EP0757174A2 - Method of changing the timing of fuel injection pumps on a fuel injection pump thereof - Google Patents

Method of changing the timing of fuel injection pumps on a fuel injection pump thereof Download PDF

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Publication number
EP0757174A2
EP0757174A2 EP96111818A EP96111818A EP0757174A2 EP 0757174 A2 EP0757174 A2 EP 0757174A2 EP 96111818 A EP96111818 A EP 96111818A EP 96111818 A EP96111818 A EP 96111818A EP 0757174 A2 EP0757174 A2 EP 0757174A2
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EP
European Patent Office
Prior art keywords
roller
bolt
fuel injection
tappet
injection pump
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
EP96111818A
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German (de)
French (fr)
Other versions
EP0757174B1 (en
EP0757174A3 (en
Inventor
Hans Werner
Erhard Hilliger
Klaus Merseburg
Frank Prautzsch
Peter Teichert
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WOODWARD GOVERNOR GERMANY GmbH
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WOODWARD GOVERNOR GERMANY GmbH
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Publication of EP0757174A2 publication Critical patent/EP0757174A2/en
Publication of EP0757174A3 publication Critical patent/EP0757174A3/en
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Publication of EP0757174B1 publication Critical patent/EP0757174B1/en
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Classifications

    • 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
    • F02M59/48—Assembling; Disassembling; Replacing
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams

Definitions

  • the invention relates to a method for changing the start of delivery of fuel injection pumps for internal combustion engines, in particular diesel engines, and a suitable fuel injection pump.
  • the delivery start setting of injection pumps for internal combustion engines is carried out by adjusting the stroke, ie setting the distance between the pump support flange and the associated roller tappet or camshaft. With the adjustment of the advance stroke, the ignition timing, the stroke of the pump piston from the bottom dead center of the cam to the start of delivery, is changed.
  • Various solutions for setting the start of delivery of injection pumps are already known from literature and practice. In practice, for example, injection pumps are used in which the pump piston is actuated via adjustable fuel cams mounted on the camshaft. The start of delivery of the injection pump can be changed by rotating the two-part fuel cam. This solution has the disadvantage that the maximum possible shaft diameter is not available for transmitting the torque from the camshaft to the pump piston.
  • DE 40 03 469 A1 discloses a delivery start setting in which the dead center of the respective associated engine cylinder is determined by means of a piston distance measurement and is used as the basis for the delivery start setting. The actual adjustment is done by placing spacers under it. Placing shims or spacers requires repeated disassembly and assembly of the injection pump as well as the fuel supply, the lubricating oil supply and the injection pressure line.
  • the invention had for its object to provide a method for changing the start of delivery of fuel injection pumps with a roller tappet drive, which, even with injection pumps already mounted on the engine, including those with an integrated roller tappet drive, significantly reduces dismantling and assembly work, and is safe and reliable Correction of the injection time enables. Furthermore, it is an object of the invention to provide a correspondingly suitable fuel injection pump.
  • the object is achieved in that the securing and fastening elements for the roller bolt are solved, the roller bolt with the roller is displaced in the transverse direction to the camshaft axis and aligned by means of test gauges of the roller bolts in the desired start of delivery position and then fixed to the roller tappet.
  • This new procedure enables for the first time a correction of the ignition timing of injection pumps mounted on the engine with very little disassembly and assembly effort.
  • the transverse displacement of the roller pin with the roller transversely to the camshaft axis changes the horizontal distance between the roller of the roller tappet and the camshaft path, depending on the required adjustment, and the forward stroke of the pump piston is thereby adjusted.
  • the roller bolt is arranged to be displaceable transversely to the axis of the camshaft, the bores in the roller bolt for fastening the roller bolt to the roller tappet being designed as elongated holes which run transversely to the longitudinal axis of the roller bolt.
  • the contact surfaces between the roller pin and the roller tappet are designed in a form-fitting manner in such a way that after the roller pin has been moved with the roller transverse to the camshaft axis, a secure, accurate positional fixation of the roller pin on the roller tappet is ensured.
  • the roller pin can thus be non-positively and positively connected to the roller tappet.
  • Control means for example markings
  • a marking can be provided on the roller bolt and / or roller tappet for checking the position of the roller bolt.
  • a positioning screw or a positioning step can also be attached to the roller tappet on both sides in order to be able to check the exact alignment and the distance of the squeeze shift by means of a gauge.
  • the form-fitting formation of the contact surfaces between the roller tappet and the roller bolt can be carried out in various ways.
  • the contact surfaces are flat and are profiled.
  • the profiles run parallel to the longitudinal axis of the roller pin and the profiles between the roller tappet and the roller pin correspond to each other.
  • the profiles are designed so that they allow the roller bolt to be shifted at intervals of a few tenths of a millimeter.
  • the profiles After moving and aligning the roller bolt into the desired position, the profiles snap into place and ensure that the roller bolt cannot slip when the roller bolt is screwed onto the roller tappet.
  • Sawtooth-like profiling is particularly suitable.
  • the profiles of the two contact surfaces can also be designed as tongues and grooves, as pins and holes or as a hemisphere and hemispherical recess.
  • the width of the profiled surface on the roller tappet is larger than on the roller bolt.
  • the length of the elongated holes on the roller pin should be adapted to the desired maximum pre-stroke change on the pump piston.
  • each of these In order to prevent lubricating oil from escaping through the elongated holes due to the lubrication of the roller mounted on the roller bolt, it is expedient to cover each of these with a plate which is held by the fastening screw.
  • the plate can be marked in a visible position, which enables the exact alignment and transverse displacement of the roller bolt to be checked.
  • To feed the lubricating oil into the bearing points between the roller and roller bolt there is an annular channel around a section of the fastening screw arranged, which is connected to the lubrication channel system of the roller pin.
  • the injection pump shown in Figure 1 consists of a one-piece pump housing 1, in which a pump cylinder 2, which has an axial bore in which the pump piston 3 is axially and rotatably guided, the stroke of the pump piston 3 is limited.
  • a pump work chamber 4 Above the pump piston 3 is a pump work chamber 4, which is connected via inlet bores 5 to the fuel chamber 6 incorporated in the pump housing 1 when the pump piston 3 is in the bottom dead center position.
  • the inlet bores 5 are sealed.
  • the fuel is fed into the fuel chamber 6 via pipelines which are connected to a fuel reservoir, which is not shown in detail.
  • the pump piston 3 is provided in its upper region with a helical control edge 7 for realizing different useful strokes.
  • a helical groove 8 and a vertically running groove 9 are incorporated, via which a connection between the pump working chamber 4 and the fuel chamber 6 can be established via the inlet bores 5 after the injection has taken place.
  • a spring-loaded pressure valve 10 is arranged at the upper end of the pump work chamber 4 and is connected to the injection valve via a bore 12 arranged in the valve carrier 11 and an injection pressure line. The pressure line, the injection valve and the injection nozzle are not shown in the drawing.
  • the pump cylinder 2 is followed by a spring chamber 13, in which a pump spring 14 is arranged, which ensures that the roller 17 of the roller tappet 16 attached to the pump piston 3 is constantly in contact with the injection cam 18 of the camshaft 19 (FIG. 2 ) stands.
  • a lubricating oil chamber with a lubricating oil supply and lubricating oil discharge line is arranged in a manner known per se.
  • a leakage barrier is provided in the lower region of the pump piston 3, which prevents fuel leaks from entering the camshaft chamber of the engine via the spring chamber 13.
  • the operation of the injection pump is as follows. The pump piston 3 is driven via the camshaft 19 mounted in the engine housing with the injection cam 18.
  • the stroke movement of the injection cam 18 is transmitted to the pump piston 3 via the roller 17 of the roller tappet 16.
  • the pump work chamber 4 is filled with fuel, which is drawn in from the fuel chamber 6 via the inlet bores 5.
  • the inlet bores 5 in the pump cylinder 2 are closed after a certain stroke and the fuel is compressed.
  • the pressure valve 10 is opened and fuel is pressed into the combustion chamber of the engine under high pressure through the bore 12 in the valve carrier 11, the injection pressure line, the injection valve and the injection nozzle.
  • the very small flow cross-sections of the nozzle bores in relation to the pump piston area cause the pressure to rise sharply.
  • the injection is ended by the helical groove 8 and the vertical groove 9 in the pump piston 3 when the connection of the pump working chamber 4 via the inlet bores 5 to the fuel chamber 6 is restored via these two grooves .
  • the pressure in the pump working space suddenly collapses and the injection is ended by the closing of the spring-loaded nozzle needle.
  • the continuous change in the injection quantity is achieved by a relative rotary movement of the pump piston 3 to the pump cylinder 2, which is initiated via a regulating shaft of the motor, not shown, and is transmitted to the pump piston by a regulating rod and regulating sleeve.
  • a spring-loaded check valve ensures a defined residual pressure in the injection pressure line after the injection has ended.
  • the roller tappet 16 is integrated in the pump housing 1 and attached to the pressure piece 15 of the injection pump.
  • the structural design of the roller tappet 16 with the roller 17 for transmitting the lifting movement for the pump piston 3 is shown in more detail in FIGS. 2 to 4.
  • FIG. 2 shows the roller tappet 16 with the roller 17 in cooperation with the injection cam 18 of the camshaft 19.
  • the roller 17, which is rotatably mounted on the roller pin 20, runs on the cam track of the injection cam 18.
  • the roller 17 is kept in constant contact with the cam track of the injection cam 18 via the pressure piece 15 under spring pressure and the roller tappet 16.
  • the roller pin 20 is fastened to the roller tappet 16 by means of two fastening screws 21 which are guided through the roller pin.
  • the two bores of the roller bolt 20 for the fastening screws 21 are designed as elongated holes 22 which are arranged transversely to the longitudinal axis of the roller bolt 20 (FIG. 4).
  • the roller pin 20 has a flat, flat region 23 at both ends, with a sawtooth-like profile 25, which is arranged around the elongated holes 22.
  • the teeth of the profile 25 run parallel to the longitudinal axis of the roller bolt 20 and are each identical.
  • the rows of teeth are formed by milling or driving in using a suitable device.
  • the axial distance between the injection cam 18 and the roller 17 is changed and thus the forward stroke of the pump piston 3 of the injection pump and thus the ignition point, as the stroke of the pump piston from the bottom dead center of the cam to the start of the delivery .
  • more parallel rows of teeth are arranged on the contact surfaces of the roller tappet 16 than on the roller pin.
  • roller bolt This enables the roller bolt to be shifted by 5 rows of teeth from the center position to the right or left, resulting in a change in the start of injection by ⁇ 2 o crankshaft angle.
  • Two position pins 26 are attached to the roller plunger 16 on one side and two corresponding markings are attached to the roller bolt 20, making it possible to check the desired displacement and exact alignment of the roller bolt by means of a distance gauge. Depending on the requirements of the engine manufacturer, the correction of the position of the roller pin can be repeated as often as required.
  • a channel 27 is provided on the roller tappet 16, which opens into an annular channel 28 which is guided over a section around the fastening screw 21 and into an axial channel 29 of the roller bolt 20 opens, from which a channel 30 leads to the lubrication point ( Figure 3).
  • the elongated holes 22 in the roller bolt 20 are covered by a plate 31 held by the fastening screw 21. At a visible location of the roller pin 20 and the plate 31, markings can be made at which the transverse displacement of the roller pin 20 can be read.
  • the change in the start of delivery of the injection pump which is usually required by the engine manufacturer, can now be carried out in a very simple and quick manner for injection pumps already mounted on the engine.
  • the two fastening screws on the roller bolt 20 are loosened until the roller bolt has come loose from the toothing with the corresponding contact surface 24 on the roller tappet and is freely displaceable.
  • the roller bolt 20 is brought into the desired position with the roller 17, pressed upwards until the respective rows of teeth lock together and at the same time the fastening screws are tightened again.
  • the distance between the respective positioning screw and the marking on the roller pin is checked and, if necessary, changed using a test gauge.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Abstract

The roller rotatably located on a roller bolt runs on the path of a camshaft cam. The roller bolt is releasably fixed to the roller tappet. Above the pump piston in the bottom dead centre position is arranged a pump work chamber connected by holes with a fuel chamber and by at least one injection valve with nozzle with the combustion chamber of the engine. The roller bolt (20) is crossways displaceable to the axis of the camshaft (19). The holes in the roller bolt for fixing the bolt to the tappet (16) are formed as long holes running crossways to the longitudinal axis of the bolt. The contact surfaces (24) between the roller bolt and the roller tappet are of the positive engagement type.

Description

Die Erfindung betrifft ein Verfahren zur Veränderung des Förderbeginns von Kraftstoffeinspritzpumpen für Verbrennungsmotoren, insbesondere Dieselmotoren, und eine geeignete Kraftstoffeinspritzpumpe.The invention relates to a method for changing the start of delivery of fuel injection pumps for internal combustion engines, in particular diesel engines, and a suitable fuel injection pump.

Die Förderbeginneinstellung von Einspritzpumpen für Verbrennungsmotoren erfolgt durch Vorhubeinstellung, d.h. Einstellung des Abstandes zwischen Pumpenauflageflansch und zugehörigem Rollenstößel bzw. Nockenwelle. Mit der Verstellung des Vorhubes wird der Zündzeitpunkt, der Hub des Pumpenkolbens vom unteren Totpunkt des Nockens bis zum Beginn der Förderung, verändert.
Aus der Literatur und Praxis sind bereits verschiedene Lösungen zur Förderbeginneinstellung von Einspritzpumpen bekannt.
In der Praxis werden z.B. Einspritzpumpen angewendet, bei denen der Pumpenkolben über auf der Nockenwelle aufgesetzte, verstellbare Kraftstoffnocken betätigt wird.
Durch Verdrehen des zweiteilig ausgebildeten Krafstoffnockens kann der Förderbeginn der Einspritzpumpe verändert werden. Diese Lösung hat den Nachteil, daß zur Übertragung des Drehmomentes von der Nockenwelle auf den Pumpenkolben nicht der maximal mögliche Wellendurchmesser zur Verfügung steht. Außerdem sind zur Verstellung des Nockens hydraulische Aggregate erforderlich und die Verstellung ist mit einem hohen Demontage- und Montageaufwand verbunden.
Bekannt ist auch, die Verstellung der Rollenstößel mittels einer Stößelschraube oder das Unterlegen von Ausgleichsscheiben zwischen dem Pumpenflansch und dem Motorblock.
Aus der DE 40 03 469 A1 ist eine Förderbeginneinstellung bekannt, bei der der Totpunkt des jeweiligen zugehörenden Motorzylinders über eine Kolbenabstandsmessung ermittelt und als Basis für die Förderbeginneinstellung herangezogen wird.
Die eigentliche Verstellung erfolgt dabei durch Unterlegen von Abstandsscheiben.
Das Unterlegen von Ausgleichs- oder Abstandsscheiben erfordert mehrmalige Demontagen und Montagen der Einspritzpumpe sowie der Kraftstoffversorgung, der Schmierölversorgung und der Einspritzdruckleitung.The delivery start setting of injection pumps for internal combustion engines is carried out by adjusting the stroke, ie setting the distance between the pump support flange and the associated roller tappet or camshaft. With the adjustment of the advance stroke, the ignition timing, the stroke of the pump piston from the bottom dead center of the cam to the start of delivery, is changed.
Various solutions for setting the start of delivery of injection pumps are already known from literature and practice.
In practice, for example, injection pumps are used in which the pump piston is actuated via adjustable fuel cams mounted on the camshaft.
The start of delivery of the injection pump can be changed by rotating the two-part fuel cam. This solution has the disadvantage that the maximum possible shaft diameter is not available for transmitting the torque from the camshaft to the pump piston. In addition, hydraulic units are required to adjust the cam and the adjustment is associated with a high disassembly and assembly effort.
It is also known to adjust the roller tappets by means of a tappet screw or to place shims between the pump flange and the engine block.
DE 40 03 469 A1 discloses a delivery start setting in which the dead center of the respective associated engine cylinder is determined by means of a piston distance measurement and is used as the basis for the delivery start setting.
The actual adjustment is done by placing spacers under it.
Placing shims or spacers requires repeated disassembly and assembly of the injection pump as well as the fuel supply, the lubricating oil supply and the injection pressure line.

Bekannt ist auch eine Förderbeginnverstellung mittels eines über dem Pumpenkolben angeordneten bewegbaren Steuerschiebers, der mittels eines Schrittmotors verstellt wird.
Diese Lösung verursacht hohe Kosten und ist in ihrer praktischen Anwendung sehr aufwendig.
In der Praxis werden seitens der Motorenhersteller Einspritzpumpen gefordert, mit denen hohe Einspritzdrücke realisiert werden können und die einen erheblich reduzierten Bauraum aufweisen. Das hat zur Folge, daß der Rollenstößelantrieb in die Einspritzpumpe verlegt werden muß. Eine Verstellung des Nockens auf der Nockenwelle wirkt sich nachteilig auf die erzielbaren Einspritzdrücke aus. Außerdem wird von den Motorenherstellern gefordert, daß der Demontage- und Montageaufwand zur Förderbeginnverstellung an bereits auf dem Motor montierter Einspritzpumpen gesenkt wird. Nach der Montage der Einspritzpumpen auf dem Motor sind durch baulich bedingte Motortoleranzen Zünddruckangleichungen durch Veränderungen des Förderbeginns der Einspritzpumpen vorzunehmen.Also known is a start of delivery adjustment by means of a movable control slide arranged above the pump piston, which is adjusted by means of a stepping motor.
This solution causes high costs and is very complex to use in practice.
In practice, the engine manufacturers require injection pumps with which high injection pressures can be achieved and which have a significantly reduced installation space. The consequence of this is that the roller tappet drive must be moved into the injection pump. Adjustment of the cam on the camshaft has a disadvantageous effect on the injection pressures that can be achieved. In addition, the engine manufacturers are required to reduce the disassembly and assembly work required for adjusting the start of delivery on injection pumps already mounted on the engine. After mounting the injection pumps on the engine, ignition tolerances must be adjusted due to structural engine tolerances by changing the start of delivery of the injection pumps.

Der Erfindung lag die Aufgabe zugrunde, ein Verfahren zur Veränderung des Förderbeginns von Kraftstoffeinspritzpumpen mit einem Rollenstößelantrieb zu schaffen, das auch bei bereits auf dem Motor montierten Einspritzpumpen, auch solchen mit integriertem Rollenstößelantrieb, eine wesentliche Verringerung des Demontage- und Montageaufwandes sowie eine sichere und zuverlässige Korrektur des Einspritzzeitpunktes ermöglicht.
Ferner ist es Aufgabe der Erfindung, eine entsprechend geeignete Kraftstoffeinspritzpumpe zu schaffen.The invention had for its object to provide a method for changing the start of delivery of fuel injection pumps with a roller tappet drive, which, even with injection pumps already mounted on the engine, including those with an integrated roller tappet drive, significantly reduces dismantling and assembly work, and is safe and reliable Correction of the injection time enables.
Furthermore, it is an object of the invention to provide a correspondingly suitable fuel injection pump.

Erfindungsgemäß wird die Aufgabe dadurch gelöst, daß die Sicherungs- und Befestigungselemente für den Rollenbolzen gelöst werden, der Rollenbolzen mit der Rolle in Querrichtung zur Nockenwellenachse verschoben wird und mittels Prüflehren der Rollenbolzen in der gewünschten Förderbeginnstellung ausgerichtet und anschließend am Rollenstößel fixiert wird.
Diese neue Verfahrensweise ermöglicht erstmalig eine Korrektur des Zündzeitpunktes von auf dem Motor montierten Einspritzpumpen bei sehr geringem Demontage- und Montageaufwand. Durch die Querverschiebung des Rollenbolzens mit der Rolle quer zur Nockenwellenachse wird je nach der erforderlichen Verstellung der horizontale Abstand zwischen der Rolle des Rollenstößels und der Nockenwellenbahn verändert, und dadurch der Vorhub des Pumpenkolbens eingestellt.According to the invention the object is achieved in that the securing and fastening elements for the roller bolt are solved, the roller bolt with the roller is displaced in the transverse direction to the camshaft axis and aligned by means of test gauges of the roller bolts in the desired start of delivery position and then fixed to the roller tappet.
This new procedure enables for the first time a correction of the ignition timing of injection pumps mounted on the engine with very little disassembly and assembly effort. The transverse displacement of the roller pin with the roller transversely to the camshaft axis changes the horizontal distance between the roller of the roller tappet and the camshaft path, depending on the required adjustment, and the forward stroke of the pump piston is thereby adjusted.

Erfindungsgemäß ist der Rollenbolzen quer verschiebbar zur Achse der Nockenwelle angeordnet, wobei die Bohrungen im Rollenbolzen zur Befestigung des Rollenbolzens am Rollenstößel als quer zur Längsachse des Rollenbolzens verlaufende Langlöcher ausgebildet sind. Die Berührungsflächen zwischen dem Rollenbolzen und dem Rollenstößel sind formschlüssig ausgebildet, derart, daß nach dem Verschieben des Rollenbolzens mit der Rolle quer zur Nockenwellenachse eine sichere, genaue örtliche Lagefixierung des Rollenbolzens am Rollenstößel gewährleistet ist. Der Rollenbolzen ist somit kraft- und formschlüssig mit dem Rollenstößel verbindbar. Am Rollenbolzen und/oder Rollenstößel können Kontrollmittel, z.B. Markierungen, zur Überprüfung der Position des Rollenbolzens vorgesehen sein. Anstelle einer Markierung kann auch eine Positionierschraube oder ein Positionierstitt jeweils beidseitig am Rollenstößel befestigt sein, um mittels einer Lehre die genaue Ausrichtung und den Abstand der Quetuerschiebung überprüfen zu können. Die formschlüssige Ausbildung der Berührungsflächen zwischen dem Rollenstößel und dem Rollenbolzen kann auf verschiedene Art und Weise erfolgen. Die Berührungsflächen sind dabei eben ausgebildet und mit einer Profilierung versehen. Die Profilierungen verlaufen parallel zur Längsachse des Rollenbolzens und die Profilierungen zwischen dem Rollenstößel und dem Rollenbolzen korrespondieren miteinander. Die Profilierungen sind so ausgebildet, daß sie eine Verschiebung des Rollenbolzens in Abständen von einigen Zehntelmillimetern ermöglichen. Nach dem Verschieben und Ausrichten des Rollenbolzens in die gewünschte Position rasten die Profilierungen ein und gewährleisten, daß während des Festschraubens des Rollenbolzens am Rollstößel ein Verrutschen des Rollenbolzens ausgeschlossen ist. Besonders gut geeignet ist eine sägezahnartige Profilierung. Die Profilierungen der beiden Berührungsflächen können auch als Federn und Nuten, als Stifte und Löcher oder als Halbkugel und halbkugelförmige Ausnehmung ausgebildet sein. Um die erforderliche Querverschiebung realisieren zu können, ist die profilierte Fläche am Rollenstößel in ihrer Breite größer als am Rollenbolzen. Die Länge der Langlöcher am Rollenbolzen sollte der gewünschten maximalen Vorhubveränderung am Pumpenkolben angepaßt sein.
Um zu verhindern, daß Schmieröl, bedingt durch die Schmierung der auf dem Rollenbolzen gelagerten Rolle, durch die Langlöcher austreten kann, ist es zweckmäßig, diese jeweils mit einer Platte abzudecken, die von der Befestigungsschraube gehalten wird. Die Platte kann an einer sichtbaren Stelle mit einer Markierung versehen werden, die es ermöglicht, die exakte Ausrichtung und Querverschiebung des Rollenbolzens überprüfen zu können. Zur Zuführung des Schmieröls in die Lagerstellen zwischen Rolle und Rollenbolzen ist um ein Teilstück der Befestigungsschraube ein Ringkanal angeordnet, der mit dem Schmierkanalsystem des Rollenbolzens verbunden ist. Der Vorteil dieser Förderbeginneinstellung unmittelbar am Rollenstößel ermöglicht, den Rollenstößelantrieb in das Pumpengehäuse der Einspritzpumpe zu verlegen und damit die Bauhöhe der Einspritzpumpe zu reduzieren. Die Förderbeginneinstellung kann unmittelbar vor Ort beim Motorenhersteller erfolgen und erfordert nur wenige Handgriffe.According to the invention, the roller bolt is arranged to be displaceable transversely to the axis of the camshaft, the bores in the roller bolt for fastening the roller bolt to the roller tappet being designed as elongated holes which run transversely to the longitudinal axis of the roller bolt. The contact surfaces between the roller pin and the roller tappet are designed in a form-fitting manner in such a way that after the roller pin has been moved with the roller transverse to the camshaft axis, a secure, accurate positional fixation of the roller pin on the roller tappet is ensured. The roller pin can thus be non-positively and positively connected to the roller tappet. Control means, for example markings, can be provided on the roller bolt and / or roller tappet for checking the position of the roller bolt. Instead of a marking, a positioning screw or a positioning step can also be attached to the roller tappet on both sides in order to be able to check the exact alignment and the distance of the squeeze shift by means of a gauge. The form-fitting formation of the contact surfaces between the roller tappet and the roller bolt can be carried out in various ways. The contact surfaces are flat and are profiled. The profiles run parallel to the longitudinal axis of the roller pin and the profiles between the roller tappet and the roller pin correspond to each other. The profiles are designed so that they allow the roller bolt to be shifted at intervals of a few tenths of a millimeter. After moving and aligning the roller bolt into the desired position, the profiles snap into place and ensure that the roller bolt cannot slip when the roller bolt is screwed onto the roller tappet. Sawtooth-like profiling is particularly suitable. The profiles of the two contact surfaces can also be designed as tongues and grooves, as pins and holes or as a hemisphere and hemispherical recess. In order to be able to implement the required transverse displacement, the width of the profiled surface on the roller tappet is larger than on the roller bolt. The length of the elongated holes on the roller pin should be adapted to the desired maximum pre-stroke change on the pump piston.
In order to prevent lubricating oil from escaping through the elongated holes due to the lubrication of the roller mounted on the roller bolt, it is expedient to cover each of these with a plate which is held by the fastening screw. The plate can be marked in a visible position, which enables the exact alignment and transverse displacement of the roller bolt to be checked. To feed the lubricating oil into the bearing points between the roller and roller bolt, there is an annular channel around a section of the fastening screw arranged, which is connected to the lubrication channel system of the roller pin. The advantage of this delivery start setting directly on the roller tappet enables the roller tappet drive to be moved into the pump housing of the injection pump and thus to reduce the overall height of the injection pump. The start of delivery can be set directly on site at the engine manufacturer and requires only a few simple steps.

Die Erfindung soll nachstehend an einem Ausführungsbeispiel näher erläutert werden. In der zugehörigen Zeichnung zeigen

Fig. 1
eine Kraftstoffeinspritzpumpe als Schnittdarstellung,
Fig. 2
den Rollenstößel der Einspritzpumpe gemäß Fig. 1 im Zusammenwirken mit der Nockenwelle in vergrößerter Schnittdarstellung,
Fig. 3
einen Schnitt gemäß der Linie A-A in Fig. 2 als Teilansicht und
Fig. 4
einen verstellbaren Rollenbolzen im Längsschnitt in vergrößerter Darstellung.
The invention will be explained in more detail below using an exemplary embodiment. Show in the accompanying drawing
Fig. 1
a fuel injection pump as a sectional view,
Fig. 2
1 in cooperation with the camshaft in an enlarged sectional view,
Fig. 3
a section along the line AA in Fig. 2 as a partial view
Fig. 4
an adjustable roller pin in longitudinal section in an enlarged view.

Die in Figur 1 dargestellte Einspritzpumpe besteht aus einem einteiligen Pumpengehäuse 1, in dem ein Pumpenzylinder 2, der eine axiale Bohrung aufweist, in der der Pumpenkolben 3 axial- und drehbeweglich geführt ist, wobei der Hub des Pumpenkolbens 3 begrenzt ist. Oberhalb des Pumpenkolbens 3 befindet sich ein Pumpenarbeitsraum 4, der über Zulaufbohrungen 5 mit dem im Pumpengehäuse 1 eingearbeiteten Kraftstoffraum 6 verbunden ist, wenn sich der Pumpenkolben 3 in unterer Totpunktlage befindet. Während der Aufwärtsbewegung des Pumpenkolbens 3 werden die Zulaufbohrungen 5 dicht verschlossen. Die Zuführung des Kraftstoffes in den Kraftstoffraum 6 erfolgt über Rohrleitungen, die mit einem Kraftstoffvorratsbehälter verbunden sind, der nicht näher dargestellt ist. Der Pumpenkolben 3 ist in seinem oberen Bereich mit einer wendelförmigen Steuerkante 7 versehen, zur Realisierung unterschiedlicher Nutzhübe. Im oberen Bereich des Pumpenkolbens 3 sind eine wendelförmige Nut 8 und eine senkrecht verlaufende Nut 9 eingearbeitet, über die nach erfolgter Einspritzung eine Verbindung zwischen dem Pumpenarbeitsraum 4 und dem Kraftstoffraum 6 über die Zulaufbohrungen 5 herstellbar ist. Am oberen Ende des Pumpenarbeitsraumes 4 ist ein federbelastetes Druckventil 10 angeordnet, das über eine im Ventilträger 11 angeordnete Bohrung 12 und eine Einspritzdruckleitung mit dem Einspritzventil in Verbindung steht. Die Druckleitung, das Einspritzventil und die Einspritzdüse sind in der Zeichnung nicht näher dargestellt.The injection pump shown in Figure 1 consists of a one-piece pump housing 1, in which a pump cylinder 2, which has an axial bore in which the pump piston 3 is axially and rotatably guided, the stroke of the pump piston 3 is limited. Above the pump piston 3 is a pump work chamber 4, which is connected via inlet bores 5 to the fuel chamber 6 incorporated in the pump housing 1 when the pump piston 3 is in the bottom dead center position. During the upward movement of the pump piston 3, the inlet bores 5 are sealed. The fuel is fed into the fuel chamber 6 via pipelines which are connected to a fuel reservoir, which is not shown in detail. The pump piston 3 is provided in its upper region with a helical control edge 7 for realizing different useful strokes. In the upper area of the pump piston 3, a helical groove 8 and a vertically running groove 9 are incorporated, via which a connection between the pump working chamber 4 and the fuel chamber 6 can be established via the inlet bores 5 after the injection has taken place. A spring-loaded pressure valve 10 is arranged at the upper end of the pump work chamber 4 and is connected to the injection valve via a bore 12 arranged in the valve carrier 11 and an injection pressure line. The pressure line, the injection valve and the injection nozzle are not shown in the drawing.

An den Pumpenzylinder 2 schließt sich nach unter ein Federnraum 13 an, in dem eine Pumpenfeder 14 angeordnet ist, die dafür sorgt, daß die Rolle 17 des am Pumpenkolben 3 befestigten Rollenstößels 16 ständig in Berührungskontakt mit dem Einspritznocken 18 der Nockenwelle 19 (Fig. 2) steht.
Im Pumpenzylinder 2 ist in an sich bekannter Weise eine Schmierölkammer mit einer Schmierölzu- und Schmierölablaufleitung angeordnet. Außerdem ist im unteren Bereich des Pumpenkolbens 3 eine Leckagesperre vorgesehen, die verhindert, daß Kraftstoffleckagen über den Federnraum 13 in den Nockenwellenraum des Motors gelangen können.
Die Funktionsweise der Einspritzpumpe ist folgende.
Der Antrieb des Pumpenkolbens 3 erfolgt über die im Motorengehäuse gelagerte Nockenwelle 19 mit dem Einspritznocken 18. Dabei wird die Hubbewegung des Einspritznockens 18 über die Rolle 17 des Rollenstößels 16 auf den Pumpenkolben 3 übertragen. Während der Abwärtsbewegung des Pumpenkolbens 3 wird der Pumpenarbeitsraum 4 mit Kraftstoff gefüllt, der aus dem Kraftstoffraum 6 über die Zulaufbohrungen 5 angesaugt wird. Während der Aufwärtsbewegung des Pumpenkolbens werden nach einem bestimmten Hub die Zulaufbohrungen 5 im Pumpenzylinder 2 verschlossen und der Kraftstoff wird verdichtet. Vor Erreichen des oberen Totpunktes des Pumpenkolbens 3 wird das Druckventil 10 geöffnet und durch die Bohrung 12 im Ventilträger 11, die Einspritzdruckleitung, das Einspritzventil und die Einspritzdüse Kraftstoff unter hohem Druck in den Brennraum des Motors gedrückt. Die im Verhältnis zur Pumpenkolbenfläche sehr kleinen Durchflußquerschnitte der Düsenbohrungen bewirken ein starkes Ansteigen des Druckes. Während der weiteren Aufwärtsbewegung des Pumpenkolbens 3 bis zur oberen Totpunktlage wird durch die wendelförmige Nut 8 und die senkrechte Nut 9 im Pumpenkolben 3 die Einspritzung beendet, wenn über diese beiden Nuten die Verbindung des Pumpenarbeitsraumes 4 über die Zulaufbohrungen 5 mit dem Kraftstoffraum 6 wieder hergestellt ist. Durch diese Möglichkeit des Abfließens des Kraftstoffes bricht der Druck im Pumpenarbeitsraum schlagartig zusammen und die Einspritzung wird durch das Schließen der federbelasteten Düsennadel beendet. Die stufenlose Änderung der Einspritzmenge wird durch eine relative Drehbewegung des Pumpenkolbens 3 zum Pumpenzylinder 2 erreicht, die über eine nicht dargestellte Regulierwelle des Motors eingeleitet und durch eine Regelstange und Regelhülse auf den Pumpenkolben übertragen wird. Ein federbelastetes Rückschlagventil sorgt für einen definierten Restdruck in der Einspritzdruckleitung nach Beendigung der Einspritzung. Nach der Montage der Einspritzpumpe auf dem Motor ist in der Regel eine Anpassung des Zündzeitpunktes und damit des Förderbeginns der Kraftstoffeinspritzpumpe infolge herstellungsbedingt auftretender Motortoleranzen erforderlich. Wie die Ausführung der Kraftstoffeinspritzpumpe gemäß Figur 1 zeigt, ist der Rollenstößel 16 im Pumpengehäuse 1 integriert und am Druckstück 15 der Einspritzpumpe befestigt.
Der konstruktive Aufbau des Rollenstößels 16 mit der Rolle 17 zur Übertragung der Hubbewegung für den Pumpenkolben 3 ist in den Figuren 2 bis 4 näher dargestellt. In der Figur 2 ist der Rollenstößel 16 mit der Rolle 17 im Zusammenwirken mit dem Einspritznocken 18 der Nockenwelle 19 gezeigt.
Die auf dem Rollenbolzen 20 drehbeweglich gelagerte Rolle 17 läuft auf der Nockenbahn des Einspritznockens 18 ab. Die Rolle 17 wird dabei über das unter Federdruck stehende Druckstück 15 und den Rollenstößel 16 ständig in Berührungskontakt mit der Kurvenbahn des Einspritznockens 18 gehalten. Der Rollenbolzen 20 ist mittels zweier Befestigungsschrauben 21, die durch den Rollenbolzen geführt sind, am Rollenstößel 16 befestigt. Die beiden Bohrungen des Rollenbolzens 20 für die Befestigungsschrauben 21 sind als Langlöcher 22 ausgebildet, die quer zur Längsachse des Rollenbolzens 20 angeordnet sind (Figur 4). Der Rollenbolzen 20 weist an seinen beiden Enden jeweils einen flachen ebenen Bereich 23, mit einer sägezahnartigen Profilierung 25 auf, die um die Langlöcher 22 angeordnet ist. Die Zähne der Profilierung 25 verlaufen parallel zur Längsachse des Rollenbolzens 20 und sind jeweils identisch ausgebildet. Die Zahnreihen werden durch Fräsen oder Einschlagen mittels einer geeigneten Vorrichtung gebildet. An den beiden ebenen Befestigungsflächen 24 des Rollenstößels 16 für den Rollenbolzen 20 sind ebenfalls parallel verlaufende Zahnreihen als Profilierung eingearbeitet, derart, daß zwischen den Berührungsflächen 23, 24 zwischen Rollenstößel 16 und Rollenbolzen 20 eine einrastbare formschlüssige Verbindung herstellbar ist. Die Profilierung zwischen den beiden Berührungsflächen 23, 24, die exakt parallel zur Nockenwellenachse ausgerichtet ist, ermöglicht eine sichere und genau einstellbare Querverschiebung des Rollenbolzens 20 mit der Rolle 17, bezogen auf die Nockenwellenachse.
Entsprechend der vorgesehenen Verschiebbarkeit des Rollenbolzens 20 in Querrichtung wird der axiale Abstand zwischen dem Einspritznocken 18 und der Rolle 17 verändert und damit der Vorhub des Pumpenkolbens 3 der Einspritzpumpe und somit der Zündzeitpunkt, als Hub des Pumpenkolbens vom unteren Totpunkt des Nockens bis zum Beginn der Förderung. An den Berührungsflächen des Rollenstößels 16 sind je nach der erforderlichen Verschiebbarkeit des Rollenbolzens 20 aus der Mittellage mehr parallel verlaufende Zahnreihen angeordnet als am Rollenbolzen. Am Rollenstößel sind. z.B. 30 Zahnreihen und am Rollenbolzen 20 Zahnreihen angebracht.The pump cylinder 2 is followed by a spring chamber 13, in which a pump spring 14 is arranged, which ensures that the roller 17 of the roller tappet 16 attached to the pump piston 3 is constantly in contact with the injection cam 18 of the camshaft 19 (FIG. 2 ) stands.
In the pump cylinder 2, a lubricating oil chamber with a lubricating oil supply and lubricating oil discharge line is arranged in a manner known per se. In addition, a leakage barrier is provided in the lower region of the pump piston 3, which prevents fuel leaks from entering the camshaft chamber of the engine via the spring chamber 13.
The operation of the injection pump is as follows.
The pump piston 3 is driven via the camshaft 19 mounted in the engine housing with the injection cam 18. The stroke movement of the injection cam 18 is transmitted to the pump piston 3 via the roller 17 of the roller tappet 16. During the downward movement of the pump piston 3, the pump work chamber 4 is filled with fuel, which is drawn in from the fuel chamber 6 via the inlet bores 5. During the upward movement of the pump piston, the inlet bores 5 in the pump cylinder 2 are closed after a certain stroke and the fuel is compressed. Before the top dead center of the pump piston 3 is reached, the pressure valve 10 is opened and fuel is pressed into the combustion chamber of the engine under high pressure through the bore 12 in the valve carrier 11, the injection pressure line, the injection valve and the injection nozzle. The very small flow cross-sections of the nozzle bores in relation to the pump piston area cause the pressure to rise sharply. During the further upward movement of the pump piston 3 to the top dead center position, the injection is ended by the helical groove 8 and the vertical groove 9 in the pump piston 3 when the connection of the pump working chamber 4 via the inlet bores 5 to the fuel chamber 6 is restored via these two grooves . As a result of this possibility of the fuel flowing away, the pressure in the pump working space suddenly collapses and the injection is ended by the closing of the spring-loaded nozzle needle. The continuous change in the injection quantity is achieved by a relative rotary movement of the pump piston 3 to the pump cylinder 2, which is initiated via a regulating shaft of the motor, not shown, and is transmitted to the pump piston by a regulating rod and regulating sleeve. A spring-loaded check valve ensures a defined residual pressure in the injection pressure line after the injection has ended. After mounting the injection pump on the engine, there is usually an adjustment of the ignition timing and so that the start of delivery of the fuel injection pump is required due to manufacturing tolerances. As the design of the fuel injection pump according to FIG. 1 shows, the roller tappet 16 is integrated in the pump housing 1 and attached to the pressure piece 15 of the injection pump.
The structural design of the roller tappet 16 with the roller 17 for transmitting the lifting movement for the pump piston 3 is shown in more detail in FIGS. 2 to 4. FIG. 2 shows the roller tappet 16 with the roller 17 in cooperation with the injection cam 18 of the camshaft 19.
The roller 17, which is rotatably mounted on the roller pin 20, runs on the cam track of the injection cam 18. The roller 17 is kept in constant contact with the cam track of the injection cam 18 via the pressure piece 15 under spring pressure and the roller tappet 16. The roller pin 20 is fastened to the roller tappet 16 by means of two fastening screws 21 which are guided through the roller pin. The two bores of the roller bolt 20 for the fastening screws 21 are designed as elongated holes 22 which are arranged transversely to the longitudinal axis of the roller bolt 20 (FIG. 4). The roller pin 20 has a flat, flat region 23 at both ends, with a sawtooth-like profile 25, which is arranged around the elongated holes 22. The teeth of the profile 25 run parallel to the longitudinal axis of the roller bolt 20 and are each identical. The rows of teeth are formed by milling or driving in using a suitable device. On the two flat fastening surfaces 24 of the roller plunger 16 for the roller bolt 20, parallel rows of teeth are also incorporated as a profile, such that a snap-fit connection can be produced between the contact surfaces 23, 24 between roller plunger 16 and roller bolt 20. The profiling between the two contact surfaces 23, 24, which is aligned exactly parallel to the camshaft axis, enables a safe and precisely adjustable transverse displacement of the roller bolt 20 with the roller 17, based on the camshaft axis.
According to the intended displaceability of the roller pin 20 in the transverse direction, the axial distance between the injection cam 18 and the roller 17 is changed and thus the forward stroke of the pump piston 3 of the injection pump and thus the ignition point, as the stroke of the pump piston from the bottom dead center of the cam to the start of the delivery . Depending on the required displaceability of the roller pin 20 from the central position, more parallel rows of teeth are arranged on the contact surfaces of the roller tappet 16 than on the roller pin. Are on the roller tappet. eg 30 rows of teeth and 20 rows of teeth attached to the roller pin.

Dadurch wird eine Verschiebbarkeit des Rollenbolzens um jeweils 5 Zahnreihen aus der Mittellage nach rechts bzw. links ermöglicht, wodurch sich eine Einspritzbeginnveränderung um ± 2o Kurbelwellenwinkel ergibt. Am Rollenstößel 16 sind an einer Seite zwei Positionsstifte 26 befestigt und am Rollenbolzen 20 sind zwei entsprechende Markierungen angebracht, wodurch es möglich ist, mittels einer Abstandslehre die gewünschte Verschiebung und exakte Ausrichtung des Rollenbolzens zu überprüfen.
Je nach den Erfordernissen beim Motorenhersteller kann die Korrektur der Lage des Rollenbolzens beliebig oft wiederholt werden. Um infolge der Verschiebbarkeit des Rollenbolzens 20 die erforderliche Ölschmierung der Rolle 17 zu gewährleisten, ist am Rollenstößel 16 ein Kanal 27 vorgesehen, der in einen Ringkanal 28 mündet, der über ein Teilstück um die Befestigungsschraube 21 geführt ist und in einen axialen Kanal 29 des Rollenbolzens 20 mündet, von dem aus ein Kanal 30 zur Schmierstelle führt (Figur 3).
Um ein Austreten von Schmieröl durch die Langlöcher 22 zu verhindern, werden die Langlöcher 22 im Rollenbolzen 20 mittels einer von der Befestigungsschraube 21 gehaltenen Platte 31 abgedeckt. An einer sichtbaren Stelle des Rollenbolzens 20 und der Platte 31 können Markierungen angebracht werden, an denen die Querverschiebung des Rollenbolzens 20 abgelesen werden kann.
Die in der Regel beim Motorenhersteller erforderliche Veränderung des Förderbeginns der Einspritzpumpe kann nunmehr für bereits am Motor montierte Einspritzpumpen auf sehr einfache und schnelle Art und Weise erfolgen. Am Rollenbolzen 20 werden die beiden Befestigungsschrauben soweit gelockert, bis sich der Rollenbolzen aus der Verzahnung mit der korrespondierenden Berührungsfläche 24 am Rollenstößel gelöst hat und frei querverschiebbar ist. Der Rollenbolzen 20 wird mit der Rolle 17 in die gewünschte Position gebracht, nach oben gedrückt, bis die jeweiligen Zahnreihen miteinander verrasten und dabei werden gleichzeitig die Befestigungsschrauben wieder angezogen. Vor der endgültigen Fixierung des Rollenbolzens in seiner geänderten Lage wird mittels einer Prüflehre der Abstand zwischen der jeweiligen Positionierschraube und der Markierung am Rollenbolzen überprüft und gegebenenfalls verändert.This enables the roller bolt to be shifted by 5 rows of teeth from the center position to the right or left, resulting in a change in the start of injection by ± 2 o crankshaft angle. Two position pins 26 are attached to the roller plunger 16 on one side and two corresponding markings are attached to the roller bolt 20, making it possible to check the desired displacement and exact alignment of the roller bolt by means of a distance gauge.
Depending on the requirements of the engine manufacturer, the correction of the position of the roller pin can be repeated as often as required. In order to ensure the necessary oil lubrication of the roller 17 due to the displaceability of the roller bolt 20, a channel 27 is provided on the roller tappet 16, which opens into an annular channel 28 which is guided over a section around the fastening screw 21 and into an axial channel 29 of the roller bolt 20 opens, from which a channel 30 leads to the lubrication point (Figure 3).
In order to prevent lubricant oil from escaping through the elongated holes 22, the elongated holes 22 in the roller bolt 20 are covered by a plate 31 held by the fastening screw 21. At a visible location of the roller pin 20 and the plate 31, markings can be made at which the transverse displacement of the roller pin 20 can be read.
The change in the start of delivery of the injection pump, which is usually required by the engine manufacturer, can now be carried out in a very simple and quick manner for injection pumps already mounted on the engine. The two fastening screws on the roller bolt 20 are loosened until the roller bolt has come loose from the toothing with the corresponding contact surface 24 on the roller tappet and is freely displaceable. The roller bolt 20 is brought into the desired position with the roller 17, pressed upwards until the respective rows of teeth lock together and at the same time the fastening screws are tightened again. Before the roller pin is finally fixed in its changed position, the distance between the respective positioning screw and the marking on the roller pin is checked and, if necessary, changed using a test gauge.

Claims (15)

Verfahren zur Veränderung des Förderbeginns von Kraftstoffeinspritzpumpen für Verbrennungsmotoren, insbesondere Dieselmotoren, mit einem am unteren Ende des Pumpenkolbens befestigten Rollenstößel mit einer drehbeweglich gelagerten Rolle, wobei der Rollenbolzen am Rollenstößel lösbar befestigt ist, und die Rolle auf der Nockenbahn des fest mit der Nockenwelle verbundenen Nockens abläuft, dadurch gekennzeichnet, daß die Sicherungs- und Befestigungselemente für den Rollenbolzen gelöst werden, der Rollenbolzen mit der Rolle in Querrichtung zur Nockenwellenachse verschoben wird und mittels Prüflehren der Rollenbolzen in der gewünschten Förderbeginnstellung ausgerichtet und anschließend am Rollenstößel fixiert wird.Method for changing the start of delivery of fuel injection pumps for internal combustion engines, in particular diesel engines, with a roller tappet attached to the lower end of the pump piston with a rotatably mounted roller, the roller bolt being detachably attached to the roller tappet, and the roller on the cam track of the cam firmly connected to the camshaft expires, characterized in that the securing and fastening elements for the roller pin are loosened, the roller pin is moved with the roller in the transverse direction to the camshaft axis and aligned by means of test gauges of the roller pin in the desired start of delivery position and then fixed to the roller tappet. Kraftstoffeinspritzpumpe für Verbrennungsmotoren, insbesondere Dieselmotoren, bestehend aus einem Pumpengehäuse mit einem Pumpenzylinder und einem Pumpenkolben, der axial- und drehbeweglich geführt ist und von einem am unteren Ende des Pumpenkolbens befestigten Rollenstößel angetrieben wird, wobei die auf einem Rollenbolzen drehbeweglich gelagerte Rolle auf der Nockenbahn eines fest mit der Nockenwelle verbundenen Nockens abläuft und der Rollenbolzen lösbar an dem Rollenstößel befestigt ist, einem oberhalb des in unterer Totpunktlage befindlichen Pumpenkolbens angeordneten Pumpenarbeitsraum, der über Bohrungen mit einem Kraftstoffraum in Verbindung steht, und über mindestens ein Einspritzventil mit Einspritzdüse mit dem Verbrennungsraum des Motors verbunden ist, einem oberhalb der Nockenwelle liegenden Federnraum sowie mindestens einer Schmierölkammer im Pumpenzylinder, die mit einer Schmierölzuund -ablaufleitung verbunden ist, dadurch gekennzeichnet, daß der Rollenbolzen (20) quer verschiebbar zur Achse der Nockenwelle (19) angeordnet ist, wobei die Bohrungen im Rollenbolzen (20) zur Befestigung des Rollenbolzens (20) am Rollenstößel (16) als quer zur Längsachse des Rollenbolzens (20) verlaufende Langlöcher (22) ausgebildet sind, und die Berührungsflächen (23, 24) zwischen dem Rollenbolzen (20) und dem Rollenstößel (16) formschlüssig ausgebildet sind, derart, daß nach dem Verschieben des Rollenbolzen (20) mit der Rolle (17) quer zur Nockenwellenachse (19) eine sichere, genaue örtliche Lagefixierung des Rollenbolzens (20) am Rollenstößel (16) gewährleistet ist.Fuel injection pump for internal combustion engines, in particular diesel engines, consisting of a pump housing with a pump cylinder and a pump piston, which is guided axially and rotatably and is driven by a roller tappet fastened to the lower end of the pump piston, the roller rotatably mounted on a roller bolt on the cam track of one fixed cam connected to the camshaft and the roller pin is releasably attached to the roller tappet, a pump work chamber located above the pump piston in the bottom dead center position, which is connected to a fuel chamber via bores, and via at least one injection valve with an injection nozzle to the combustion chamber of the engine is connected, a spring chamber located above the camshaft and at least one lubricating oil chamber in the pump cylinder, which is connected to a lubricating oil supply and drain line, characterized in that the roller bolt n (20) is arranged such that it can be moved transversely to the axis of the camshaft (19), the bores in the roller bolt (20) for fastening the roller bolt (20) to the roller tappet (16) as elongated holes (22) extending transversely to the longitudinal axis of the roller bolt (20). are formed, and the contact surfaces (23, 24) between the roller pin (20) and the roller tappet (16) are designed such that after moving the roller pin (20) with the roller (17) transverse to Camshaft axis (19) a secure, precise location fixation of the roller pin (20) on the roller tappet (16) is guaranteed. Kraftstoffeinspritzpumpe nach Anspruch 2, dadurch gekennzeichnet, daß am Rollenbolzen (20) und/oder Rollenstößel (16) Kontrollmittel (26) zur Überprüfung der Position des Rollenbolzens (20) vorgesehen sind.Fuel injection pump according to Claim 2, characterized in that control means (26) for checking the position of the roller bolt (20) are provided on the roller bolt (20) and / or roller tappet (16). Kraftstoffeinspritzpumpe nach Anspruch 3, dadurch gekennzeichnet, daß als Kontrollmittel beidseitig am Rollenstößel (16) und/oder Rollenbolzen (20) Markierungen angebracht sind.Fuel injection pump according to Claim 3, characterized in that markings are provided on both sides of the roller tappet (16) and / or roller bolt (20) as control means. Kraftstoffeinspritzpumpe nach Anspruch 3, dadurch gekennzeichnet, daß beidseitig am Rollenstößel (16) Stifte (26) für eine Abstandsmessung angebracht sind.Fuel injection pump according to Claim 3, characterized in that pins (26) are attached to the roller tappet (16) on both sides for a distance measurement. Kraftstoffeinspritzpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Berührungsflächen (23, 24) zwischen dem Rollenstößel (16) und dem Rollenbolzen (20) als ebene Flächen mit einer Profilierung (25) ausgebildet sind, wobei die Profilierungen (25) parallel zur Längsachse des Rollenbolzens (20) verlaufen.Fuel injection pump according to one of Claims 1 to 5, characterized in that the contact surfaces (23, 24) between the roller tappet (16) and the roller bolt (20) are designed as flat surfaces with a profile (25), the profiles (25) run parallel to the longitudinal axis of the roller pin (20). Kraftstoffeinspritzpumpe nach Anspruch 6, dadurch gekennzeichnet, daß die Profilierungen (25) sägezahnartig ausgebildet sind.Fuel injection pump according to Claim 6, characterized in that the profiles (25) are of sawtooth-like design. Kraftstoffeinspritzpumpe nach Anspruch 6, dadurch gekennzeichnet, daß die Profilierungen (25) als ineinandereingreifbare Federn und Nuten ausgebildet sind.Fuel injection pump according to Claim 6, characterized in that the profiles (25) are designed as interlocking tongues and grooves. Kraftstoffeinspritzpumpe nach Anspruch 6, dadurch gekennzeichnet, daß die Profilierungen (25) als ineinandereingreifbare Stifte und Löcher ausgebildet sind.Fuel injection pump according to Claim 6, characterized in that the profiles (25) are designed as interlocking pins and holes. Kraftstoffeinspritzpumpe nach Anspruch 6, dadurch gekennzeichnet, daß die Profilierungen (25) als ineinandereingreifbare Halbkugeln und halbkugelförmige Ausnehmungen ausgebildet sind.Fuel injection pump according to Claim 6, characterized in that the profiles (25) are designed as intermeshing hemispheres and hemispherical recesses. Kraftstoffeinspritzpumpe nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß die Breite der profilierten Berührungsfläche (24) am Rollenstößel (16) größer ist als die Breite der profilierten Berührungsfläche (23) am Rollenbolzen (20).Fuel injection pump according to one of claims 1 to 10, characterized in that the width of the profiled contact surface (24) on Roller plunger (16) is larger than the width of the profiled contact surface (23) on the roller bolt (20). Kraftstoffeinspritzpumpe nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, daß die Länge der Langlöcher (22) des Rollenbolzens (20) der maximalen Vorhubänderung des Pumpenkolbens (3) angepaßt ist.Fuel injection pump according to one of claims 1 to 11, characterized in that the length of the elongated holes (22) of the roller bolt (20) is adapted to the maximum change in the forward stroke of the pump piston (3). Kraftstoffeinspritzpumpe nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, daß die Langlöcher (22) des Rollenbolzens (20) mittels jeweils einer von der Befestigungsschraube (21) gehaltenen Platte (31) abgedeckt sind.Fuel injection pump according to one of claims 1 to 12, characterized in that the elongated holes (22) of the roller bolt (20) are covered by means of a plate (31) held by the fastening screw (21). Kraftstoffeinspritzpumpe nach Anspruch 13, dadurch gekennzeichnet, daß an der Platte (31) Markierungen angebracht sind.Fuel injection pump according to Claim 13, characterized in that markings are made on the plate (31). Kraftstoffeinspritzpumpe nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, daß zur Schmierung der auf dem Rollenbolzen (20) drehbar gelagerten Rolle (17) um ein Teilstück der Befestigungsschraube (21) ein Ringkanal (28) angeordnet ist, der mit dem Schmierkanalsystem im Rollenbolzen (20) verbunden ist.Fuel injection pump according to one of claims 1 to 14, characterized in that for lubricating the roller (17) rotatably mounted on the roller bolt (20), an annular channel (28) is arranged around a part of the fastening screw (21), which is connected to the lubrication channel system in the roller bolt (20) is connected.
EP96111818A 1995-07-31 1996-07-23 Method of changing the timing of fuel injection pumps on a fuel injection pump thereof Expired - Lifetime EP0757174B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19527720A DE19527720A1 (en) 1995-07-31 1995-07-31 Procedure for changing the start of delivery of fuel injection pumps and fuel injection pump
DE19527720 1995-07-31

Publications (3)

Publication Number Publication Date
EP0757174A2 true EP0757174A2 (en) 1997-02-05
EP0757174A3 EP0757174A3 (en) 1997-11-26
EP0757174B1 EP0757174B1 (en) 2002-03-20

Family

ID=7768090

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96111818A Expired - Lifetime EP0757174B1 (en) 1995-07-31 1996-07-23 Method of changing the timing of fuel injection pumps on a fuel injection pump thereof

Country Status (5)

Country Link
EP (1) EP0757174B1 (en)
JP (1) JPH09100760A (en)
AT (1) ATE214787T1 (en)
DE (2) DE19527720A1 (en)
DK (1) DK0757174T3 (en)

Cited By (3)

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Publication number Priority date Publication date Assignee Title
GB2324123A (en) * 1997-01-28 1998-10-14 Cummins Engine Co Inc A fuel pump with means to minimise side loads on plunger
EP1076174A2 (en) * 1999-08-13 2001-02-14 Robert Bosch Gmbh Single cylinder high pressure pump
EP1312801A2 (en) * 2001-11-16 2003-05-21 Robert Bosch Gmbh Fuel cooled pumping stage for high pressure fuel pump

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19729793A1 (en) * 1997-07-11 1999-01-14 Bosch Gmbh Robert Piston pump for high-pressure fuel supply
DE19857376A1 (en) 1998-12-12 2000-06-15 Mahle Ventiltrieb Gmbh Roller plunger
JP3905282B2 (en) 2000-04-18 2007-04-18 トヨタ自動車株式会社 High pressure pump
DE102016224347B4 (en) * 2016-12-07 2018-06-21 Robert Bosch Gmbh Pump, in particular high-pressure pump of a fuel injection system, with a plunger assembly which has a rotation and a Schmierstoffversor- supply of the roller by an extended bearing pin

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JPS5765806A (en) * 1980-10-07 1982-04-21 Hitachi Zosen Corp Computer controlling diesel engine
JPS6267278A (en) * 1985-09-20 1987-03-26 Mitsubishi Heavy Ind Ltd Fuel injection timing changing device
DE3643271A1 (en) * 1986-12-18 1988-06-23 Kloeckner Humboldt Deutz Ag Fuel injection pump with built-in timing device
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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2324123A (en) * 1997-01-28 1998-10-14 Cummins Engine Co Inc A fuel pump with means to minimise side loads on plunger
GB2324123B (en) * 1997-01-28 2000-11-08 Cummins Engine Co Inc High pressure fuel pump assembly
EP1076174A2 (en) * 1999-08-13 2001-02-14 Robert Bosch Gmbh Single cylinder high pressure pump
EP1076174A3 (en) * 1999-08-13 2003-11-19 Robert Bosch Gmbh Single cylinder high pressure pump
EP1312801A2 (en) * 2001-11-16 2003-05-21 Robert Bosch Gmbh Fuel cooled pumping stage for high pressure fuel pump
EP1312801A3 (en) * 2001-11-16 2004-05-12 Robert Bosch Gmbh Fuel cooled pumping stage for high pressure fuel pump

Also Published As

Publication number Publication date
DE59608903D1 (en) 2002-04-25
ATE214787T1 (en) 2002-04-15
JPH09100760A (en) 1997-04-15
EP0757174B1 (en) 2002-03-20
DK0757174T3 (en) 2002-07-15
DE19527720A1 (en) 1997-02-06
EP0757174A3 (en) 1997-11-26

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