EP1311762A1 - Internal geared wheel pump - Google Patents

Internal geared wheel pump

Info

Publication number
EP1311762A1
EP1311762A1 EP01960144A EP01960144A EP1311762A1 EP 1311762 A1 EP1311762 A1 EP 1311762A1 EP 01960144 A EP01960144 A EP 01960144A EP 01960144 A EP01960144 A EP 01960144A EP 1311762 A1 EP1311762 A1 EP 1311762A1
Authority
EP
European Patent Office
Prior art keywords
sealing plate
internal gear
gear pump
pump housing
suction channel
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.)
Granted
Application number
EP01960144A
Other languages
German (de)
French (fr)
Other versions
EP1311762B1 (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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1311762A1 publication Critical patent/EP1311762A1/en
Application granted granted Critical
Publication of EP1311762B1 publication Critical patent/EP1311762B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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 into a pressure channel, with a pump housing in which an internally toothed toothed ring and an externally toothed pinion driven by a drive shaft are mounted, the pinion being arranged eccentrically to the toothed ring and for producing a pumping effect cooperates with the toothed ring, the
  • Pinion and the toothed ring rest with their one end on the pump housing and with their other end on a sealing plate.
  • Such an internal gear pump is also called
  • Called gerotor pump or gerotor pump The toothed ring and the pinion represent the pump elements and are also referred to as the outer rotor and inner rotor.
  • DE 38 27 573 AI describes an internal gear pump, the gear ring of which is driven by an electric motor.
  • the delivery chambers of the internal gear pump between the teeth of the two pump elements are covered in the axial direction by a thrust washer.
  • the object of the invention is an internal gear pump . of the type described at the outset, which has zero axial play at the starting speed and whose delivery capacity decreases after the starting speed is exceeded.
  • the internal gear pump according to the invention should be inexpensive to manufacture and have a long service life.
  • the task is for an internal gear pump for conveying fuel from a suction channel into a pressure channel, with a pump housing in which an internally toothed toothed ring and an externally toothed pinion driven by a drive shaft are mounted, the pinion being arranged eccentrically to the toothed ring and for generating one Pumping action cooperates with the toothed ring, the pinion and the toothed ring bearing with one end face against the pump housing and with their other end face against a sealing plate, in that the suction channel is arranged in the sealing plate, and in that the sealing plate relative to the pump housing 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 duct is formed by an elongated recess in the circumferential direction of the sealing plate, and that the sealing plate relative to the pump housing between two 'positions is rotatable.
  • the two positions of the sealing plate are made possible by stop surfaces which are formed on the sealing plate.
  • Another special embodiment of the invention is characterized in that; that the sealing plate is biased in the axial direction by means of a spring which is coupled to the pump housing and to the sealing plate.
  • the spring preload in the axial direction ensures that the sealing plate does not move in the axial direction until a certain pressure in the pump chamber is exceeded.
  • 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.
  • the spring preload in the circumferential direction ensures that the sealing plate only rotates when a certain speed of the pinion is exceeded.
  • a further special embodiment of the invention is characterized in that the spring comprises two curved legs which are connected to one another at one end connected and coupled to the sealing plate, and which are coupled at the other end to the pump housing.
  • the inventive design of the spring enables the spring to be pretensioned both in the axial direction and in the circumferential direction by simple means.
  • a further special embodiment of the invention is characterized in that on the side of the sealing plate facing away from the toothed ring and the pinion, a pin is guided axially displaceably at a certain distance and cooperates with a further spring in order to counteract 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 into contact with an end face of the pin in full load operation. If the pressure in the pump chamber continues to rise, the sealing plate continues to move against the biasing force of the additional spring.
  • the preload force of the additional spring, its spring rate and the displacement of the sealing plate in the axial direction up to a stop define the maximum operating pressure of the internal gear pump.
  • a further special embodiment of the invention is characterized in that the suction channel is connected to 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.
  • a further special embodiment of the invention is characterized in that the fuel inlet opens into a sleeve in which the further spring is received and in which radial bores for the passage of fuel are made.
  • the sleeve forms a stop that limits the axial movement of the sealing plate.
  • a further special embodiment of the invention is characterized in that a bypass valve is accommodated in the pump housing, which is connected to the suction channel via an axial bore and to the pressure channel via a second axial bore.
  • axially in the direction of the longitudinal axis of the drive shaft means the internal gear pump.
  • the bypass valve allows, for example with the help of an additional manually operated pump, the fuel to be bypassed when the internal gear pump is not driven.
  • Figure 1 shows an embodiment of an inventive
  • FIG. 2 shows the view of a section along the line II -II in Figure 1;
  • FIGS. 1 to 4 shows the view of a section along the line IV-IV in FIG.
  • the internal gear pump shown in FIGS. 1 to 4 comprises a pump housing 1.
  • a drive shaft 2 is rotatably mounted in the pump housing 1.
  • the drive shaft 2 drives an internal gear or pinion 3, which is attached to the end of the drive shaft 2 with the aid 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 fastened to the pump housing 1 with the aid of screws 7 and 8.
  • the internal gear pump shown in FIGS. 1 to 4 comprises a pump housing 1.
  • a drive shaft 2 is rotatably mounted in the pump housing 1.
  • the drive shaft 2 drives an internal gear or pinion 3, which is attached to the end of the drive shaft 2 with the aid 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
  • Screw heads of screws 7 and 8 are designated 9 and 10.
  • the drive shaft 2 is biased away from the internal gear 3 to the left by means of a plate spring 12, which is supported against a circlip 11 fastened in a groove in the drive shaft 2.
  • the internal gear 3 is held in contact with the pump housing 1 by the biasing force of the plate spring 12.
  • a sealing plate 13 rests on the other end face of the gear wheels 3 and 5.
  • Sealing plate 13 is held in contact with the gears 3 and 5 by means of a spring 14.
  • the spring 14 comprises 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.
  • connection bores 21 and 20 with a bypass valve 22 in connection When the spring-loaded check valve 22 is open, the two connecting bores 20 and 21 are connected to one another. When the bypass valve 22 is closed, the connection between the connection bores 20 and 21 is closed and the pressure channel 19 is connected to a pressure connection 23 via the connection bore 20.
  • the suction channel recessed in the sealing plate 13 is connected to a suction chamber 24 which is surrounded by a housing cover 35.
  • the housing cover 35 is placed on the pump housing 1.
  • a central fuel inlet bore 36 is recessed in the housing cover 35.
  • Sealing plate 13 In the position of the sealing plate 13 shown in FIG. 3, the stop surfaces 26 are in contact with the screw heads 9 and 10. An arrow 44 indicates that the sealing plate 13 rotates with increasing speed of the drive shaft 2 until the stop surfaces 25 rest on the screw heads 9 and 10.
  • a pin 28 is arranged on the side of the sealing plate 13 facing away from the drive shaft 2. Between the sealing plate 13 and one A certain distance is provided on the end face of the pin 28. The pin 28 is acted upon by the prestressing 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 fastened coaxially to the fuel inlet bore 36 in the interior of the housing cover 35. Holes 31 and 32 are recessed in the lateral surface of the sleeve 30 in order to ensure the passage of fuel from the fuel inlet 36 into the suction space 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 against the axial face of the drive clutch in contact with the flat surface of the pump housing 1 against a possible axial force
  • the bore 21 connects the bypass valve 22 to the suction chamber 24
  • Internal gear pump and allowed, e.g. by means of a manually operated pump to call the fuel past the pump elements when the internal gear pump is not driven.
  • the pump housing 1 supports the external gear 5 with the aid of the bearing ring 6.
  • the sealing plate 13 is placed against the gear wheels 3 and 5 without play and is lightly pressed by means of the spring 14.
  • the force of the spring 14 is designed for the start of the internal gear pump so that a sufficient Kra material pressure is guaranteed for filling the low pressure system.
  • the second function of the spring 14 is to hold the sealing plate 13 in a position rotated counter to the direction of gear rotation during the starting process. This position guarantees the maximum flow rate Starting speed.
  • the . Sealing plate 13 is thus pressed by the spring 14 against the gear rotation direction against 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 play of approximately 0.01 mm.

Landscapes

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

Abstract

The invention relates to an internal geared wheel pump for conveying motor fuel from a suction channel port (18) into a pressure channel (19), comprising a pump housing (1) wherein an internally toothed annular gear (5) and an externally toothed pinion gear (3) are disposed and are operated by a drive shaft (2). The pinion gear (3) is arranged eccentrically to the annular gear (5) and interacts with the annular gear (5) to generate a pump effect. One front face of the pinion gear (3) and the annular gear (5) lies on the pump housing (1) while the other front face lies on a sealing plate (13). In order to increase the life expectancy of the internal geared wheel pump, the suction channel (18) is arranged in the sealing plate (13). The sealing plate (13) can move in relation to the pump housing (1) so that the distance between the suction channel (18) and the pressure channel (19) can be altered.

Description

InnenzahnradpumpeInternal gear pump
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 Erzeuge einer Pumpwirkung mit dem Zahnring zusammenwirkt, wobei dasThe invention relates to an internal gear pump for conveying fuel from a suction channel into a pressure channel, with a pump housing in which an internally toothed toothed ring and an externally toothed pinion driven by a drive shaft are mounted, the pinion being arranged eccentrically to the toothed ring and for producing a pumping effect cooperates with the toothed ring, the
Ritzel und der Zahnring mit ihrer einen Stirnseite an dem Pumpengehäuse und mit ihrer anderen Stirnseite an einer Dichtplatte anliegen.Pinion and the toothed ring rest with their one end on the pump housing and with their other end on a sealing plate.
Eine derartige Innenzahnradpumpe wird auch alsSuch an internal gear pump is also called
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 AI 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 derCalled gerotor pump or gerotor pump. The toothed ring and the pinion represent the pump elements and are also referred to as the outer rotor and inner rotor. DE 38 27 573 AI describes an internal gear pump, the gear ring of which is driven by an electric motor. The delivery chambers of the internal gear pump between the teeth of the two pump elements are covered in the axial direction by a thrust washer. A coil spring designed as a compression spring, which is biased against the pressure plate, ensures when starting the
Brennkraftmaschine dafür, dass das Axialspiel gleich Null ist . 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 .Internal combustion engine for the fact that the axial play is zero. When operating an internal combustion engine with such an internal gear pump, it has been found that the maximum delivery capacity of the internal gear pump is required when the internal combustion engine is started. When the internal combustion engine has reached its full speed, a lower delivery rate is sufficient to ensure an adequate 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 an internal gear pump . of the type described at the outset, which has zero axial play at the starting speed and whose delivery capacity decreases after the starting speed is exceeded. The internal gear pump according to the invention should be inexpensive to manufacture 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 task is for an internal gear pump for conveying fuel from a suction channel into a pressure channel, with a pump housing in which an internally toothed toothed ring and an externally toothed pinion driven by a drive shaft are mounted, the pinion being arranged eccentrically to the toothed ring and for generating one Pumping action cooperates with the toothed ring, the pinion and the toothed ring bearing with one end face against the pump housing and with their other end face against a sealing plate, in that the suction channel is arranged in the sealing plate, and in that the sealing plate relative to the pump housing 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 Innenzahnradp.umpen erforderliche Saugdrossel verzichtet werden kann.If the distance between the suction channel and the pressure channel is reduced, this has the consequence that the Delivery capacity of the internal gear pump decreases. This provides the advantage that there is no need for a suction throttle, which is required for 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 duct is formed by an elongated recess in the circumferential direction of the sealing plate, and that the sealing plate relative to the pump housing between two 'positions is rotatable. The two positions of the sealing plate are made possible by stop surfaces which are formed on the sealing plate. By choosing a suitable geometry of the elongated recess, it can also be achieved that the effective flow cross-section of the suction channel changes when twisted.
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 special embodiment of the invention is characterized in that; that the sealing plate is biased in the axial direction by means of a spring which is coupled to the pump housing and to the sealing plate. The spring preload in the axial direction ensures that the sealing plate does not move in the axial direction until 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. The spring preload in the circumferential direction ensures that the sealing plate only rotates 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.A further special embodiment of the invention is characterized in that the spring comprises two curved legs which are connected to one another at one end connected and coupled to the sealing plate, and which are coupled at the other end to the pump housing. The inventive design of the spring enables the spring to be pretensioned both in the axial direction and in the circumferential direction 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.A further special embodiment of the invention is characterized in that on the side of the sealing plate facing away from the toothed ring and the pinion, a pin is guided axially displaceably at a certain distance and cooperates with a further spring in order to counteract 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 into contact with an end face of the pin in full load operation. If the pressure in the pump chamber continues to rise, the sealing plate continues to move against the biasing force of the additional spring. The preload force of the additional spring, its spring rate and the displacement of the sealing plate in the axial direction up 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 .A further special embodiment of the invention is characterized in that the suction channel is connected to 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. 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 vorliegende ■ 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 vorbeizuforder .A further special embodiment of the invention is characterized in that the fuel inlet opens into a sleeve in which the further spring is received and in which radial bores for the passage of fuel are made. The sleeve forms a stop that limits the axial movement of the sealing plate. A further special embodiment of the invention is characterized in that a bypass valve is accommodated in the pump housing, which is connected to the suction channel via an axial bore and to the pressure channel via a second axial bore. In the context of the present invention, axially in the direction of the longitudinal axis of the drive shaft means the internal gear pump. The bypass valve allows, for example with the help of an additional manually operated pump, the fuel to be bypassed 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 result from the following description, in which an embodiment of the invention is described in detail with reference to the drawing. The features mentioned in the claims and in the description can be essential to the invention individually or in any combination.
Zeichnungdrawing
In der Zeichnung zeigen:The drawing shows:
Figur 1 eine Ausführungsform einer erfindungsgemäßenFigure 1 shows an embodiment of an inventive
Innenzahnradpumpe im Längsschnitt;Internal gear pump in longitudinal section;
Figur 2 die Ansicht eines Schnitts entlang der Linie II -II in Figur 1 ;2 shows the view of a section along the line II -II in Figure 1;
Figur 3 die Ansicht eines Schnitts entlang der Linie III-III in Figur 1; und3 shows the view of a section along the line III-III in Figure 1; and
Figur 4 die Ansicht eines Schnitts entlang der Linie IV- IV in Figur 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. Die4 shows the view of a section along the line IV-IV in FIG. The internal gear pump shown in FIGS. 1 to 4 comprises a pump housing 1. A drive shaft 2 is rotatably mounted in the pump housing 1. The drive shaft 2 drives an internal gear or pinion 3, which is attached to the end of the drive shaft 2 with the aid 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 fastened to the pump housing 1 with the aid of screws 7 and 8. The
Schraubenköpfe der Schrauben 7 und 8 sind mit 9 und 10 bezeichnet .Screw heads of 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. DieThe drive shaft 2 is biased away from the internal gear 3 to the left by means of a plate spring 12, which is supported against a circlip 11 fastened in a groove in the drive shaft 2. The internal gear 3 is held in contact with the pump housing 1 by the biasing force of the plate spring 12. A sealing plate 13 rests on the other end face of the gear wheels 3 and 5. The
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.Sealing plate 13 is held in contact with the gears 3 and 5 by means of a spring 14. As can be seen in FIG. 3, the spring 14 comprises 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.
Die beiden anderen Enden der Schenkel 15 und 16 sind an den Schraubenköpfen 9 und 10 und somit am Pumpengehäuse 1 befestigt .The other two ends of the legs 15 and 16 are fastened to the screw heads 9 and 10 and thus to 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 arrow 34, the fuel in a pressure chamber 17 is compressed. At the same time, as can be seen in FIG. 3, fuel is drawn in from a suction channel 18, which is recessed in the sealing plate 13. The fuel drawn in compressed in the pressure chamber 17 and then enters a pressure channel 19 which, as indicated by dashed lines in FIG. 3, is recessed in the pump housing 1.
Der Saugkanal 18 und der Druckkanal 19 stehen überThe suction channel 18 and the pressure channel 19 protrude
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.Connection bores 21 and 20 with a bypass valve 22 in connection. When the spring-loaded check valve 22 is open, the two connecting bores 20 and 21 are connected to one another. When the bypass valve 22 is closed, the connection between the connection bores 20 and 21 is closed and the pressure channel 19 is connected to a pressure connection 23 via the connection 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 suction channel recessed in the sealing plate 13 is connected to a suction chamber 24 which is surrounded by a housing cover 35. The housing cover 35 is placed on the pump housing 1. A central fuel inlet bore 36 is recessed in the housing cover 35.
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 derOn the outer periphery of the sealing plate 13, two rectangular recesses are provided diametrically opposite. The two opposite sides of the recesses form together with the screw heads 9 and 10 stops 25 and 26 for a rotary movement of the
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.Sealing plate 13. In the position of the sealing plate 13 shown in FIG. 3, the stop surfaces 26 are in contact with the screw heads 9 and 10. An arrow 44 indicates that the sealing plate 13 rotates with increasing speed of the drive shaft 2 until the stop surfaces 25 rest on 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 FIG. 1 it can be seen that a pin 28 is arranged on the side of the sealing plate 13 facing away from the drive shaft 2. Between the sealing plate 13 and one A certain distance is provided on the end face of the pin 28. The pin 28 is acted upon by the prestressing 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 fastened coaxially to the fuel inlet bore 36 in the interior of the housing cover 35. Holes 31 and 32 are recessed in the lateral surface of the sleeve 30 in order to ensure the passage of fuel from the fuel inlet 36 into the suction space 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 derThe 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 against the axial face of the drive clutch in contact with the flat surface of the pump housing 1 against a possible axial force The bore 21 connects the bypass valve 22 to the suction chamber 24
Innenzahnradpumpe und erlaubt, z.B. durch eine handbetätigte Pumpe, den Kraftstoff bei nicht angetriebener Innenzahnradpumpe an den Pumpelementen vorbeizufordern.Internal gear pump and allowed, e.g. by means of a manually operated pump to call the fuel past the pump elements when the internal gear pump is not driven.
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 Kra stoffdruck zur Befüllung des Niederdrucksystems gewährleistet ist.The pump housing 1 supports the external gear 5 with the aid of the bearing ring 6. In the starting state, the sealing plate 13 is placed against the gear wheels 3 and 5 without play and is lightly pressed by means of the spring 14. The force of the spring 14 is designed for the start of the internal gear pump so that a sufficient Kra material pressure is guaranteed for filling the low pressure system.
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 in a position rotated counter to the direction of gear rotation during the starting process. This position guarantees the maximum flow rate Starting speed. The . Sealing plate 13 is thus pressed by the spring 14 against the gear rotation direction against 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 play of approximately 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 rate through the suction channel 18 reaches the idling amount, the plate 13 rotates until the opposite stop surface 25 bears against the screw head 10. This limits the delivery rate as the speed increases. It is therefore not necessary to reduce the suction of the pump, which reduces the tendency to cavitation. In full load operation, the sealing plate 13 rests on the pin 28. When the pressure in the pressure chamber 17 reaches a limit value, the plate 13 moves further to the right and presses on the spring 29 via the pin 28.

Claims

Ansprüche Expectations
1. Innenzahnradpumpe zum Fördern von Kraftstoff aus einem Saugkanal (18) in einen Druckkanal (19), mit einem Pumpengehäuse (1) , in dem ein innenverzahnter Zahnring (5) und ein durch eine Antriebswelle (2) angetriebenes außenverzahntes Ritzel (3) gelagert sind, wobei das Ritzel (3) exzentrisch zu dem Zahnring (5) angeordnet ist und zum Erzeugen einer Pumpwirkung mit dem Zahnring (5) zusammenwirkt, wobei das Ritzel (3) und der Zahnring (5) mit ihrer einen Stirnseite an dem Pumpengehäuse (1) und mit ihrer anderen Stirnseite an einer Dichtplatte (13) anliegen, dadurch gekennzeichnet, dass der Saugkanal (18) in der Dichtplatte (13) angeordnet ist, und dass die Dichtplatte (13) relativ zu dem Pumpengehäuse (1) so bewegbar ist, dass der Abstand zwischen dem Saugkanal (18) und dem Druckkanal (19) verändert werden kann.1. Internal gear pump for conveying fuel from a suction channel (18) into a pressure channel (19), with a pump housing (1) in which an internally toothed ring gear (5) and an externally toothed pinion (3) driven by a drive shaft (2) are mounted , the pinion (3) being arranged eccentrically to the toothed ring (5) and cooperating with the toothed ring (5) to produce a pumping action, the pinion (3) and the toothed ring (5) having one end face on the pump housing ( 1) and rest with its other end face on a sealing plate (13), characterized in that the suction channel (18) is arranged in the sealing plate (13) and that the sealing plate (13) can be moved relative to the pump housing (1) that the distance between the suction channel (18) and the pressure channel (19) can be changed.
2. Innenzahnradpumpe nach Anspruch 1, dadurch gekennzeichnet, dass der Saugkanal (18) von einer länglichen Aussparung in Umfangsrichtung der Dichtplatte (13) gebildet wird, und dass die Dichtplatte (13) relativ zu dem Pumpengehäuse (1) zwischen zwei Stellen drehbar ist.2. Internal gear pump according to claim 1, characterized in that the suction channel (18) is formed by an elongated recess in the circumferential direction of the sealing plate (13), and that the sealing plate (13) is rotatable relative to the pump housing (1) between two locations.
3. Innenzahnradpumpe nach Anspruch 2, dadurch gekennzeichnet, dass die Dichtplatte (13) mit Hilfe einer Feder (14) , die mit dem Pumpengehäuse (1) und mit der Dichtplatte (13) gekoppelt ist, in axialer Richtung vorgespannt ist . 3. Internal gear pump according to claim 2, characterized in that the sealing plate (13) by means of a spring (14) which is coupled to the pump housing (1) and with the sealing plate (13) is biased in the axial direction.
4. Innenzahnradpumpe nach Anspruch 3, dadurch gekennzeichnet, dass die Feder (14) in Umfangsrichtung entgegen der Antriebsrichtung der Innenzahnradpumpe vorgespannt ist .4. Internal gear pump according to claim 3, characterized in that the spring (14) is biased in the circumferential direction against the drive direction of the internal gear pump.
5. Innenzahnradpumpe nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die Feder (14) zwei gekrümmte Schenkel (15, 16) umfasst, die an dem einen Ende miteinander verbunden und mit der Dichtplatte (13) gekoppelt sind, und die an dem anderen Ende mit dem Pumpengehäuse (1) gekoppelt sind.5. Internal gear pump according to claim 3 or 4, characterized in that the spring (14) comprises two curved legs (15, 16) which are connected to one another at one end and coupled to the sealing plate (13), and which on the other End are coupled to the pump housing (1).
6. Innenzahnradpumpe nach einem der Ansprüche 3 bis 5, dadurch gekennzeichnet, dass auf der von dem Zahnring (5) und dem Ritzel (3) abgewandten 'Seite der Dichtplatte (13) in einem bestimmten Abstand ein Stift (28) axial verschiebbar geführt ist, der mit einer weiteren Feder (29) zusammenwirkt, um einer Bewegung der Dichtplatte (13) in axialer Richtung entgegenzuwirken.6. An internal gear pump of claims 3 to 5, characterized in that remote from the gear ring (5) and the pinion (3) on the 'side of the sealing plate (13) at a certain distance a pin is guided axially displaceably (28) for a which interacts with another spring (29) to counteract movement of the sealing plate (13) in the axial direction.
7. Innenzahnradpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Saugkanal (18) mit einem Kraftstoffzulauf (36) in Verbindung steht, dessen Längsachse mit der Längsachse der Antriebswelle (2) zusammenfällt.7. Internal gear pump according to one of the preceding claims, characterized in that the suction channel (18) is connected to a fuel inlet (36), the longitudinal axis of which coincides with the longitudinal axis of the drive shaft (2).
8. Innenzahnradpumpe nach Anspruch 7, dadurch gekennzeichnet, dass der Kraftstoffzulauf (36) in eine Hülse (30) mündet, in der die weitere Feder (29) aufgenommen ist und in der radiale Bohrungen (31, 32) zum Durchtritt von Kraftstoff angebracht sind.8. Internal gear pump according to claim 7, characterized in that the fuel inlet (36) opens into a sleeve (30) in which the further spring (29) is received and in the radial bores (31, 32) are made for the passage of fuel ,
9. Innenzahnradpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass in dem Pumpengehäuse ein U gehungsvenil (22) ungebracht ist, das über eine erste axiale Bohrung (21) mit dem Saugkanal (18) und über eine zweite axiale Bohrung (20) mit dem Druckkanal (19) in Verbindung steht. 9. Internal gear pump according to one of the preceding claims, characterized in that in the pump housing, a U housing valve (22) is not brought, which has a first axial bore (21) with the suction channel (18) and is connected to the pressure channel (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)

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

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US (1) US6764283B2 (en)
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JP (1) JP2004507640A (en)
CZ (1) CZ299441B6 (en)
DE (2) DE10040692C1 (en)
WO (1) WO2002016772A1 (en)

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EP1209359A2 (en) * 2000-11-23 2002-05-29 Robert Bosch Gmbh Gear pump
US10337512B2 (en) 2014-08-25 2019-07-02 Carrier Corporation Gear pump with dual pressure relief

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EP1209359A2 (en) * 2000-11-23 2002-05-29 Robert Bosch Gmbh Gear pump
EP1209359A3 (en) * 2000-11-23 2003-07-23 Robert Bosch Gmbh Gear pump
US10337512B2 (en) 2014-08-25 2019-07-02 Carrier Corporation Gear pump with dual pressure relief

Also Published As

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WO2002016772A1 (en) 2002-02-28
DE50111053D1 (en) 2006-11-02
EP1311762B1 (en) 2006-09-20
CZ299441B6 (en) 2008-07-30
US20030026711A1 (en) 2003-02-06
CZ20021352A3 (en) 2002-10-16
JP2004507640A (en) 2004-03-11
DE10040692C1 (en) 2001-09-20
US6764283B2 (en) 2004-07-20

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