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EP1311762B1 - Internal geared wheel pump - Google Patents

Internal geared wheel pump Download PDF

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Publication number
EP1311762B1
EP1311762B1 EP01960144A EP01960144A EP1311762B1 EP 1311762 B1 EP1311762 B1 EP 1311762B1 EP 01960144 A EP01960144 A EP 01960144A EP 01960144 A EP01960144 A EP 01960144A EP 1311762 B1 EP1311762 B1 EP 1311762B1
Authority
EP
European Patent Office
Prior art keywords
sealing plate
internal gear
gear pump
spring
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
EP01960144A
Other languages
German (de)
French (fr)
Other versions
EP1311762A1 (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
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP1311762A1 publication Critical patent/EP1311762A1/en
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Publication of EP1311762B1 publication Critical patent/EP1311762B1/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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C14/14—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/70—Safety, emergency conditions or requirements
    • F04C2270/701—Cold start

Definitions

  • the invention relates to an internal gear pump for conveying fuel from a suction channel in a pressure channel, with a pump housing, in which an internally toothed ring gear and driven by a drive shaft external gear pinion are mounted, wherein the pinion is arranged eccentrically to the toothed ring and for generating a pumping action cooperates with the toothed ring, wherein the pinion and the toothed ring abut with its one end face on the pump housing and with its other end face on a sealing plate.
  • Such an internal gear pump is known for example from US-A-3 515 496 and is also referred to as a gerotor pump or gerotopump.
  • the toothed ring and the pinion represent the pump elements and are also referred to as outer rotor and inner rotor.
  • 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 engine ensures that the axial play is equal to zero.
  • the object is in an internal gear pump for conveying fuel from a suction channel in a pressure channel, with a pump housing in which an internally toothed ring and a drive shaft driven by an externally toothed pinion are mounted, wherein the pinion is arranged eccentrically to the toothed ring and for generating a Pumping action cooperates with the toothed ring, wherein the pinion and the toothed ring abut with its one end face on the pump housing and with its other end face on a sealing plate, achieved in that the suction channel is arranged in the sealing plate, and that the sealing plate relative to the pump housing so is movable, that the distance between the suction channel and the pressure channel can be changed.
  • a particular embodiment of the invention is characterized in that the suction channel is formed by an elongated recess in the circumferential direction of the sealing plate, and that the sealing plate is rotatable relative to the pump housing between two positions.
  • the two positions of the sealing plate are made possible by abutment surfaces which are formed on the sealing plate.
  • Another particular embodiment of the invention is characterized; in that the sealing plate is prestressed in the axial direction by means of a spring, which is coupled to the pump housing and to the sealing plate.
  • a spring which is coupled to the pump housing and to the sealing plate.
  • Another particular embodiment of the invention is characterized in that the spring is biased in the circumferential direction against the drive direction of the internal gear pump. Due to the spring preload in the circumferential direction is achieved that the sealing plate only rotated when a certain speed of the pinion is exceeded.
  • the spring comprises two curved legs which at one end with each other connected and coupled to the sealing plate, and which are coupled at the other end to the pump housing. Due to the inventive design of the spring, a bias of the spring in both the axial direction and in the circumferential direction is made possible by simple means.
  • Another particular embodiment of the invention is characterized in that on the side facing away from the toothed ring and the pinion side of the sealing plate at a certain distance a pin is axially displaceable, which cooperates with a further spring to counteract a movement of the sealing plate in the axial direction ,
  • the distance between the sealing plate and the pin is chosen so that the sealing plate comes in full load operation on one end of the pin to the plant.
  • the biasing force of the other spring, its spring rate and the displacement of the sealing plate in the axial direction to a stop define the maximum operating pressure of the internal gear pump.
  • suction channel is in communication with a fuel inlet whose longitudinal axis coincides with the longitudinal axis of the drive shaft. This design has proven to be particularly advantageous in practice.
  • Another particular embodiment of the invention is characterized in that the fuel inlet opens into a sleeve in which the further spring is received and are mounted in the radial holes for the passage of fuel.
  • the sleeve forms a stop which limits the axial movement of the sealing plate.
  • a bypass valve is housed, which communicates via an axial bore with the suction channel and via a second axial bore with the pressure channel in connection.
  • a bypass valve in the context of the present invention means axially in the direction of the longitudinal axis of the drive shaft of the internal gear pump.
  • the bypass valve allows, e.g. with the help of an additional hand-operated pump to pump the fuel at the same when the internal gear pump is not driven.
  • the internal gear pump shown in Figures 1 to 4 comprises a pump housing 1.
  • a drive shaft 2 is rotatably mounted.
  • an internal gear or pinion 3 is driven, which is attached to the end of the drive shaft 2 by means of a tolerance ring 4.
  • the internal gear 3 is in engagement with an external gear 5, which is also referred to as a toothed ring.
  • the external gear 5 is surrounded by a bearing ring 6 which is fixed by means of screws 7 and 8 on the pump housing 1.
  • the screw heads of the screws 7 and 8 are designated 9 and 10.
  • the drive shaft 2 is biased by means of a plate spring 12, which is supported against an attached in a groove of the drive shaft 2 Seeger ring 11, away from the internal gear 3 to the left.
  • a plate spring 12 which is supported against an attached in a groove of the drive shaft 2 Seeger ring 11, away from the internal gear 3 to the left.
  • the internal gear 3 is held on the pump housing 1 in abutment.
  • a sealing plate 13 At the other end of the gears 3 and 5 is a sealing plate 13 at.
  • the sealing plate 13 is held by means of a spring 14 in contact with the gears 3 and 5.
  • the spring 14 comprises, as can be seen in Figure 3, two curved legs 15 and 16. Two bent ends of the curved legs 15 and 16 are received in a blind hole 27 of the sealing plate 13. The other two ends of the legs 15 and 16 are attached to the screw heads 9 and 10 and thus on the pump housing 1.
  • connection bores 21 and 20 The suction channel 18 and the pressure channel 19 are connected via connection bores 21 and 20 with a bypass valve 22 in connection.
  • the spring-biased check valve 22 When the spring-biased check valve 22 is opened, the two communication holes 20 and 21 communicate with each other.
  • the bypass valve 22 When the bypass valve 22 is closed, the communication between the communication holes 20 and 21 is closed, and the pressure passage 19 communicates with a pressure port 23 via the communication bore 20.
  • the recessed in the sealing plate 13 suction channel communicates with a suction chamber 24 in communication, which is surrounded by a housing cover 35.
  • the housing cover 35 is placed on the Pumpengekorue 1.
  • a central fuel inlet bore 36 is recessed.
  • FIG. 1 it can be seen that on the side facing away from the drive shaft 2 side of the sealing plate 13, a pin 28 is arranged. Between the sealing plate 13 and a Front side of the pin 28 is provided a certain distance. The pin 28 is acted upon by the biasing force of a compression spring 29 which is received in a sleeve 30. In addition, the pin 28 is slidably guided in the sleeve 30 in the axial direction. The sleeve 30 is fixed coaxially to the fuel inlet bore 36 in the interior of the housing cover 35. In the lateral surface of the sleeve 30 holes 31 and 32 are recessed to ensure the passage of fuel from the fuel inlet 36 into the suction chamber 24.
  • the internal gear 3 of the pump is driven by the drive shaft 2 and the tolerance ring 4.
  • the diaphragm spring 12 also holds the internal gear 3 in contact against the plane surface of the pump housing 1, against any axial force from the input clutch.
  • the pump housing 1 supports the drive shaft 2 and includes the pressure passage 19, the communication bore 20 to the pressure port 23, and the bypass valve 22
  • the bore 21 connects the bypass valve 22 with the suction chamber 24 of the internal gear pump and allows, for example by a hand-operated pump to convey the fuel with non-driven internal gear pump on the pumping elements.
  • the pump housing 1 is supported by means of the bearing ring 6, the outer gear 5.
  • the sealing plate 13 is applied without play in the start state to the gears 3 and 5 and slightly pressed by the spring 14.
  • the force of the spring 14 is designed for the start of the internal gear pump so that a sufficient fuel pressure to fill the low pressure system is ensured.
  • the second function of the spring 14 is to hold the sealing plate 13 during the starting process in a rotated against the gear direction of rotation position. This position guarantees maximum delivery Starting speed. Die.Dichtplatte 13 is therefore pressed by the spring 14 against the gear direction of rotation of the stop 26, designed as a screw head 10.
  • the plate 13 has no contact with the bearing ring 6, which is achieved by a clearance of about 0.01 mm.

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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 aus einem Saugkanal in einen Druckkanal, mit einem Pumpengehäuse, in dem ein innenverzahnter Zahnring und ein durch eine Antriebswelle angetriebenes außenverzahntes Ritzel gelagert sind, wobei das Ritzel exzentrisch zu dem Zahnring angeordnet ist und zum Erzeugen einer Pumpwirkung mit dem Zahnring zusammenwirkt, wobei das Ritzel und der Zahnring mit ihrer einen Stirnseite an dem Pumpengehäuse und mit ihrer anderen Stirnseite an einer Dichtplatte anliegen.The invention relates to an internal gear pump for conveying fuel from a suction channel in a pressure channel, with a pump housing, in which an internally toothed ring gear and driven by a drive shaft external gear pinion are mounted, wherein the pinion is arranged eccentrically to the toothed ring and for generating a pumping action cooperates with the toothed ring, wherein the pinion and the toothed ring abut with its one end face on the pump housing and with its other end face on a sealing plate.

Eine derartige Innenzahnradpumpe ist z.B. aus der US-A-3 515 496 bekannt und wird auch als Zahnringpumpe oder Gerotopumpe 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 Druckscheibe vorgespannt ist, sorgt beim Starten der Brennkraftmaschine dafür, dass das Axialspiel gleich Null ist.Such an internal gear pump is known for example from US-A-3 515 496 and is also referred to as a gerotor pump or gerotopump. The toothed ring and the pinion represent the pump elements and are also referred to as outer rotor and inner rotor. In 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 engine ensures that the axial play is equal to zero.

Beim Betreiben einer Brennkraftmaschine mit einer derartigen Innenzahnradpumpe hat sich herausgestellt, dass beim Starten der Brennkraftmaschine die maximale Förderleistung der Innenzahnradpumpe erforderlich ist. Wenn die Brennkraftmaschine ihre volle Drehzahl erreicht hat, reicht eine geringere Förderleistung aus, um eine ausreichende Kraftstoffversorgung der Brennkraftmaschine sicherzustellen.When operating an internal combustion engine with such an internal gear pump has been found that when starting the internal combustion engine, the maximum capacity of the internal gear pump is required. When the internal combustion engine has reached its full speed, a lower delivery rate is sufficient to ensure sufficient fuel supply to the internal combustion engine.

Aufgabe der Erfindung ist es, eine Innenzahnradpumpe der eingangs geschilderten Art bereitzustellen, die bei Startdrehzahl Null-Axialspiel aufweist und deren Förderleistung nach Überschreiten der Startdrehzahl abnimmt. Dabei soll die erfindungsgemäße Innenzahnradpumpe kostengünstig herstellbar sein und eine hohe Lebensdauer aufweisen.The object of the invention is to provide an internal gear pump of the type described, which has zero axial play at start speed and whose delivery rate decreases after exceeding the starting speed. In this case, the internal gear pump according to the invention should be inexpensive to produce and have a long service life.

Die Aufgabe ist bei einer Innenzahnradpumpe zum Fördern von Krafststoff aus einem Saugkanal in einen Druckkanal, mit einem Pumpengehäuse, in dem ein innenverzahnter Zahnring und ein durch eine Antriebswelle angetriebenes außenverzahntes Ritzel gelagert sind, wobei das Ritzel exzentrisch zu dem Zahnring angeordnet ist und zum Erzeugen einer Pumpwirkung mit dem Zahnring zusammenwirkt, wobei das Ritzel und der Zahnring mit ihrer einen Stirnseite an dem Pumpengehäuse und mit ihrer anderen Stirnseite an einer Dichtplatte anliegen, dadurch gelöst, dass der Saugkanal in der Dichtplatte angeordnet ist, und dass die Dichtplatte relativ zum dem Pumpengehäuse so bewegbar ist, dass der Abstand zwischen dem Saugkanal und dem Druckkanal verändert werden kann.The object is in an internal gear pump for conveying fuel from a suction channel in a pressure channel, with a pump housing in which an internally toothed ring and a drive shaft driven by an externally toothed pinion are mounted, wherein the pinion is arranged eccentrically to the toothed ring and for generating a Pumping action cooperates with the toothed ring, wherein the pinion and the toothed ring abut with its one end face on the pump housing and with its other end face on a sealing plate, achieved in that the suction channel is arranged in the sealing plate, and that the sealing plate relative to the pump housing so is movable, that the distance between the suction channel and the pressure channel can be changed.

Vorteile der ErfindungAdvantages of the invention

Wenn der Abstand zwischen dem Saugkanal und dem Druckkanal verkleinert wird, hat dies zur Folge, dass die Förderleistung der Innenzahnradpumpe abnimmt. Das liefert den Vorteil, dass auf eine bei herkömmlichen Innenzahnradpumpen erforderliche Saugdrossel verzichtet werden kann.If the distance between the suction channel and the pressure channel is reduced, this has the consequence that the Flow rate of the internal gear pump decreases. This provides the advantage that it can be dispensed with a suction throttle required in conventional internal gear pumps.

Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Saugkanal von einer länglichen Aussparung in Umfangsrichtung der Dichtplatte gebildet wird, und dass die Dichtplatte relativ zu dem Pumpengehäuse zwischen zwei Stellungen drehbar ist. Die zwei Stellungen der Dichtplatte werden durch Anschlagflächen ermöglicht, die an der Dichtplatte ausgebildet sind. Über die Wahl einer geeigneten Geometrie der länglichen Aussparung kann zudem erreicht werden, dass sich der wirksame Durchflussquerschnitt des Saugkanals beim Verdrehen ändert.A particular embodiment of the invention is characterized in that the suction channel is formed by an elongated recess in the circumferential direction of the sealing plate, and that the sealing plate is rotatable relative to the pump housing between two positions. The two positions of the sealing plate are made possible by abutment surfaces which are formed on the sealing plate. By choosing a suitable geometry of the elongate recess can also be achieved that the effective flow cross-section of the suction channel changes during rotation.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet; dass die Dichtplatte mit Hilfe einer Feder, die mit dem Pumpengehäuse und mit der Dichtplatte gekoppelt ist, in axialer Richtung vorgespannt ist. Durch die Federvorspannung in axialer Richtung wird erreicht, dass eine Bewegung der Dichtplatte in axialer Richtung erst dann erfolgt, wenn ein bestimmter Druck im Pumpenraum überschritten wird.Another particular embodiment of the invention is characterized; in that the sealing plate is prestressed in the axial direction by means of a spring, which is coupled to the pump housing and to the sealing plate. By the spring bias in the axial direction is achieved that a movement of the sealing plate in the axial direction takes place only when a certain pressure in the pump chamber is exceeded.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Feder in Umfangsrichtung entgegen der Antriebsrichtung der Innenzahnradpumpe vorgespannt ist. Durch die Federvorspannung in Umfangsrichtung wird erreicht, dass sich die Dichtplatte erst dann verdreht, wenn eine bestimmte Drehzahl des Ritzels überschritten wird.Another particular embodiment of the invention is characterized in that the spring is biased in the circumferential direction against the drive direction of the internal gear pump. Due to the spring preload in the circumferential direction is achieved that the sealing plate only rotated when a certain speed of the pinion is exceeded.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Feder zwei gekrümmte Schenkel umfasst, die an dem einen Ende miteinander verbunden und mit der Dichtplatte gekoppelt sind, und die an dem anderen Ende mit dem Pumpengehäuse gekoppelt sind. Durch die erfindungsgemäße Ausgestaltung der Feder wird mit einfachen Mitteln eine Vorspannung der Feder sowohl in axialer Richtung als auch in Umfangsrichtung ermöglicht.Another particular embodiment of the invention is characterized in that the spring comprises two curved legs which at one end with each other connected and coupled to the sealing plate, and which are coupled at the other end to the pump housing. Due to the inventive design of the spring, a bias of the spring in both the axial direction and in the circumferential direction is made possible by simple means.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass auf der von dem Zahnring und dem Ritzel abgewandten Seite der Dichtplatte in einem bestimmten Abstand ein Stift axial verschiebbar geführt ist, der mit einer weiteren Feder zusammenwirkt, um eine Bewegung der Dichtplatte in axialer Richtung entgegenzuwirken. Der Abstand zwischen der Dichtplatte und dem Stift ist dabei so gewählt, dass die Dichtplatte im Volllastbetrieb an einer Stirnseite des Stifts zur Anlage kommt. Wenn der Druck im Pumpenraum weiter ansteigt, bewegt sich die Dichtplatte weiter gegen die Vorspannkraft der weiteren Feder. Die Vorspannkraft der weiteren Feder, ihre Federrate und die Verschiebung der Dichtplatte in axialer Richtung bis zu einem Anschlag definieren den maximalen Betriebsdruck der Innenzahnradpumpe.Another particular embodiment of the invention is characterized in that on the side facing away from the toothed ring and the pinion side of the sealing plate at a certain distance a pin is axially displaceable, which cooperates with a further spring to counteract a movement of the sealing plate in the axial direction , The distance between the sealing plate and the pin is chosen so that the sealing plate comes in full load operation on one end of the pin to the plant. As the pressure in the pump chamber continues to rise, the sealing plate continues to move against the biasing force of the other spring. The biasing force of the other spring, its spring rate and the displacement of the sealing plate in the axial direction to a stop define the maximum operating pressure of the internal gear pump.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Saugkanal mit einem Kraftstoffzulauf in Verbindung steht, dessen Längsachse mit der Längsachse der Antriebswelle zusammenfällt. Diese Bauform hat sich in der Praxis als besonders vorteilhaft erwiesen.Another particular embodiment of the invention is characterized in that the suction channel is in communication with a fuel inlet whose longitudinal axis coincides with the longitudinal axis of the drive shaft. This design has proven to be particularly advantageous in practice.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Kraftstoffzulauf in eine Hülse mündet, in der die weitere Feder aufgenommen ist und in der radiale Bohrungen zum Durchtritt von Kraftstoff angebracht sind. Die Hülse bildet einen Anschlag, der die axiale Bewegung der Dichtplatte begrenzt.Another particular embodiment of the invention is characterized in that the fuel inlet opens into a sleeve in which the further spring is received and are mounted in the radial holes for the passage of fuel. The sleeve forms a stop which limits the axial movement of the sealing plate.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass in dem Pumpengehäuse ein Umgehungsventil untergebracht ist, das über eine axiale Bohrung mit dem Saugkanal und über eine zweite axiale Bohrung mit dem Druckkanal in Verbindung steht. Im Rahmen der vorliegenden Erfindung bedeutet axial in Richtung der Längsachse der Antriebswelle der Innenzahnradpumpe. Das Umgehungsventil erlaubt, z.B. mit Hilfe einer zusätzlichen handbetätigten Pumpe, den Kraftstoff bei nicht angetriebener Innenzahnradpumpe an der selben vorbeizufördern.Another particular embodiment of the invention is characterized in that in the pump housing, a bypass valve is housed, which communicates via an axial bore with the suction channel and via a second axial bore with the pressure channel in connection. In the context of the present invention means axially in the direction of the longitudinal axis of the drive shaft of the internal gear pump. The bypass valve allows, e.g. with the help of an additional hand-operated pump to pump the fuel at the same when the internal gear pump is not driven.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung ein Ausführungsbeispiel der Erfindung im Einzelnen beschrieben ist. Dabei können die in den Ansprüche und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein.Further advantages, features and details of the invention will become apparent from the following description in which, with reference to the drawing, an embodiment of the invention is described in detail. The features mentioned in the claims and in the description may each be essential to the invention individually or in any desired combination.

Zeichnungdrawing

In der Zeichnung zeigen:

Figur 1
eine Ausführungsform einer erfindungsgemäßen Innenzahnradpumpe im Längsschnitt;
Figur 2
die Ansicht eines Schnitts entlang der Linie II-II in Figur 1;
Figur 3
die Ansicht eines Schnitts entlang der Linie III-III in Figur 1; und
Figur 4
die Ansicht eines Schnitts entlang der Linie IV-IV in Figur 1.
In the drawing show:
FIG. 1
an embodiment of an internal gear pump according to the invention in longitudinal section;
FIG. 2
the view of a section along the line II-II in Figure 1;
FIG. 3
the view of a section along the line III-III in Figure 1; and
FIG. 4
the view of a section along the line IV-IV in Figure 1.

Die in den Figuren 1 bis 4 dargestellte Innenzahnradpumpe umfasst ein Pumpengehäuse 1. In dem Pumpengehäuse 1 ist eine Antriebswelle 2 drehbar gelagert. Mit der Antriebswelle 2 wird ein Innenzahnrad oder Ritzel 3 angetrieben, das am Ende der Antriebswelle 2 mit Hilfe eines Toleranzrings 4 angebracht ist. Das Innenzahnrad 3 befindet sich in Eingriff mit einem Außenzahnrad 5, das auch als Zahnring bezeichnet wird. Das Außenzahnrad 5 wird von einem Lagerring 6 umgeben, der mit Hilfe von Schrauben 7 und 8 am Pumpengehäuse 1 befestigt ist. Die Schraubenköpfe der Schrauben 7 und 8 sind mit 9 und 10 bezeichnet.The internal gear pump shown in Figures 1 to 4 comprises a pump housing 1. In the pump housing 1, a drive shaft 2 is rotatably mounted. With the drive shaft 2, an internal gear or pinion 3 is driven, which is attached to the end of the drive shaft 2 by means of a tolerance ring 4. The internal gear 3 is in engagement with an external gear 5, which is also referred to as a toothed ring. The external gear 5 is surrounded by a bearing ring 6 which is fixed by means of screws 7 and 8 on the pump housing 1. The screw heads of the screws 7 and 8 are designated 9 and 10.

Die Antriebswelle 2 ist mit Hilfe einer Tellerfeder 12, die sich gegen eine in einer Nut der Antriebswelle 2 befestigten Seegerring 11 abstützt, von dem Innenzahnrad 3 weg nach links vorgespannt. Durch die Vorspannkraft der Tellerfeder 12 wird das Innenzahnrad 3 an dem Pumpengehäuse 1 in Anlage gehalten. An der anderen Stirnseite der Zahnräder 3 und 5 liegt eine Dichtplatte 13 an. Die Dichtplatte 13 wird mit Hilfe einer Feder 14 in Anlage an den Zahnrädern 3 und 5 gehalten. Die Feder 14 umfasst, wie in Figur 3 zu sehen ist, zwei gekrümmte Schenkel 15 und 16. Zwei umgebogene Enden der gekrümmten Schenkel 15 und 16 sind in einem Sackloch 27 der Dichtplatte 13 aufgenommen. Die beiden anderen Enden der Schenkel 15 und 16 sind an den Schraubenköpfen 9 und 10 und somit am Pumpengehäuse 1 befestigt.The drive shaft 2 is biased by means of a plate spring 12, which is supported against an attached in a groove of the drive shaft 2 Seeger ring 11, away from the internal gear 3 to the left. By the biasing force of the plate spring 12, the internal gear 3 is held on the pump housing 1 in abutment. At the other end of the gears 3 and 5 is a sealing plate 13 at. The sealing plate 13 is held by means of a spring 14 in contact with the gears 3 and 5. The spring 14 comprises, as can be seen in Figure 3, two curved legs 15 and 16. Two bent ends of the curved legs 15 and 16 are received in a blind hole 27 of the sealing plate 13. The other two ends of the legs 15 and 16 are attached to the screw heads 9 and 10 and thus on the pump housing 1.

In Figur 4 ist die Drehrichtung der Antriebswelle 2 durch einen Pfeil 34 angedeutet. Wenn das Innenzahnrad 3 in Richtung des Pfeils 34 angetrieben wird, wird der in einem Druckraum 17 befindliche Kraftstoff komprimiert. Gleichzeitig wird, wie in Figur 3 zu sehen ist, Kraftstoff aus einem Saugkanal 18, der in der Dichtplatte 13 ausgespart ist, angesaugt. Der angesaugte Kraftstoff wird in dem Druckraum 17 komprimiert und gelangt dann in einen Druckkanal 19, der, wie in Figur 3 gestrichelt angedeutet ist, in dem Pumpengehäuse 1 ausgenommen ist.In Figure 4, the direction of rotation of the drive shaft 2 is indicated by an arrow 34. When the internal gear 3 is driven in the direction of the arrow 34, the fuel located in a pressure chamber 17 is compressed. At the same time, as can be seen in Figure 3, fuel from a suction channel 18, which is recessed in the sealing plate 13, sucked. The sucked fuel is compressed in the pressure chamber 17 and then passes into a pressure channel 19, which, as indicated by dashed lines in Figure 3, is excluded in the pump housing 1.

Der Saugkanal 18 und der Druckkanal 19 stehen über Verbindungsbohrungen 21 und 20 mit einem Umgehungsventil 22 in Verbindung. Wenn das federvorgespannte Rückschlagventil 22 geöffnet ist, stehen die beiden Verbindungsbohrungen 20 und 21 miteinander in Verbindung. Wenn das Umgehungsventil 22 geschlossen ist, ist die Verbindung zwischen den Verbindungsbohrungen 20 und 21 geschlossen und der Druckkanal 19 steht über die Verbindungsbohrung 20 mit einem Druckanschluss 23 in Verbindung.The suction channel 18 and the pressure channel 19 are connected via connection bores 21 and 20 with a bypass valve 22 in connection. When the spring-biased check valve 22 is opened, the two communication holes 20 and 21 communicate with each other. When the bypass valve 22 is closed, the communication between the communication holes 20 and 21 is closed, and the pressure passage 19 communicates with a pressure port 23 via the communication bore 20.

Der in der Dichtplatte 13 ausgesparte Saugkanal steht mit einem Saugraum 24 in Verbindung, der von einem Gehäusedeckel 35 umgeben ist. Der Gehäusedeckel 35 ist auf das Pumpengehäue 1 aufgesetzt. In dem Gehäusedeckel 35 ist eine zentrale Kraftstoffzulaufbohrung 36 ausgespart.The recessed in the sealing plate 13 suction channel communicates with a suction chamber 24 in communication, which is surrounded by a housing cover 35. The housing cover 35 is placed on the Pumpengehäue 1. In the housing cover 35, a central fuel inlet bore 36 is recessed.

Am äußeren Umfang der Dichtplatte 13 sind diametral entgegengesetzt zwei rechteckförmige Ausnehmungen vorgesehen. Die beiden gegenüberliegenden Seiten der Ausnehmungen bilden zusammen mit den Schraubenköpfen 9 und 10 Anschläge 25 und 26 für eine Drehbewegung der Dichtplatte 13. In der in Figur 3 dargestellten Stellung der Dichtplatte 13 befinden sich die Anschlagflächen 26 in Anlage an den Schraubenköpfen 9 und 10. Durch einen Pfeil 44 ist angedeutet, dass sich die Dichtplatte 13 mit zunehmender Drehzahl der Antriebswelle 2 verdreht, bis die Anschlagflächen 25 an den Schraubenköpfen 9 und 10 anliegen.At the outer periphery of the sealing plate 13 diametrically opposite two rectangular recesses are provided. The two opposite sides of the recesses form together with the screw heads 9 and 10 stops 25 and 26 for a rotational movement of the sealing plate 13. In the position of the sealing plate 13 shown in Figure 3, the stop surfaces 26 are in abutment with the screw heads 9 and 10. Durch an arrow 44 is indicated that the sealing plate 13 is rotated with increasing speed of the drive shaft 2 until the stop surfaces 25 abut the screw heads 9 and 10.

In Figur 1 sieht man, dass auf der von der Antriebswelle 2 abgewandten Seite der Dichtplatte 13 ein Stift 28 angeordnet ist. Zwischen der Dichtplatte 13 und einer Stirnseite des Stifts 28 ist ein bestimmter Abstand vorgesehen. Der Stift 28 ist mit der Vorspannkraft einer Druckfeder 29 beaufschlagt, die in einer Hülse 30 aufgenommen ist. Außerdem ist der Stift 28 in axialer Richtung verschiebbar in der Hülse 30 geführt. Die Hülse 30 ist koaxial zu der Kraftstoffzulaufbohrung 36 im Inneren des Gehäusedeckels 35 befestigt. In der Mantelfläche der Hülse 30 sind Bohrungen 31 und 32 ausgespart, um den Durchtritt von Kraftstoff von dem Kraftstoffzulauf 36 in den Saugraum 24 zu gewährleisten.In Figure 1 it can be seen that on the side facing away from the drive shaft 2 side of the sealing plate 13, a pin 28 is arranged. Between the sealing plate 13 and a Front side of the pin 28 is provided a certain distance. The pin 28 is acted upon by the biasing force of a compression spring 29 which is received in a sleeve 30. In addition, the pin 28 is slidably guided in the sleeve 30 in the axial direction. The sleeve 30 is fixed coaxially to the fuel inlet bore 36 in the interior of the housing cover 35. In the lateral surface of the sleeve 30 holes 31 and 32 are recessed to ensure the passage of fuel from the fuel inlet 36 into the suction chamber 24.

Das Innenzahnrad 3 der Pumpe ist durch die Antriebswelle 2 und den Toleranzring 4 angetrieben. Die Tellerfeder 12 hält das Innenzahnrad 3 auch entgegen einer eventuell auftretenden Axialkraft von der Antriebskupplung nach innen in Kontakt zur Planfläche des Pumpengehäuses 1. Das Pumpengehäuse 1 lagert die Antriebswelle 2, und enthält den Druckkanal 19, die Verbindungsbohrung 20 zum Druckanschluss 23 und das Umgehungsventil 22. Die Bohrung 21 verbindet das Umgehungsventil 22 mit dem Saugraum 24 der Innenzahnradpumpe und erlaubt, z.B. durch eine handbetätigte Pumpe, den Kraftstoff bei nicht angetriebener Innenzahnradpumpe an den Pumpelementen vorbeizufördern.The internal gear 3 of the pump is driven by the drive shaft 2 and the tolerance ring 4. The diaphragm spring 12 also holds the internal gear 3 in contact against the plane surface of the pump housing 1, against any axial force from the input clutch. The pump housing 1 supports the drive shaft 2 and includes the pressure passage 19, the communication bore 20 to the pressure port 23, and the bypass valve 22 The bore 21 connects the bypass valve 22 with the suction chamber 24 of the internal gear pump and allows, for example by a hand-operated pump to convey the fuel with non-driven internal gear pump on the pumping elements.

Das Pumpengehäuse 1 lagert mit Hilfe des Lagerrings 6 das Außenzahnrad 5. Die Dichtplatte 13 ist im Startzustand an die Zahnräder 3 und 5 spielfrei angelegt und mittels der Feder 14 leicht angedrückt. Die Kraft der Feder 14 ist für den Start der Innenzahnradpumpe so ausgelegt, dass ein ausreichender Kraftstoffdruck zur Befüllung des Niederdrucksystems gewährleistet ist.The pump housing 1 is supported by means of the bearing ring 6, the outer gear 5. The sealing plate 13 is applied without play in the start state to the gears 3 and 5 and slightly pressed by the spring 14. The force of the spring 14 is designed for the start of the internal gear pump so that a sufficient fuel pressure to fill the low pressure system is ensured.

Die zweite Funktion der Feder 14 besteht darin, die Dichtplatte 13 beim Startvorgang in einer gegen die Zahnraddrehrichtung verdrehten Position zu halten. Diese Position garantiert das Maximum an Fördermenge bei Startdrehzahl. Die.Dichtplatte 13 ist also durch die Feder 14 gegen die Zahnraddrehrichtung an den Anschlag 26 gedrückt, ausgebildet als Schraubenkopf 10. Die Platte 13 hat mit dem Lagerring 6 keinen Kontakt, was durch ein Spiel von etwa 0,01 mm erreicht wird.The second function of the spring 14 is to hold the sealing plate 13 during the starting process in a rotated against the gear direction of rotation position. This position guarantees maximum delivery Starting speed. Die.Dichtplatte 13 is therefore pressed by the spring 14 against the gear direction of rotation of the stop 26, designed as a screw head 10. The plate 13 has no contact with the bearing ring 6, which is achieved by a clearance of about 0.01 mm.

Wenn die Drehzahl steigt und der Durchfluss durch den Saugkanal 18 die Leerlaufmenge erreicht, verdreht sich die Platte 13, bis die gegenüberliegende Anschlagfläche 25 sich an den Schraubenkopf 10 anlegt. Das bewirkt eine Begrenzung der Fördermenge bei steigender Drehzahl. Es ist somit keine Saugdrosselung der Pumpe notwendig, wodurch die Kavitationsneigung verringert wird. Im Volllastbetrieb legt sich die Dichtplatte 13 an den Stift 28 an. Wenn der Druck im Druckraum 17 einen Grenzwert erreicht, bewegt sich die Platte 13 weiter nach rechts und drückt über den Stift 28 auf die Feder 29.When the speed increases and the flow through the suction channel 18 reaches the idling amount, the plate 13 rotates until the opposing abutment surface 25 abuts the screw head 10. This causes a limitation of the flow rate with increasing speed. There is thus no Saugdrosselung the pump necessary, whereby the Kavitationsneigung is reduced. In full load operation, the sealing plate 13 applies to the pin 28. When the pressure in the pressure chamber 17 reaches a limit, the plate 13 moves further to the right and pushes on the pin 28 on the spring 29th

Claims (9)

  1. Internal gear pump for the conveyance of fuel out of a suction duct (18) into a delivery duct (19), with a pump casing (1) in which an internally toothed ring (5) and an externally toothed pinion (3) driven by a drive shaft (2) are mounted, the pinion (3) being arranged eccentrically with respect to the toothed ring (5) and cooperating with the toothed ring (5) in order to generate a pumping action, the pinion (3), and the toothed ring (5) bearing with their first end face against the pump case (1) and with their other end face against the sealing plate (13), characterized in that the suction duct (18) is arranged in the sealing plate (13), and in that the sealing plate (13) is movable in relation to the pump casing (1) such that the distance between the suction duct (18) and the delivery duct (19) can be varied.
  2. Internal gear pump according to Claim 1, characterized in that the suction duct (18) is formed by an elongate clearance in the circumferential direction of the sealing plate (13) and in that the sealing plate (13) is rotatable between two points in relation to the pump casing (1).
  3. Internal gear pump according to Claim 2, characterized in that the sealing plate (13) is prestressed in the axial direction with the aid of a spring (14) which is coupled to the pump casing (1) and to the sealing plate (13).
  4. Internal gear pump according to Claim 3, characterized in that the spring (14) is prestressed in the circumferential direction counter to the driving direction of the internal gear pump.
  5. Internal gear pump according to Claim 3 or 4, characterized in that the spring (14) comprises two curved legs (15, 16) which at one end are connected to one another and are coupled to the sealing plate (13) and at the other end are coupled to the pump casing (1).
  6. Internal gear pump according to one of Claims 3 to 5, characterized in that, on that side of the sealing plate (13) which faces away from the toothed ring (5) and the pinion (3), a pin (28) is guided axially displaceably at a specific distance and cooperates with a further spring (29), in order to counteract the movement of the sealing plate (13) in the axial direction.
  7. Internal gear pump according to one of the preceding claims, characterized in that the suction duct (18) is connected to a fuel inflow (36), the longitudinal axis of which coincides with the longitudinal axis of the drive shaft (2).
  8. Internal gear pump according to Claim 7, characterized in that the fuel inflow (36) issues into a sleeve (30), in which the further spring (29) is received and in which radial bores (31, 32) for the passage of fuel are formed.
  9. Internal gear pump according to one of the preceding claims, characterized in that the pump casing accommodates a bypass valve (22) which is connected to the suction duct (18) via a first axial bore (21) and is connected to the delivery duct (19) via a second axial bore (20).
EP01960144A 2000-08-19 2001-08-03 Internal geared wheel pump Expired - Lifetime EP1311762B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10040692 2000-08-19
DE10040692A DE10040692C1 (en) 2000-08-19 2000-08-19 Internal gear pump to supply fuel from suction to pressure channel has internally toothed ring gear and eccentric outer toothed pinion driven on drive shaft, to form pump action
PCT/DE2001/002965 WO2002016772A1 (en) 2000-08-19 2001-08-03 Internal geared wheel pump

Publications (2)

Publication Number Publication Date
EP1311762A1 EP1311762A1 (en) 2003-05-21
EP1311762B1 true EP1311762B1 (en) 2006-09-20

Family

ID=7653068

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01960144A Expired - Lifetime EP1311762B1 (en) 2000-08-19 2001-08-03 Internal geared wheel pump

Country Status (6)

Country Link
US (1) US6764283B2 (en)
EP (1) EP1311762B1 (en)
JP (1) JP2004507640A (en)
CZ (1) CZ299441B6 (en)
DE (2) DE10040692C1 (en)
WO (1) WO2002016772A1 (en)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN106795878A (en) * 2014-08-25 2017-05-31 开利公司 Gear pump with double pressure reduction

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Publication number Priority date Publication date Assignee Title
DE10058012A1 (en) * 2000-11-23 2002-05-29 Bosch Gmbh Robert Gear pump, in particular for delivering fuel to a high-pressure fuel pump
WO2007120503A2 (en) * 2006-03-31 2007-10-25 Metaldyne Company, Llc Variable displacement gerotor pump
JP4842341B2 (en) * 2009-03-23 2011-12-21 日立オートモティブシステムズ株式会社 Gear pump and gear pump for brake device
DE102011075415A1 (en) * 2011-05-06 2012-11-08 Robert Bosch Gmbh Gear pump e.g. outer gear wheel pump, for use in fuel injection system of Otto engine to convey fuel from low pressure region into high pressure region, has axially displaceable sealing plates resiliently prestressed in direction of chamber
DE102015010997B4 (en) * 2015-08-21 2025-07-03 Bernd Niethammer Eccentric pump, in particular feed pump for aqueous urea solutions, and feed device with an eccentric pump

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US2405061A (en) * 1942-12-02 1946-07-30 Eaton Mfg Co Pump structure
US3026809A (en) * 1956-04-06 1962-03-27 Borg Warner Internal-external gear pump
US3515496A (en) * 1968-05-06 1970-06-02 Reliance Electric Co Variable capacity positive displacement pump
DE2650908A1 (en) * 1976-11-06 1978-05-11 Bosch Gmbh Robert INTERNAL GEAR MACHINE (PUMP OR MOTOR)
US4492539A (en) * 1981-04-02 1985-01-08 Specht Victor J Variable displacement gerotor pump
DE3827573A1 (en) * 1988-08-13 1990-02-15 Bosch Gmbh Robert DEVICE FOR PROMOTING FUEL FROM A STORAGE TANK FOR THE INTERNAL COMBUSTION ENGINE, ESPECIALLY A MOTOR VEHICLE
DE4142799C1 (en) * 1991-12-26 1993-04-15 J.M. Voith Gmbh, 7920 Heidenheim, De
CA2219062C (en) * 1996-12-04 2001-12-25 Siegfried A. Eisenmann Infinitely variable ring gear pump

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106795878A (en) * 2014-08-25 2017-05-31 开利公司 Gear pump with double pressure reduction
CN106795878B (en) * 2014-08-25 2019-04-09 开利公司 Gear pump with double pressure relief
US10337512B2 (en) 2014-08-25 2019-07-02 Carrier Corporation Gear pump with dual pressure relief

Also Published As

Publication number Publication date
US6764283B2 (en) 2004-07-20
JP2004507640A (en) 2004-03-11
CZ299441B6 (en) 2008-07-30
WO2002016772A1 (en) 2002-02-28
EP1311762A1 (en) 2003-05-21
US20030026711A1 (en) 2003-02-06
DE50111053D1 (en) 2006-11-02
DE10040692C1 (en) 2001-09-20
CZ20021352A3 (en) 2002-10-16

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