EP1890040B1 - Vacuum pump - Google Patents

Vacuum pump Download PDF

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Publication number
EP1890040B1
EP1890040B1 EP07022290A EP07022290A EP1890040B1 EP 1890040 B1 EP1890040 B1 EP 1890040B1 EP 07022290 A EP07022290 A EP 07022290A EP 07022290 A EP07022290 A EP 07022290A EP 1890040 B1 EP1890040 B1 EP 1890040B1
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EP
European Patent Office
Prior art keywords
area
rotor
housing
pump
pressure
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
EP07022290A
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German (de)
French (fr)
Other versions
EP1890040A3 (en
EP1890040A2 (en
Inventor
Dieter Otto
Ulrich Hiltemann
Andreas Moje
Antonio Pace
Ulrich Pabst
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.)
Magna Powertrain Hueckeswagen GmbH
Original Assignee
Ixetic Hueckeswagen GmbH
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Publication date
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Publication of EP1890040A2 publication Critical patent/EP1890040A2/en
Publication of EP1890040A3 publication Critical patent/EP1890040A3/en
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Publication of EP1890040B1 publication Critical patent/EP1890040B1/en
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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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/04—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for reversible pumps
    • 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
    • F04C2220/00—Application
    • F04C2220/10—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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/101—Geometry of the inlet or outlet of the inlet

Definitions

  • the invention relates to a vacuum pump, in particular for automotive brake boosters, wherein the pump is normally driven by the automotive internal combustion engine in a rotational direction ("forward"). Accordingly, the vacuum pumps have a fixed direction of rotation. Such vacuum pumps are known.
  • Such pumps are normally driven by the automotive internal combustion engine in a rotational ("forward") direction, the vacuum pump having a device which serves to prevent damage during reverse rotation.
  • Such pumps are for example from the EP-A-0439672 known and correspond to the preamble of claim 1.
  • this known device has an outlet valve for the residual oil to the cylinder head of the internal combustion engine.
  • an additional valve is provided, which opens a path for the oil to the cylinder head backwards.
  • this check valve is closed and does not allow air to flow from the cylinder head as external air into the pump.
  • this valve is combined with the pump outlet valve, so that a spring plate valve has two tongues and is secured with a screw.
  • the object of the invention is to present an improved vacuum pump.
  • a vacuum pump in which a device having the features of claim 1 has a bypass device for the residual oil.
  • a bypass device designed as a pivoting wing mounted, which is positioned in the region of a Schmiegespaltes.
  • the swing wing abuts the rotor, which can be caused by a pressure difference and / or a spring force.
  • the pressure in front of the wing causes the swinging wing to lift, thus clearing the way for the residual oil, either to the cylinder head or to the other wing side.
  • the pivoting pad device is used in a pump with a Monoeriel without moving caps, because the monoeriel then always rests by the centrifugal force on the opposite side and thus has no contact with the swing wing.
  • the pivoting wing is preferably designed as a plastic part, but can also be designed as a sheet metal part and can be shown either pivotally or elastically deformable.
  • a vacuum pump in which the device has a bypass groove.
  • a bypass groove in the housing and / or lid is arranged in the region of the air inlet opening, so the suction nozzle. This bypass allows the residual oil to flow back past the wing, avoiding pressure spikes due to residual oil being forced backwards.
  • the invention describes a vacuum pump in which the device has a storage volume for residual oil. Pressure peaks through the residual oil can thus be avoided by the remaining oil is pushed into the storage volume during reverse rotation of the pump, so that the pump can rotate without residual oil in front of the wing and thus without squeezing oil backwards.
  • This memory is to be housed in the pump housing.
  • Another known pump is characterized in that the device has a bypass in the lid.
  • a pressure-dependent bypass is integrated in the lid of the pump, which opens at elevated pressure in front of the intake valve and drain oil from this area in the other pump chamber and / or the rotor inner bore leaves.
  • This bypass can be designed as a resilient sheet, which lies on the inside of the lid and which can be pushed away under pressure load at least partially into corresponding recesses of the lid.
  • the bypass can be designed as a piston in the lid.
  • a vacuum pump in which the rotor has a clamping roller freewheel, which in one direction of rotation (“forward"), the connection between the rotor and drive element, such as a clutch blocks, ie jams, and in the opposite direction of rotation (“backwards”) allows the drive element to be fritted without the rotor engaging in reverse rotation.
  • the freewheel can be pressed onto the rotor, wherein the known slide bearing between the rotor and the pump housing is replaced by the roller bearing of the clamping roller freewheel.
  • FIG. 1a is a perspective view of a known vacuum pump 1 is shown.
  • the vacuum pump has a housing 3 in which an eccentrically arranged rotor with a monoeriel is not visible here.
  • Such vacuum pumps are known in their construction and function and should therefore not be further explained.
  • the direction of rotation of the rotor is represented by an arrow 5, so that it can be seen that increases in this direction of rotation in the region 7, the delivery volume upon rotation of the rotor and thus leads to suction and in the area 9 of the pump, the delivery volume and reduced thus leading to the ejection of the conveyor.
  • the conveyor is thus sucked in the area 7 via a suction nozzle 11 and then ejected when exceeding the top dead center and the reduction of the delivery volume in the area 9 via an outlet valve 13.
  • an additional valve 15 is arranged, which opens during reverse rotation to the cylinder head and thereby can drain the residual oil in this area, that is analogous to how normally the outlet valve 13 behaves in normal conveying direction 5.
  • the outlet valve 15 remains closed for the residual oil, since builds up in the region 7 negative pressure and therefore the tongue pressure in the cylinder head keeps the reed valve 15 closed.
  • the valve 15 for the reverse run is combined with the pump outlet valve 13, so that a spring plate valve has two tongues and is secured with a screw 17.
  • FIG. 1b the corresponding individual parts of the valves are shown in disassembled state.
  • the spring 17 secures the pressurized state, the pump outlet opening 27, while the spring tongue 25 of the reverse flow valve 15, the outlet opening 29th
  • the spring tongue 23 of the Pumpenaustrittventils 13 closes the hold-tongue 19 and the spring tongue valve 23 of the pump outlet valve 13 and the spring tongue closes in normal direction of rotation of the pump.
  • FIG. 2 a bypass device according to the invention for the residual oil during reverse rotation is shown in the form of a swing-wing device.
  • a rotor 30, which is shown simplified here without the monoeriel is arranged eccentrically in a housing 32.
  • the housing 32 has a recess 34 in which a pivoting device 36 is arranged.
  • the swing-wing device 36 abuts the rotor 38 in the area 38.
  • the direction of rotation of the rotor in normal operation is with the Arrow 40 indicated. In normal operation, therefore, the pivoting leaf seals against the rotor, wherein the pressure zone of the vacuum pump is in the region 48 and the suction zone of the vacuum pump is in the region 50.
  • the rotor and the housing can have an approximately equal radius of curvature over an angular range ⁇ , here denoted by the reference number 46 between the housing 32 and the rotor 30, so that a good Schmiegespaltabdichtung even then is present when the swinging wing performs its real safety function in reverse.
  • This crevice seal also prevents pressure spikes from lifting the mono wing. In reverse, so the suction area 50 is suddenly the pressure range, which can then build a pressure peak in this area by the reverse crushed squeeze oil. However, this pressure peak is then relieved by opening the pivoting vane 36 in the area 42 which is connected to the cylinder head area.
  • the pressure in the cylinder head region which corresponds approximately to the atmospheric pressure, normally prevails.
  • a monoeriel is used without moving caps in a pump with this swing-wing device, because the monoeriel then always rests by the centrifugal force on the opposite side and thus has no contact with the swing wing 36.
  • the pivoting blade 36 itself can be pressed against the rotor 30 in a sealing manner by a spring force 44 as well as by the pressure force of the pressure in the region 42.
  • FIG. 3 is shown as a known reverse-flow relief device, a bypass groove 54 on the back 52 of the pump housing 3.
  • the bypass groove 54 is arranged in the suction region of the pump and thus in the region of the suction nozzle 11. Opposite is the outlet opening 56 of the outlet valve when the pump is rotated in the normal direction of rotation 40. Runs the pump when reversing the engine the other way round, so the squeezing oil can be displaced by the bypass groove 54 laterally past the wing to the rear, thereby avoiding the build-up of pressure peaks.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Rotary Pumps (AREA)

Description

Die Erfindung betrifft eine Vakuumpumpe, insbesondere für Bremskraftverstärker für Kraftfahrzeuge, wobei die Pumpe normalerweise vom Kraftfahrzeugverbrennungsmotor in einer Drehrichtung ("vorwärts") angetrieben wird. Die Vakuumpumpen haben also dementsprechend eine fest definierte Drehrichtung. Derartige Vakuumpumpen sind bekannt.The invention relates to a vacuum pump, in particular for automotive brake boosters, wherein the pump is normally driven by the automotive internal combustion engine in a rotational direction ("forward"). Accordingly, the vacuum pumps have a fixed direction of rotation. Such vacuum pumps are known.

Es gibt allerdings Situationen, in denen der Motor rückwärts dreht. Dabei ist z. B. der Motor ausgeschaltet, ein Vorwärtsgang eingekuppelt, und der Wagen wird rückwärts bewegt. In diesen Situationen dreht sich der Motor und damit auch die Vakuumpumpe entgegen der normalen Drehrichtung. Üblicherweise ist die Pumpe für diese Drehrichtung nicht ausgelegt, und dementsprechend können Einzelteile der Pumpe stark belastet werden und zur Beschädigung oder sogar zur Zerstörung der Pumpe führen.However, there are situations where the engine is turning backwards. It is z. As the engine is off, a forward gear engaged, and the carriage is moved backwards. In these situations, the motor and thus also the vacuum pump rotates in the opposite direction to the normal direction of rotation. Usually, the pump is not designed for this direction of rotation, and accordingly, individual parts of the pump can be heavily loaded and lead to damage or even destruction of the pump.

Solche Pumpen werden normalerweise vom Kraftfahrzeugverbrennungsmotor in einer Drehrichtung ("vorwärts") angetrieben, wobei die Vakuumpumpe eine Vorrichtung aufweist, welche zur Vermeidung von Beschädigungen beim Rückwärtsdrehen dient. Solche Pumpen sind beispielsweise aus der EP-A-0439672 bekannt und entsprechen dem Oberbegriff von Anspruch 1.Such pumps are normally driven by the automotive internal combustion engine in a rotational ("forward") direction, the vacuum pump having a device which serves to prevent damage during reverse rotation. Such pumps are for example from the EP-A-0439672 known and correspond to the preamble of claim 1.

Beispielsweise weist diese bekannte Vorrichtung ein Austrittsventil für das Restöl zum Zylinderkopf des Verbrennungsmotors auf. Dabei ist ein zusätzliches Ventil vorgesehen, das bei Rückwärtslauf einen Weg für das Öl zum Zylinderkopf hin öffnet. Bei Normalbetrieb der Pumpe ist dieses Rückschlagventil geschlossen und lässt keine Luft vom Zylinderkopf als Fremdluft in die Pumpe strömen. Vorzugsweise wird dieses Ventil mit dem Pumpenaustrittsventil kombiniert, so dass ein Federblechventil zwei Zungen aufweist und mit einer Schraube gesichert wird.For example, this known device has an outlet valve for the residual oil to the cylinder head of the internal combustion engine. In this case, an additional valve is provided, which opens a path for the oil to the cylinder head backwards. During normal operation of the pump, this check valve is closed and does not allow air to flow from the cylinder head as external air into the pump. Preferably, this valve is combined with the pump outlet valve, so that a spring plate valve has two tongues and is secured with a screw.

Aufgabe der Erfindung ist es, eine verbesserte Vakuumpumpe darzustellen.The object of the invention is to present an improved vacuum pump.

Die Aufgabe wird gelöst durch eine Vakuumpumpe, bei welcher eine Vorrichtung mit den Merkmalen des Anspruches 1 eine Bypassvorrichtung für das Restöl aufweist. Dabei ist im Pumpengehäuse eine Bypassvorrichtung, als Schwenkflügel ausgeführt, angebracht, welche im Bereich eines Schmiegespaltes positioniert ist. Im Normalbetrieb liegt der Schwenkflügel am Rotor an, was durch eine Druckdifferenz und/oder eine Federkraft verursacht werden kann. Bei Rückwärtsdrehung der Pumpe führt der Druck vor dem Flügel zum Abheben des Schwenkflügels und gibt damit den Weg für das Restöl frei, entweder zum Zylinderkopf oder auf die andere Flügelseite. Vorzugsweise gibt es noch einen Winkelbereich α, in dem Rotor und Gehäuse einen annähemd gleichen Krümmungsradius aufweisen, so dass eine gute Schmiegespaltdichtung zusätzlich zum Schwenkflügel vorhanden ist. Vorzugsweise wird die Schwenkfügelvorrichtung bei einer Pumpe mit einem Monoflügel ohne bewegliche Kappen eingesetzt, weil der Monoflügel dann immer durch die Fliehkraft auf der gegenüberliegenden Seite anliegt und somit keinen Kontakt zum Schwenkflügel aufweist. Der Schwenkflügel ist vorzugsweise als Kunststoffteil ausgeführt, kann aber auch als Blechteil ausgeführt sein und kann entweder schwenkbar oder elastisch verformbar dargestellt werden.The object is achieved by a vacuum pump, in which a device having the features of claim 1 has a bypass device for the residual oil. In this case, in the pump housing, a bypass device, designed as a pivoting wing mounted, which is positioned in the region of a Schmiegespaltes. In normal operation, the swing wing abuts the rotor, which can be caused by a pressure difference and / or a spring force. When the pump is rotated backwards, the pressure in front of the wing causes the swinging wing to lift, thus clearing the way for the residual oil, either to the cylinder head or to the other wing side. Preferably, there is still an angle range α, in which the rotor and the housing have an approximately equal radius of curvature, so that a good spline seal is present in addition to the pivoting wing. Preferably, the pivoting pad device is used in a pump with a Monoflügel without moving caps, because the monoflügel then always rests by the centrifugal force on the opposite side and thus has no contact with the swing wing. The pivoting wing is preferably designed as a plastic part, but can also be designed as a sheet metal part and can be shown either pivotally or elastically deformable.

Weiterhin ist eine Vakuumpumpe bekannt, bei welcher die Vorrichtung eine Bypassnut aufweist. Vorzugsweise wird im Bereich der Lufteintrittsöffnung, also des Saugstutzens, eine Bypassnut im Gehäuse und/oder Deckel angeordnet. Dieser Bypass ermöglicht, dass das Restöl am Flügel vorbei zurückströmt und dass auf diese Weise Druckspitzen durch beim Rückwärtslauf zurückgedrängtes Restöl vermieden werden.Furthermore, a vacuum pump is known in which the device has a bypass groove. Preferably, a bypass groove in the housing and / or lid is arranged in the region of the air inlet opening, so the suction nozzle. This bypass allows the residual oil to flow back past the wing, avoiding pressure spikes due to residual oil being forced backwards.

Durch die Erfindung wird eine Vakuumpumpe beschrieben, bei welcher die Vorrichtung ein Speichervolumen für Restöl aufweist. Druckspitzen durch das Restöl können also vermieden werden, indem bei Rückwärtsdrehen der Pumpe das Restöl in das Speichervolumen geschoben wird, so dass die Pumpe ohne Restöl vor dem Flügel und damit ohne Quetschöl rückwärts rotieren kann. Dieser Speicher ist im Pumpengehäuse untergebracht werden.The invention describes a vacuum pump in which the device has a storage volume for residual oil. Pressure peaks through the residual oil can thus be avoided by the remaining oil is pushed into the storage volume during reverse rotation of the pump, so that the pump can rotate without residual oil in front of the wing and thus without squeezing oil backwards. This memory is to be housed in the pump housing.

Eine weitere bekannte Pumpe zeichnet sich dadurch aus, dass die Vorrichtung einen Bypass im Deckel aufweist. Dazu ist im Deckel der Pumpe ein druckabhängiger Bypass integriert, der bei erhöhtem Druck vor dem Ansaugventil öffnet und Öl aus diesem Bereich in die andere Pumpenkammer und/oder zur Rotorinnenbohrung abströmen lässt. Dieser Bypass kann als federndes Blech ausgeführt sein, das auf der Innenseite des Deckels liegt und das bei Druckbelastung zumindest partiell in entsprechende Vertiefungen des Deckels weggedrückt werden kann. Alternativ kann der Bypass als Kolben im Deckel ausgeführt sein.Another known pump is characterized in that the device has a bypass in the lid. For this purpose, a pressure-dependent bypass is integrated in the lid of the pump, which opens at elevated pressure in front of the intake valve and drain oil from this area in the other pump chamber and / or the rotor inner bore leaves. This bypass can be designed as a resilient sheet, which lies on the inside of the lid and which can be pushed away under pressure load at least partially into corresponding recesses of the lid. Alternatively, the bypass can be designed as a piston in the lid.

Weiterhin ist eine Vakuumpumpe bekannt, bei welcher der Rotor einen Klemmrollenfreilauf aufweist, welcher in einer Drehrichtung ("vorwärts") die Verbindung zwischen Rotor und Antriebselement, wie beispielsweise einer Kupplung, blockiert, also klemmt, und in der entgegengesetzten Drehrichtung ("rückwärts") das Antriebselement freitagfen lässt, ohne dass der Rotor die Rückwärtsdrehung mitmacht. Der Freilauf kann auf den Rotor aufgepresst werden, wobei die bekannte Gleitlagerung zwischen Rotor und Pumpengehäuse durch das Rollenlager des Klemmrollenfreilaufs ersetzt wird.Furthermore, a vacuum pump is known, in which the rotor has a clamping roller freewheel, which in one direction of rotation ("forward"), the connection between the rotor and drive element, such as a clutch blocks, ie jams, and in the opposite direction of rotation ("backwards") allows the drive element to be fritted without the rotor engaging in reverse rotation. The freewheel can be pressed onto the rotor, wherein the known slide bearing between the rotor and the pump housing is replaced by the roller bearing of the clamping roller freewheel.

Die Erfindung wird nun anhand der Figuren beschrieben.

Figur 1
zeigt eine bekannte Pumpe mit einem Austrittsventil für das Restöl.
Figur 2
zeigt einen als Schwenkflügel ausgeführten Bypass für das Restöl gemäß der Erfindung.
Figur 3
zeigt eine bekannte Pumpe mit Bypassnut im Gehäuse für das Restöl.
The invention will now be described with reference to the figures.
FIG. 1
shows a known pump with a discharge valve for the residual oil.
FIG. 2
shows a designed as a swing wing bypass for the residual oil according to the invention.
FIG. 3
shows a known pump with bypass groove in the housing for the residual oil.

In Figur 1a ist in perspektivischer Darstellung eine bekannte Vakuumpumpe 1 dargestellt. Die Vakuumpumpe besitzt ein Gehäuse 3, in welchem hier nicht sichtbar ein exzentrisch angeordneter Rotor mit einem Monoflügel angeordnet ist. Derartige Vakuumpumpen sind in ihrer Konstruktion und Funktion bekannt und sollen deswegen nicht weiter erläutert werden. Auf dem Gehäuse ist die Drehrichtung des Rotors durch einen Pfeil 5 dargestellt, so dass erkennbar ist, dass in dieser Drehrichtung sich im Bereich 7 das Fördervolumen bei Umdrehung des Rotors vergrößert und somit zum Ansaugen führt und im Bereich 9 der Pumpe sich das Fördervolumen verkleinert und somit zum Ausstoßen des Fördermittels führt. Das Fördermittel wird also im Bereich 7 über einen Saugstutzen 11 angesaugt und danach bei Überschreiten des oberen Totpunkts und dem Verkleinern des Fördervolumens im Bereich 9 über ein Austrittsventil 13 ausgestoßen. Wird nun durch Rückwärtsdrehen einer derartigen Vakuumpumpe im Bereich 7 das Fördervolumen verkleinert und der Flügel zurückgedrückt, so kann das dabei zurückgedrängte Restöl, welches nur in den Ansaugstutzen entweichen kann, zu Beschädigungen oder gar zur Zerstörung der Pumpe führen, da im Ansaugstutzen ein Rückschlagventil in dieser Richtung sperrt und das Restöl dadurch zu hohen Druckspitzen führen kann.In FIG. 1a is a perspective view of a known vacuum pump 1 is shown. The vacuum pump has a housing 3 in which an eccentrically arranged rotor with a monoflügel is not visible here. Such vacuum pumps are known in their construction and function and should therefore not be further explained. On the housing, the direction of rotation of the rotor is represented by an arrow 5, so that it can be seen that increases in this direction of rotation in the region 7, the delivery volume upon rotation of the rotor and thus leads to suction and in the area 9 of the pump, the delivery volume and reduced thus leading to the ejection of the conveyor. The conveyor is thus sucked in the area 7 via a suction nozzle 11 and then ejected when exceeding the top dead center and the reduction of the delivery volume in the area 9 via an outlet valve 13. Now, if the delivery volume is reduced by turning back such a vacuum pump in the area 7 and the wing is pushed back, so can the thereby pushed back residual oil, which can escape only in the intake, lead to damage or even the destruction of the pump, as in the intake a check valve blocks in this direction and the residual oil can thereby lead to high pressure peaks.

Im Stand der Technik wird deshalb ein zusätzliches Ventil 15 angeordnet, welches beim Rückwärtsdrehen zum Zylinderkopf hin öffnet und dabei das Restöl in diesen Bereich ablassen kann, also analog, wie sich normalerweise das Austrittsventil 13 bei normaler Förderrichtung 5 verhält. Bei normaler Drehrichtung bleibt das Austrittsventil 15 für das Restöl geschlossen, da sich im Bereich 7 Unterdruck aufbaut und deswegen der Atmosphärendruck im Zylinderkopf das Zungenventil 15 geschlossen hält. Vorzugsweise ist das Ventil 15 für den Rückwärtslauf mit dem Pumpenaustrittsventil 13 kombiniert, so dass ein Federblechventil zwei Zungen aufweist und mit einer Schraube 17 gesichert ist.In the prior art, therefore, an additional valve 15 is arranged, which opens during reverse rotation to the cylinder head and thereby can drain the residual oil in this area, that is analogous to how normally the outlet valve 13 behaves in normal conveying direction 5. In the normal direction of rotation, the outlet valve 15 remains closed for the residual oil, since builds up in the region 7 negative pressure and therefore the tongue pressure in the cylinder head keeps the reed valve 15 closed. Preferably, the valve 15 for the reverse run is combined with the pump outlet valve 13, so that a spring plate valve has two tongues and is secured with a screw 17.

In Figur 1b sind die entsprechenden Einzelteile der Ventile im demontierten Zustand dargestellt. Die Schraube 17 befestigt den Niederhalter 19 und das Federzungenventil 23 des Pumpenaustrittventils 13 sowie den Niederhalter 21 und die Federzunge 25 des Rückwärtslaufventiles 15. Die Federzunge 23 des Pumpenaustrittventils 13 verschließt im drucklosen Zustand die Pumpenaustrittsöffnung 27, während die Federzunge 25 des Rückwärtslaufventils 15 die Austrittsöffnung 29 bei normaler Drehrichtung der Pumpe verschließt. Somit ist durch eine sehr einfache Kombination des Austrittsventils 13 mit dem Rückwärtslaufventil 15 eine sichere Lösung für die Rückwärtslaufprobleme der Pumpe gegeben, ohne dass zusätzliche Bauteile benötigt werden. Es muss nur der Niederhalter des Austrittsventils um den Bereich 21 verlängert werden sowie die Federzunge 23 des Austrittsventils um den Bereich 25.In FIG. 1b the corresponding individual parts of the valves are shown in disassembled state. The spring 17 secures the pressurized state, the pump outlet opening 27, while the spring tongue 25 of the reverse flow valve 15, the outlet opening 29th The spring tongue 23 of the Pumpenaustrittventils 13 closes the hold-tongue 19 and the spring tongue valve 23 of the pump outlet valve 13 and the spring tongue closes in normal direction of rotation of the pump. Thus, a safe solution for the backward running problems of the pump is given by a very simple combination of the outlet valve 13 with the reverse flow valve 15, without additional components are needed. It is only the hold-down valve of the outlet valve to be extended by the area 21 and the spring tongue 23 of the outlet valve to the area 25th

In Figur 2 ist eine erfindungsgemäße Bypassvorrichtung für das Restöl beim Rückwärtsdrehen in Form einer Schwenkflügelvorrichtung dargestellt. Ein Rotor 30, der hier vereinfacht ohne den Monoflügel dargestellt ist, ist exzentrisch in einem Gehäuse 32 angeordnet. Das Gehäuse 32 hat eine Ausbuchtung 34, in welcher eine Schwenkflügelvorrichtung 36 angeordnet ist. Die Schwenkflügelvorrichtung 36 liegt im Bereich 38 dichtend am Rotor an. Die Drehrichtung des Rotors im Normalbetrieb ist mit dem Pfeil 40 angedeutet. Im Normalbetrieb liegt also der Schwenkflügel dichtend am Rotor an, wobei sich im Bereich 48 die Druckzone der Vakuumpumpe und im Bereich 50 die Saugzone der Vakuumpumpe befindet. Zur sicheren Abdichtung im Schmiegespaltbereich zwischen dem Rotor 30 und dem Gehäuse 32 können über einen Winkelbereich α, hier mit der Bezugsziffer 46 zwischen Gehäuse 32 und Rotor 30 gekennzeichnet, der Rotor und das Gehäuse den annähernd gleichen Krümmungsradius aufweisen, so dass eine gute Schmiegespaltabdichtung auch dann vorhanden ist, wenn der Schwenkflügel bei Rückwärtslauf seine eigentliche Sicherheitsfunktion wahrnimmt. Diese Schmiegespaltabdichtung verhindert auch, dass Druckspitzen den Monoflügel zum Abheben bringen. Bei Rückwärtslauf wird also der Saugbereich 50 plötzlich zum Druckbereich, wobei sich in diesem Bereich dann durch das rückwärtsgedrückte Quetschöl eine Druckspitze aufbauen kann. Diese Druckspitze wird aber dann durch Öffnen des Schwenkflügels 36 in den Bereich 42, welcher mit dem Zylinderkopfbereich verbunden ist, entlastet. Im Bereich 42 herrscht normalerweise der Druck im Zylinderkoptbereich, welcher in etwa dem Atmosphärendruck entspricht. Vorzugsweise wird bei einer Pumpe mit dieser Schwenkflügeleinrichtung ein Monoflügel ohne bewegliche Kappen eingesetzt, weil der Monoflügel dann durch die Fliehkraft immer auf der gegenüberliegenden Seite anliegt und somit keinen Kontakt zum Schwenkflügel 36 aufweist. Der Schwenkflügel 36 selbst kann sowohl durch eine Federkraft 44 als auch durch die Druckkraft des Druckes im Bereich 42 dichtend gegen den Rotor 30 gepresst werden.In FIG. 2 a bypass device according to the invention for the residual oil during reverse rotation is shown in the form of a swing-wing device. A rotor 30, which is shown simplified here without the monoflügel is arranged eccentrically in a housing 32. The housing 32 has a recess 34 in which a pivoting device 36 is arranged. The swing-wing device 36 abuts the rotor 38 in the area 38. The direction of rotation of the rotor in normal operation is with the Arrow 40 indicated. In normal operation, therefore, the pivoting leaf seals against the rotor, wherein the pressure zone of the vacuum pump is in the region 48 and the suction zone of the vacuum pump is in the region 50. For safe sealing in the nip region between the rotor 30 and the housing 32, the rotor and the housing can have an approximately equal radius of curvature over an angular range α, here denoted by the reference number 46 between the housing 32 and the rotor 30, so that a good Schmiegespaltabdichtung even then is present when the swinging wing performs its real safety function in reverse. This crevice seal also prevents pressure spikes from lifting the mono wing. In reverse, so the suction area 50 is suddenly the pressure range, which can then build a pressure peak in this area by the reverse crushed squeeze oil. However, this pressure peak is then relieved by opening the pivoting vane 36 in the area 42 which is connected to the cylinder head area. In region 42, the pressure in the cylinder head region, which corresponds approximately to the atmospheric pressure, normally prevails. Preferably, a monoflügel is used without moving caps in a pump with this swing-wing device, because the monoflügel then always rests by the centrifugal force on the opposite side and thus has no contact with the swing wing 36. The pivoting blade 36 itself can be pressed against the rotor 30 in a sealing manner by a spring force 44 as well as by the pressure force of the pressure in the region 42.

In Figur 3 ist als bekannte Rückwärtslauf-Entlastungsvorrichtung eine Bypassnut 54 auf der Rückseite 52 des Pumpengehäuses 3 dargestellt. Die Bypassnut 54 ist im Saugbereich der Pumpe und damit im Bereich des Saugstutzens 11 angeordnet. Gegenüberliegend befindet sich die Auslassöffnung 56 des Auslassventils, wenn die Pumpe in der normalen Drehrichtung 40 gedreht wird. Läuft die Pumpe beim Rückwärtsdrehen des Verbrennungsmotors anders herum, so kann durch die Bypassnut 54 das Quetschöl seitlich am Flügel vorbei nach hinten verdrängt werden und dadurch der Aufbau von Druckspitzen vermieden werden.In FIG. 3 is shown as a known reverse-flow relief device, a bypass groove 54 on the back 52 of the pump housing 3. The bypass groove 54 is arranged in the suction region of the pump and thus in the region of the suction nozzle 11. Opposite is the outlet opening 56 of the outlet valve when the pump is rotated in the normal direction of rotation 40. Runs the pump when reversing the engine the other way round, so the squeezing oil can be displaced by the bypass groove 54 laterally past the wing to the rear, thereby avoiding the build-up of pressure peaks.

Claims (4)

  1. Vacuum vane cell pump for brake boosters for motor vehicles, wherein the pump has a housing (32) and a rotor (30) which in normal operating mode is driven by a vehicle combustion engine in one direction of rotation ("forwards"), with a device for preventing damage during reverse rotation, with an area (48) of a pressure zone and an area (50) of a suction zone, characterised in that a swivel vane device is mounted in a region (38) of the housing (32) between the area (48) of the pressure zone and the area (50) of the suction zone and has a bulge (34) in the housing (32) and a swivel vane (36) which in normal operating mode sealingly adjoins the rotor in the direction of rotation (40) of the rotor (30) wherein during reverse rotation residual oil present in the pump is forced into a volume in an area (42) inside the bulge (34) of the housing (32) in that during reverse running by opening the swivel vane (36) into the area (42) a pressure peak is relieved through the squeezed oil which is pushed backwards.
  2. Vacuum vane cell pump according to claim 1 characterised in that the swivel vane (36) is pressed sealingly against the rotor (30) by spring force of a spring (44) and/or by the compressive force of the pressure in the area (42).
  3. Vacuum vane cell pump according to claim 1 or claim 2 characterised in that in a lubricating gap area between the rotor (30) and the housing (32) over an angular area a (46) the rotor (30) and the housing (32) have approximately the same radius of curvature so that a good lubricating gap seal is also then present when the swivel vane adopts its actual safety function during reverse running.
  4. Vacuum vane cell pump according to claim 1 or 2 or 3 characterised in that the area (42) is connected to a cylinder head area in which more or less atmospheric pressure prevails.
EP07022290A 2002-11-13 2003-11-12 Vacuum pump Expired - Lifetime EP1890040B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10252769 2002-11-13
EP03779691A EP1563190A2 (en) 2002-11-13 2003-11-12 Vacuum pump

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP03779691.9 Division 2003-11-12
EP03779691A Division EP1563190A2 (en) 2002-11-13 2003-11-12 Vacuum pump

Publications (3)

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EP1890040A2 EP1890040A2 (en) 2008-02-20
EP1890040A3 EP1890040A3 (en) 2008-02-27
EP1890040B1 true EP1890040B1 (en) 2012-06-27

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ID=32308526

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EP03779691A Withdrawn EP1563190A2 (en) 2002-11-13 2003-11-12 Vacuum pump
EP07022290A Expired - Lifetime EP1890040B1 (en) 2002-11-13 2003-11-12 Vacuum pump

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EP03779691A Withdrawn EP1563190A2 (en) 2002-11-13 2003-11-12 Vacuum pump

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EP (2) EP1563190A2 (en)
AU (1) AU2003287863A1 (en)
DE (1) DE10393279D2 (en)
WO (1) WO2004044431A2 (en)

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US8469684B2 (en) 2005-07-07 2013-06-25 Oerlikon Leybold Vacuum Gmbh Rotary vacuum pump with a discharge compensating channel
US11306718B2 (en) 2016-11-03 2022-04-19 Taiho Kogyo Co., Ltd. Vane pump
US11346343B2 (en) 2016-11-03 2022-05-31 Taiho Kogyo Co., Ltd. Vane pump including pressure relief groove

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Publication number Priority date Publication date Assignee Title
US8469684B2 (en) 2005-07-07 2013-06-25 Oerlikon Leybold Vacuum Gmbh Rotary vacuum pump with a discharge compensating channel
US9017051B2 (en) 2005-07-07 2015-04-28 Oerlikon Leybold Vacuum Gmbh Rotary vacuum pump with a discharge compensating channel
US11306718B2 (en) 2016-11-03 2022-04-19 Taiho Kogyo Co., Ltd. Vane pump
US11346343B2 (en) 2016-11-03 2022-05-31 Taiho Kogyo Co., Ltd. Vane pump including pressure relief groove

Also Published As

Publication number Publication date
WO2004044431A2 (en) 2004-05-27
AU2003287863A8 (en) 2004-06-03
WO2004044431A3 (en) 2004-09-16
EP1890040A3 (en) 2008-02-27
EP1890040A2 (en) 2008-02-20
AU2003287863A1 (en) 2004-06-03
EP1563190A2 (en) 2005-08-17
DE10393279D2 (en) 2005-06-02

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