EP0709568A1 - Fuel injection pump - Google Patents

Fuel injection pump Download PDF

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Publication number
EP0709568A1
EP0709568A1 EP95115126A EP95115126A EP0709568A1 EP 0709568 A1 EP0709568 A1 EP 0709568A1 EP 95115126 A EP95115126 A EP 95115126A EP 95115126 A EP95115126 A EP 95115126A EP 0709568 A1 EP0709568 A1 EP 0709568A1
Authority
EP
European Patent Office
Prior art keywords
distributor
fuel injection
injection pump
bore
pin
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
EP95115126A
Other languages
German (de)
French (fr)
Other versions
EP0709568B1 (en
Inventor
Wolfgang Fehlmann
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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Publication date
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Publication of EP0709568A1 publication Critical patent/EP0709568A1/en
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    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/02—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements
    • F02M41/06—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis

Definitions

  • the invention is based on a fuel injection pump according to the preamble of claim 1.
  • a screw is provided as a closure piece of the longitudinal bore emerging coaxially at the end face of the distributor, which screw is screwed into the end of the longitudinal bore there.
  • This represents a considerable effort since the end of the longitudinal bore must also be provided with a thread into which the screw is screwed.
  • additional safety measures must be provided so that the screw does not loosen during operation of the fuel injection pump and the longitudinal channel thus leaks to the outside.
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that the cylindrical pin used transversely to the axis is not loaded by the pressure acting on it in the direction of insertion, so that due to the pressure, the pin does not come loose from its anchoring in the distributor can.
  • the pin can be pressed into the bore in a conventional manner in a press fit or can be glued in place of it or in addition.
  • the pin itself also serves as part of a coupling for the rotary drive of the distributor if the part comprising the distributor is at the same time a coupling part which is driven by the drive of the fuel injection pump. which consists in the fact that the pin is optimally secured against falling out and at the same time ensures the required drive of the distributor.
  • This solution can be used particularly advantageously in the case of so-called radial piston distributor injection pumps, in which the longitudinal channel opens directly into the pump work space at the foot of the distributor and then emerges shortly thereafter at the end face of the distributor and is closed there by the pin inserted transversely.
  • the configuration analogous to claims 4 and 5 can also be implemented according to claims 8 and 9.
  • FIG. 1 shows a partial longitudinal section through a fuel injection pump of the radial piston distributor pump type
  • FIG. 2 a partial view in section perpendicular to FIG. 1
  • FIG. 3 a section along the line III-III through the illustration of FIG. 1
  • FIG. 4 a side view of the drive shaft with receptacles for the coupling part.
  • FIG. 1 shows a partial section through the parts of such a fuel injection pump that are essential for the use of the invention.
  • This consists of a distributor 2, which is mounted in a cylinder 3 of a cylinder liner 4 inserted into the housing 1 of the fuel injection pump and projects with a foot 6 protruding from the cylinder 3 into a fuel-filled interior 7 of the fuel injection pump.
  • Radial bores 8 are made in this foot, into which pump pistons 9 are inserted, which with their inner end face 10 enclose a common pump working space 11 with respect to one another.
  • a roller shoe 12 lies against the pump piston, each with a roller 14, which run on a cam track 15 of a cam ring 16 comprising the distributor.
  • the cam ring is symmetrical to a radial plane defined by the axes of the pump pistons 9, is essentially stationary and is adjusted in the circumferential direction by an injection adjuster 18 to change the start of the pump piston stroke. It is supported radially with its peripheral surface in the pump housing.
  • the distributor together with the roller shoes, represents the moving part of the cam drive of the fuel injection pump.
  • the distributor is driven by a drive shaft 19 of the fuel injection pump, which, in a manner not shown, is synchronous with the internal combustion engine is driven.
  • this embodiment consists of a head 20 which has axial longitudinal slots 22 from the front side 21, into which the roller shoes 12 can be inserted from the front side 21 and are guided radially displaceably in the slots.
  • a part 23 of reduced diameter adjoins the end face 21 and serves to receive a ball bearing 25, as can be seen in FIG. 1.
  • This is secured to the wider part 20 of the head by a locking ring 26.
  • the drive shaft is thus guided on one side in a slide bearing 27 and on the other side in a ball bearing 25.
  • a clutch disc 29 is also provided which, as can be seen in FIG. 3, is of star-shaped design with radially projecting webs 30 corresponding to the number of longitudinal slots 22 and the number of pump pistons with roller shoes. The webs have parallel side edges 31 and are guided over these in the slots 22.
  • the clutch disc has a circular opening 33, from which diametrically opposite recesses 34 extend. This opening 33, which is coaxial to the drive shaft, serves to receive a shaft journal 35 at the base of the distributor.
  • a longitudinal bore 37 is made in the distributor, which intersects the radial bores 8 in the area of the pump work chamber 11 and leads to a control point on the distributor in the form of a distributor groove 39 on the lateral surface of the distributor.
  • This distributor groove is alternately connected to an injection line 40 at a respective delivery stroke of the pump piston 9, which leads to an injection valve on the associated one Internal combustion engine leads.
  • the fuel delivered by the pump pistons 9 during their inward stroke, forced by the cams 41 of the cam track, is to be fed to one of these injection lines under high pressure.
  • the longitudinal bore 37 is closed in the area of the shaft journal 35, and a filling and relief line 42 starting from the distributor groove 39 is closed by a valve member 43 of a solenoid valve, not shown, in order to generate the high-pressure delivery stroke.
  • the valve member 43 is opened.
  • the longitudinal bore in the area of the shaft journal is closed by a pin 45 which, as can be seen more clearly in FIG. 2, is inserted into a bore 46 running transversely to the longitudinal axis of the distributor.
  • This bore cuts the longitudinal bore 37 over its entire cross section and has a diameter which is at least as large as the diameter of the longitudinal bore 37, but is preferably larger.
  • the pin inserted into this bore thus closes the longitudinal bore 37 completely tight.
  • the pin 45 is only radially loaded by the high pressure prevailing in the longitudinal bore 37 in such a way that no axial force component is exerted on the pin which could drive it out. The forces holding the pin in the bore 46 can thus be low.
  • the pin can be fitted in a known manner with an interference fit, but for safety's sake it can also be glued in, with larger fitting tolerances being permitted. So that the pin cannot also move out of the bore 46 due to shaking stresses that occur in the distributor pump during its operation, the clutch disc 29 is advantageously arranged in such a way that it lies in the plane of the longitudinal axis of the pin 45 and with its opening 33 directly adjoins the shaft journal and thus also on the end faces of the pin 45.
  • the breakthrough can initially be a breakthrough adapted to the cross-sectional shape of the shaft journal be. Is the shaft journal z. B. provided with shaped surfaces, via which the clutch disc is to be coupled, this carries the same shaped surface in the area of the opening.
  • the pin 45 can also serve as part of the coupling between the distributor and the drive in addition to its function of closing the longitudinal axis.
  • the shaft journal 35 is, for example, circular in cross section and the pin is designed such that it is longer than the shaft journal diameter according to FIG. that when the clutch disc 29 is driven through the slot 22 on the drive shaft 19, its movement is transmitted to the distributor 2 via the pin 47.

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

Abstract

A lengthwise drilling (37) in the rotary distributor (2) connects a high-pressure chamber (11) with a control position (39) in it. The drilling is formed in the distributor from one end and then sealed off from the outside by a plug (45). The latter is cylindrical, being inserted in a transverse drilling (46) intersecting the lengthwise one and at least of the same diameter. The plug is prevented from moving in the drilling, in which it is typically a press-fit. Alternatively, it can be glued in place. There can also be a component (29) enclosing the rotor at the transverse drilling and forming a wall preventing the plug sliding out. The component can contain a recess, while the plug is longer than its drilling, protruding from it to form a driving dog engaging in the recess.

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzpumpe gemäß der Gattung des Patentanspruchs 1 aus. Bei einer solchen, durch die DE-A1-36 15 286 bekannten Einspritzpumpe ist als Verschlußstück der koaxial an der Stirnseite der Verteilers austretenden Längsbohrung eine Schraube vorgesehen, die am dortigen Ende der Längsbohrung eingeschraubt ist. Dies stellt einen erheblichen Aufwand dar, da das Ende der Längsbohrung zusätzlich mit einem Gewinde versehen werden muß, in das die Schraube eingeschraubt wird. Weiterhin müssen zusätzliche Sicherungsmaßnahmen vorgesehen werden, daß sich die Schraube im Betrieb der Kraftstoffeinspritzpumpe nicht löst und damit der Längskanal nach außen undicht wird.The invention is based on a fuel injection pump according to the preamble of claim 1. In such an injection pump, known from DE-A1-36 15 286, a screw is provided as a closure piece of the longitudinal bore emerging coaxially at the end face of the distributor, which screw is screwed into the end of the longitudinal bore there. This represents a considerable effort, since the end of the longitudinal bore must also be provided with a thread into which the screw is screwed. Furthermore, additional safety measures must be provided so that the screw does not loosen during operation of the fuel injection pump and the longitudinal channel thus leaks to the outside.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß der quer zur Achse eingesetzte zylindrische Stift vom an ihm angreifenden Druck nicht in Einsetzrichtung belastet wird, so daß aufgrund der Druckeinwirkung ein Lösen des Stiftes aus seiner Verankerung im Verteiler nicht erfolgen kann. Dabei kann der Stift gemäß Patentanspruch 2 in die Bohrung in üblicher Weise in Preßpassung eingepreßt sein oder statt dessen oder ergänzend eingeklebt werden. Es gibt heute Kunststoffkleber, die selbst glatte Narbenverbindungen hochfest miteinander verbinden und somit ein sicheres Haften der Teile aneinander gewährleisten auch unter schwellender und starker Belastung. Soll der Aufwand zur Sicherung des Stiftes gegen Herausfallen, was unter Umständen durch eine Schüttelbeanspruchung auftreten könnte, zumal eine Kraftstoffeinspritzpumpe im Betrieb erheblichen Schwingungsbelastungen ausgesetzt ist, so kann der Stift in einfacher Weise eingesetzt werden, z. B. eingepreßt werden, und zusätzlich durch ein umfassendes Teil gemäß Patentanspruch 4 gesichert werden. In weiterer vorteilhafter Ausgestaltung dient dabei aber auch der Stift selbst als Teil einer Kupplung für den Drehantrieb des Verteilers, wenn das den Verteiler umfassende Teil zugleich ein Kupplungsteil ist, das vom Antrieb der Kraftstoffeinspritzpumpe angetrieben wird gemäß Patentanspruch 5. Dabei wird ein doppelter Vorteil erzielt, der darin besteht, daß einmal der Stift gegen Herausfallen optimal gesichert ist und zugleich für den erforderlichen Antrieb des Verteilers sorgt. Besonders vorteilhaft läßt sich diese Lösung gemäß Patentanspruch 7 bei sogenannten Radialkolbenverteilereinspritzpumpen einsetzen, bei denen der Längskanal direkt in den Pumpenarbeitsraum am Fuße des Verteilers mündet und dann kurz danach an der Stirnseite des Verteilers austritt und dort durch den quer eingesetzten Stift verschlossen wird. Dabei kann die Ausgestaltung analog zu den Patentansprüchen 4 und 5 auch gemäß Patentansprüchen 8 und 9 verwirklicht werden.The fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that the cylindrical pin used transversely to the axis is not loaded by the pressure acting on it in the direction of insertion, so that due to the pressure, the pin does not come loose from its anchoring in the distributor can. The pin can be pressed into the bore in a conventional manner in a press fit or can be glued in place of it or in addition. Today there are plastic adhesives that bond even smooth grain connections to one another and thus ensure that the parts adhere to one another even under swelling and heavy loads. If the effort to secure the pin against falling out, which could possibly occur due to shaking stress, especially since a fuel injection pump is exposed to considerable vibration during operation, the pin can be used in a simple manner, for. B. be pressed, and additionally secured by a comprehensive part according to claim 4. In a further advantageous embodiment, the pin itself also serves as part of a coupling for the rotary drive of the distributor if the part comprising the distributor is at the same time a coupling part which is driven by the drive of the fuel injection pump. which consists in the fact that the pin is optimally secured against falling out and at the same time ensures the required drive of the distributor. This solution can be used particularly advantageously in the case of so-called radial piston distributor injection pumps, in which the longitudinal channel opens directly into the pump work space at the foot of the distributor and then emerges shortly thereafter at the end face of the distributor and is closed there by the pin inserted transversely. The configuration analogous to claims 4 and 5 can also be implemented according to claims 8 and 9.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Teillängsschnitt durch eine Kraftstoffeinspritzpumpe der Radialkolbenverteilerpumpenbauart, Figur 2 eine Teilansicht im Schnitt senkrecht zu Figur 1, Figur 3 einen Schnitt entlang der Linie III-III durch die Darstellung von Figur 1 und Figur 4 eine Seitenansicht der Antriebswelle mit Aufnahmen für das Kupplungsteil.An embodiment of the invention is shown in the drawing and is explained in more detail in the following description. 1 shows a partial longitudinal section through a fuel injection pump of the radial piston distributor pump type, FIG. 2 a partial view in section perpendicular to FIG. 1, FIG. 3 a section along the line III-III through the illustration of FIG. 1 and FIG. 4 a side view of the drive shaft with receptacles for the coupling part.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die Erfindung wird am Beispiel einer Radialkolbenkraftstoffverteilereinspritzpumpe dargestellt, bei der sie in besonders vorteilhafter Weise zum Einsatz kommt. In der Figur 1 ist dazu ein Teilschnitt durch die für den Einsatz der Erfindung wesentlichen Teile einer solchen Kraftstoffeinspritzpumpe dargestellt. Diese besteht aus einem Verteiler 2, der in einem Zylinder 3 einer in das Gehäuse 1 der Kraftstoffeinspritzpumpe eingesetzten Zylinderbüchse 4 gelagert ist und mit einem aus dem Zylinder 3 herausragenden Fuß 6 in einem kraftstoffgefüllten Innenraum 7 der Kraftstoffeinspritzpumpe ragt. In diesem Fuß sind Radialbohrungen 8 eingebracht, in die Pumpenkolben 9 eingesetzt sind, die mit ihrer innenliegenden Stirnseite 10 einen gemeinsamen Pumpenarbeitsraum 11 zueinander einschließen. An ihrem aus der Radialbohrung 8 jeweils herausragenden Ende liegt jeweils ein Rollenschuh 12 an den Pumpenkolben an mit je einer Rolle 14, die auf einer Nockenbahn 15 eines den Verteiler umfassenden Nockenrings 16 ablaufen. Der Nockenring liegt dabei symmetrisch zu einer durch die Achsen der Pumpenkolben 9 definierten Radialebene, ist im wesentlichen feststehend und wird zur Veränderung des Beginns des Pumpenkolbenshubs durch einen Spritzversteller 18 in Umfangsrichtung verstellt. Er ist mit seiner Umfangsfläche im Pumpengehäuse radial gelagert. Demgegenüber stellt der Verteiler zusammen mit den Rollenschuhen den bewegten Teil des Nockenantriebs der Kraftstoffeinspritzpumpe dar. Dabei wird der Verteiler durch eine Antriebswelle 19 der Kraftstoffeinspritzpumpe angetrieben, die in nicht weiter gezeigter Weise synchron zur Brennkraftmaschine angetrieben wird. Diese weist mit ihrem in den Innenraum 7 ragenden Ende eine gabelkopfähnliche Ausgestaltung auf, die der Figur 4 näher entnehmbar ist. Diese Ausgestaltung besteht in einem Kopf 20, der von der Stirnseite 21 her axiale Längsschlitze 22 aufweist, in die die Rollenschuhe 12 von der Stirnseite 21 her einsetzbar sind und in den Schlitzen radial verschiebbar geführt werden. An dem im Durchmesser breiteren Teil des Kopfes 20 schließt sich zur Stirnseite 21 hin ein im Durchmesser reduzierter Teil 23 an, der zur Aufnahme eines Kugellagers 25, wie Figur 1 entnehmbar, dient. Dieses wird zum durchmesserbreiteren Teil 20 des Kopfes hin durch einen Sicherungsring 26 gesichert. Damit wird die Antriebswelle auf der einen Seite in einem Gleitlager 27 und auf der anderen Seite in einem Kugellager 25 geführt.The invention is illustrated using the example of a radial piston fuel distributor injection pump, in which it is used in a particularly advantageous manner. For this purpose, FIG. 1 shows a partial section through the parts of such a fuel injection pump that are essential for the use of the invention. This consists of a distributor 2, which is mounted in a cylinder 3 of a cylinder liner 4 inserted into the housing 1 of the fuel injection pump and projects with a foot 6 protruding from the cylinder 3 into a fuel-filled interior 7 of the fuel injection pump. Radial bores 8 are made in this foot, into which pump pistons 9 are inserted, which with their inner end face 10 enclose a common pump working space 11 with respect to one another. At their respective ends protruding from the radial bore 8, a roller shoe 12 lies against the pump piston, each with a roller 14, which run on a cam track 15 of a cam ring 16 comprising the distributor. The cam ring is symmetrical to a radial plane defined by the axes of the pump pistons 9, is essentially stationary and is adjusted in the circumferential direction by an injection adjuster 18 to change the start of the pump piston stroke. It is supported radially with its peripheral surface in the pump housing. In contrast, the distributor, together with the roller shoes, represents the moving part of the cam drive of the fuel injection pump. The distributor is driven by a drive shaft 19 of the fuel injection pump, which, in a manner not shown, is synchronous with the internal combustion engine is driven. With its end projecting into the interior 7, this has a fork-head-like configuration which can be seen in more detail in FIG. This embodiment consists of a head 20 which has axial longitudinal slots 22 from the front side 21, into which the roller shoes 12 can be inserted from the front side 21 and are guided radially displaceably in the slots. On the part of the head 20 which is wider in diameter, a part 23 of reduced diameter adjoins the end face 21 and serves to receive a ball bearing 25, as can be seen in FIG. 1. This is secured to the wider part 20 of the head by a locking ring 26. The drive shaft is thus guided on one side in a slide bearing 27 and on the other side in a ball bearing 25.

Zur Übertragung der Drehbewegung der Antriebswelle auf den Verteiler ist ferner eine Kupplungsscheibe 29 vorgesehen, die, wie Figur 3 entnehmbar ist, sternförmig ausgebildet ist mit entsprechend der Zahl der Längsschlitze 22 bzw. der Zahl der Pumpenkolben mit Rollenschuh vorgesehenen radial abstehenden Stegen 30. Die Stege haben zueinander parallele Seitenkanten 31 und werden über diese in den Schlitzen 22 geführt. In der Mitte weist die Kupplungsscheibe einen kreisförmigen Durchbruch 33 auf, von dem aus diametral einander gegenüberliegende Ausnehmungen 34 ausgehen. Dieser koaxial zur Antriebswelle liegende Durchbruch 33 dient zur Aufnahme eines Wellenzapfens 35 am Fuß des Verteilers. Von diesem Fuß aus, an seiner Stirnseite 36, ist in dem Verteiler eine Längsbohrung 37 eingebracht, die die Radialbohrungen 8 im Bereich des Pumpenarbeitsraumes 11 schneidet und zu einer Steuerstelle am Verteiler in Form einer Verteilernut 39 an der Mantelfläche des Verteilers führt. Diese Verteilernut wird im Wechsel bei einem jeweiligen Förderhüb der Pumpenkolben 9 mit einer Einspritzleitung 40 in Verbindung gebracht, die zu einem Einspritzventil an der zugehörigen Brennkraftmaschine führt. Der von den Pumpenkolben 9 bei ihrem Einwärtshub, gezwungen durch die Nocken 41 der Nockenbahn, geförderte Kraftstoff soll unter Hochdruck jeweils einer dieser Einspritzleitungen zugeführt werden. Dazu wird die Längsbohrung 37 im Bereich des Wellenzapfens 35 verschlossen, und es ist zur Erzeugung des Hochdruckförderhubs eine von der Verteilernut 39 ausgehende Füll- und Entlastungsleitung 42 durch ein Ventilglied 43 eines nicht weiter gezeigten Magnetventils verschlossen. Zur Beendigung der Hochdruckeinspritzung wird das Ventilglied 43 geöffnet.To transmit the rotary movement of the drive shaft to the distributor, a clutch disc 29 is also provided which, as can be seen in FIG. 3, is of star-shaped design with radially projecting webs 30 corresponding to the number of longitudinal slots 22 and the number of pump pistons with roller shoes. The webs have parallel side edges 31 and are guided over these in the slots 22. In the middle, the clutch disc has a circular opening 33, from which diametrically opposite recesses 34 extend. This opening 33, which is coaxial to the drive shaft, serves to receive a shaft journal 35 at the base of the distributor. From this foot, on its end face 36, a longitudinal bore 37 is made in the distributor, which intersects the radial bores 8 in the area of the pump work chamber 11 and leads to a control point on the distributor in the form of a distributor groove 39 on the lateral surface of the distributor. This distributor groove is alternately connected to an injection line 40 at a respective delivery stroke of the pump piston 9, which leads to an injection valve on the associated one Internal combustion engine leads. The fuel delivered by the pump pistons 9 during their inward stroke, forced by the cams 41 of the cam track, is to be fed to one of these injection lines under high pressure. For this purpose, the longitudinal bore 37 is closed in the area of the shaft journal 35, and a filling and relief line 42 starting from the distributor groove 39 is closed by a valve member 43 of a solenoid valve, not shown, in order to generate the high-pressure delivery stroke. To end the high-pressure injection, the valve member 43 is opened.

Der Verschluß der Längsbohrung im Bereich des Wellenzapfens erfolgt durch einen Stift 45, der, wie Figur 2 besser entnehmbar ist, in eine zur Längsachse des Verteilers quer verlaufende Bohrung 46 eingesetzt wird. Diese Bohrung schneidet die Längsbohrung 37 auf deren gesamten Querschnitt und hat einen Durchmesser, der mindestens gleich groß ist wie der Durchmesser der Längsbohrung 37, vorzugsweise jedoch größer ist. Der in diese Bohrung eingesetzte Stift verschließt somit die Längsbohrung 37 völlig dicht. Dabei wird der Stift 45 durch den in der Längsbohrung 37 herrschenden Hochdruck nur radial belastet derart, daß keine axiale Kraftkomponente auf den Stift ausgeübt wird, die ihn austreiben könnte. Somit können die den Stift in der Bohrung 46 haltenden Kräfte gering sein. Der Stift kann dabei in bekannter Weise mit Preßpassung eingepaßt sein, er kann allerdings sicherheitshalber auch eingeklebt sein, wobei größere Paßtoleranzen erlaubt wären. Damit der Stift nicht auch durch Schüttelbeanspruchungen, die bei der Verteilerpumpe in deren Betrieb auftreten, aus der Bohrung 46 hinauswandern kann, ist in vorteilhafter zusätzlicher Weise die Kupplungsscheibe 29 so angeordnet, daß sie in der Ebene der Längsachse des Stiftes 45 liegt und mit ihrem Durchbruch 33 unmittelbar an den Wellenzapfen und damit auch an die Stirnseiten des Stiftes 45 angrenzt. Der Durchbruch kann dabei zunächst als ein der Querschnittsform des Wellenzapfens angepaßter Durchbruch sein. Ist der Wellenzapfen z. B. mit Formflächen versehen, über die der mit der Kupplungsscheibe gekoppelt werden soll, so trägt diese dieselbe Formfläche im Bereich des Durchbruchs. Vorzugsweise kann jedoch in Weiterbildung der beschriebenen Ausgestaltung der Stift 45 über seine Funktion des Verschließens der Längsachse hinaus noch als Teil der Kupplung zwischen Verteiler und Antrieb dienen. In diesem Falle ist der Wellenzapfen 35 beispielsweise kreisrund im Querschnitt und der Stift so gestaltet, daß er länger ist als der Wellenzapfendurchmesser gemäß Figur 3. Die über die Wellenzapfen hinausragenden Teile 47 des Stiftes 45 greifen dann in die Ausnehmungen 34 in der Kupplungsscheibe ein derart, daß bei durch den Schlitz 22 an der Antriebswelle 19 mitgenommener Kupplungsscheibe 29 deren Bewegung über den Stift 47 auf den Verteiler 2 übertragen wird. Auf diese Weise ergibt sich eine äußerst wirtschaftliche Verbindung zwischen Verteiler und seinem Antrieb und zugleich eine sehr wirksame und wirtschaftliche Möglichkeit, den Längskanal 37 nach außen sicher zu verschließen.The longitudinal bore in the area of the shaft journal is closed by a pin 45 which, as can be seen more clearly in FIG. 2, is inserted into a bore 46 running transversely to the longitudinal axis of the distributor. This bore cuts the longitudinal bore 37 over its entire cross section and has a diameter which is at least as large as the diameter of the longitudinal bore 37, but is preferably larger. The pin inserted into this bore thus closes the longitudinal bore 37 completely tight. The pin 45 is only radially loaded by the high pressure prevailing in the longitudinal bore 37 in such a way that no axial force component is exerted on the pin which could drive it out. The forces holding the pin in the bore 46 can thus be low. The pin can be fitted in a known manner with an interference fit, but for safety's sake it can also be glued in, with larger fitting tolerances being permitted. So that the pin cannot also move out of the bore 46 due to shaking stresses that occur in the distributor pump during its operation, the clutch disc 29 is advantageously arranged in such a way that it lies in the plane of the longitudinal axis of the pin 45 and with its opening 33 directly adjoins the shaft journal and thus also on the end faces of the pin 45. The breakthrough can initially be a breakthrough adapted to the cross-sectional shape of the shaft journal be. Is the shaft journal z. B. provided with shaped surfaces, via which the clutch disc is to be coupled, this carries the same shaped surface in the area of the opening. However, in a further development of the described embodiment, the pin 45 can also serve as part of the coupling between the distributor and the drive in addition to its function of closing the longitudinal axis. In this case, the shaft journal 35 is, for example, circular in cross section and the pin is designed such that it is longer than the shaft journal diameter according to FIG. that when the clutch disc 29 is driven through the slot 22 on the drive shaft 19, its movement is transmitted to the distributor 2 via the pin 47. In this way, there is an extremely economical connection between the distributor and its drive and at the same time a very effective and economical possibility of securely closing the longitudinal channel 37 from the outside.

Claims (9)

Kraftstoffeinspritzpumpe mit einem von einer Antriebswelle (19) der Kraftstoffeinspritzpumpe rotierend angetriebenen Verteiler (2), in dem eine im wesentlichen in Achsrichtung des Verteilers verlaufende Längsbohrung (37) angeordnet ist, die einen Hochdruckraum (11) mit einer Steuerstelle (39) des Verteilers (2) verbindet und die von einer Stirnseite (36) des Verteilers her in den Verteiler eingebracht ist und anschließend durch ein Verschlußstück (45) nach außen verschlossen wird, dadurch gekennzeichnet, daß als Verschlußstück ein zylindrischer Stift (45) vorgesehen ist, der in eine quer zur Achse des Verteilers (2) verlaufende, die Längsbohrung (37) schneidende Bohrung (46), deren Durchmesser wenigstens so groß wie der Durchmesser der Längsbohrung ist, gegen Verschieben gesichert eingepaßt ist.Fuel injection pump with a distributor (2) rotatably driven by a drive shaft (19) of the fuel injection pump, in which a longitudinal bore (37), which runs essentially in the axial direction of the distributor, is arranged, which has a high-pressure chamber (11) with a control point (39) of the distributor ( 2) connects and which is introduced from an end face (36) of the distributor into the distributor and is then closed to the outside by a closure piece (45), characterized in that a cylindrical pin (45) is provided as the closure piece, which in a The bore (46), which crosses the axis of the distributor (2) and intersects the longitudinal bore (37) and whose diameter is at least as large as the diameter of the longitudinal bore, is fitted so that it cannot move. Kraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß der Stift (45) in die Bohrung (46) eingepreßt ist.Fuel injection pump according to Claim 1, characterized in that the pin (45) is pressed into the bore (46). Kraftstoffeinspritzpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Stift (45) in die Bohrung (46) eingeklebt ist.Fuel injection pump according to Claim 1 or 2, characterized in that the pin (45) is glued into the bore (46). Kraftstoffeinspritzpumpe nach Anspruch 1 bis 3, dadurch gekennzeichnet, daß in der Radialebene zur Verteilerachse ein den Verteiler (2) umfassendes Teil (29) vorgesehen ist, das mit einer zum Verteiler weisenden Begrenzungswand einem Verschieben des Stiftes (45) aus der Bohrung (46) heraus entgegensteht.Fuel injection pump according to Claims 1 to 3, characterized in that a part (29) comprising the distributor (2) is provided in the radial plane to the distributor axis, which prevents the pin (45) from being displaced out of the bore (46) with a boundary wall facing the distributor. Kraftstoffeinspritzpumpe nach Anspruch 4, dadurch gekennzeichnet, daß der Stift (45) länger als die Bohrung (46) ist und mit wenigstens einem aus der Bohrung herausragenden Teil (47) als Mitnehmer in eine Ausnehmung (34) des als Kupplungsteil (29) ausgebildeten, am Umfang des Verteilers angrenzenden Teils eingreift, durch das der Verteiler (2) wenigstens mittelbar mit der Antriebswelle (19) der Kraftstoffeinspritzpumpe zu seiner Verdrehung gekoppelt ist.Fuel injection pump according to Claim 4, characterized in that the pin (45) is longer than the bore (46) and with at least one part (47) protruding from the bore as a driver in a recess (34) of the coupling part (29), engages on the periphery of the distributor adjacent part, through which the distributor (2) is at least indirectly coupled to the drive shaft (19) of the fuel injection pump for its rotation. Kraftstoffeinspritzpumpe nach Anspruch 5, dadurch gekennzeichnet, daß der Stift (45) an beiden Seiten des Endes der Bohrung (46) aus dieser in gleicher Länge herausragt und dort in entsprechnend je eine Ausnehmung (34) des Kupplungsteils (29) eingreift.Fuel injection pump according to claim 5, characterized in that the pin (45) on both sides of the end of the bore (46) protrudes from the same length and engages in a corresponding recess (34) of the coupling part (29) there. Kraftstoffeinspritzpumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Pumpenkolben (9) der Kraftstoffeinspritzpumpe in radial zur Achse des Verteilers (2) ausgerichteten Radialbohrungen (8) angeordnete sind, die zwischen ihren zueinander weisenden Stirnseiten im Verteiler (2) einen gemeinsamen Pumpenarbeitsraum (11) einschließen, der als Druckraum mit der Steuerstelle (39) durch die Längsbohrung (37) verbunden ist, die als den Arbeitsraum schneidende Bohrung ausgeführt ist und ihren Austritt an der Stirnseite (36) des Verteilers (2) in einem Wellenzapfen (35) des Verteilers hat.Fuel injection pump according to one of the preceding claims, characterized in that the pump pistons (9) of the fuel injection pump are arranged in radial bores (8) which are aligned radially to the axis of the distributor (2) and which have a common pump working space (1) between their mutually facing end faces in the distributor (2). 11), which is connected as a pressure chamber to the control point (39) through the longitudinal bore (37), which is designed as a bore that intersects the work space and has its outlet on the end face (36) of the distributor (2) in a shaft journal (35) of the distributor. Kraftstoffeinspritzpumpe nach Anspruch 7, dadurch gekennzeichnet, daß der Wellenzapfen (35) von einem zusammen mit dem Verteiler bewegten Teil (29) umschlossen ist.Fuel injection pump according to Claim 7, characterized in that the shaft journal (35) is enclosed by a part (29) which is moved together with the distributor. Kraftstoffeinspritzpumpe nach Anspruch 8, dadurch gekennzeichnet, daß das bewegte Teil (29) ein mit wenigstens einer radial zum Wellenzapfen (35) weisenden Ausnehmung (34) versehenes Teil ist, in das wenigstens ein aus dem Wellenzapfen (35) herausragendes Ende des Stiftes (45) eingreift, über das der Verteiler (2) mit dem bewegten, als Kupplungsteil dienende Teil (29) mit dem Antrieb (19) des Verteilers (2) verbunden ist.Fuel injection pump according to Claim 8, characterized in that the moving part (29) is a part provided with at least one recess (34) pointing radially to the shaft journal (35), into which at least one end of the pin (45) protruding from the shaft journal (35) ) engages, via which the distributor (2) is connected to the moving part (29) serving as a coupling part with the drive (19) of the distributor (2).
EP95115126A 1994-10-26 1995-09-26 Fuel injection pump Expired - Lifetime EP0709568B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4438251A DE4438251A1 (en) 1994-10-26 1994-10-26 Fuel injection pump
DE4438251 1994-10-26

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EP0709568A1 true EP0709568A1 (en) 1996-05-01
EP0709568B1 EP0709568B1 (en) 1997-09-03

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US (1) US5782619A (en)
EP (1) EP0709568B1 (en)
JP (1) JP3738064B2 (en)
KR (1) KR100373807B1 (en)
DE (2) DE4438251A1 (en)
ES (1) ES2106604T3 (en)

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US6415769B1 (en) 2000-04-24 2002-07-09 Blue Chip Diesel Performance Performance enhancing system for electronically controlled engines

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GB2012864A (en) * 1978-12-18 1979-08-01 Lucas Industries Ltd Fuel Pumping Apparatus
DE3615286A1 (en) 1985-05-28 1986-12-04 Lucas Industries Public Ltd. Co., Birmingham FUEL INJECTION PUMP
EP0381201A1 (en) * 1989-02-01 1990-08-08 Yamaha Hatsudoki Kabushiki Kaisha 2-cycle engine with direct lubricating structure

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US3107661A (en) * 1962-07-23 1963-10-22 Cav Ltd Liquid fuel pumps for internal combustion engines
GB1046951A (en) * 1964-02-25 1966-10-26 Cav Ltd Liquid fuel injection pumps for use with internal combustion engines
GB1486931A (en) * 1974-01-04 1977-09-28 Cav Ltd Liquid fuel injection pumping apparatus
US4040405A (en) * 1975-06-10 1977-08-09 Nippon Soken, Inc. Fuel injection system for internal combustion engine
GB2086490B (en) * 1980-11-01 1984-08-08 Lucas Industries Ltd Liquid fuel injection pumping apparatus
US4453896A (en) * 1980-12-17 1984-06-12 The Bendix Corporation Distributor pump with floating piston single control valve
US4446835A (en) * 1980-12-31 1984-05-08 Lucas Industries Limited Liquid fuel injection pumping apparatus
JPS5835260A (en) * 1981-08-28 1983-03-01 Hitachi Ltd Distribution-type fuel injection pump
GB2116263B (en) * 1982-02-20 1985-10-09 Lucas Ind Plc Fuel injection pumping apparatus
GB8613409D0 (en) * 1986-06-03 1986-07-09 Lucas Ind Plc Fuel injection pumps
US5617826A (en) * 1995-02-06 1997-04-08 Performance Corporation Synchronized compression ignition engine

Patent Citations (3)

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Publication number Priority date Publication date Assignee Title
GB2012864A (en) * 1978-12-18 1979-08-01 Lucas Industries Ltd Fuel Pumping Apparatus
DE3615286A1 (en) 1985-05-28 1986-12-04 Lucas Industries Public Ltd. Co., Birmingham FUEL INJECTION PUMP
EP0381201A1 (en) * 1989-02-01 1990-08-08 Yamaha Hatsudoki Kabushiki Kaisha 2-cycle engine with direct lubricating structure

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EP0709568B1 (en) 1997-09-03
JP3738064B2 (en) 2006-01-25
US5782619A (en) 1998-07-21
KR960014637A (en) 1996-05-22
KR100373807B1 (en) 2003-05-09
ES2106604T3 (en) 1997-11-01
JPH08210214A (en) 1996-08-20
DE59500600D1 (en) 1997-10-09
DE4438251A1 (en) 1996-05-02

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