EP1305523B1 - Internal gear pump - Google Patents

Internal gear pump Download PDF

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Publication number
EP1305523B1
EP1305523B1 EP01953920A EP01953920A EP1305523B1 EP 1305523 B1 EP1305523 B1 EP 1305523B1 EP 01953920 A EP01953920 A EP 01953920A EP 01953920 A EP01953920 A EP 01953920A EP 1305523 B1 EP1305523 B1 EP 1305523B1
Authority
EP
European Patent Office
Prior art keywords
internal gear
gear pump
pinion
bearing
pump according
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
EP01953920A
Other languages
German (de)
French (fr)
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EP1305523A1 (en
Inventor
Stanislaw Bodzak
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1305523A1 publication Critical patent/EP1305523A1/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
    • 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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/51—Bearings for cantilever assemblies

Definitions

  • the invention relates to an internal gear pump for conveying fuel in an internal combustion engine, with an internally toothed ring gear and an externally toothed pinion, which cooperates with the toothed ring for generating a pumping action, as defined in the preamble of claim 1.
  • a pump is eg from the US-A-5,226,798 known.
  • Such an internal gear pump is also referred to as a gerotor pump or gerotor pump.
  • the toothed ring and the pinion represent the pump elements and are also referred to as outer rotor and inner rotor.
  • the toothed ring is driven by an electric motor.
  • the existing between the teeth of the two pump elements conveying chambers of the internal gear pump are covered in the axial direction by a pressure plate. Trained as a compression spring coil spring, which is biased against the pressure plate, when starting the internal combustion engines ensures that the axial play is equal to zero.
  • the object of the invention is to increase the Forder amalgam at start speed and the life of the initially described internal gear pump.
  • the internal gear pump according to the invention is inexpensive be produced.
  • the pressure in the internal gear pump is equal to zero.
  • the head clearance between two mutually engaged teeth of the pump elements when starting the internal combustion engine is compensated.
  • the pump pressure increases and acts against the spring force.
  • the radial clearance increases, which decreases the delivery rate and improves the tribological conditions in the pump by increasing the head clearance.
  • the two flats serve to guide a bushing for the pinion in the radial direction.
  • the two flats also serve to axially guide a sealing plate for sealing the delivery chambers of the pump and to secure against rotation of the sealing plate.
  • the device is formed by a leaf spring of two legs, which are arranged substantially at right angles to each other, wherein the one leg on the end face of the bearing stub and the other leg between the bearing stub and a bearing bush for the pinion is arranged.
  • the spring device is fixed in the installed state.
  • the other leg of the spring device is used to compensate for the radial clearance.
  • Another particular embodiment of the invention is characterized in that between the bearing stub and the bearing bush for the pinion arranged leg of the leaf spring is curved in the longitudinal direction and / or in the transverse direction.
  • the curved design of the leg provides improved spring action of the leaf spring.
  • the leaf spring may be formed simply or repeatedly curved.
  • the device is formed by a helical spring which is arranged between the bearing stub and a bearing bushing for the pinion. It can be formed in the bearing stub a recess for receiving a portion of the coil spring to hold the coil spring in the installed state in position.
  • Another particular embodiment of the invention is characterized in that a stop for the bearing bush is formed on the bearing stub.
  • the stop serves to limit the radial clearance after the starting process.
  • Another particular embodiment of the invention is characterized in that the means for compensating the radial clearance is formed by a slot extending in the longitudinal direction of the bearing stub. Characterized an elasticity of the bearing stub in the radial direction is made possible in a particularly simple manner. On the above-described bearing bush and the spring can be omitted.
  • a further particular embodiment of the invention is characterized in that the device for compensating the radial play is formed by an oblong recess with a chamfer, against which a ball is biased by means of a spring.
  • the recess in the bearing stub is designed so that the ball abuts both the bearing stub and on the inner circumference of the bearing bush.
  • biasing force of the spring is adjustable by means of a screw.
  • the screw may e.g. be guided in a threaded bore in the housing of the internal gear pump. By turning the screw, the biasing force of the spring and thus the radial clearance between the pinion and the toothed ring can be adjusted continuously.
  • Another particular embodiment of the invention is characterized in that the pinion is coupled by an Oldham coupling or a radially elastic coupling with a drive shaft.
  • the Oldham clutch which is also referred to as a cross-plate clutch, also allows the to Balancing the radial clearance required radial movement of the pinion.
  • FIG. 1 shows a high-pressure pad 1, to which an internal gear pump 2 is attached.
  • an externally toothed pinion 3 is rotatably supported by means of a bearing bush 4 on a bearing stub 5.
  • the externally toothed pinion 3 is mounted eccentrically to an internally toothed ring gear 11.
  • the internal gear pump 2 is connected to the high-pressure pump 1 via a suction channel 6 and a pressure channel 7.
  • the cross section of the bearing bush 4 has the shape of a slot 10 whose dimensions are adapted to the dimensions of the bearing stub 5. In the direction of the line II-II is between the bearing bush 4 and the bearing stub 5 on both sides of some game available. This radial clearance allows radial play compensation when bearing wear and / or gear wear occurs.
  • a spring 12 is received on one side in the clearance between the bearing stub 5 and the bearing bush 4. The spring 12 ensures that a tooth tip 13 of the pinion 3 is held when starting the internal combustion engine in abutment against a tooth tip 14 of the toothed ring 11.
  • the internal gear 2 is surrounded by a housing 20 which is fixed to the housing of the high-pressure pump 1.
  • the bearing stub 5 is part of the housing 20 of the internal gear pump 2. From the high-pressure pump 1 protrudes a shaft end 21 in the internal gear pump 2. At the shaft end 21 two flats are formed, of which in Figure 2, only one flattening 26 can be seen.
  • the drive shaft end 21 is received in a coupling part 22.
  • the Clutch part 22 belongs to a so-called Oldham coupling, which is also referred to as a cross-plate clutch.
  • the Kreuzusionnkupplung serves to transmit the rotational movement of the drive shaft end 21 to the externally toothed pinion 3 of the internal gear pump 2.
  • the cross-plate clutch allows an axial offset between the drive shaft end 21 and the bearing stub 5 can be compensated.
  • the radial play of the bearing bush 4 relative to the bearing stub 5 is designated R in FIG.
  • the radial movement of the bearing bush 4 is limited by a stop 23 which is formed on the bearing stub 5.
  • a radial movement of the bearing bush 4 is only possible if the pressure in the internal gear pump 2 is sufficient to overcome the biasing force of the spring 12.
  • the trained between the outer teeth of the pinion 3 and the internal toothing of the toothed ring 11 pump chamber is sealed to the housing 20 through a sealing plate 24.
  • the sealing plate 24 by means of a plate spring 25, which is supported on the housing 20 of the internal gear pump 2, biased against the pinion 3 and the toothed ring 11.
  • a bore 34 is provided, which establishes a connection to the pressure side.
  • the internal gear pump 2 mounted on the housing of the high-pressure pump 1 is driven by the drive shaft 21 of the high-pressure pump 1.
  • a possibly occurring axial offset between the drive shaft end 21 and the bearing stub 5 in the housing 20 is compensated by the Oldham coupling 22.
  • the Oldham coupling 22 also has the task of allowing a radial movement of the pinion 3.
  • the two flats 8 and 9 at the Bearing stub 5 serve on the one hand to guide the sealing plate 24 axially.
  • the two flats serve 8 and 9 on the bearing stub 5 to guide the bearing bush 4 in the radial direction.
  • flat surfaces 8 and 9 on the bearing stub 5 must be aligned approximately parallel to the eccentric axis II-II of the internal gear pump 2.
  • the spring force of the spring 12 acts on the bearing bush 4 and the pinion 3.
  • the head clearance 13/14 is reduced to zero.
  • the pump pressure increases and the bearing bush 4 moves up to the stop 23 on the bearing stub 5.
  • the radial play is set to the tooth tips 13 and 14 with the continuous operation of the internal combustion engine to a value greater than zero.
  • the leaf springs 12 each have two legs 31 and 32, which are arranged at a right angle to each other.
  • the leg 31 of the leaf spring 12 is flat and is in the installed state at the free end of the bearing stub 5.
  • the leg 32 is formed corrugated in the longitudinal direction.
  • the leg 32 of the leaf spring 12 is formed curved in the longitudinal direction outwards.
  • the leg 32 of the leaf spring 12 is curved in the transverse direction. The curvature of the leg 32 is best in that in FIG. 6 see cross-sectional view seen.
  • a coil spring 12 between the bearing stub 5 and the bearing bush 4 of the pinion 3 is arranged.
  • the axis of the coil spring 12 is perpendicular to the axis of the bearing stub 5.
  • the coil spring 12 is formed on the bearing stub 5 a semi-circular in cross section recess.
  • an elongated recess 41 is formed in the bearing stub 5.
  • the elongate recess 41 has the shape of a circular cylinder halved in the longitudinal direction, one end face of which is provided with a chamfer 42.
  • the elongate recess 41 serves to receive a ball 43 whose dimensions are larger than that of the recess 41. This ensures that a portion of the ball 43 protrudes from the recess 41. This protruding portion of the ball 43 is in contact with the inner circumference of the bearing bushing 4th

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

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Innenzahnradpumpe zum Fördern von Kraftstoff in einer Brennkraftmaschine, mit einem innenverzahnten Zahnring und einem außenverzahnten Ritzel, das zum Erzeugen einer Pumpwirkung mit dem Zahnring zusammenwirkt, wie im Oberbegriff von Anspruch 1 definiert wird. Eine solche Pumpe ist z.B aus der US-A-5 226 798 bekannt.The invention relates to an internal gear pump for conveying fuel in an internal combustion engine, with an internally toothed ring gear and an externally toothed pinion, which cooperates with the toothed ring for generating a pumping action, as defined in the preamble of claim 1. Such a pump is eg from the US-A-5,226,798 known.

Eine derartige Innenzahnradpumpe wird auch als Zahnringpumpe oder Gerotorpumpe bezeichnet. Der Zahnring und das Ritzel stellen die Pumpenelemente dar und werden auch als Außenrotor und Innenrotor bezeichnet. In der DE 38 27 573 A1 ist eine Innenzahnradpumpe beschrieben, deren Zahnring über einen Elektromotor angetrieben ist. Die zwischen den Verzahnungen der beiden Pumpenelemente vorhandenen Förderkammern der Innenzahnradpumpe werden in axialer Richtung durch eine Druckscheibe abgedeckt. Eine als Druckfeder ausgebildete Schraubenfeder, die gegen die Druckplatte vorgespannt ist, sorgt beim Starten der Brennkraftmaschien dafür, dass das Axialspiel gleich Null ist.Such an internal gear pump is also referred to as a gerotor pump or gerotor pump. The toothed ring and the pinion represent the pump elements and are also referred to as outer rotor and inner rotor. In the DE 38 27 573 A1 an internal gear pump is described, the toothed ring is driven by an electric motor. The existing between the teeth of the two pump elements conveying chambers of the internal gear pump are covered in the axial direction by a pressure plate. Trained as a compression spring coil spring, which is biased against the pressure plate, when starting the internal combustion engines ensures that the axial play is equal to zero.

Aus der DE-U 297 03 656 ist eine Gerotorpumpe mit einer Einrichtung zum Ausgleichen des Radialspiels zwischen Ritzel und Zahnring bekannt. Bei dieser Einrichtung ist der der Zahnring schwenkbar an dem Pumpengehäuse gelagert, so dass er durch den während des Betriebs im Inneren der Pumpe herrschenden Druck gegen das Ritzel gepresst wird.From the DE-U 297 03 656 is a gerotor pump with a device for balancing the radial clearance between pinion and ring gear known. In this device, the toothed ring is pivotally mounted on the pump housing so that it is pressed by the pressure prevailing during operation inside the pump against the pinion.

Aufgabe der Erfindung ist es, die Forderleistung bei Startdrehzahl und die Lebensdauer bei der eingangs geschilderten Innenzahnradpumpe zu erhöhen. Dabei soll die erfindungsgemäße Innenzahnradpumpe kostengünstig herstellbar sein.The object of the invention is to increase the Forderleistung at start speed and the life of the initially described internal gear pump. In this case, the internal gear pump according to the invention is inexpensive be produced.

Die Aufgabe ist durch die Merkmalskombination von Anspruch 1 gelöst.The object is achieved by the feature combination of claim 1.

Vorteile der ErfindungAdvantages of the invention

Beim Starten der Brennkraftmaschine ist der Druck in der Innenzahnradpumpe gleich Null. Durch die erfindungsgemäße Federeinrichtung wird das Kopfspiel zwischen zwei miteinander in Eingriff befindlichen Zähnen der Pumpenelemente beim Starten der Brennkraftmaschine ausgeglichen. Nach Erreichen der Leerlaufdrehzahl steigt der Pumpendruck und wirkt gegen die Federkraft. Das führt dazu, dass das Radialspiel zunimmt, wodurch die Förderleistung sinkt und die tribologischen Bedingungen in der Pumpe durch eine Vergrößerung des Kopfspiels verbessert werden.When starting the internal combustion engine, the pressure in the internal gear pump is equal to zero. By the spring device according to the invention, the head clearance between two mutually engaged teeth of the pump elements when starting the internal combustion engine is compensated. After reaching the idle speed, the pump pressure increases and acts against the spring force. As a result, the radial clearance increases, which decreases the delivery rate and improves the tribological conditions in the pump by increasing the head clearance.

Die beiden Abflachungen dienen dazu, eine Lagerbuchse für das Ritzel in radialer Richtung zu führen. Die beiden Abflachungen dienen außerdem dazu, eine Dichtplatte zum Abdichten der Förderkammern der Pumpe axial zu führen und gegen eine Drehbewegung der Dichtplatte zu sichern.The two flats serve to guide a bushing for the pinion in the radial direction. The two flats also serve to axially guide a sealing plate for sealing the delivery chambers of the pump and to secure against rotation of the sealing plate.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Einrichtung von einer Blattfeder von zwei Schenkeln gebildet wird, die im Wesentlichen rechtwinklig zueinander angeordnet sind, wobei der eine Schenkel an der Stirnseite des Lagerstummels und der andere Schenkel zwischen dem Lagerstummel und einer Lagerbuchse für das Ritzel angeordnet ist. Durch den am Lagerstummel anliegenden Schenkel wird die Federeinrichtung im eingebauten Zustand fixiert. Der andere Schenkel der Federeinrichtung dient zum Ausgleich des Radialspiels.Another particular embodiment of the invention is characterized in that the device is formed by a leaf spring of two legs, which are arranged substantially at right angles to each other, wherein the one leg on the end face of the bearing stub and the other leg between the bearing stub and a bearing bush for the pinion is arranged. By the adjacent stub leg, the spring device is fixed in the installed state. The other leg of the spring device is used to compensate for the radial clearance.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der zwischen dem Lagerstummel und der Lagerbuchse für das Ritzel angeordnete Schenkel der Blattfeder in Längsrichung und/oder in Querrichtung gekrümmt ausgebildet ist. Die gekrümmte Ausbildung des Schenkels sorgt für eine verbesserte Federwirkung der Blattfeder. Dabei kann die Blattfeder einfach oder mehrfach gekrümmt ausgebildet sein.Another particular embodiment of the invention is characterized in that between the bearing stub and the bearing bush for the pinion arranged leg of the leaf spring is curved in the longitudinal direction and / or in the transverse direction. The curved design of the leg provides improved spring action of the leaf spring. In this case, the leaf spring may be formed simply or repeatedly curved.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Einrichtung von einer Schraubenfeder gebildet wird, die zwischen dem Lagerstummel und einer Lagerbuchse für das Ritzel angeordnet ist. Dabei kann in dem Lagerstummel eine Vertiefung zur Aufnahme eines Teils der Schraubenfeder ausgebildet sein, um die Schraubenfeder im eingebauten Zustand in Position zu halten.Another particular embodiment of the invention is characterized in that the device is formed by a helical spring which is arranged between the bearing stub and a bearing bushing for the pinion. It can be formed in the bearing stub a recess for receiving a portion of the coil spring to hold the coil spring in the installed state in position.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass an dem Lagerstummel ein Anschlag für die Lagerbuchse ausgebildet ist. Der Anschlag dient dazu, das Radialspiel nach dem Startvorgang zu begrenzen.Another particular embodiment of the invention is characterized in that a stop for the bearing bush is formed on the bearing stub. The stop serves to limit the radial clearance after the starting process.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Einrichtung zum Ausgleichen des Radialspiels von einem Schlitz gebildet wird, der in Längsrichtung des Lagerstummels verläuft. Dadurch wird auf besonders einfache Art und Weise eine Elastizität des Lagerstummel in radialer Richtung ermöglicht. Auf die vorab beschriebene Lagerbuchse und die Feder kann verzichtet werden.Another particular embodiment of the invention is characterized in that the means for compensating the radial clearance is formed by a slot extending in the longitudinal direction of the bearing stub. Characterized an elasticity of the bearing stub in the radial direction is made possible in a particularly simple manner. On the above-described bearing bush and the spring can be omitted.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Einrichtung zum Ausgleichen des Radialspiels von einer länglichen Ausnehmung mit einer Abschrägung gebildet wird, gegen die eine Kugel mit Hilfe einer Feder vorgespannt ist. Je stärker die Kugel gegen die Abschrägung gedrückt wird, desto kleiner ist das Radialspiel zwischen dem Ritzel und dem Zahnring. Die Ausnehmung in dem Lagerstummel ist so gestaltet, dass die Kugel sowohl an dem Lagerstummel als auch am inneren Umfang der Lagerbuchse anliegt.A further particular embodiment of the invention is characterized in that the device for compensating the radial play is formed by an oblong recess with a chamfer, against which a ball is biased by means of a spring. The stronger the ball is pressed against the bevel, the smaller is the radial play between the pinion and the toothed ring. The recess in the bearing stub is designed so that the ball abuts both the bearing stub and on the inner circumference of the bearing bush.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Vorspannkraft der Feder mit Hilfe einer Schraube verstellbar ist. Die Schraube kann z.B. in einer Gewindebohrung in dem Gehäuse der Innenzahnradpumpe geführt sein. Über ein Verdrehen der Schraube kann die Vorspannkraft der Feder und somit das Radialspiel zwischen dem Ritzel und dem Zahnring stufenlos eingestellt werden.Another particular embodiment of the invention is characterized in that the biasing force of the spring is adjustable by means of a screw. The screw may e.g. be guided in a threaded bore in the housing of the internal gear pump. By turning the screw, the biasing force of the spring and thus the radial clearance between the pinion and the toothed ring can be adjusted continuously.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass das Ritzel durch eine Oldham-Kupplung oder eine radial elastische Kupplung mit einer Antriebswelle gekoppelt ist. Durch die Oldham-Kupplung kann ein eventuell vorhandener Axialversatz zwischen der Antriebswelle und dem Lagerstummel ausgeglichen werden. Die Oldham-Kupplung, die auch als Kreuzscheibenkupplung bezeichnet wird, ermöglicht darüber hinaus die zum Ausgleich des Radialspiels erforderliche Radialbewegung des Ritzels.Another particular embodiment of the invention is characterized in that the pinion is coupled by an Oldham coupling or a radially elastic coupling with a drive shaft. Through the Oldham coupling any existing axial offset between the drive shaft and the bearing stub can be compensated. The Oldham clutch, which is also referred to as a cross-plate clutch, also allows the to Balancing the radial clearance required radial movement of the pinion.

Zeichnungendrawings

In der Zeichnung zeigen:

Figur 1
eine Ausführungsform der erfindungsgemäßen Innenzahnradpumpe in der Draufsicht;
Figur 2
die Ansicht eines Schnitts entlang der Linie II-II in Figur 1;
Figuren 3 bis 5
drei verschiedene Ausführungsformen einer erfindungsgemäßen Federeinrichtung in perspektivischer Darstellung;
Figur 6
die Ansicht eines Schnitts entlang der Linie VI-VI in Figur 5;
Figur 7
einen Ausschnitt aus Figur 1 mit einer weiteren Ausführungsform einer erfindungsgemäßen Federeinrichtung;
Figur 8
eine weitere Ausführungsform der erfindungsgemäßen Innenzahnradpumpe mit Einstellschraube in der Draufsicht;
Figur 9
die Ansicht eines Schnitts entlang der Linie IX-IX in Figur 8.
In the drawing show:
FIG. 1
an embodiment of the internal gear pump according to the invention in plan view;
FIG. 2
the view of a section along the line II-II in Figure 1;
FIGS. 3 to 5
three different embodiments of a spring device according to the invention in a perspective view;
FIG. 6
the view of a section along the line VI-VI in Figure 5;
FIG. 7
a section of Figure 1 with a further embodiment of a spring device according to the invention;
FIG. 8
a further embodiment of the internal gear pump according to the invention with adjusting screw in plan view;
FIG. 9
the view of a section along the line IX-IX in Figure 8.

In Figur 1 sieht man eine Hochdruckpümpe 1, an die eine Innenzahnradpumpe 2 angebaut ist. In der Innenzahnradpumpe 2 ist ein außenverzahntes Ritzel 3 mit Hilfe einer Lagerbuchse 4 auf einem Lagerstummel 5 drehbar gelagert. Das außenverzahnte Ritzel 3 ist exzentrisch zu einem innenverzahnten Zahnring 11 gelagert. Die Innenzahnradpumpe 2 ist über einen Saugkanal 6 und einen Druckkanal 7 mit der Hochdruckpumpe 1 verbunden.FIG. 1 shows a high-pressure pad 1, to which an internal gear pump 2 is attached. In the internal gear pump 2, an externally toothed pinion 3 is rotatably supported by means of a bearing bush 4 on a bearing stub 5. The externally toothed pinion 3 is mounted eccentrically to an internally toothed ring gear 11. The internal gear pump 2 is connected to the high-pressure pump 1 via a suction channel 6 and a pressure channel 7.

An dem Lagerstummel 5 sind zwei Abflachungen 8 und 9 ausgebildet. Der Querschnitt der Lagerbuchse 4 hat die Form eines Langlochs 10, dessen Abmessungen an die Abmessungen des Lagerstummels 5 angepasst sind. In Richtung der Linie II-II ist zwischen der Lagerbuchse 4 und dem Lagerstummel 5 auf beiden Seiten etwas Spiel vorhanden. Dieses radiale Spiel ermöglicht bei einem Auftreten von Lagerungsverschleiss und/oder Zahnräderverschleiss einen Radialspielausgleich. Zu diesem Zweck ist auf einer Seite in dem Spielraum zwischen dem Lagerstummel 5 und der Lagerbuchse 4 eine Feder 12 aufgenommen. Die Feder 12 sorgt dafür, dass ein Zahnkopf 13 des Ritzels 3 beim Starten der Brennkraftmaschine in Anlage an einem Zahnkopf 14 des Zahnrings 11 gehalten wird.At the bearing stub 5 two flats 8 and 9 are formed. The cross section of the bearing bush 4 has the shape of a slot 10 whose dimensions are adapted to the dimensions of the bearing stub 5. In the direction of the line II-II is between the bearing bush 4 and the bearing stub 5 on both sides of some game available. This radial clearance allows radial play compensation when bearing wear and / or gear wear occurs. For this purpose, a spring 12 is received on one side in the clearance between the bearing stub 5 and the bearing bush 4. The spring 12 ensures that a tooth tip 13 of the pinion 3 is held when starting the internal combustion engine in abutment against a tooth tip 14 of the toothed ring 11.

In der in Figur 2 dargestellten Schnittansicht sieht man, dass die Innenzahnradpumpe 2 von einem Gehäuse 20 umgeben ist, das an dem Gehäuse der Hochdruckpumpe 1 befestigt ist. Der Lagerstummel 5 ist Teil des Gehäuses 20 der Innenzahnradpumpe 2. Von der Hochdruckpumpe 1 ragt ein Wellenende 21 in die Innenzahnradpumpe 2. An dem Wellenende 21 sind zwei Abflachungen ausgebildet, von denen in Figur 2 nur eine Abflachung 26 zu sehen ist. Das Antriebswellenende 21 ist in einem Kupplungsteil 22 aufgenommen. Das Kupplungsteil 22 gehört zu einer sogenannten Oldham-Kupplung, die auch als Kreuzscheibenkupplung bezeichnet wird. Die Kreuzscheibenkupplung dient dazu, die Drehbewegung des Antriebswellenendes 21 auf das außenverzahnte Ritzel 3 der Innenzahnradpumpe 2 zu übertragen. Dabei ermöglicht die Kreuzscheibenkupplung, dass ein axialer Versatz zwischen dem Antriebswellenende 21 und dem Lagerstummel 5 ausgeglichen werden kann.In the sectional view shown in Figure 2 it can be seen that the internal gear 2 is surrounded by a housing 20 which is fixed to the housing of the high-pressure pump 1. The bearing stub 5 is part of the housing 20 of the internal gear pump 2. From the high-pressure pump 1 protrudes a shaft end 21 in the internal gear pump 2. At the shaft end 21 two flats are formed, of which in Figure 2, only one flattening 26 can be seen. The drive shaft end 21 is received in a coupling part 22. The Clutch part 22 belongs to a so-called Oldham coupling, which is also referred to as a cross-plate clutch. The Kreuzscheibenkupplung serves to transmit the rotational movement of the drive shaft end 21 to the externally toothed pinion 3 of the internal gear pump 2. In this case, the cross-plate clutch allows an axial offset between the drive shaft end 21 and the bearing stub 5 can be compensated.

Das radiale Spiel der Lagerbuchse 4 relativ zu dem Lagerstummel 5 ist in Figur 2 mit R bezeichnet. Die Radialbewegung der Lagerbuchse 4 wird durch einen Anschlag 23 begrenzt, der an dem Lagerstummel 5 ausgebildet ist. Innerhalb des Radialspiels R ist eine Radialbewegung der Lagerbuchse 4 nur dann möglich, wenn der Druck in der Innenzahnradpumpe 2 ausreicht, um die Vorspannkraft der Feder 12 zu überwinden.The radial play of the bearing bush 4 relative to the bearing stub 5 is designated R in FIG. The radial movement of the bearing bush 4 is limited by a stop 23 which is formed on the bearing stub 5. Within the radial clearance R, a radial movement of the bearing bush 4 is only possible if the pressure in the internal gear pump 2 is sufficient to overcome the biasing force of the spring 12.

Der zwischen der Außenverzahnung des Ritzels 3 und der Innenverzahnung des Zahnrings 11 ausgebildete Pumpenraum ist zum Gehäuse 20 hin durch eine Dichtplatte 24 abgedichtet. Zu diesem Zweck ist die Dichtplatte 24 mit Hilfe einer Tellerfeder 25, die sich an dem Gehäuse 20 der Innenzahnradpumpe 2 abstützt, gegen das Ritzel 3 und dem Zahnring 11 vorgespannt. In der Dichtplatte 24 ist eine Bohrung 34 vorgesehen, die eine Verbindung zur Druckseite herstellt.The trained between the outer teeth of the pinion 3 and the internal toothing of the toothed ring 11 pump chamber is sealed to the housing 20 through a sealing plate 24. For this purpose, the sealing plate 24 by means of a plate spring 25, which is supported on the housing 20 of the internal gear pump 2, biased against the pinion 3 and the toothed ring 11. In the sealing plate 24, a bore 34 is provided, which establishes a connection to the pressure side.

Im Betrieb wird die an dem Gehäuse der Hochdruckpumpe 1 montierte Innenzahnradpumpe 2 durch die Antriebswelle 21 der Hochdruckpumpe 1 angetrieben. Ein eventuell auftretender Axialversatz zwischen dem Antriebswellenende 21 und dem Lagerstummel 5 im Gehäuse 20 wird durch die Oldham-Kupplung 22 ausgeglichen. Die Oldham-Kupplung 22 hat darüberhinaus die Aufgabe, eine Radialbewegung des Ritzels 3 zu ermöglichen. Die beiden Abflachungen 8 und 9 an dem Lagerstummel 5 dienen einerseits dazu, die Dichtplatte 24 axial zu führen. Andererseits dienen die beiden Abflachungen 8 und 9 an dem Lagerstummel 5 dazu, die Lagerbuchse 4 in radialer Richtung zu führen. Zu diesem Zweck müssen Planflächen 8 und 9 an dem Lagerstummel 5 etwa parallel zur Exzenterachse II-II der Innenzahnradpumpe 2 ausgerichtet sein.In operation, the internal gear pump 2 mounted on the housing of the high-pressure pump 1 is driven by the drive shaft 21 of the high-pressure pump 1. A possibly occurring axial offset between the drive shaft end 21 and the bearing stub 5 in the housing 20 is compensated by the Oldham coupling 22. The Oldham coupling 22 also has the task of allowing a radial movement of the pinion 3. The two flats 8 and 9 at the Bearing stub 5 serve on the one hand to guide the sealing plate 24 axially. On the other hand, the two flats serve 8 and 9 on the bearing stub 5 to guide the bearing bush 4 in the radial direction. For this purpose, flat surfaces 8 and 9 on the bearing stub 5 must be aligned approximately parallel to the eccentric axis II-II of the internal gear pump 2.

Beim Starten der Brennkraftmaschine wirkt die Federkraft der Feder 12 auf die Lagerbuchse 4 und das Ritzel 3. Dadurch wird das Kopfspiel 13/14 auf Null reduziert. Nach Erreichen der Leerlaufdrehzahl der Brennkraftmaschine steigt der Pumpendruck und die Lagerbuchse 4 bewegt sich bis an den Anschlag 23 an dem Lagerstummel 5. Somit wird das Radialspiel an den Zahnköpfen 13 und 14 mit dem Dauerbetrieb der Brennkraftmaschine auf einen Wert größer als Null eingestellt.When starting the internal combustion engine, the spring force of the spring 12 acts on the bearing bush 4 and the pinion 3. As a result, the head clearance 13/14 is reduced to zero. After reaching the idling speed of the internal combustion engine, the pump pressure increases and the bearing bush 4 moves up to the stop 23 on the bearing stub 5. Thus, the radial play is set to the tooth tips 13 and 14 with the continuous operation of the internal combustion engine to a value greater than zero.

In den Figuren 3 bis 5 sind drei verschiedene Ausführungsformen der Blattfeder 12 perspektivisch dargestellt. Der Einfachheit halber werden zur Bezeichnung ähnlicher Teile die gleichen Bezugszeichen verwendet. Die Blattfedern 12 weisen jeweils zwei Schenkel 31 und 32 auf, die in einem rechten Winkel zueinander angeordnet sind. Der Schenkel 31 der Blattfeder 12 ist eben ausgebildet und liegt im eingebauten Zustand an dem freien Ende des Lagerstummels 5 an.In the figures 3 to 5, three different embodiments of the leaf spring 12 are shown in perspective. For simplicity, the same reference numerals will be used to designate similar parts. The leaf springs 12 each have two legs 31 and 32, which are arranged at a right angle to each other. The leg 31 of the leaf spring 12 is flat and is in the installed state at the free end of the bearing stub 5.

Bei der in Figur 3 dargestellten Ausführungsform der Blattfeder 12 ist der Schenkel 32 in Längsrichtung gewellt ausgebildet. Bei der in Figur 4 dargestellten Ausführungsform ist der Schenkel 32 der Blattfeder 12 in Längsrichtung nach außen gekrümmt ausgebildet. Bei der in Figur 5 dargestellten Ausführungsform ist der Schenkel 32 der Blattfeder 12 in Querrichtung gekrümmt ausgebildet. Die Krümmung des Schenkels 32 ist am Besten in der in Figur 6 dargestellten Querschnittansicht zu sehen.In the embodiment of the leaf spring 12 shown in Figure 3, the leg 32 is formed corrugated in the longitudinal direction. In the embodiment shown in Figure 4, the leg 32 of the leaf spring 12 is formed curved in the longitudinal direction outwards. In the embodiment shown in Figure 5, the leg 32 of the leaf spring 12 is curved in the transverse direction. The curvature of the leg 32 is best in that in FIG. 6 see cross-sectional view seen.

Bei der in Figur 7 dargestellten Ausführungsform der Erfindung ist eine Schraubenfeder 12 zwischen dem Lagerstummel 5 und der Lagerbuchse 4 des Ritzels 3 angeordnet. Dabei verläuft die Achse der Schraubenfeder 12 senkrecht zur Achse des Lagerstummels 5. Zur Fixierung der Schraubenfeder 12 ist an dem Lagerstummel 5 eine im Querschnitt halbkreisförmige Vertiefung ausgebildet.In the embodiment of the invention shown in Figure 7, a coil spring 12 between the bearing stub 5 and the bearing bush 4 of the pinion 3 is arranged. In this case, the axis of the coil spring 12 is perpendicular to the axis of the bearing stub 5. For fixing the coil spring 12 is formed on the bearing stub 5 a semi-circular in cross section recess.

Die in den Figuren 8, 9 und 10, 11 dargestellten Ausführungsformen der erfindungsgemäßen Innenzahnradpumpe ähneln der in den Figuren 1 und 2 dargestellten Ausführungsform. Der Einfachheit halber werden zur Bezeichnung gleicher oder ähnlicher Teile die selben Bezugszeichen verwendet. Um Wiederholungen zu vermeiden, wird im Folgenden nur auf die Unterschiede zwischen den einzelnen Ausführungsformen eingegangen.The embodiments of the internal gear pump according to the invention shown in Figures 8, 9 and 10, 11 are similar to the embodiment shown in Figures 1 and 2. For simplicity, the same reference numerals will be used to designate the same or similar parts. In order to avoid repetition, only the differences between the individual embodiments will be discussed below.

Bei der in den Figuren 8 und 9 dargestellten Ausführungsform ist in dem Lagerstummel 5 eine längliche Ausnehmung 41 ausgebildet. Die längliche Ausnehmung 41 hat die Form eines in Längsrichtung halbierten Kreiszylinders, dessen eine Stirnseite mit einer Abschrägung 42 versehen ist. Die längliche Ausnehmung 41 dient zur Aufnahme einer Kugel 43, deren Abmessungen größer als die der Ausnehmung 41 sind. Dadurch ist gewährleistet, dass ein Abschnitt der Kugel 43 aus der Ausnehmung 41 herausragt. Dieser herausragende Abschnitt der Kugel 43 befindet sich in Anlage an dem inneren Umfang der Lagerbuchse 4.In the embodiment illustrated in FIGS. 8 and 9, an elongated recess 41 is formed in the bearing stub 5. The elongate recess 41 has the shape of a circular cylinder halved in the longitudinal direction, one end face of which is provided with a chamfer 42. The elongate recess 41 serves to receive a ball 43 whose dimensions are larger than that of the recess 41. This ensures that a portion of the ball 43 protrudes from the recess 41. This protruding portion of the ball 43 is in contact with the inner circumference of the bearing bushing 4th

In der in Figur 9 dargestellten Schnittansicht sieht man, dass die Kugel 43 mit Hilfe einer Feder 44 gegen die Abschrägung 42 in der länglichen Ausnehmung 41 gedrückt wird. Die Vorspannkraft der Feder 44 kann über eine Schraube 45 eingestellt werden, deren freies Ende an der Feder 44 anliegt. Die Schraube 45 ist drehbar in einer Gewindebohrung des.Gehäuses 20 der Innenzahnradpumpe aufgenommen.In the sectional view shown in Figure 9 it can be seen that the ball 43 is pressed by means of a spring 44 against the chamfer 42 in the elongated recess 41. The biasing force of the spring 44 can be adjusted by a screw 45, the free end of the Spring 44 is present. The screw 45 is rotatably received in a threaded bore des.Gehäuses 20 of the internal gear pump.

Claims (9)

  1. Internal gear pump for the conveyance of fuel in an internal combustion engine, with an internally toothed gear ring (11) and with an externally toothed pinion (3) which cooperates with the gear ring (11) to generate a pumping action, a device (12) being provided for compensating the radial play (R) between the pinion (3) and the gear ring (11), the pinion (3) being mounted eccentrically to the gear ring (11) and radially moveably, characterized in that the pinion (3) is mounted rotatably on a bearing stub (5) via a bearing bush (4), in that, on the circumference of the bearing stub (5), two flattenings (8, 9) are formed, which are arranged essentially parallel to the eccentric axis of the internal gear pump (2) and which serve for guiding the bearing bush (4) for the pinion (3) in a radial direction.
  2. Internal gear pump according to Claim 1, characterized in that the device is formed by a leaf spring (12) with two legs (31, 32) which are arranged essentially at right angles to one another, one leg (31) being arranged on the end face of the bearing stub (5) and the other leg (32) being arranged between the bearing stub (5) and a bearing bush (4) for the pinion (3).
  3. Internal gear pump according to Claim 2, characterized in that that leg (32) of the leaf spring (12) which is arranged between the bearing stub (5) and the bearing bush (4) for the pinion (3) is designed to be curved in the longitudinal direction and/or the transverse direction.
  4. Internal gear pump according to Claim 1, characterized in that the device (12) is formed by a helical spring which is arranged between the bearing stub (5) and a bearing bush (4) for the pinion (3).
  5. Internal gear pump according to one of the preceding claims, characterized in that a stop (23) for the bearing bush (4) is formed on the bearing stub (5).
  6. Internal gear pump according to Claim 1 or 5, characterized in that the device for compensating the radial play is formed by a slot (51) which runs in the longitudinal direction of the bearing stub (5).
  7. Internal gear pump according to Claim 1 or 5, characterized in that the device for compensating the radial play is formed by an elongate recess (41) having a slope (42), against which a ball (43) is prestressed with the aid of a spring (44).
  8. Internal gear pump according to Claim 7, characterized in that the prestressing force of the spring (44) can be adjusted with the aid of a screw (45).
  9. Internal gear pump according to one of the preceding claims, characterized in that the pinion (3) is coupled to a drive shaft (21) by means of an Oldham coupling (22) or a radially elastic coupling.
EP01953920A 2000-07-21 2001-07-14 Internal gear pump Expired - Lifetime EP1305523B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10035900A DE10035900A1 (en) 2000-07-21 2000-07-21 Internal gear pump
DE10035900 2000-07-21
PCT/DE2001/002633 WO2002008608A1 (en) 2000-07-21 2001-07-14 Internal gear pump

Publications (2)

Publication Number Publication Date
EP1305523A1 EP1305523A1 (en) 2003-05-02
EP1305523B1 true EP1305523B1 (en) 2008-01-09

Family

ID=7649963

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01953920A Expired - Lifetime EP1305523B1 (en) 2000-07-21 2001-07-14 Internal gear pump

Country Status (7)

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US (1) US6676394B2 (en)
EP (1) EP1305523B1 (en)
JP (1) JP2004504545A (en)
KR (1) KR100770965B1 (en)
CN (1) CN1236211C (en)
DE (2) DE10035900A1 (en)
WO (1) WO2002008608A1 (en)

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BRPI0414235A (en) * 2003-09-11 2006-10-31 Cor Pumps & Compressors Ag rotary plunger machine
EP1837522A4 (en) * 2005-01-12 2012-12-05 Diamet Corp Inner rotor for internal gear pump
US7438542B2 (en) * 2005-12-19 2008-10-21 Dana Automotive Systems Group, Llc. Fluid pump assembly
TW200911329A (en) * 2007-09-05 2009-03-16 jun-cheng Wu Directional putting practice device
DE102010001122A1 (en) 2010-01-22 2011-07-28 Robert Bosch GmbH, 70469 Pump assembly for common rail injection system of combustion engine, has high pressure pump and feed pump that are commonly driven by drive shaft of high pressure pump, where feed pump is electrically driven in phasing manner
JP5622033B2 (en) * 2010-07-20 2014-11-12 アイシン精機株式会社 Fluid pump
DE102010031609A1 (en) 2010-07-21 2012-01-26 Robert Bosch Gmbh Pump for supplying fluid, particularly fuel pump for conveying fuel into fuel injection system of internal combustion engine, comprises pump chamber, which is formed as resonator pipe that is closed at primary pipe end
DE102010031614A1 (en) 2010-07-21 2012-01-26 Robert Bosch Gmbh Gear pump for feeding fuel into fuel injection system, particularly in common-rail system of internal combustion engine, comprises shaft assembly, which lies from drive shaft and gear wheel driven by drive shaft
DE102010038893A1 (en) 2010-08-04 2012-02-09 Robert Bosch Gmbh Fuel pump for supplying fuel in fuel injection system, has drive wheel that is propelled by drive shaft, where drive wheel is mounted on bearing pin by friction bearing
DE102011007783A1 (en) 2011-04-20 2012-10-25 Robert Bosch Gmbh Gear pump for conveying fluids, such as fuel in fuel injection system of internal combustion engine, has external gear and ring, where predetermined axis of another axis is defined by eccentricity of bearing points
DE102011075423A1 (en) 2011-05-06 2012-11-08 Robert Bosch Gmbh Gear pump e.g. internal gear pump for delivering fuel into fuel injection system of internal combustion engine, has internally toothed ring aligned with externally toothed gear by forming line contact between mold drafts
DE102011079671A1 (en) 2011-07-22 2013-01-24 Robert Bosch Gmbh Gear pump and method for operating a gear pump
DE102011082578A1 (en) 2011-09-13 2013-03-14 Robert Bosch Gmbh Gear pump for conveying fluid, particularly for delivering fuel in high-pressure fuel injection system, has internally toothed ring, which has multiple tooth heads, where externally toothed gear has multiple other tooth heads
DE102012207259A1 (en) * 2012-05-02 2013-11-07 Robert Bosch Gmbh Internal gear pump
KR101381883B1 (en) * 2012-07-19 2014-04-18 ㈜성신이엔지 Cam structure of air compressure
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US20030077196A1 (en) 2003-04-24
EP1305523A1 (en) 2003-05-02
CN1386171A (en) 2002-12-18
KR100770965B1 (en) 2007-10-30
KR20020033178A (en) 2002-05-04
JP2004504545A (en) 2004-02-12
US6676394B2 (en) 2004-01-13
WO2002008608A1 (en) 2002-01-31
CN1236211C (en) 2006-01-11
DE50113477D1 (en) 2008-02-21
DE10035900A1 (en) 2002-01-31

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