EP0517014B1 - Lubrication gear pump for internal combustion engines, especially for vehicles - Google Patents

Lubrication gear pump for internal combustion engines, especially for vehicles Download PDF

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Publication number
EP0517014B1
EP0517014B1 EP92108169A EP92108169A EP0517014B1 EP 0517014 B1 EP0517014 B1 EP 0517014B1 EP 92108169 A EP92108169 A EP 92108169A EP 92108169 A EP92108169 A EP 92108169A EP 0517014 B1 EP0517014 B1 EP 0517014B1
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EP
European Patent Office
Prior art keywords
pump
set forth
pump housing
crankshaft
outer rotor
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
EP92108169A
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German (de)
French (fr)
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EP0517014A1 (en
Inventor
Kurt Hoffmann
Franz Maucher
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.)
Schwaebische Huettenwerke Automotive GmbH
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Schwaebische Huettenwerke Automotive GmbH
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Publication of EP0517014A1 publication Critical patent/EP0517014A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00

Definitions

  • the invention relates to a gear pump for oil for an internal combustion engine, in particular for motor vehicles, with the features which are listed in the preamble of claim 1, such oil pumps are known from DE-A-3 603 773 and US-A-4 827 881.
  • gear pumps are used in various technical areas.
  • gear pumps according to the preamble of claim 1 are increasingly used for internal combustion engines, in particular motor vehicle internal combustion engines, mostly for piston engines.
  • the crankshaft is extended at its free end in order to drive the inner rotor or the outer rotor.
  • the inner rotor or the driven outer rotor can be driven directly by the free end of the crankshaft.
  • embodiments are also known in which the inner rotor can be found on a separate bearing collar formed in the housing of the pump. The collar is penetrated by the crankshaft and driven by a driver.
  • the flow direction in a feed channel is approximately tangential to the central circumferential direction of the pump gearwheels in the so-called suction kidney region. Accordingly, the projection of the direction of flow in the feed channel at the beginning of the area in which it merges with the suction kidneys, i.e. in the area of the inlet opening of the working chamber, on a normal plane to the pump axis has a direction which is in line with the direction of movement of the teeth of the inner rotor or of the outer rotor this area coincides.
  • the feed channel which at the connection of the oil suction pipe can have the same circular cross section as the oil suction pipe, extends with a tapering circular cross section at the beginning of the suction kidney.
  • the oil supply duct runs partly in front of the end wall of the working chamber and partly over the circumferential surface of the Chamber of Labor.
  • the oil flow not only flows around the end face of the outer rotor, but also a part of the circumferential surface of the outer rotor.
  • the suction kidney ie the area of the opening of the working chamber, also extends over the end wall and its circumference.
  • suction kidney in which the oil flow no longer comes into contact with the peripheral surface of the outer rotor.
  • the arrangement of the suction kidneys is only provided in one end wall of the working chamber.
  • gear pumps or internal rotor gear pumps for oil for motor vehicle internal combustion engines are unanimously known from the prior art, which are provided as separate pumps and must also be driven separately.
  • the present invention is intended to solve the problem of remedying the disadvantages of the prior art and, in particular, of proposing a space-saving and simple solution for a gear pump for oil for internal combustion engines.
  • the gear pump is arranged in a drive wheel provided on the motor or in a deflection roller provided there.
  • the pump wheels provided for the actual pumping process or the pump wheel provided for this purpose are actuated via the Motor driven drive wheel or the existing deflection roller.
  • the camshaft or the crankshaft of the internal combustion engine can be used to drive the drive wheel.
  • a deflection roller present on the motor, which is used according to the invention for receiving the pump according to the invention, can be set in motion via a toothed belt, a chain or a pinion.
  • a compensation plate can be provided in the drive wheel, which is connected to the drive shaft.
  • the compensation plate should be arranged between the drive wheel and the pump wheels or the pump housing.
  • a guide device should be provided, which is designed, for example, in the form of a cylindrical pin. So that the existing compensation plate is in permanent contact has to the conveying pump wheels, a spring device is provided which biases the compensation plate against the pump wheels or presses against them. In this way, a constant delivery volume can be guaranteed regardless of the axial movement of the drive shaft. If this were not available, pressure fluctuations would result or the delivery pressure would even completely collapse at times.
  • one of the pump wheels could also be designed according to the function of the compensation plate.
  • the camshaft or crankshaft should be sealed off from the drive wheel by means of a seal, in particular an O-ring seal. This prevents oil losses.
  • An air gap should be provided between the camshaft or crankshaft and the pump housing and in particular the compensation plate, in which the drive shaft can rotate freely.
  • the pump according to the invention is provided in a deflection roller provided on the internal combustion engine, then at least the outer rotor should be firmly connected to the deflection roller.
  • the outer rotor can be pressed into the deflection roller.
  • the outer rotor meshes with the inner rotor and can interact with it in the manner of a so-called Eaton pump.
  • the inner rotor should be slidably mounted on the pump housing so that it can perform the required rotational movements.
  • the guide roller is held on the motor by means of a bearing pin.
  • the bearing pin is held or supported on the motor by a ball bearing.
  • Another bearing, in particular a needle bearing, is provided between the pump housing and the bearing pin.
  • This embodiment has the advantages that an outer rotor slide bearing is completely eliminated, since the bearing can be taken over by the roller bearing bearing pin via the deflection roller. With this, friction power reductions of approximately 50% can be achieved. In addition, the outer rotor is only braked on one side via an axial friction surface.
  • a seal is provided between the drive wheel or the deflection roller and the pump housing. Shaft seals are usually used for this.
  • the gear pump according to the invention is driven externally parasitically.
  • the force transmission takes place via the camshaft or the crankshaft to the drive wheel and from there via existing guide devices, for example cylindrical pins, to the outer rotor.
  • the power transmission is taken over by a drive shaft which is extended or provided especially for the pump.
  • the drive path is analogous, but in a slightly modified form, since no forces are transmitted via the bearing pin and the outer rotor can be firmly clamped into the drive wheel.
  • the gear pump for oil according to the invention for an internal combustion engine is generally identified by reference number 10.
  • an internal combustion engine is provided, to which the pump according to the invention is fastened by means of fastening means 32, for example screws, rivets or bolts.
  • the crankshaft 20 protrudes from the internal combustion engine 8, to which the drive wheel 12 is fastened by means of a screw 36.
  • a washer or a spring washer 26 can be provided between the screw 36 and the drive wheel 12.
  • the crankshaft 20 is sealed off from the drive wheel 12 via an O-ring seal 28.
  • teeth 30 are provided on the outer circumference of the drive wheel 12, via which teeth, for example, a toothed belt can be driven.
  • An air gap 38 is between the crankshaft 20 and one Pump housing 14 provided. In this way, the crankshaft 20 can rotate freely within the pump housing, which is firmly connected to the engine block.
  • a shaft seal 34 seals the pump housing 14 from the drive wheel 12.
  • a compensation plate 60 is provided to compensate for the axial movement of the crankshaft 20. This is provided between the drive wheel 12 and the outer rotor 18, the inner rotor 16 and the pump housing 14.
  • the inner rotor 16 is generally freely rotatable.
  • the compensation plate makes the movements of the crankshaft 20 coaxial with it.
  • the compensation plate is guided on guide devices 24, in the present case cylindrical pins 24, which is at least partially displaceably held in the adjacent components.
  • the outer rotor 18 is driven via said cylinder pins 24, with which the outer rotor 18 is connected in a rotationally fixed manner to the drive wheel 12.
  • the compensation plate 60 is permanently held in contact with the pump wheels 16, 18 by a spring device 22.
  • the outer rotor 18 meshes with the inner rotor 16 and interacts with it in the manner of an Eaton pump.
  • the crankshaft 20 drives the drive wheel 12, which in turn rotates the outer rotor 18 via the cylinder pins 24.
  • the inner rotor 18 could be provided with a ridge or a groove, which have a corresponding counterpart in the drive wheel 12.
  • the outer rotor 18 takes the inner rotor 16 with it through its toothing.
  • the cross section shown in FIG. 2 through the gear pump 10 shows the inlet or outlet opening 40, 42 through which the oil to be pumped is sucked in or pushed out.
  • the fastening parts 32 to recognize.
  • the crankshaft 20 or the screw 36 holding the drive wheel 12 is provided centrally.
  • the rotary movement is indicated by arrow 6 and runs in a clockwise direction.
  • FIG. 3 shows an analog representation of the features depicted in FIG. 2.
  • FIG. 4 shows the same features as the embodiment according to FIG. 1, the reference numerals from FIG. 1 being added to 100.
  • a camshaft 121 is provided, which is generally smaller in diameter than a crankshaft.
  • the oil to be conveyed is introduced or sucked into the pump according to the invention via an inlet opening 142 and is conveyed between the outer rotor 118 equipped with a varying inner diameter and the inner rotor 116 to the pressure or outlet opening 140.
  • the pressures that can be achieved are between 1 and 5 bar, but can be further influenced by constructive measures. Both the achievable pressure and the delivery rate depend on the speed. As a rule, the delivery pressure that can be achieved falls with decreasing speed. In contrast, the oil flow increases with speed.
  • the necessary amounts of oil can be achieved by different types of wheelsets.
  • the above-mentioned performance values of the pump according to the invention also result in remarkable reductions in the friction losses, so that there are outstanding advantages.
  • FIG. 5 shows a cross section through the embodiment according to FIG. 4.
  • the suction or pressure openings are indicated by the reference numerals 140, 142.
  • the embodiment 100 in question also conveys in the direction of arrow 106 in the clockwise direction.
  • FIG. 6 shows the same features as FIG. 5, but in a different sectional plane.
  • FIG. 7 shows the embodiment in which the pump according to the invention is driven by means of an existing deflecting roller 212 which is provided with external teeth 230.
  • the illustrated embodiment 200 has a pump housing 214, which can be made of aluminum.
  • An inner rotor 216 which advantageously consists of a sintered material, slides directly on the pump housing 214.
  • a bearing pin 254 Within the pump housing 214, a bearing pin 254, guided by a needle bearing 258, is guided.
  • the bearing pin 254 is rotatably supported on the motor block 208 via the pump housing 214 and a ball bearing 256 located between them.
  • the pump housing is connected to the motor block 208 via fastening means 232, namely a cylinder screw.
  • a seal 234 is arranged between the deflection roller 212 and the pump housing 214, a shaft sealing ring generally being used.
  • the outer rotor 218 is pressed into the deflection roller 212.
  • the suction opening is provided in the right half of FIG. 7, while the pressure opening can be seen in the left half of the section.
  • the friction losses compared to the known gear pumps are considerable, i.e. by about 60%.
  • the bearing of the deflection roller 212 over the roller-mounted bearing pin 254 results in a reduction of the required friction by 50%.
  • the lower axial friction surface which only engages on one side on the outer rotor and the positively changed relative speed between the inner rotor and the deflection pulley 212, result in further savings in friction, so that overall a 60% more favorable power consumption situation results than in the prior art.
  • Corresponding advantages can also arise for the embodiments 10, 100.
  • FIG 8 and 9 show cross sections through embodiment 200, from which the suction and pressure feeds and the associated compression and decompression spaces can be seen.
  • suction kidney shapes reference is made to the introduction to the description.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

The invention relates to a lubrication gear pump for an internal combustion engine, especially for motorised vehicles, having a pump casing attached to the engine and also having an external rotor which is arranged in the pump casing, in addition an internal rotor being arranged inside the external rotor or inside the pump casing, and at least one suction duct and/or at least one discharge duct being provided in the pump casing, and a drive also being provided, according to the invention the pump being integrated in a pinion or a pulley of the combustion engine, and the external rotor or external rotors being driven by the pinion or the pulley. <IMAGE>

Description

Die Erfindung betrifft eine Zahnradpumpe für Öl für einen Verbrennungsmotor, insbesondere für Kraftfahrzeuge, mit den Merkmalen, die im Oberbegriff des Patentanspruchs 1 aufgeführt sind, solche Ölpumpen sind durch DE-A-3 603 773 bzw US-A-4 827 881 bekannt.The invention relates to a gear pump for oil for an internal combustion engine, in particular for motor vehicles, with the features which are listed in the preamble of claim 1, such oil pumps are known from DE-A-3 603 773 and US-A-4 827 881.

Gattungsgemäße Pumpen werden auf verschiedensten technischen Bereichen eingesetzt. Allerdings werden Zahnradpumpen gemäß dem Oberbegriff des Patentanspruchs 1 in zunehmendem Maße für Verbrennungsmotoren, insbesondere Kraftfahrzeugverbrennungsmotoren, meist für Kolbenmotoren, eingesetzt. Zu diesem Zweck wird die Kurbelwelle an ihrem freien Ende verlängert, um den Innenrotor bzw. den Außenrotor anzutreiben. Der Innenrotor bzw. der angetriebene Außenrotor kann unmittelbar von dem freien Ende der Kurbelwelle angetrieben werden. Bekannt sind jedoch auch Ausführungsformen, bei denen an einem gesonderten, im Gehäuse der Pumpe ausgebildeten Lagerkragen der Innenrotor zu finden ist. Der Kragen wird von der Kurbelwelle durchsetzt und über einen Mitnehmer angetrieben.Generic pumps are used in various technical areas. However, gear pumps according to the preamble of claim 1 are increasingly used for internal combustion engines, in particular motor vehicle internal combustion engines, mostly for piston engines. For this purpose, the crankshaft is extended at its free end in order to drive the inner rotor or the outer rotor. The inner rotor or the driven outer rotor can be driven directly by the free end of the crankshaft. However, embodiments are also known in which the inner rotor can be found on a separate bearing collar formed in the housing of the pump. The collar is penetrated by the crankshaft and driven by a driver.

Wie es auch bei der Pumpe gemäß der vorliegenden Erfindung sein kann, verläuft die Strömungsrichtung in einem Zuführkanal zur mittleren Umfangsrichtung der Pumpenzahnräder im sogenannten Saugnierenbereich angenähert tangential. Demnach hat die Projektion der Strömungsrichtung im Zuführkanal zu Beginn des Bereichs, in dem dieser in die Saugnieren übergeht, also im Bereich der Einlaßöffnung der Arbeitskammer, auf eine Normalebene zur Pumpenachse eine Richtung, die mit der Bewegungsrichtung der Zähne des Innenrotors bzw. des Außenrotors in diesem Bereich etwa zusammenfällt.As can also be the case with the pump according to the present invention, the flow direction in a feed channel is approximately tangential to the central circumferential direction of the pump gearwheels in the so-called suction kidney region. Accordingly, the projection of the direction of flow in the feed channel at the beginning of the area in which it merges with the suction kidneys, i.e. in the area of the inlet opening of the working chamber, on a normal plane to the pump axis has a direction which is in line with the direction of movement of the teeth of the inner rotor or of the outer rotor this area coincides.

Bei den bekannten Ölpumpen, wie es auch bei der Pumpe gemäß der vorliegenden Erfindung möglich ist, erstreckt sich der Zuführkanal, der am Anschluß des Ölsaugrohres den gleichen Kreisquerschnitt wie das Ölsaugrohr aufweisen kann, mit sich verjüngendem Kreisquerschnitt zum Beginn der Saugniere. Der Ölzuführkanal verläuft von da ab zum Teil vor der Stirnwand der Arbeitskammer und zum Teil über der Umfangsfläche der Arbeitskammer. So umfließt der Ölstrom nicht nur die Stirnfläche des Außenrotors, sondern auch einen Teil der Umfangsfläche des Außenrotors. Die Saugniere, also der Bereich der Öffnung der Arbeitskammer, erstreckt sich ebenfalls über die Stirnwand und deren Umfang.In the known oil pumps, as is also possible with the pump according to the present invention, the feed channel, which at the connection of the oil suction pipe can have the same circular cross section as the oil suction pipe, extends with a tapering circular cross section at the beginning of the suction kidney. From there, the oil supply duct runs partly in front of the end wall of the working chamber and partly over the circumferential surface of the Chamber of Labor. The oil flow not only flows around the end face of the outer rotor, but also a part of the circumferential surface of the outer rotor. The suction kidney, ie the area of the opening of the working chamber, also extends over the end wall and its circumference.

Andererseits ist es möglich, eine Ausbildung für die Saugniere zu wählen, bei der der Ölstrom mit der Umfangsfläche des Außenrotors nicht mehr in Berührung kommt. Dabei ist die Anordnung der Saugniere nur in einer Stirnwand der Arbeitskammer vorgesehen.On the other hand, it is possible to choose a design for the suction kidney in which the oil flow no longer comes into contact with the peripheral surface of the outer rotor. The arrangement of the suction kidneys is only provided in one end wall of the working chamber.

Aus dem Stand der Technik sind jedoch einhellig nur Zahnradpumpen bzw. Innenläuferzahnradpumpen für Öl für Kraftfahrzeug-Verbrennungsmotoren bekannt, die als separate Pumpen vorgesehen sind und auch separat angetrieben werden müssen.However, only gear pumps or internal rotor gear pumps for oil for motor vehicle internal combustion engines are unanimously known from the prior art, which are provided as separate pumps and must also be driven separately.

Damit einhergehend ist jedoch verbunden, daß von dem mit den bekannten Pumpen verbundenen Motoren eine Antriebsenergie abgezweigt werden muß, womit Leistungsverluste verbunden sind. Auch zusätzlicher Platz für die Ölpumpen muß vorgesehen werden.Associated with this, however, is the fact that drive energy has to be diverted from the motors connected to the known pumps, with which power losses are associated. Additional space for the oil pumps must also be provided.

Durch die vorliegende Erfindung soll das Problem gelöst werden, den Nachteilen des Standes der Technik abzuhelfen und insbesondere eine platzsparende und einfache Lösung für eine Zahnradpumpe für Öl für Verbrennungsmotoren vorzuschlagen.The present invention is intended to solve the problem of remedying the disadvantages of the prior art and, in particular, of proposing a space-saving and simple solution for a gear pump for oil for internal combustion engines.

Diese Aufgabe wird durch die Merkmale des Patentanspruchs 1 gelöst. Zweckmäßige Ausgestaltungen ergeben sich aus den Merkmalen, die in den Unteransprüchen aufgeführt sind.This object is achieved by the features of patent claim 1. Appropriate configurations result from the features that are listed in the subclaims.

Erfindungsgemäß ist vorgesehen, daß die Zahnradpumpe in einem am Motor vorhandenen Antriebsrad bzw. einer dort vorhandenen Umlenkrolle angeordnet wird. Dabei werden die für den eigentlichen Pumpvorgang vorgesehenen Pumpenräder bzw. das dafür vorgesehene Pumpenrad über das am Motor jedenfalls vorhandene Antriebsrad bzw. die jedenfalls vorhandene Umlenkrolle angetrieben.According to the invention it is provided that the gear pump is arranged in a drive wheel provided on the motor or in a deflection roller provided there. The pump wheels provided for the actual pumping process or the pump wheel provided for this purpose are actuated via the Motor driven drive wheel or the existing deflection roller.

Durch die Integration der erfindungsgemäßen Zahnradpumpe in einem am Motor bereits vorhandenen Antriebsrad bzw. in einer bereits vorhandenen Umlenkrolle ergeben sich, zum Teil im Zusammenhang mit den Merkmalen in den Unteransprüchen, die folgenden Vorteile: Gegebenüber den herkömmlichen Lösungen wird wesentlich weniger Leistung benötigt bzw. es treten geringere Reibungsverluste auf. Zudem wird kein zusätzlicher Bauraum beansprucht, da die erfindungsgemäße Pumpe innerhalb der Umlenkrolle bzw. des Antriebsrades integriert werden kann. Außerdem wird durch den Antrieb über den Außenrotor eine schnellere Übersetzung erzielt, wodurch der Radsatz kleinere Abmessungen aufweisen kann. Damit einher geht eine günstigere Produktion, wobei weniger Einzelteile notwendig sind, und ein geringerer Montageaufwand anfällt.By integrating the gear pump according to the invention in a drive wheel already present on the motor or in an already existing deflection roller, the following advantages result, in part in connection with the features in the subclaims: Given the conventional solutions, significantly less power is required or it there are less friction losses. In addition, no additional installation space is required, since the pump according to the invention can be integrated within the deflection roller or the drive wheel. In addition, a faster translation is achieved by the drive via the outer rotor, which means that the wheel set can have smaller dimensions. This goes hand in hand with cheaper production, fewer parts are required and less assembly work.

Erfindungsgemäß kann für den Antrieb des Antriebsrades die Nockenwelle oder die Kurbelwelle des Verbrennungsmotors eingesetzt werden. Eine am Motor vorhandene Umlenkrolle, die erfindungsgemäß für die Aufnahme der erfindungsgemäßen Pumpe verwendet wird, kann über einen Zahnriemen, eine Kette oder ein Ritzel in Bewegung versetzt werden. Um eine notwendige Axialbewegung der Antriebswelle (Nockenwelle oder Kurbelwelle) auszugleichen, kann eine Kompensationsplatte in dem Antriebsrad, das mit der Antriebswelle verbunden ist, vorgesehen werden.According to the invention, the camshaft or the crankshaft of the internal combustion engine can be used to drive the drive wheel. A deflection roller present on the motor, which is used according to the invention for receiving the pump according to the invention, can be set in motion via a toothed belt, a chain or a pinion. In order to compensate for a necessary axial movement of the drive shaft (camshaft or crankshaft), a compensation plate can be provided in the drive wheel, which is connected to the drive shaft.

Die Kompensationsplatte sollte zwischen dem Antriebsrad und den Pumpenrädern bzw. dem Pumpengehäuse angeordnet werden. Um gleichzeitig die Rotation der Kompensationsplatte bzw. des Außenrotors frei zum Antriebsrad zu vermeiden und eine koaxial zur Antriebs- bzw. Kurbelwelle ausgerichtete Bewegung zuzulassen, sollte eine Führungseinrichtung vorgesehen sein, die beispielsweise in Form eines Zylinderstiftes ausgebildet ist. Damit die gegebenenfalls vorhandene Kompensationsplatte permanent Kontakt zu den fördernden Pumpenrädern hat, ist eine Federeinrichtung vorgesehen, die die Kompensationsplatte gegen die Pumpenräder vorspannt bzw. gegen diese preßt. Auf diese Weise kann unabhängig von der Axialbewegung der Antriebswelle ein konstantes Fördervolumen garantiert werden. Wäre dieses nicht vorhanden, würden Druckschwankungen die Folge sein oder der Förderdruck zeitweise sogar vollkommen zusammenbrechen.The compensation plate should be arranged between the drive wheel and the pump wheels or the pump housing. In order to simultaneously avoid the rotation of the compensation plate or the outer rotor relative to the drive wheel and to allow a movement aligned coaxially to the drive or crankshaft, a guide device should be provided, which is designed, for example, in the form of a cylindrical pin. So that the existing compensation plate is in permanent contact has to the conveying pump wheels, a spring device is provided which biases the compensation plate against the pump wheels or presses against them. In this way, a constant delivery volume can be guaranteed regardless of the axial movement of the drive shaft. If this were not available, pressure fluctuations would result or the delivery pressure would even completely collapse at times.

Statt der Kompensationsplatte könnte auch eines der Pumpenräder entsprechend der Funktion der Kompensationsplatte ausgebildet sein.Instead of the compensation plate, one of the pump wheels could also be designed according to the function of the compensation plate.

Die Nocken- bzw. Kurbelwelle sollte mittels einer Dichtung, insbesondere einer O-Ring-Dichtung, gegenüber dem Antriebsrad abgedichtet sein. Hierdurch werden Ölverluste vermieden.The camshaft or crankshaft should be sealed off from the drive wheel by means of a seal, in particular an O-ring seal. This prevents oil losses.

Zwischen der Nocken- bzw. Kurbelwelle und dem Pumpengehäuse sowie insbesondere der Kompensationsplatte sollte ein Luftspalt vorgesehen sein, in dem die Antriebswelle frei rotieren kann.An air gap should be provided between the camshaft or crankshaft and the pump housing and in particular the compensation plate, in which the drive shaft can rotate freely.

Ist die erfindungsgemäße Pumpe in einer am Verbrennungsmotor vorgesehenen Umlenkrolle vorgesehen, so sollte zumindest der Außenrotor fest mit der Umlenkrolle verbunden sein. Hierzu kann der Außenrotor in die Umlenkrolle eingepreßt sein. Der Außenrotor kämmt mit dem Innenrotor und kann mit diesem nach Art einer sogenannten Eaton-Pumpe zusammenwirken.If the pump according to the invention is provided in a deflection roller provided on the internal combustion engine, then at least the outer rotor should be firmly connected to the deflection roller. For this purpose, the outer rotor can be pressed into the deflection roller. The outer rotor meshes with the inner rotor and can interact with it in the manner of a so-called Eaton pump.

Demgegenüber sollte der Innenrotor auf dem Pumpengehäuse gleitend angeordnet sein, so daß es die erforderlichen Rotationsbewegungen ausführen kann.In contrast, the inner rotor should be slidably mounted on the pump housing so that it can perform the required rotational movements.

Die Umlenkrolle wird über einen Lagerbolzen am Motor gehaltert. Der Lagerbolzen ist demgegenüber durch ein Kugellager am Motor gehaltert bzw. gelagert. Zwischen dem Pumpengehäuse und dem Lagerbolzen ist ein weiteres Lager, insbesondere ein Nadellager, vorgesehen.The guide roller is held on the motor by means of a bearing pin. In contrast, the bearing pin is held or supported on the motor by a ball bearing. Another bearing, in particular a needle bearing, is provided between the pump housing and the bearing pin.

Durch diese Ausführungsform ergeben sich die Vorteile, daß ein Außenrotor-Gleitlager vollkommen entfällt, da die Lagerung über die Umlenkrolle von dem wälzgelagerten Lagerbolzen übernommen werden kann. Damit können Reibleistungsreduzierungen von ungefähr 50 % erzielt werden. Außerdem ist der Außenrotor nur noch einseitig über eine axiale Reibfläche gebremst.This embodiment has the advantages that an outer rotor slide bearing is completely eliminated, since the bearing can be taken over by the roller bearing bearing pin via the deflection roller. With this, friction power reductions of approximately 50% can be achieved. In addition, the outer rotor is only braked on one side via an axial friction surface.

Schließlich ergibt sich an der Anlagefläche von der Umlenkrolle zum Innenrotor noch eine günstige Relativdrehzahl, so daß im Zusammenhang mit den oben aufgeführten, verringerten Reibungsverlusten gegenüber den bekannten Lösungen eine Ersparnis von ungefähr 60 % erzielt werden kann.Finally, a favorable relative speed results on the contact surface from the deflection roller to the inner rotor, so that in connection with the above-mentioned, reduced friction losses compared to the known solutions, savings of approximately 60% can be achieved.

Um die Dichtigkeit der erfindungsgemäßen Pumpe zu sichern, ist zwischen dem Antriebsrad bzw. der Umlenkrolle und dem Pumpengehäuse eine Dichtung vorgesehen. Üblicherweise werden hierfür Wellendichtringe verwendet.In order to ensure the tightness of the pump according to the invention, a seal is provided between the drive wheel or the deflection roller and the pump housing. Shaft seals are usually used for this.

Bei sämtlichen Ausführungsformen wird die erfindungsgemäße Zahnradpumpe extern parasitär angetrieben. Bei der Ausführungsform, die ein Antriebsrad aufweist, erfolgt die Kraftübertragung über die Nockenwelle bzw. die Kurbelwelle auf das Antriebsrad und von dort über vorhandenen Führungseinrichtungen, beispielsweise Zylinderstifte, auf den Außenrotor. Demgegenüber wird beim Stand der Technik die Kraftübertragung von einer Antriebswelle, die extra für die Pumpe verlängert oder vorgesehen ist, übernommen. Bei der Variante mit der Umlenkrolle verläuft der Antriebsweg analog, allerdings in leicht abgewandelter Form, da über den Lagerbolzen keine Kräfte übertragen werden und der Außenrotor in das Antriebsrad fest eingespannt werden kann.In all embodiments, the gear pump according to the invention is driven externally parasitically. In the embodiment which has a drive wheel, the force transmission takes place via the camshaft or the crankshaft to the drive wheel and from there via existing guide devices, for example cylindrical pins, to the outer rotor. In contrast, in the prior art, the power transmission is taken over by a drive shaft which is extended or provided especially for the pump. In the variant with the deflection roller, the drive path is analogous, but in a slightly modified form, since no forces are transmitted via the bearing pin and the outer rotor can be firmly clamped into the drive wheel.

Nachfolgend wird die vorliegende Erfindung an bevorzugten Ausführungsformen näher erläutert. Dabei werden weitere erfindungsgemäße Merkmale und Vorteile der vorliegenden Erfindung offenbart. Es zeigen:

Fig. 1
einen Schnitt axialen durch eine erfindungsgemäße Zahnradpumpe, die in einem Antriebsrad vorgesehen ist;
Fig. 2
einen Querschnitt durch die erfindungsgemäße Pumpe gemäß Fig. 1
Fig. 3
einen Querschnitt durch die erfindungsgemäße Pumpe gemäß Fig. 1 in einer anderen Ebene;
Fig. 4
einen axialen Längsschnitt durch eine weitere Ausführungsform analog zur Ausführungsform gemäß Fig. 1;
Fig. 5
einen Querschnitt durch die Ausführungsform gemäß Fig. 4;
Fig. 6
einen Querschnitt durch die Ausführungsform gemäß Fig. 4 in einer anderen Ebene;
Fig. 7
eine erfindungsgemäße Ausführungsform, die in einer Umlenkrolle angeordnet ist im Längsschnitt;
Fig. 8
einen Querschnitt durch die erfindungsgemäße Ausführungsform gemäß Fig. 7; und
Fig. 9
einen Querschnitt durch die Ausführungsform gemäß Fig. 7 in einer anderen Ebene.
The present invention is explained in more detail below using preferred embodiments. Further features and advantages of the present invention are disclosed. Show it:
Fig. 1
a section axial through a gear pump according to the invention, which is provided in a drive wheel;
Fig. 2
2 shows a cross section through the pump according to the invention according to FIG. 1
Fig. 3
a cross section through the pump according to the invention according to FIG 1 in another plane.
Fig. 4
an axial longitudinal section through a further embodiment analogous to the embodiment of FIG. 1;
Fig. 5
a cross section through the embodiment of FIG. 4;
Fig. 6
a cross section through the embodiment of FIG 4 in another plane.
Fig. 7
an embodiment of the invention, which is arranged in a guide roller in longitudinal section;
Fig. 8
a cross section through the embodiment of the invention according to FIG. 7; and
Fig. 9
a cross section through the embodiment of FIG. 7 in another plane.

In Fig. 1 ist die erfindungsgemäße Zahnradpumpe für Öl für einen Verbrennungsmotor, insbesondere für Kraftfahrzeuge, allgemein durch das Bezugszeichen 10 gekennzeichnet. Im Bereich 8 ist ein Verbrennungsmotor vorgesehen, an dem die erfindungsgemäße Pumpe über Befestigungsmittel 32, z.B. Schrauben, Nieten oder Bolzen, befestigt ist. Aus dem Verbrennungsmotor 8 ragt die Kurbelwelle 20 heraus, an dem das Antriebsrad 12 über eine Schraube 36 befestigt ist. Zwischen der Schraube 36 und dem Antriebsrad 12 kann eine Unterlegescheibe bzw. ein Federring 26 vorgesehen sein. Die Kurbelwelle 20 ist gegenüber dem Antriebsrad 12 über eine O-Ring-Dichtung 28 abgedichtet. Am Außenumfang des Antriebsrades 12 sind in der Regel Zähne 30 vorgesehen, über die beispielsweise ein Zahnriemen angetrieben werden kann. Ein Luftspalt 38 ist zwischen der Kurbelwelle 20 und einem Pumpengehäuse 14 vorgesehen. Auf diese Weise kann die Kurbelwelle 20 frei innerhalb des Pumpengehäuses, das fest mit dem Motorblock verbunden ist, rotieren.In Fig. 1, the gear pump for oil according to the invention for an internal combustion engine, in particular for motor vehicles, is generally identified by reference number 10. In area 8, an internal combustion engine is provided, to which the pump according to the invention is fastened by means of fastening means 32, for example screws, rivets or bolts. The crankshaft 20 protrudes from the internal combustion engine 8, to which the drive wheel 12 is fastened by means of a screw 36. A washer or a spring washer 26 can be provided between the screw 36 and the drive wheel 12. The crankshaft 20 is sealed off from the drive wheel 12 via an O-ring seal 28. As a rule, teeth 30 are provided on the outer circumference of the drive wheel 12, via which teeth, for example, a toothed belt can be driven. An air gap 38 is between the crankshaft 20 and one Pump housing 14 provided. In this way, the crankshaft 20 can rotate freely within the pump housing, which is firmly connected to the engine block.

In der Längsschnittdarstellung ist die Saug- bzw. Drucköffnung der erfindungsgemäßen Zahnradpumpe zu erkennen. Eine Wellendichtung 34 dichtet das Pumpengehäuse 14 gegenüber dem Antriebsrad 12 ab.The suction or pressure opening of the gear pump according to the invention can be seen in the longitudinal section. A shaft seal 34 seals the pump housing 14 from the drive wheel 12.

Zum Ausgleich der Axialbewegung der Kurbelwelle 20 ist eine Kompensationsplatte 60 vorgesehen. Diese ist zwischen dem Antriebsrad 12 und dem Außenrotor 18, dem Innenrotor 16 sowie dem Pumpengehäuse 14 vorgesehen. Der Innenrotor 16 ist in der Regel frei drehbar gelagert. Die Kompensationsplatte macht die Bewegungen der Kurbelwelle 20 koaxial zu dieser mit. Dabei wird die Kompensationsplatte auf Führungsvorrichtungen 24, im vorliegenden Falle Zylinderstiften 24, geführt, die in den angrenzenden Bauteilen zumindest zum Teil verschieblich gehaltert ist. Angetrieben wird der Außenrotor 18 über die besagten Zylinderstifte 24, mit denen der Außenrotor 18 drehfest mit dem Antriebsrad 12 verbunden ist. Die Kompensationsplatte 60 wird durch eine Federvorrichtung 22 permanent im Kontakt zu den Pumpenrädern 16, 18 gehalten.A compensation plate 60 is provided to compensate for the axial movement of the crankshaft 20. This is provided between the drive wheel 12 and the outer rotor 18, the inner rotor 16 and the pump housing 14. The inner rotor 16 is generally freely rotatable. The compensation plate makes the movements of the crankshaft 20 coaxial with it. The compensation plate is guided on guide devices 24, in the present case cylindrical pins 24, which is at least partially displaceably held in the adjacent components. The outer rotor 18 is driven via said cylinder pins 24, with which the outer rotor 18 is connected in a rotationally fixed manner to the drive wheel 12. The compensation plate 60 is permanently held in contact with the pump wheels 16, 18 by a spring device 22.

Der Außenrotor 18 kämmt mit dem Innenrotor 16 und wirkt mit diesem nach Art einer Eaton-Pumpe zusammen.The outer rotor 18 meshes with the inner rotor 16 and interacts with it in the manner of an Eaton pump.

Bei der vorliegenden Ausführungsform ergibt sich folgender Kraftübertragungsweg: Die Kurbelwelle 20 treibt das Antriebsrad 12 an, welches wiederum über die Zylinderstifte 24 den Außenrotor 18 dreht. Statt der Zylinderstifte 24 könnte der Innenrotor 18 mit einem Grat oder einer Nut versehen sein, die ein entsprechendes Pendant in dem Antriebsrad 12 haben. Der Außenrotor 18 nimmt über seine Verzahnung den Innenrotor 16 mit.In the present embodiment, the following power transmission path results: The crankshaft 20 drives the drive wheel 12, which in turn rotates the outer rotor 18 via the cylinder pins 24. Instead of the cylindrical pins 24, the inner rotor 18 could be provided with a ridge or a groove, which have a corresponding counterpart in the drive wheel 12. The outer rotor 18 takes the inner rotor 16 with it through its toothing.

Der aus Fig. 2 ersichtliche Querschnitt durch die Zahnradpumpe 10 zeigt die Einlaß- bzw. Auslaßöffnung 40, 42, durch die das zu fördernde Öl angesaugt bzw. herausgedrückt wird. Außerdem sind die Befestigungsteile 32 zu erkennen. Zentral ist die Kurbelwelle 20 bzw. die das Antriebsrad 12 haltende Schraube 36 vorgesehen. Die Drehbewegung ist im vorliegenden Falle durch den Pfeil 6 angedeutet und verläuft im Uhrzeigersinn.The cross section shown in FIG. 2 through the gear pump 10 shows the inlet or outlet opening 40, 42 through which the oil to be pumped is sucked in or pushed out. In addition, the fastening parts 32 to recognize. The crankshaft 20 or the screw 36 holding the drive wheel 12 is provided centrally. In the present case, the rotary movement is indicated by arrow 6 and runs in a clockwise direction.

Fig. 3 zeigt eine analoge Darstellung der in Fig. 2 abgebildeten Merkmale.FIG. 3 shows an analog representation of the features depicted in FIG. 2.

Die in der Fig. 4 dargestellte Ausführungsform zeigt die gleichen Merkmale wie die Ausführungsform gemäß Fig. 1, wobei die Bezugsziffern von Fig. 1 mit 100 zu addieren sind. Allerdings ist statt der Kurbelwelle 20 (Fig. 1) eine Nockenwelle 121 vorgesehen, die in ihrem Durchmesser in der Regel geringer ausfällt als eine Kurbelwelle. Das zu fördernde Öl wird über eine Einlaßöffnung 142 in die erfindungsgemäße Pumpe eingeführt bzw. angesaugt und wird zwischen dem mit variierendem Innendurchmesser ausgestatteten Außenrotor 118 und dem Innenrotor 116 zur Druck- bzw. Auslaßöffnung 140 gefördert. Die erzielbaren Drücke liegen zwischen 1 und 5 bar, lassen sich jedoch durch konstruktive Maßnahme weiter beeinflussen. Abhängig von der Drehzahl sind sowohl der erzielbare Druck als auch die Fördermenge. In der Regel fällt der erreichbare Förderdruck mit abnehmender Drehzahl. Dagegen wächst die Fördermenge an Öl mit der Drehzahl. Durch unterschiedliche Radsatztypen lassen sich die notwendigen Mengen an Öl erzielen. Bei den oben angegebenen Leistungswerten der erfindungsgemäßen Pumpe ergeben sich zudem bemerkenswerte Reduzierungen der Reibungsverluste, so daß sich damit herausragende Vorteile ergeben.The embodiment shown in FIG. 4 shows the same features as the embodiment according to FIG. 1, the reference numerals from FIG. 1 being added to 100. However, instead of the crankshaft 20 (FIG. 1), a camshaft 121 is provided, which is generally smaller in diameter than a crankshaft. The oil to be conveyed is introduced or sucked into the pump according to the invention via an inlet opening 142 and is conveyed between the outer rotor 118 equipped with a varying inner diameter and the inner rotor 116 to the pressure or outlet opening 140. The pressures that can be achieved are between 1 and 5 bar, but can be further influenced by constructive measures. Both the achievable pressure and the delivery rate depend on the speed. As a rule, the delivery pressure that can be achieved falls with decreasing speed. In contrast, the oil flow increases with speed. The necessary amounts of oil can be achieved by different types of wheelsets. The above-mentioned performance values of the pump according to the invention also result in remarkable reductions in the friction losses, so that there are outstanding advantages.

Aus Fig. 5 ist ein Querschnitt durch die Ausführungsform gemäß Fig. 4 ersichtlich. Darin sind die Saug- bzw. die Drucköffnungen durch die Bezugszeichen 140, 142 angedeutet. Die betreffende Ausführungsform 100 fördert in Richtung des Pfeiles 106 gleichfalls im Uhrzeigersinn. Fig. 6 zeigt die gleichen Merkmale wie Fig. 5, jedoch in einer anderen Schnittebene.5 shows a cross section through the embodiment according to FIG. 4. The suction or pressure openings are indicated by the reference numerals 140, 142. The embodiment 100 in question also conveys in the direction of arrow 106 in the clockwise direction. FIG. 6 shows the same features as FIG. 5, but in a different sectional plane.

Aus Fig. 7 ist die Ausführungsform ersichtlich, bei der die erfindungsgemäße Pumpe mittels einer vorhandenen Umlenkrolle 212 angetrieben wird, die mit einer Außenzahnung 230 versehen ist. Bei der Ausführungsform gemäß Fig. 7, die allgemein durch das Bezugszeichen 200 gekennzeichnet ist, ist demnach keine aus dem Motorblock herausragende Nocken- bzw. Kurbelwelle erforderlich. Die dargestellte Ausführungsform 200 weist ein Pumpengehäuse 214 auf, das aus Aluminium gefertigt sein kann. Ein Innenrotor 216, der vorteilhafterweise aus einem Sintermaterial besteht, gleitet direkt auf dem Pumpengehäuse 214. Innerhalb des Pumpengehäuses 214 ist ein Lagerbolzen 254, gelagert über ein Nadellager 258, geführt. Am Motorblock 208 ist der Lagerbolzen 254 über das Pumpengehäuse 214 und ein dazwischen befindliches Kugellager 256 rotierbar gehaltert. Das Pumpengehäuse ist über Befestigungsmittel 232, nämlich eine Zylinderschraube, mit dem Motorblock 208 verbunden.7 shows the embodiment in which the pump according to the invention is driven by means of an existing deflecting roller 212 which is provided with external teeth 230. In the embodiment according to FIG. 7, which is generally identified by the reference symbol 200 is therefore no cam or crankshaft protruding from the engine block is required. The illustrated embodiment 200 has a pump housing 214, which can be made of aluminum. An inner rotor 216, which advantageously consists of a sintered material, slides directly on the pump housing 214. Within the pump housing 214, a bearing pin 254, guided by a needle bearing 258, is guided. The bearing pin 254 is rotatably supported on the motor block 208 via the pump housing 214 and a ball bearing 256 located between them. The pump housing is connected to the motor block 208 via fastening means 232, namely a cylinder screw.

Zwischen der Umlenkrolle 212 und dem Pumpengehäuse 214 ist eine Dichtung 234 angeordnet, wobei in der Regel ein Wellendichtring Anwendung findet. Der Außenrotor 218 ist in die Umlenkrolle 212 eingepreßt.A seal 234 is arranged between the deflection roller 212 and the pump housing 214, a shaft sealing ring generally being used. The outer rotor 218 is pressed into the deflection roller 212.

In der rechten Schnitthälfte der Fig. 7 ist die Saugöffnung vorgesehen, während in der linken Schnitthälfte die Drucköffnung zu erkennen ist.The suction opening is provided in the right half of FIG. 7, while the pressure opening can be seen in the left half of the section.

Bei der Ausführungsform 200 gemäß Fig. 7 werden die Reibungsverluste gegenüber den bekannten Zahnradpumpen erheblich, d.h. um ca. 60 %, verringert. Durch die Lagerung der Umlenkrolle 212 über den wälzgelagerten Lagerbolzen 254 ergibt sich eine Verringerung der erforderlichen Reibleistung um 50 %. Auch durch die geringere axiale Reibfläche, die nur noch einseitig am Außenrotor angreift und durch die positiv veränderte Relativdrehzahl zwischen dem Innenrotor und der Umlenkrolle 212 ergeben sich weitere Reibleistungsersparnisse, so daß sich insgesamt eine um 60 % günstigere Leistungsaufnahmesituation ergibt als beim Stand der Technik. Entsprechende Vorteile können sich auch für die Ausführungsformen 10, 100 einstellen.In the embodiment 200 according to FIG. 7, the friction losses compared to the known gear pumps are considerable, i.e. by about 60%. The bearing of the deflection roller 212 over the roller-mounted bearing pin 254 results in a reduction of the required friction by 50%. The lower axial friction surface, which only engages on one side on the outer rotor and the positively changed relative speed between the inner rotor and the deflection pulley 212, result in further savings in friction, so that overall a 60% more favorable power consumption situation results than in the prior art. Corresponding advantages can also arise for the embodiments 10, 100.

Aus den Fig. 8 und 9 ergeben sich Querschnitte durch die Ausführungsform 200, aus denen die Saug- und Druckzuführungen und die zugehörigen Kompressions- und Dekompressionsräume ersichtlich sind. Im Hinblick auf mögliche Saugnierenformen wird auf die Beschreibungseinleitung verwiesen.8 and 9 show cross sections through embodiment 200, from which the suction and pressure feeds and the associated compression and decompression spaces can be seen. With regard to possible suction kidney shapes, reference is made to the introduction to the description.

Claims (15)

  1. A gear pump for oil for an internal-combustion engine, particularly for motor vehicles, comprising
    a) a pump housing secured to the engine;
    b) an outer rotor arranged in the pump housing;
    c) an inner rotor arranged in the outer rotor or the pump housing;
    d) at least one suction passage and/or at least one pressure passage in the pump housing; and
    e) a drive
    characterized by the following features:
    f) said pump (10, 100, 200) is arranged in a drive gear (12, 112) or a guide pulley (212) of the internal-combustion engine (8, 108, 208) ; and
    g) said outer rotor (18, 118, 218) or said inner rotor (16, 116, 216) via said outer rotor (18, 118, 218) is driven by said drive gear (12, 112) or said guide pulley (212), which are driven via a camshaft (120) or a crankshaft (20) of the internal-combustion engine (8, 108).
  2. The pump as set forth in claim 1, characterized in that said guide pulley (212) is driven via a toothed belt or a chain.
  3. The pump as set forth in claim 1, characterized in that a compensation plate (60, 160) is provided which is preferably arranged between said drive gear (12, 112) and the pump gears or the pump housing (14, 114) .
  4. The pump as set forth in claim 3, characterized in that at least one guide means (24, 124) is provided which guides said compensation plate (60, 160) coaxially with respect to the drive shaft or crankshaft (20, 120) and prevents it from rotating.
  5. The pump as set forth in claim 4, characterized in that said guide means (24, 124) is/are mounted or guided in one of said outer rotors (18, 118) and/or said drive gear (12, 112).
  6. The pump as set forth in any of the claims 1 and/or 3 to 5, characterized in that said camshaft or crankshaft (20, 120) is sealed by means of a seal (28, 128), particularly by an O-ring seal, with respect to said drive gear (12, 112).
  7. The pump as set forth in any of the claims 1 and/or 3 to 6, characterized in that a spring member (22, 122) is provided which biases or presses said compensation plate (60, 160) against said pump gears (16, 116; 18, 118) or said pump housing (14, 114).
  8. The pump as set forth in any of the claims 3 to 7, characterized in that between said camshaft or crankshaft (20, 120) and said pump housing (14,114) and in particular said compensation plate (60, 160) a gap (38, 138) is provided.
  9. The pump as set forth in claim 1 or 2, characterized in that said outer rotor (218) is fixedly connected to said guide pulley (212), in particular as a press-fit therein.
  10. The pump as set forth in any of the claims 1,2 and/or 9, characterized in that said inner rotor (216) is disposed slidingly on said pump housing (214).
  11. The pump as set forth in any of the claims 1, 2, 9 or 10, characterized in that said guide pulley (212) is mounted on the engine (208) via an in particular roller-bearing-mounted bearing pin (254).
  12. The pump as set forth in claim 11, characterized in that said bearing pin (254) is mounted on said engine (208) via a ball bearing (256).
  13. The pump as set forth in any of the claims 11 or 12, characterized in that between said pump housing (214) or said inner rotor (216) and said bearing pin (254) a further bearing, in particular a needle bearing (258), is arranged.
  14. The pump as set forth in any of the claims 1, 2, 10 to 13, characterized in that said bearing pin (254) is sealed with respect to said guide pulley (212), in particular by an O-ring seal (228).
  15. The pump as set forth in any of the claims 1 to 14, characterized in that between said pump housing (14, 114, 214) and said drive gear or guide pulley (12, 112, 212) a seal is arranged, preferably a rotary shaft seal (34, 234).
EP92108169A 1991-06-07 1992-05-14 Lubrication gear pump for internal combustion engines, especially for vehicles Expired - Lifetime EP0517014B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4118872 1991-06-07
DE4118872 1991-06-07
DE4123190A DE4123190A1 (en) 1991-06-07 1991-07-12 GEAR PUMP FOR OIL FOR A COMBUSTION ENGINE, ESPECIALLY FOR MOTOR VEHICLES
DE4123190 1991-07-12

Publications (2)

Publication Number Publication Date
EP0517014A1 EP0517014A1 (en) 1992-12-09
EP0517014B1 true EP0517014B1 (en) 1995-11-15

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EP92108169A Expired - Lifetime EP0517014B1 (en) 1991-06-07 1992-05-14 Lubrication gear pump for internal combustion engines, especially for vehicles

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US (1) US5395217A (en)
EP (1) EP0517014B1 (en)
JP (1) JP3107646B2 (en)
KR (1) KR100250191B1 (en)
AT (1) ATE130402T1 (en)
CA (1) CA2070477C (en)
DE (2) DE4123190A1 (en)

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US5395217A (en) 1995-03-07
EP0517014A1 (en) 1992-12-09
DE59204306D1 (en) 1995-12-21
CA2070477C (en) 2003-09-02
KR930000802A (en) 1993-01-15
JP3107646B2 (en) 2000-11-13
JPH05263771A (en) 1993-10-12
DE4123190A1 (en) 1992-12-10
KR100250191B1 (en) 2000-04-01
ATE130402T1 (en) 1995-12-15
CA2070477A1 (en) 1992-12-08

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