EP0859908A1 - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines

Info

Publication number
EP0859908A1
EP0859908A1 EP97923769A EP97923769A EP0859908A1 EP 0859908 A1 EP0859908 A1 EP 0859908A1 EP 97923769 A EP97923769 A EP 97923769A EP 97923769 A EP97923769 A EP 97923769A EP 0859908 A1 EP0859908 A1 EP 0859908A1
Authority
EP
European Patent Office
Prior art keywords
inner ring
teeth
fuel injection
injection pump
drive shaft
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
EP97923769A
Other languages
German (de)
French (fr)
Other versions
EP0859908B1 (en
Inventor
Heinz Nothdurft
Wolfgang Fehlmann
Clemens Senghaas
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 EP0859908A1 publication Critical patent/EP0859908A1/en
Application granted granted Critical
Publication of EP0859908B1 publication Critical patent/EP0859908B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0076—Fixing rotors on shafts, e.g. by clamping together hub and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/005—Arrangements of fuel feed-pumps with respect to fuel injection apparatus

Definitions

  • the invention is based on a fuel injection pump according to the preamble of claim 1.
  • a fuel injection pump is known from DE-Al-30 12 983.
  • the toothing provided there on the circumference of the drive shaft has a height that is substantially lower than the axial height of the inner ring.
  • Such feed pumps also known from DE-A-28 49 012, have an inner ring and an outer ring, which are located eccentrically to one another with adjacent outer surfaces, so that an intermediate space is created between the wheels which increases continuously and is then reduced again .
  • the space is divided by vanes, which are mounted in radial slots of the inner ring and move radially outwards under the influence of centrifugal forces or also restoring forces and come to rest on the inner wall of the outer ring, thereby dividing the space into individual cell spaces.
  • the fuel is first drawn in via these cell spaces and then compressed as the radial width between the outer and inner wall of said wheels fed to an exit side.
  • the pump internal gears are connected to the drive shaft either by a toothing according to DE-A-30 12 983 or by a key / groove connection according to DE-A-28 49 012.
  • the key / groove connection can also be understood as a toothing on a partial circumference.
  • the space requirement for the coupling between the inner ring and the drive shaft is very large in the last-mentioned embodiment
  • the space requirement for the first-mentioned embodiment is considerably less due to the all-round toothing with the same force transmission.
  • the fuel injection pump according to the invention ensures that edge pressures are substantially avoided and large load-bearing surfaces are guaranteed on the individual teeth of the toothings.
  • the wear and the tendency to seize between the inner ring and the toothing of the drive shaft and / or between the inner ring and the adjacent pump housing parts is reduced. Since the inner ring no longer tilts from the drive side is exposed, the very tight guidance of the inner ring follows essentially free of tilting forces that can cause damage here.
  • the low friction results in less wear and the possibility of transmitting higher torques with the corresponding pump output.
  • the width of the toothing can be increased compared to the known solution, since due to the tooth design, no tilting moments are transmitted to the inner ring of the feed pump, even with wider teeth.
  • FIG. 1 shows a section through a fuel injection pump of the distributor type in the area of the feed pump
  • FIG. 2 shows a section through the distributor pump according to FIG. 2 along the line II-II
  • FIG. 3 shows an enlarged drive tooth of the toothing on the drive shaft according to the invention.
  • Fuel injection pumps of the distributor pump type regularly have a feed pump integrated in the housing of the fuel injection pump. They can be designed as a so-called reciprocating piston pump, as they are known from the aforementioned prior art DE-Al-30 12 983, with a reciprocating and at the same time rotating pump piston driven by a cam disk, which serves as a distributor and the distributor injection pump can be designed as a radial piston pump with a cam ring, on the inwardly facing cam Radially lying pump pistons are moved, which also supply a distributor which, when the drive shaft rotates, controls various fuel pump outlets in succession which lead to injectors. Fuel is drawn in by the feed pump and fed into a fuel injection pump interior from which fuel is drawn by a high-pressure pump to generate high injection pressures.
  • the section in FIG. 1 shows a section through such a distributor injection pump in the region of the feed pump.
  • a circular cylindrical space with a circular cylindrical inner wall 3 is provided in the housing 1 of the fuel injection pump, into which an outer ring 5 of the fuel delivery pump is inserted, the outer wall of which comes into contact with the inner wall 3.
  • the outer ring is fixedly screwed to the housing 1 by screws 6.
  • Radially on the inside, the outer ring has an inner surface 8, which in the example shown has a surface deviating from the circular cylindrical shape, which delimits a cross-section which is approximately crescent-shaped with a circular cylindrical outer surface 9 of an inner ring 10.
  • the inner ring has an inner circumferential surface 14 provided with a toothing 12, and is coupled there with a corresponding toothing on the circumference of a drive shaft 15 with this in a positive-locking manner in the direction of rotation.
  • Radial grooves 17 extend from the lateral surface 9 of the inner ring and are distributed at regular angular intervals and into which disk-shaped vanes 18 with a rectangular cross section are guided as displacement elements. These are supported by a compression spring 19 supported within the grooves 17 with its end face 20 in contact with the inner surface 8 of the
  • Figure 2 shows the placement of the outer ring 5 and inner ring 10 in the cylindrical recess 3 and the cover 25 enclosing these two rings in this recess, which is screwed together with the outer ring 5 on the housing.
  • FIG. 2 also shows the coupling between the drive shaft 15 and the inner ring 10. It can be seen that the drive shaft has a toothed ring 25 on its outer circumference with a straight serration, the axial
  • the height of the ring gear is significantly less than the axial height of the inner ring 10 and the outer ring 5.
  • This ring gear is the part of the toothing 12 of FIG. 1 on the drive shaft side. as housing parts including the feed pump is guided. These parts also axially close off the crescent-shaped space 11.
  • the wings 18 guided in the grooves are suitably arranged between these two housing parts, so that the subspaces of the crescent-shaped space 11 are sealed off from one another as closely as possible, taking into account the play required for the movement.
  • FIG. 3 shows the configuration of the teeth of the toothing according to the invention.
  • the top end face 27 of the teeth of the toothing 25 runs along a circular arc with the radius R, the center of which lies in this radial plane.
  • the tooth base 28 of the respective teeth 29 also runs accordingly. Because of this configuration, a deviation from the exactly vertical position of the axis of the drive shaft 15, which is provided in principle, from the radial plane defined by the axial boundary surfaces of the cover 5 or the recess 3, which is embodied in the sectional plane II, is possible.
  • the arc-shaped contour of the teeth 29 in the longitudinal direction of the axis ensures that, with an angular offset, there is still contact with the corresponding toothing 12 on the inner ring 10 without there being any wear-promoting edge pressures. By avoiding these edge pressures, higher torques can be transmitted overall with the same configuration, which would otherwise lead to rapid wear or destruction of the component.
  • the ring gear 25, which is kept very narrow can be widened and, due to the larger tooth surfaces, a higher torque can also be transmitted to the feed pump, which in turn can thus deliver an increased delivery rate. There are less stringent demands on the manufacturing and assembly accuracy during assembly and manufacture, which makes the manufacture of the fuel injection pump cheaper.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Rotary Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

A fuel injection pump for internal combustion engines has an integrated feed pump with an outer ring (5) and an inner ring (10) coupled by teeth (12) to a driving shaft (15) of the fuel injection pump. The individual teeth extend with their face (27) and bottom (28) along arcs of a circle around a centre which lies in the driving shaft radial plane which extends through said teeth along the axis of the driving shaft. This allows a higher angular offset between the driving shaft and the plane of the inner ring (10) without increasing the risk of damage through wear.

Description

Kraftstoffeinspritzpumpe für BrennkraftmaschinenFuel injection pump for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht von einer Kraftstoffeinspritzpumpe gemäß der Gattung des Patentanspruchs 1 aus. Eine solche Kraftstoffeinspritzpumpe ist durch die DE-Al-30 12 983 bekannt. Die dort auf dem Umfang der Antriebswelle vorgesehene Verzahnung hat dabei eine gegenüber der axialen Höhe des Innenringes wesentlich geringere Höhe. Solche auch durch die DE-A-28 49 012 bekannten Förderpumpen weisen ein Innenring und ein Außenring auf, die mit einander benach- harten Außenflächen exzentrisch zueinander liegen, so daß zwischen den Rädern ein Zwischenraum entsteht, der kontinuierlich größer wird und dann wieder verringert wird. Der Zwischenraum ist unterteilt durch Flügel, die in radialen Schlitzen des Innenrings gelagert sind und sich unter Einwirkung von Fliehkräften oder auch Rückstellkräften radial nach außen bewegen und zur Anlage an der Innenwand des Außenringes kommen und dabei den Zwischenraum in einzelne Zellräume unterteilt . Über diese Zellräume wird der Kraftstoff zunächst angesaugt und dann verdichtet bei zunehmender Verringerung der radialen Breite zwischen Außen- und Innenwand der genannten Räder einer Austrittsseite zugeführt. Die Pumpeninnenräder werden dabei entweder durch eine Verzahnung gemäß DE-A-30 12 983 oder durch eine Keil/Nut-Verbindung gemäß DE-A-28 49 012 mit der Antriebs- welle verbunden. Die Keil/Nut-Verbindung kann auch als eine Verzahnung auf einem Teilumfang aufgefaßt werden. Während der Platzbedarf für die Kupplung zwischen Innenring und Antriebswelle bei der zuletzt genannten Ausgestaltung sehr groß ist, ist der Platzbedarf bei der erstgenannten Aus- führung dagegen wegen der ringsherum erfolgenden Verzahnung bei gleicher Kraf übertragung wesentlich geringer. Aufgrund unterschiedlicher Spieltoleranzen, die im Bereich Förderpumpe wegen der erforderlichen Dichtheit besonders gering sind, dagegen im Bereich der Antriebswelle und ihrer Kuppelung mit dem Innenring jedoch größer sein kann, tritt bei der bekannten Lösung der Fall auf, daß wegen Winkelabweichungen zwischen der Ebene, in der Innenring der Förderpumpe geführt wird und der Radialebene der Antriebswelle, durch die die Achse der Antriebswelle senkrecht hindurch- tritt, im Bereich der Verzahnung hohe Kantenpressungen auftreten. Dies hat den Nachteil eines hohen Verschleißes und erfordert eine höhere Antriebsleistung.The invention is based on a fuel injection pump according to the preamble of claim 1. Such a fuel injection pump is known from DE-Al-30 12 983. The toothing provided there on the circumference of the drive shaft has a height that is substantially lower than the axial height of the inner ring. Such feed pumps, also known from DE-A-28 49 012, have an inner ring and an outer ring, which are located eccentrically to one another with adjacent outer surfaces, so that an intermediate space is created between the wheels which increases continuously and is then reduced again . The space is divided by vanes, which are mounted in radial slots of the inner ring and move radially outwards under the influence of centrifugal forces or also restoring forces and come to rest on the inner wall of the outer ring, thereby dividing the space into individual cell spaces. The fuel is first drawn in via these cell spaces and then compressed as the radial width between the outer and inner wall of said wheels fed to an exit side. The pump internal gears are connected to the drive shaft either by a toothing according to DE-A-30 12 983 or by a key / groove connection according to DE-A-28 49 012. The key / groove connection can also be understood as a toothing on a partial circumference. While the space requirement for the coupling between the inner ring and the drive shaft is very large in the last-mentioned embodiment, the space requirement for the first-mentioned embodiment, on the other hand, is considerably less due to the all-round toothing with the same force transmission. Due to different play tolerances, which are particularly low in the area of the feed pump because of the required tightness, but may be larger in the area of the drive shaft and its coupling with the inner ring, the known solution has the case that because of angular deviations between the plane in which Inner ring of the feed pump and the radial plane of the drive shaft through which the axis of the drive shaft passes vertically, high edge pressures occur in the area of the teeth. This has the disadvantage of high wear and requires a higher drive power.
Vorteile der ErfindungAdvantages of the invention
Durch die erfindungsgemäße Kraftstoffeinspritzpumpe mit den Merkmalen des Kennzeichens des Patentanspruchs 1 wird erreicht, daß Kantenpressungen im wesentlichen vermieden werden und große tragende Flächen an den einzelnen Zähnen der Verzahnungen gewährleistet sind. Der Verschleiß und die Neigung zum Fressen zwischen Innenring und Verzahnung der Antriebswelle und/oder zwischen Innenring und den angrenzenden Pumpengehäuseteilen wird verringert. Da das Innenring nunmehr keinen Kippbewegungen von der Antriebs- seite her ausgesetzt ist, folgt auch die sehr enge Führung des Innenringes im wesentlichen frei von Kippkräften, die hier Schäden verursachen können. Durch die geringe Reibung ergibt sich ein geringerer Verschleiß und die Möglichkeit höhere Drehmomente bei entsprechender Pumpenleistung zu übertragen. Die Breite der Verzahnung kann gegenüber der bekannten Lösung erhöht werden, da aufgrund der Zahngestaltung auch bei breiteren Zähnen keine Kippmomente mehr auf das Innenring der Förderpumpe übertragen werden.The fuel injection pump according to the invention with the features of the characterizing part of claim 1 ensures that edge pressures are substantially avoided and large load-bearing surfaces are guaranteed on the individual teeth of the toothings. The wear and the tendency to seize between the inner ring and the toothing of the drive shaft and / or between the inner ring and the adjacent pump housing parts is reduced. Since the inner ring no longer tilts from the drive side is exposed, the very tight guidance of the inner ring follows essentially free of tilting forces that can cause damage here. The low friction results in less wear and the possibility of transmitting higher torques with the corresponding pump output. The width of the toothing can be increased compared to the known solution, since due to the tooth design, no tilting moments are transmitted to the inner ring of the feed pump, even with wider teeth.
Zeichnungdrawing
Ein Ausführungsbeispiel ist in der Zeichnung dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Schnitt durch eine Kraftstoffeinspritzpumpe der Verteilerbauart im Bereich der Förderpumpe, Figur 2 einen Schnitt durch die Verteilerpumpe gemäß Figur 2 entlang der Linie II-II und Figur 3 einen vergrößert heraus- gezeichneten Antriebszahn der Verzahnung auf der Antriebswelle gemäß der Erfindung.An embodiment is shown in the drawing and is explained in more detail in the following description. 1 shows a section through a fuel injection pump of the distributor type in the area of the feed pump, FIG. 2 shows a section through the distributor pump according to FIG. 2 along the line II-II and FIG. 3 shows an enlarged drive tooth of the toothing on the drive shaft according to the invention.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Kraftstoffeinspritzpumpen der Verteilerpumpenbauart haben regelmäßig eine in das Gehäuse der Kraftstoffeinspritzpumpe integrierte Fδrderpumpe . Dabei können sie als sog. Hubkolbenverteilerpumpe ausgeführt werden, wie sie durch den eingangs genannten Stand der Technik DE-Al-30 12 983 bekannt sind, mit einem von einer Nockenscheibe angetriebenen, hin- und hergehenden und zugleich rotierenden Pumpenkolben, der dabei als Verteiler dient und es kann die Verteilereinspritzpumpe als Radialkolbenpumpe ausgeführt werden mit einem Nockenring, an dessen nach innen weisenden Nocken- fläche radial liegende Pumpenkolben bewegt werden, die ebenfalls einen Verteiler versorgen, der bei der Drehung der Antriebswelle nacheinander verschiedene Kraftstoffpumpen- auslasse, die zu Einspritzventilen führen, ansteuert. Durch die Förderpumpe wird Kraftstoff angesaugt und in einen Kraftstoffeinspritzpumpeninnenraum gefördert, aus dem Kraftstoff zur Erzeugung hoher Einspritzdrücke durch eine Hochdruckpumpe entnommen wird. Der Schnitt in Figur 1 zeigt einen Schnitt durch eine solche Verteilereinspritzpumpe im Bereich der Förderpumpe. Dabei ist im Gehäuse 1 der Kraftstoffeinspritzpumpe ein kreiszylindrischer Raum mit einer kreiszylindrischen Innenwandung 3 vorgesehen, in den ein Außenring 5 der Kraftstofförderpumpe eingesetzt ist, der mit seiner Außenwand zur Anlage an der Innenwand 3 kommt. Der Außenring ist durch Schrauben 6 ortsfest mit dem Gehäuse 1 verschraubt. Radial innenliegend weist der Außenring eine Innenfläche 8 auf, die im ausgeführten Beispiel eine von der kreiszylindrischen Form abweichende Fläche aufweist, die mit einer kreiszylindrischen Mantelfläche 9 eines Innenringes 10 einen im Querschnitt etwa sichelförmigen Zwischenraum 11 begrenzt. Der Innenring weist eine mit einer Verzahnung 12 versehene innere Mantelfläche 14 auf, und ist dort mit einer entsprechenden Verzahnung auf dem Umfang einer Antriebswelle 15 mit dieser in Drehrichtung formschlüssig gekoppelt. Von der Mantelfläche 9 des Innenringes gehen Radialnuten 17 aus, die in regelmäßigen Winkelabständen verteilt angeordnet sind und in die als Verdrängungselemente scheibenförmige Flügel 18 mit Rechteckquerschnitt geführt sind. Diese werden durch eine sich innerhalb der Nuten 17 abstützenden Druckfedern 19 mit ihrer Stirnseite 20 in Anlage an der Innenfläche 8 desFuel injection pumps of the distributor pump type regularly have a feed pump integrated in the housing of the fuel injection pump. They can be designed as a so-called reciprocating piston pump, as they are known from the aforementioned prior art DE-Al-30 12 983, with a reciprocating and at the same time rotating pump piston driven by a cam disk, which serves as a distributor and the distributor injection pump can be designed as a radial piston pump with a cam ring, on the inwardly facing cam Radially lying pump pistons are moved, which also supply a distributor which, when the drive shaft rotates, controls various fuel pump outlets in succession which lead to injectors. Fuel is drawn in by the feed pump and fed into a fuel injection pump interior from which fuel is drawn by a high-pressure pump to generate high injection pressures. The section in FIG. 1 shows a section through such a distributor injection pump in the region of the feed pump. In this case, a circular cylindrical space with a circular cylindrical inner wall 3 is provided in the housing 1 of the fuel injection pump, into which an outer ring 5 of the fuel delivery pump is inserted, the outer wall of which comes into contact with the inner wall 3. The outer ring is fixedly screwed to the housing 1 by screws 6. Radially on the inside, the outer ring has an inner surface 8, which in the example shown has a surface deviating from the circular cylindrical shape, which delimits a cross-section which is approximately crescent-shaped with a circular cylindrical outer surface 9 of an inner ring 10. The inner ring has an inner circumferential surface 14 provided with a toothing 12, and is coupled there with a corresponding toothing on the circumference of a drive shaft 15 with this in a positive-locking manner in the direction of rotation. Radial grooves 17 extend from the lateral surface 9 of the inner ring and are distributed at regular angular intervals and into which disk-shaped vanes 18 with a rectangular cross section are guided as displacement elements. These are supported by a compression spring 19 supported within the grooves 17 with its end face 20 in contact with the inner surface 8 of the
Außenringes gehalten, gegebenenfalls durch den Ausgangsdruck der Förderpumpe hydraulisch unterstützt. Die Flügel unterteilen den sichelförmigen Raum 11 in Teilvolumina, derart, daß bei einer Relatiwerdrehung des Innenringes zum Außen- ring die Flügel 18 diese Volumina bewegen, die sich infolge der Konfiguration des sichelförmigen Raumes verringern unter Bildung eines erhöhten Förderdrucks. Am einen Ende des sichelförmigen Raumes führt ein Austrittskanal 22 ab, in den der komprimierte Kraftstoff gefordert wird. Ihm gegenüber- liegend ist am anderen Ende des sichelförmigen Raumes 11 ein nierenförmiger Eintritt 24 vorgesehen, über den bei der Drehung des Innenringes Kraftstoff angesaugt wird. Ergänzend zeigt Figur 2 die Unterbringung von Außenring 5 und Innenring 10 in der zylindrischen Ausnehmung 3 und den diese beiden Ringe in dieser Ausnehmung einschließenden Deckel 25, der zusammen mit dem Außenring 5 am Gehäuse verschraubt ist. Der Figur 2 entnimmt man ferner die Koppelung zwischen Antriebswelle 15 und Innenring 10. Man erkennt, daß die Antriebswelle an ihren Außenumfang einen Zahnkranz 25 mit einer geraden S irnverzahnung aufweist, wobei die axialeOuter ring held, optionally supported hydraulically by the output pressure of the feed pump. The vanes divide the crescent-shaped space 11 into partial volumes, such that when the inner ring rotates relative to the outer ring, the vanes 18 move these volumes, which result as a result reduce the configuration of the crescent-shaped space with formation of an increased delivery pressure. At one end of the crescent-shaped space, an outlet duct 22 leads into which the compressed fuel is required. Opposite it, a kidney-shaped inlet 24 is provided at the other end of the crescent-shaped space 11, via which fuel is sucked in when the inner ring rotates. In addition, Figure 2 shows the placement of the outer ring 5 and inner ring 10 in the cylindrical recess 3 and the cover 25 enclosing these two rings in this recess, which is screwed together with the outer ring 5 on the housing. FIG. 2 also shows the coupling between the drive shaft 15 and the inner ring 10. It can be seen that the drive shaft has a toothed ring 25 on its outer circumference with a straight serration, the axial
Höhe des Zahnkranzes wesentlich geringer ist als die axiale Höhe von Innenring 10 und Außenring 5. Dieser Zahnkranz ist der antriebswellenseitige Teil der Verzahnung 12 von Figur 1. Man erkennt, daß durch den Deckel 25 der Innenring 10 sehr eng zwischen Deckel 25 und Gehäuse 1, als die Förderpumpe einschließende Gehäuseteile geführt ist. Diese Teile schließen auch den sichelförmigen Raum 11 axial ab. Die in den Nuten geführten Flügel 18 sind passend zwischen diesen beiden Gehäuseteilen angeordnet, so daß die Teilräume des sichelförmigen Raumes 11 gegeneinander möglichst dicht abgeschlossen werden unter Beachtung des für die Bewegung erforderlichen Spiels.The height of the ring gear is significantly less than the axial height of the inner ring 10 and the outer ring 5. This ring gear is the part of the toothing 12 of FIG. 1 on the drive shaft side. as housing parts including the feed pump is guided. These parts also axially close off the crescent-shaped space 11. The wings 18 guided in the grooves are suitably arranged between these two housing parts, so that the subspaces of the crescent-shaped space 11 are sealed off from one another as closely as possible, taking into account the play required for the movement.
In der Figur 3 ist nun die erfindungsgemäße Ausgestaltung der Zähne der Verzahnung dargestellt. Im Längsschnitt innerhalb einer Radialebene durch die Achse der Antriebswelle verläuft die oberste Stirnseite 27 der Zähne der Verzahnung 25 entlang eines Kreisbogens mit dem Radius R, dessen Mittelpunkt in dieser Radialebene liegt. Entsprechend verläuft auch der Zahngrund 28 der jeweiligen Zähne 29. Aufgrund dieser Ausgestaltung ist eine Abweichung von der im Prinzip vorgesehenen genau senkrechten Lage der Achse der Antriebswelle 15 zur durch die axialen Begrenzungsflächen des Deckels 5 bzw. der Ausnehmung 3 festgelegten Radial- ebene, die sich in der Schnittebene I-I verkörpert, möglich. Die kreisbogenförmig in Längsrichtung der Achse verlaufende Kontur der Zähne 29 gewährleistet, daß bei einem Winkelversatz immer noch flächige Anlagen zur entsprechenden Verzahnung 12 am Innenring 10 auftreten, ohne daß es hier zu verschleißfördernden Kantenpressungen kommt. Durch Vermeidung dieser Kantenpressungen können insgesamt bei gleicher Konfiguration höhere Drehmomente übertragen werden, die sonst zu schnellen Verschleiß oder Zerstörung des Bauteils führen würden. Dabei kann nach der obenstehenden Überlegungen sehr schmal gehaltene Zahnkranz 25 verbreitert werden und aufgrund größerer Zahnflächen ebenfalls ein höheres Drehmoment auf die Förderpumpe übertragen werden, die somit wiederum eine erhöhte Förderleistung abgeben kann. Es werden bei der Montage und der Herstellung weniger hohe Anforderungen an die Fertigungs- und Montiergenauigkeit gestellt, was die Herstellung der Kraftstoffeinspritzpumpe verbilligt. FIG. 3 shows the configuration of the teeth of the toothing according to the invention. In a longitudinal section within a radial plane through the axis of the drive shaft, the top end face 27 of the teeth of the toothing 25 runs along a circular arc with the radius R, the center of which lies in this radial plane. The tooth base 28 of the respective teeth 29 also runs accordingly. Because of this configuration, a deviation from the exactly vertical position of the axis of the drive shaft 15, which is provided in principle, from the radial plane defined by the axial boundary surfaces of the cover 5 or the recess 3, which is embodied in the sectional plane II, is possible. The arc-shaped contour of the teeth 29 in the longitudinal direction of the axis ensures that, with an angular offset, there is still contact with the corresponding toothing 12 on the inner ring 10 without there being any wear-promoting edge pressures. By avoiding these edge pressures, higher torques can be transmitted overall with the same configuration, which would otherwise lead to rapid wear or destruction of the component. In accordance with the above considerations, the ring gear 25, which is kept very narrow, can be widened and, due to the larger tooth surfaces, a higher torque can also be transmitted to the feed pump, which in turn can thus deliver an increased delivery rate. There are less stringent demands on the manufacturing and assembly accuracy during assembly and manufacture, which makes the manufacture of the fuel injection pump cheaper.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzpumpe für Brennkraftmaschine mit einer Antriebswelle (15) , mit der wenigstens ein Pumpenkoben der Kraftstoffeinspritzpumpe über Betätigungsnocken angetrieben wird und mit der eine innerhalb eines Gehäuses der Kraftstoffeinspritzpumpe angeordnete Kraftstofförderpumpe angetrieben wird, die aus einem Innenring (10) , der mit einer inneren Mantelfläche (14) auf der Antriebswelle (15) geführt ist und dort über eine Verzahnung (12) mit dieser gekoppelten ist und einem Außenring (5) besteht, zwischen dem und dem Innenring (10) mit einem dieser Ringen gekoppelte Verdrängungselemente (18) angeordnet sind, durch die Kraftstoff von einer Eintrittsseite (24) zu einer Austrittsseite (22) gefördert wird, wobei zwischen Innenring (10) , den Verdrägungselementen (18) , dem Außenring (5) und zwei diese Teile dicht führenden Gehäuseteilen (3, 25) das zu fördernde Kraftstoffvolumen eingeschlossen wird, dadurch gekennzeichnet, daß die Verzahnung eine Stirnverzahnung ist, mit Zähnen auf dem Umfang der Antriebswelle (15) und Zähnen (29) auf der inneren Mantelfläche (14) des Inneringes (10) , von den wenigstens die Zähne auf einem der Teile, Antriebswelle (15) oder Innenring (10) , vorzugsweise die Zähne (29) auf der Mantelfläche (14) des Innenringes (10) , eine Gerad- verzahung (12) bilden, wobei die jeweils in der in Längs- richtung der Achse der Antriebswelle (15) verlaufenden Radialebenen dieser Achse liegenden Zähne (29) in dieser jeweiligen Ebene bogenförmig verlaufen mit einem die Stirnfläche (27) der Zähne (29) begrenzenden Hüllkreis, dessen Mittelpunkt in dieser jeweiligen Radialebene liegt.1. Fuel injection pump for an internal combustion engine with a drive shaft (15) with which at least one pump piston of the fuel injection pump is driven via actuating cams and with which a fuel delivery pump arranged within a housing of the fuel injection pump is driven, which consists of an inner ring (10) with an inner lateral surface (14) is guided on the drive shaft (15) and there is a toothing (12) coupled to it and an outer ring (5), between which and the inner ring (10) with one of these rings coupled displacement elements (18) are arranged , through which fuel is conveyed from an inlet side (24) to an outlet side (22), between the inner ring (10), the displacement elements (18), the outer ring (5) and two housing parts (3, 25) tightly leading these parts Fuel volume to be delivered is included, characterized in that the toothing has a spur toothing is, with teeth on the circumference of the drive shaft (15) and teeth (29) on the inner lateral surface (14) of the inner ring (10), of which at least the teeth on one of the parts, drive shaft (15) or inner ring (10), preferably the teeth (29) on the circumferential surface (14) of the inner ring (10) form a straight toothing (12), the respective in the longitudinal Direction of the axis of the drive shaft (15) extending radial planes of this axis lying teeth (29) arcuate in this respective plane with an enveloping circle defining the end face (27) of the teeth (29), the center of which lies in this respective radial plane.
2. Kraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß sowohl die Stirnseite (27) als auch der Zahngrund (28) der Zähne (29) jeweils bogenförmig verlaufen.2. Fuel injection pump according to claim 1, characterized in that both the end face (27) and the tooth base (28) of the teeth (29) are each arcuate.
3. Kraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Verdrängungselemente in Radialnuten3. Fuel injection pump according to claim 1, characterized in that the displacement elements in radial grooves
(17) des Innenringes (10) geführte Flügel (18) sind, die zur Anlage an der Innenfläche (8) des Außenringes (5) und an die angrenzenden der Gehäuseteile (3, 25) kommen und die äußere Mantelfläche (9) des Innenringes (10) mit der Innenfläche(17) of the inner ring (10) are guided wings (18) which come to rest on the inner surface (8) of the outer ring (5) and on the adjoining housing parts (3, 25) and the outer lateral surface (9) of the inner ring (10) with the inner surface
(8) des Außenringes (5) einen etwa sichelförmigen Raum (11) begrenzen. (8) of the outer ring (5) delimit an approximately sickle-shaped space (11).
EP97923769A 1996-07-29 1997-04-30 Fuel injection pump for internal combustion engines Expired - Lifetime EP0859908B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19630537A DE19630537A1 (en) 1996-07-29 1996-07-29 Fuel injection pump for internal combustion engines
DE19630537 1996-07-29
PCT/DE1997/000882 WO1998004825A1 (en) 1996-07-29 1997-04-30 Fuel injection pump for internal combustion engines

Publications (2)

Publication Number Publication Date
EP0859908A1 true EP0859908A1 (en) 1998-08-26
EP0859908B1 EP0859908B1 (en) 2002-03-27

Family

ID=7801160

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97923769A Expired - Lifetime EP0859908B1 (en) 1996-07-29 1997-04-30 Fuel injection pump for internal combustion engines

Country Status (8)

Country Link
US (1) US6086348A (en)
EP (1) EP0859908B1 (en)
JP (1) JPH11514719A (en)
KR (1) KR100534186B1 (en)
CN (1) CN1077219C (en)
DE (2) DE19630537A1 (en)
HK (1) HK1046575B (en)
WO (1) WO1998004825A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6773240B2 (en) 2002-01-28 2004-08-10 Visteon Global Technologies, Inc. Single piston dual chamber fuel pump

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
US2832199A (en) * 1953-04-30 1958-04-29 American Brake Shoe Co Vane pump
US2910976A (en) * 1954-02-17 1959-11-03 Bosch Arma Corp Timing device for fuel injection pump
DE1063036B (en) * 1954-07-26 1959-08-06 Jabsco Pump Company Fixing a pump impeller on its shaft
NL270028A (en) * 1960-10-07
US3113527A (en) * 1962-08-01 1963-12-10 Ingersoll Rand Co Pump or motor shaft and rotor coupling means
FR1493235A (en) * 1966-09-16 1967-08-25 Netzsch Maschinenfabrik Fa Geb Advanced coupling for worm pumps
US3785758A (en) * 1972-04-24 1974-01-15 Abex Corp Vane pump with ramp on minor diameter
US4041921A (en) * 1973-12-13 1977-08-16 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
GB9206099D0 (en) * 1992-03-20 1992-05-06 Lucas Ind Plc Fuel pump
JP3101165B2 (en) * 1994-11-04 2000-10-23 三菱電機株式会社 Vacuum pump with planetary gearbox
JPH09256977A (en) * 1996-03-25 1997-09-30 Zexel Corp Vane type compressor

Non-Patent Citations (1)

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Title
See references of WO9804825A1 *

Also Published As

Publication number Publication date
HK1046575A1 (en) 2003-01-17
CN1198198A (en) 1998-11-04
KR100534186B1 (en) 2006-02-28
HK1046575B (en) 2005-08-12
DE59706757D1 (en) 2002-05-02
DE19630537A1 (en) 1998-02-05
JPH11514719A (en) 1999-12-14
US6086348A (en) 2000-07-11
WO1998004825A1 (en) 1998-02-05
EP0859908B1 (en) 2002-03-27
CN1077219C (en) 2002-01-02
KR19990063792A (en) 1999-07-26

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