the pneumatic system is not particularly susceptible to malfunctions, other servo drives are actuated by means of the negative pressure, such as in particular the gear adjustment, the headlight adjustment, the seat adjustment, etc.

Die bekannten Vakuumpumpen sind meist direkt an das Gehäuse des Antriebsmotors angeflanscht und die Antriebswelle der Pumpe ist mit einer Welle des Antriebsmotors, beispielsweise der Nockenwelle direkt durch eine Kupplung verbunden. Die Schmierung der Lagerstellen der Vakuumpumpe erfolgt beispielsweise durch eine Axialbohrung der Antriebswelle des Motors und der damit gekuppelten Welle der Vakuumpumpe. Bei den bekannten Flügelzellenvakuumpumpen der eingangs genannten Art wird das in die Hohlwelle der Pumpe gelangende Schmieröl durch radiale Bohrungen auch in die Flügelfußräume gefördert und zur Dichtung der Spalte an den Führungsflächen der Flügel sowie zur Verminderung der Reibung an den Flügelköpfen benutzt.The known vacuum pumps are usually flanged directly to the housing of the drive motor and the drive shaft of the pump is connected directly to a shaft of the drive motor, for example the camshaft, by a coupling. The bearing points of the vacuum pump are lubricated, for example, by an axial bore in the drive shaft of the motor and the shaft of the vacuum pump coupled therewith. In the known vane vacuum pumps of the type mentioned, the lubricating oil entering the hollow shaft of the pump is also conveyed through radial bores into the wing root spaces and used to seal the gaps on the guide surfaces of the wings and to reduce the friction on the wing heads.

Die Kupplung zwischen der Antriebswelle der Brennkraftmaschine und der Hohlwelle der Flügelzellenpumpe wird bei bekannten Baueinheiten als Ausgleichskupplung ausgeführt, die eine sichere Mitnahme des Pumpenrotors gewährleistet und Fluchtungsfehler ausgleicht. Sie ist als loses, mit Kupplungszähnen oder Mitnehmern versehenes Zwischenstück mit Spiel zwischen die treibende Welle auf der Motorseite und die Pumpenwelle eingesetzt.The coupling between the drive shaft of the internal combustion engine and the hollow shaft of the vane pump is carried out in known units as a compensating coupling, which ensures safe driving of the pump rotor and compensates for misalignments. It is used as a loose adapter with coupling teeth or drivers with play between the driving shaft on the motor side and the pump shaft.

Bei der Montage der Flügelzellenvakuumpumpe am Motorblock und insbesondere auch bei Reparaturen oder dem Austausch einer Flügelzellenvakuumpumpe besteht die Gefahr, daß die zwischen die Wellen einzusetzende, lose Kupplung (Zwischenstück) vergessen wird. Dies erfolgt versehentlich bei schlechter Beleuchtung und Arbeiten am in das Fahrzeug eingebauten Motor bzw. bei Reparaturarbeiten und dann, wenn die ausgebauten oder auszutauschenden Bauteile stark eingefettet sind. Da das Fehlen der Kupplung jedoch erst später bei der Kontrolle der Servosysteme festgestellt wird, geht wertvolle Arbeitszeit durch eine entsprechende Nacharbeit verloren.When installing the vane vacuum pump on the engine block and especially when repairs or replacing a vane vacuum pump, there is a risk that the loose coupling (intermediate piece) to be inserted between the shafts will be forgotten. This happens accidentally when lighting is poor and when working on the engine installed in the vehicle or during repair work and when the components that have been removed or replaced are heavily greased. However, since the lack of the clutch is only determined later when the servo systems are checked, valuable rework is lost through appropriate rework.

Durch die US-A 2 068 803 ist eine Flügelzellenpumpe zur Erzeugung von Druckluft bekannt, bei der die Kupplung durch ein topfförmiges Element an der Rotorwelle festgehalten wird, wobei das topfförmige Element über das Kupplungs-Zwischenstück gestülpt und um einen Flansch der Rotorwelle umgebördelt wird. Dieses Element ist nachteilig, da es einen großen Durchmesser besitzt, da es bei der Montage und bei der Demontage verformt werden muß und da es außerdem in den Spalt zwischen dem Kupplungs-Zwischenstück und der Antriebswelle ragt und daher in reibenden Kontakt mit zumindest einem von beiden kommt. Aufgabe der vorliegenden Erfindung ist es, diese Nachteile zu vermeiden und eine Flügelzellenvakuumpumpe zu schaffen, bei der einerseits der Pumpenrotor und die Kupplung für die Montage und Demontage eine Einheit bilden, so daß sichergestellt ist, daß die zur Drehmomentübertragung erforderlichen Bauteile ohne besondere Überprüfung mit dem für ihre Funktion notwendigen Bewegungsspiel eingebaut sind, bei der andererseits aber die Elemente zur Verbindung des Pumpenrotors und der Kupplung ohne besondere Verformung einbaubar und lösbar und ohne besonderen Platzbedarf und ohne Verschleiß in die Pumpe einbaubar sind.From US-A 2 068 803 a vane pump for generating compressed air is known, in which the clutch is held by a cup-shaped element on the rotor shaft, the cup-shaped element being put over the coupling intermediate piece and flanged over a flange of the rotor shaft. This element is disadvantageous because it has a large diameter, because it has to be deformed during assembly and disassembly and because it also projects into the gap between the coupling intermediate piece and the drive shaft and therefore in frictional contact with at least one of the two is coming. The object of the present invention is to avoid these disadvantages and to provide a vane vacuum pump, in which on the one hand the pump rotor and the coupling form a unit for assembly and disassembly, so that it is ensured that the components required for torque transmission without special inspection with the necessary movement play for their function are built in, on the other hand, however, the elements for connecting the pump rotor and the coupling can be installed and detached without any particular deformation and can be installed in the pump without requiring particular space and without wear.

Die Lösung dieser Aufgabe erfolgt erfindungsgemäß durch die im Kennzeichenteil des Anspruchs 1 angegebenen Merkmale.This object is achieved according to the invention by the features specified in the characterizing part of claim 1.

Hierdurch wird erreicht, daß die Ausgleichskupplung in axialer Richtung an der Rotorwelle unverlierbar befestigt ist, so daß sie bei der Montage oder bei Reparaturarbeiten, bei denen die Flügelzellenvakuumpumpe vom Motorblock abgebaut werden muß, nicht mehr vergessen oder verloren werden kann.This ensures that the compensating clutch is captively attached to the rotor shaft in the axial direction, so that it can no longer be forgotten or lost during assembly or during repair work in which the vane-cell vacuum pump has to be removed from the engine block.

Eine vorteilhafte, konstruktive Ausbildung und Anordnung der Ausgleichskupplung ist in den Ansprüchen 2 und 3 angegeben. Diese Lösung hat den Vorteil, daß die mit der Rotorwelle zusammenwirkenden, radialen Zähne oder Mitnehmer der Ausgleichskupplung axial in die Rotorwelle und das Lagergehäuse des Rotors hineinragen und vorzugsweise bündig mit diesem abschließen. Nur noch die zum Eingriff mit der treibenden Welle des Motors bestimmten, axialen Zähne oder Mitnehmer der Ausgleichskupplung ragen aus dem Pumpengehäuse axial heraus und werden beim Zusammenbau mit der Antriebswelle formschlüssig in einen entsprechenden radialen Schlitz dieser Welle eingesetzt.An advantageous, constructive design and arrangement of the compensating clutch is specified in claims 2 and 3. This solution has the advantage that the radial teeth or drivers of the compensating coupling, which cooperate with the rotor shaft, project axially into the rotor shaft and the bearing housing of the rotor and are preferably flush with the latter. Only the axial teeth or drivers of the compensating coupling, which are intended for engagement with the driving shaft of the motor, protrude axially from the pump housing and are positively inserted into a corresponding radial slot of this shaft during assembly with the drive shaft.

Die unverlierbare Befestigung der Ausgleichskupplung am Wellenzapfen des Rotors erfolgt konstruktiv durch einen zur Ausgleichskupplung und zur Rotorwelle koaxialen Stift, der in der Rotorwelle verklemmbar ist. Die Befestigung kann auch durch ein Rohr bewerkstelligt werden, das der Zufuhr des Schmieröls aus dem Schmierölvorrat des Antriebsmotors in die Flügelzellenvakuumpumpe dient und zusätzlich die Funktion hat, die Kupplung mit der Rotorwelle zu verklemmen. Einzelheiten, die die konstruktive Gestaltung dieses Verbindungs- und Befestigungsstiftes oder -rohres betreffen, sind in den Ansprüchen 4 und 5 bis 7 und der nachfolgenden Beschreibung angegeben. Hinsichtlich der Befestigung der Ausgleichskupplung an der Rotorwelle sind verschiedene Ausführungen möglich, je nachdem, wie leicht oder schwer es möglich sein soll, die Bauteile wieder zu trennen.The captive coupling is captively attached to the shaft journal of the rotor by means of a pin which is coaxial with the compensating coupling and the rotor shaft and which can be clamped in the rotor shaft. The attachment can also be accomplished by a pipe which serves to supply the lubricating oil from the lubricating oil supply of the drive motor into the vane vacuum pump and additionally has the function of clamping the coupling to the rotor shaft. Details relating to the structural design of this connecting and fastening pin or pipe are given in claims 4 and 5 to 7 and the following description. With regard to the attachment of the compensating coupling to the rotor shaft, different designs are possible, depending on how easy or difficult it should be possible to separate the components again.

Die Erfindung ist anhand der ein Ausführungsbeispiel darstellenden Zeichnung näher erläutert.The invention is explained in more detail with reference to the drawing which shows an embodiment.

Es ist:

  • Fig. 1 ein axialer Teillängsschnitt einer Flügelzellenvakuumpumpe gemäß Schnitt I-I in Fig. 2;
  • Fig. 2 ein Querschnitt der Pumpe gemäß Schnitt 11-11 in Fig. 1;
  • Fig. 3a/b alternative Ausführungsbeispiele der Befestigung der Ausgleichskupplung am Wellenzapfen des Pumpenrotors im Teillängsschnitt;
  • Fig. 4 die Ausgleichskupplung in der Ansicht und im Querschnitt.
It is:
  • 1 shows an axial partial longitudinal section of a vane vacuum pump according to section II in FIG. 2;
  • FIG. 2 shows a cross section of the pump according to section 11-11 in FIG. 1;
  • 3a / b alternative embodiments of the fastening of the compensating coupling on the shaft journal of the pump rotor in a partial longitudinal section;
  • Fig. 4, the compensating coupling in view and in cross section.

Die in Fig. 1 in einem Teillängsschnitt dargestellte Flügelzellenvakuumpumpe besteht aus dem Pumpengehäuse 1, welches durch einen plan gedrehten Deckel 2, in dem ein Ansaugstutzen 3 ausgebildet ist und der durch umfangsverteilte Schrauben 4 am Gehäuse 1 befestigt ist, dicht verschlossen wird. Das Pumpengehäuse 1 besitzt eine zylindrische Ausdrehung 5 und hat im Gehäuseboden 6 ein hierzu exzentrisch angeordnetes Lagerauge 7 zur einseitigen Lagerung des am Rotor 9 fest angesetzten Wellenzapfens 8. Im Rotor 9 sind beispielsweise vier Flügel 10 in radialen Führungsschlitzen radial beweglich angeordnet. Die Flügel 10 sind aus Symmetriegründen gleichmäßig auf dem Umfang des Rotors 9 verteilt, wobei jeweils zwei Führungsschlitze sich diametral gegenüberliegen und benachbarte Flügel 10 ein Rotorsegment von 90° einschließen. Vorzugsweise sind zur Verringerung des Rotorgewichtes zwischen benachbarten Flügelschlitzen Materialausnehmungen, beispielsweise Axialbohrungen 11, vorgesehen, die sich von einer Stirnseite des Rotors 9 zur anderen erstrecken.The vane vacuum pump shown in Fig. 1 in a partial longitudinal section consists of the pump housing 1, which is tightly closed by a flat turned cover 2, in which an intake port 3 is formed and which is fastened to the housing 1 by screws 4 distributed around the circumference. The pump housing 1 has a cylindrical recess 5 and has, in the housing base 6, an eccentrically arranged bearing eye 7 for one-sided mounting of the shaft journal 8 fixedly attached to the rotor 9. In the rotor 9, for example, four vanes 10 are arranged so as to be radially movable in radial guide slots. For reasons of symmetry, the blades 10 are evenly distributed on the circumference of the rotor 9, two guide slots in each case being diametrically opposed and adjacent blades 10 enclosing a rotor segment of 90 °. To reduce the rotor weight, material recesses, for example axial bores 11, are preferably provided between adjacent wing slots and extend from one end face of the rotor 9 to the other.

Der Gehäuseboden ist an seinem Umfang als Zentrierflansch 12 ausgebildet, um die Flügelzellenvakuumpumpe am Gehäuse 13 einer Brennkraftmaschine, insbesondere koaxial zur Nockenwelle 14 befestigen zu können.The circumference of the housing base is designed as a centering flange 12 in order to be able to fasten the vane vacuum pump to the housing 13 of an internal combustion engine, in particular coaxially to the camshaft 14.

Der im Lagerauge des Gehäusebodens 6 fliegend gelagerte Wellenzapfen 8 besitzt eine Axialbohrung 18, die sich bis ans stirnseitige Ende des Rotors 9 erstreckt. Von dieser gehen radiale Bohrungen 15 aus, die mit den Flügelfußräumen 16 der Flügelschlitze kommunizieren und durch die an den Flügelfüßen befestigte Koppelstifte 17 in die Axialbohrung 18 eintauchen. Beim Hängenbleiben oder Verklemmen eines Flügels 10 in seiner eingefahrenen Stellung (unterer Totpunkt) wird dieser Flügel 10 vom Koppelstift 17 des gegenüberliegenden Flügels 10 beim Weiterdrehen des Rotors 9 radial auswärts geschoben.The shaft journal 8, which is mounted in a floating manner in the bearing eye of the housing base 6, has an axial bore 18 which extends to the front end of the rotor 9. Radial bores 15 emanate from this and communicate with the wing root spaces 16 of the wing slots and dip into the axial bore 18 through the coupling pins 17 fastened to the wing feet. If a wing 10 gets stuck or jammed in its retracted position (bottom dead center), this wing 10 is pushed radially outward by the coupling pin 17 of the opposite wing 10 as the rotor 9 continues to rotate.

Es sei erwähnt, daß auch konstruktiv anders aufgebaute Flügelzellenvakuumpumpen, beispielsweise solche mit zwei hakenförmigen Flügeln nach der DE-OS 35 07 176, bekannt sind, für die der Erfindungsgegenstand in analoger Weise anwendbar ist.It should be mentioned that vane cell vacuum pumps of a different design, for example those with two hook-shaped vanes according to DE-OS 35 07 176, are known for which the subject matter of the invention can be applied in an analogous manner.

Die Axialbohrung 18 hat im äußeren Bereich des Wellenzapfens 8 eine zentrische Ausnehmung oder Erweiterung 25, in die eine Ausgleichskupplung 19 mit radialem Spiel eingesetzt ist. Die Ausgleichskupplung ist gemäß Fig. 4 als Ringelement 26 ausgebildet, an dessen Umfang zwei diametral gegenüberliegende, radiale Kupplungszähne oder Mitnehmer 30 befestigt sind, die in einen Radialschlitz oder entsprechend geformte Ausnehmungen des Wellenzapfens 8 formschlüssig eingreifen. Der Radialschlitz bzw. die entsprechend geformten Ausnehmungen des Wellenzapfens haben eine solche axiale Tiefe, daß die in die Erweiterung 25 eingesetzte Ausgleichskupplung 19 mit ihrem Ringelement 26 und den Mitnehmern 30 mit der Stirnseite des Lagerauges 7 in der Ebene des Zentrierflansches 12 im wesentlichen bündig abschließt. Die axial gegenüberliegenden, um 90° am Umfang versetzten Mitnehmer 31 der Ausgleichskupplung 19 ragen in einen Schlitz 20 an der Stirnseite der Antriebswelle (Nockenwelle 14) und werden formschlüssig von dieser angetrieben. Durch die Ausgleichskupplung und deren in bestimmten Grenzen zugelassene Radial- und Axialbeweglichkeit können Versetzungen, insbesondere Axial- und/oder Winkelversetzung der beiden Wellen 8, 14 ,auf einfache Weise ausgeglichen werden.The axial bore 18 has a central recess or extension 25 in the outer region of the shaft journal 8, into which a compensating coupling 19 with radial play is inserted. 4 is designed as a ring element 26, on the circumference of which two diametrically opposed, radial coupling teeth or drivers 30 are fastened, which engage in a radial slot or correspondingly shaped recesses in the shaft journal 8 in a form-fitting manner. The radial slot or the correspondingly shaped recesses of the shaft journal have such an axial depth that the compensating coupling 19 used in the extension 25 with its ring element 26 and the drivers 30 with the end face of the bearing eye 7 in the plane of the centering flange 12 is essentially flush. The axially opposite drivers 31 of the compensating clutch 19, offset by 90 ° on the circumference, protrude into a slot 20 on the end face of the drive shaft (camshaft 14) and are driven positively by the latter. The compensating coupling and its radial and axial mobility permitted within certain limits can be used to compensate for displacements, in particular axial and / or angular displacement of the two shafts 8, 14 in a simple manner.

Das Schmieröl zur Lagerschmierung und Dichtung der Vakuumpumpe wird durch eine Axialbohrung 21 in der Antriebswelle 14 von der Ölpumpe geliefert oder durch den in der Vakuumpumpe erzeugten Unterdruck angesaugt. Dabei ist zwischen der Antriebswelle 14 und dem Wellenzapfen 8 der Vakuumpumpe ein am Umfang durch elastische Radialdichtringe 22 leckfrei abgedichtetes und in die Antriebswelle 14 und den Wellenzapfen 9 hineinragendes Verbindungsrohr 23 vorgesehen. Dieses Verbindungsrohr ist mit einem solchen radialen Spiel durch das Zentrum der Ausgleichskupplung 19 hindurchgesteckt, daß die Ausgleichsbewegungen der Wellen nicht behindert werden.The lubricating oil for bearing lubrication and sealing of the vacuum pump is supplied by the oil pump through an axial bore 21 in the drive shaft 14 or is sucked in by the negative pressure generated in the vacuum pump. In this case, between the drive shaft 14 and the shaft journal 8 of the vacuum pump, a connecting tube 23 is provided which is leak-free sealed on the circumference by elastic radial sealing rings 22 and projects into the drive shaft 14 and the shaft journal 9. This connecting tube is inserted with such radial play through the center of the compensating coupling 19 that the compensating movements of the shafts are not hindered.

Der in den Wellenzapfen 8 gelieferte Ölstrom wird im Bereich des Lagerauges 7 durch eine Düse 24 in die Axialbohrung 18 des Rotors 9 eingespritzt. Die Düse 24 ist jedoch für die Schmierölzufuhr in die Vakuumpumpe nicht unbedingt erforderlich. Weitere Details, die sich auf das Verbindungsrohr 23 und die Ausgleichskupplung 19 beziehen, werden später anhand der Figuren 3 und 4 erläutert.The oil flow supplied in the shaft journal 8 is injected in the area of the bearing eye 7 through a nozzle 24 into the axial bore 18 of the rotor 9. However, the nozzle 24 is not absolutely necessary for the supply of lubricating oil to the vacuum pump. Further details relating to the connecting pipe 23 and the compensating coupling 19 will be explained later with reference to FIGS. 3 and 4.

Im Gehäuseboden ist gemäß Fig. 2 neben der Auslaßniere 28 für die Abluft und das überschüssige Schmieröl noch eine Entlastungsbohrung 29 vorgesehen. Diese ist gegen die Auslaßniere winkelversetzt und liegt hinsichtlich ihres Niveaus im höchsten Bereich der Pumpe, wobei ihr Abstand vom Lagerauge 7 jedoch kleiner ist als der Rotorradius, so daß sie von der Rotorstirnseite überdeckt wird. Der Abstand der Entlastungsbohrung 29 vom Lagerauge 7 und der Radius, auf dem die Axialbohrungen 11 des Rotors 9 liegen, korrespondieren miteinander in der Weise, daß das von den Axialbohrungen 11 von der Rotorstirnseite aufgenommene Schmieröl drucklos über die Entlastungsbohrung 29 in den Ölsumpf der Antriebsmaschine zurückfließen kann. Hierdurch wird gewährleistet, daß selbst bei hohen Drehzahlen der Pumpe und starker Ölförderung überschüssiges Schmieröl nicht zu einer Erhöhung der Antriebsleistung führt. Die Entlastungsöffnung 29 kann selbstverständlich auch als Langloch auf dem entsprechenden Radius der axialen Ausnehmungen des Rotors 9 ausgebildet sein.According to FIG. 2, in addition to the outlet kidney 28 for the exhaust air and the excess lubricating oil, a relief bore 29 is also provided in the housing base. This is angularly offset from the outlet kidney and is in terms of its level in the highest area of the pump, but its distance from the bearing eye 7 is smaller than the rotor radius, so that it is covered by the rotor end face. The distance of the relief bore 29 from the bearing eye 7 and the radius on which the axial bores 11 of the rotor 9 lie correspond to one another in such a way that the lubricating oil received by the axial bores 11 from the rotor end face flows back without pressure via the relief bore 29 into the oil sump of the drive machine can. This ensures that excess lubricating oil does not lead to an increase in drive power even at high pump speeds and strong oil production. The relief opening 29 can of course also be designed as an elongated hole on the corresponding radius of the axial recesses of the rotor 9.

Fig. 3a zeigt in einem Teillängsschnitt ein Detail der Wellenverbindung im gegenüber Fig. 1 vergrößerten Maßstab. Dabei ist aus Fig. 3a zu erkennen, daß der Wellenzapfen 8 an seinem vom Rotor 9 abgewandten Ende die zentrische Erweiterung 25 der im Durchmesser abgesetzten Axialbohrung 18 hat, in die das Ringelement 26 der Ausgleichskupplung 19 mit seinen in den Radialschlitz des Wellenzapfens 8 eingreifenden Mitnehmern 30 eingesetzt ist. Die axial gegenüberliegenden Mitnehmer 31 greifen in den Schlitz 20 an der Stirnseite der Antriebswelle 14 formschlüssig ein. Es ist in Fig. 3a auch zu sehen, daß die Ausgleichskupplung 19 in Axialrichtung eine Bohrung 32 aufweist, die im Ringelement 26 eine radiale Stufe 33 hat. Das Verbindungsrohr 23 ist durch die Bohrung 32 der Ausgleichskupplung 19 in die zentrische Axialbohrung 18 des Wellenzapfens 8 bzw. 21 der Antriebswelle 14 dichtend eingesetzt (Radialdichtringe 22), wobei die Einschublänge durch die radiale Stufe der Axialbohrung 18 begrenzt ist.3a shows in a partial longitudinal section a detail of the shaft connection on an enlarged scale compared to FIG. 1. It can be seen from Fig. 3a that the shaft journal 8 has at its end facing away from the rotor 9 the central extension 25 of the axial bore 18 with its diameter, into which the ring element 26 of the compensating clutch 19 is inserted with its drivers 30 which engage in the radial slot of the shaft journal 8. The axially opposite drivers 31 engage positively in the slot 20 on the end face of the drive shaft 14. It can also be seen in FIG. 3a that the differential coupling 19 has a bore 32 in the axial direction, which has a radial step 33 in the ring element 26. The connecting tube 23 is inserted through the bore 32 of the compensating coupling 19 into the central axial bore 18 of the shaft journal 8 or 21 of the drive shaft 14 in a sealing manner (radial sealing rings 22), the insertion length being limited by the radial step of the axial bore 18.

Zur unverlierbaren Befestigung der Ausgleichskupplung 19 am Wellenzapfen 8 hat das Verbindungsrohr 23 einerseits etwa in seiner Längsmitte eine Ringschulter (Bund) 34, deren Außendurchmesser etwas größer als der kleinere Durchmesser der Bohrung 32 an der radialen Stufe 33 ist. Zum anderen ist am Ende des Verbindungsrohres 23 eine Nut eingestochen, in die ein Federring 35 lose eingesetzt ist, welcher in die Radialnut 36 der Axialbohrung 18 des Wellenzapfens 8 einklipsbar ist. Durch das Verbindungsrohr 23 ist das Kupplungszwischenstück 19 somit an dem Wellenzapfen 8 festgesetzt und besitzt eine vorgebbare axiale Beweglichkeit.For captive fastening of the compensating coupling 19 to the shaft journal 8, the connecting tube 23 has, on the one hand, approximately in its longitudinal center an annular shoulder (collar) 34, the outer diameter of which is somewhat larger than the smaller diameter of the bore 32 on the radial step 33. On the other hand, a groove is inserted at the end of the connecting tube 23 into which a spring ring 35 is loosely inserted, which can be clipped into the radial groove 36 of the axial bore 18 of the shaft journal 8. Through the connecting tube 23, the coupling intermediate piece 19 is thus fixed on the shaft journal 8 and has a predeterminable axial mobility.

Fig. 3b zeigt eine modifizierte konstruktive Lösung, bei der das Schmieröl als Freistrahl in die Längsbohrung 18 im Wellenzapfen 8 eingespritzt wird. Dabei ist in den Wellenzapfen 8 ein kurzes Rohr 23.1, das am Einlaß trichterförmig erweitert ist, um den in axialem Abstand aus der Düse 37 austretenden Ölstrahl aufzufangen, fest eingepreßt (Preßsitz). Die Ringschulter 34.1 am Einlaß des Rohres 23.1 hat ebenfalls die zuvor beschriebene Funktion, mit der Stufe 33 der Bohrung 32 in der Ausgleichskupplung 19 zusammenzuwirken und diese unverlierbar, aber mit einem vorgebbaren, axialen Spiel am Wellenzapfen 8 zu befestigen.3b shows a modified constructive solution in which the lubricating oil is injected as a free jet into the longitudinal bore 18 in the shaft journal 8. In this case, a short tube 23.1, which is funnel-shaped at the inlet in order to catch the oil jet emerging from the nozzle 37 at an axial distance, is firmly pressed into the shaft journal 8 (press fit). The annular shoulder 34.1 at the inlet of the tube 23.1 also has the previously described function to cooperate with the step 33 of the bore 32 in the compensating coupling 19 and to fix it captively, but with a definable axial play on the shaft journal 8.

In einer vorteilhaften Ausgestaltung des Verbindungsrohres 23 bzw. 23.1 kann dieses aus insbesondere thermoplastischem Kunststoff hergestellt sein und in die Radialnut 36 der Axialbohrung 18 im Wellenzapfen eingeklipst werden.In an advantageous embodiment of the connecting tube 23 or 23.1, this can be made of, in particular, thermoplastic and can be clipped into the radial groove 36 of the axial bore 18 in the shaft journal.

Die Lösung nach Fig. 3b wird bevorzugt, wenn das Schmieröl aus der Bohrung 21 der Antriebswelle 14 im Überschuß angeliefert wird, da das vom Rohr 23.1 nicht aufgenommene Öl frei ab- und in den Ölsumpf des Motors zurückfließen kann. Bei niedrigen Drehzahlen und geringer Öllieferung wird aber durch die von dem Olstrahl in die trichterförmige Erweiterung des Rohres 23.1 durch Injektorwirkung mitgeschleppte Luft gewährleistet, daß in der Axialbohrung 18 des Rotors 9 und somit auch in den Flügelfußräumen 16 der Pumpe immer ein Druck von ca. 1 bar herrscht.The solution according to FIG. 3b is preferred if the lubricating oil is supplied in excess from the bore 21 of the drive shaft 14, since the oil not taken up by the tube 23.1 can freely flow off and flow back into the oil sump of the engine. At low speeds and low oil delivery, however, the air entrained by the oil jet into the funnel-shaped extension of the tube 23.1 by means of an injector action ensures that a pressure of approx. 1 is always in the axial bore 18 of the rotor 9 and thus also in the wing root spaces 16 of the pump bar prevails.

Die Figuren 4a bis 4c zeigen die Ausgleichskupplung 19 in der Auf- und Seitenansicht sowie im Axialschnitt entsprechend der vorangegangenen Beschreibung.Figures 4a to 4c show the compensating coupling 19 in the top and side view and in axial section according to the preceding description.

BEZUGSZEICHENAUFSTELLUNGREFERENCE SIGN LISTING

  • 1 Pumpengehäuse1 pump housing
  • 2 Deckel2 lids
  • 3 Ansaugstutzen3 intake manifolds
  • 4 Schrauben4 screws
  • 5 Ausdrehung5 turn
  • 6 Gehäuseboden6 case back
  • 7 Lagerauge7 bearing eye
  • 8 Wellenzapfen, Rotorwelle8 shaft journals, rotor shaft
  • 9 Rotor9 rotor
  • 10 Flügel10 wings
  • 11 Axialbohrung, Ausnehmung11 axial bore, recess
  • 12 Zentrierflansch12 centering flange
  • 13 Gehäuse der Brennkraftmaschine13 housing of the internal combustion engine
  • 14 Nockenwelle, Antriebswelle, treibende Welle14 camshaft, drive shaft, driving shaft
  • 15 Radialbohrung des Rotors unter dem Flügelfußraum15 Radial bore of the rotor under the wing footwell
  • 16 Flügelfußraum16 wing footwell
  • 17 Koppelstift17 coupling pin
  • 18 zentrische Axialbohrung18 centric axial bore
  • 19 Ausgleichskupplung, Zwischenstück19 compensating coupling, intermediate piece
  • 20 Schlitz20 slot
  • 21 Axialbohrung der Nockenwelle, Ölzufuhrkanal 22 Radialdichtung21 Axial bore of the camshaft, oil feed channel 22 Radial seal
  • 23 Verbindungsrohr, Rohr23 connecting pipe, pipe
  • 23.1 Rohr mit Düseneinlaß23.1 Pipe with nozzle inlet
  • 24 Düse24 nozzle
  • 25 Erweiterung der zentrischen Axialbohrung im Wellenzapfen25 Expansion of the central axial bore in the shaft journal
  • 26 Ringelement26 ring element
  • 27 Ringkanal27 ring channel
  • 28 Auslaßniere28 outlet kidney
  • 29 Entlastungsbohrung29 relief bore
  • 30 Mitnehmer, Zahn30 driver, tooth
  • 31 Mitnehmer, Zahn31 driver, tooth
  • 32 Bohrung32 hole
  • 33 radiale Stufe33 radial stage
  • 34 Ringschulter (Fig. 3a), Bund34 ring shoulder (Fig. 3a), collar
  • 34.1 Ringschulter (Fig. 3b), Bund34.1 ring shoulder (Fig. 3b), collar
  • 35 Federring35 spring washer
  • 36 Radialnut36 radial groove

Claims (7)

1. Rotary vane vacuum pump, in particular for servosystems, such as servo brakes or the like in internal combustion engines, comprising a rotor (9) mounted excentrically in a pump housing (1) and in which at least one pair of vanes (10) is guided in slots, wherein the rotor (9) is driven by a driving shaft (14) via a coupling (19) and wherein the coupling is a connecting piece in the form of a flexible coupling and is provided with coupling teeth (30, 31), said connecting piece being in positive axial engagement with the rotor shaft (8) at one side and with the driving shaft (14) at the other side, characterised in that the connecting piece has a bore (32), that a pin provided with a shoulder (34) passes via its free end through the connecting piece (19), that the pin can be clamped, preferably clipped, via its free end into a corresponding bore (18) in the rotor shaft (8), and that the shoulder is larger than the bore in the connecting piece (19).
2. Pump according to claim 1, characterised in that the connecting piece (19) is a circular cylindrical member having radial teeth, that the rotor shaft (8) has a circular cylindrical recess (25) at its front end, the cylindrical wall of which has radial slots, wherein the connecting piece (19) is fitted, with play, into the cylindrical recess (25) and the radial teeth (30) are fitted, with play, into the radial slots.
3. Rotary vane vacuum pump according to claim 2, characterised in that the connecting piece (19) has teeth (31) on its free front face, said teeth (31) engaging a radial slot (20) in the driving shaft (14).
4. Rotary vane vacuum pump according to claim 3, characterised in that the connecting piece (19) has a central stepped bore (32), the smaller diameter of which is greater than the external diameter of the pin, but smaller than the external diameter of the shoulder (34) provided on the pin.
5. Rotary vane vacuum pump according to one of claims 1 to 4, characterised in that the pin is a hollow central pipe (23) which is aligned with the oil feed bore (21) in the driving shaft (14).
6. Rotary vane vacuum pump according to claim 5, characterised in that the pin is an oil feed pipe (23) which projects into the driving shaft (14) and connects the central oil feed duct (21) in the interior of the driving shaft (14) with a central oil feed duct (18) in the interior of the rotor shaft (8).
7. Rotary vane vacuum pump according to claim 6, characterised in that the oil feed pipe (23) is sealed off from the rotor (9) and the driving shaft (14) by means of sealings (22).
EP19860103981 1985-03-29 1986-03-22 Rotary vane vacuum pump Expired EP0199984B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3511559 1985-03-29
DE3511559 1985-03-29
DE3515634 1985-05-02
DE3515634 1985-05-02

Publications (3)

Publication Number Publication Date
EP0199984A2 EP0199984A2 (en) 1986-12-10
EP0199984A3 EP0199984A3 (en) 1987-06-24
EP0199984B1 true EP0199984B1 (en) 1989-11-15

Family

ID=25830903

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860103981 Expired EP0199984B1 (en) 1985-03-29 1986-03-22 Rotary vane vacuum pump

Country Status (2)

Country Link
EP (1) EP0199984B1 (en)
DE (1) DE3666969D1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102472279A (en) * 2009-08-12 2012-05-23 约马-综合技术有限公司 Vacuum pump

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19519841B4 (en) * 1995-05-31 2004-02-12 Luk Automobiltechnik Gmbh & Co. Kg Vane pump
EP1117933B2 (en) * 1998-09-30 2013-04-17 ixetic Hückeswagen GmbH Vacuum pump
DE10150302B4 (en) * 2001-10-11 2004-08-12 Pierburg Gmbh Device for generating vacuum for consumers in a motor vehicle
FR2886696B1 (en) * 2005-06-03 2007-08-31 Renault Sas DEVICE FOR COUPLING A VACUUM PUMP WITH A CAMSHAFT COMPRISING LUBRICANT FLUID FEED MEANS

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2068803A (en) * 1935-03-14 1937-01-26 James P Johnson Vacuum pump
US2762349A (en) * 1953-07-31 1956-09-11 Int Harvester Co Pump drive and lubrication
FR2384137A1 (en) * 1977-03-15 1978-10-13 Barmag Barmer Maschf MULTICELLULAR MACHINE WITH FINES
DE2952401A1 (en) 1978-07-28 1981-06-25 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid PRESSURE OIL LUBRICATION FOR A VACUUM PUMP, IN PARTICULAR LEAF CELL VACUUM PUMP
JPS5919719A (en) * 1982-07-27 1984-02-01 Fanuc Ltd Coupling structure for servo-motor and detector
DE3507176A1 (en) 1984-04-09 1985-10-31 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Vane pump
FR2571455A4 (en) * 1984-06-25 1986-04-11 Doletina Jean Pierre Shaft-to-disc tenons and collar coupling ("Oldham" coupling with a collar)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102472279A (en) * 2009-08-12 2012-05-23 约马-综合技术有限公司 Vacuum pump

Also Published As

Publication number Publication date
EP0199984A3 (en) 1987-06-24
DE3666969D1 (en) 1989-12-21
EP0199984A2 (en) 1986-12-10

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