EP0055245A2 - Device for adjusting and coordinating a plurality of injection devices - Google Patents

Device for adjusting and coordinating a plurality of injection devices Download PDF

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Publication number
EP0055245A2
EP0055245A2 EP81890198A EP81890198A EP0055245A2 EP 0055245 A2 EP0055245 A2 EP 0055245A2 EP 81890198 A EP81890198 A EP 81890198A EP 81890198 A EP81890198 A EP 81890198A EP 0055245 A2 EP0055245 A2 EP 0055245A2
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EP
European Patent Office
Prior art keywords
pump
crank
control rod
stop
rotational position
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
EP81890198A
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German (de)
French (fr)
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EP0055245B1 (en
EP0055245A3 (en
Inventor
Anton Dipl. Ing. Dr. Techn. Pischinger
Heinz Rathmayr
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Friedmann and Maier AG
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Friedmann and Maier AG
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Publication date
Application filed by Friedmann and Maier AG filed Critical Friedmann and Maier AG
Publication of EP0055245A2 publication Critical patent/EP0055245A2/en
Publication of EP0055245A3 publication Critical patent/EP0055245A3/en
Application granted granted Critical
Publication of EP0055245B1 publication Critical patent/EP0055245B1/en
Expired legal-status Critical Current

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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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F02M59/28—Mechanisms therefor

Definitions

  • the invention relates to a method for adjusting and equating a plurality of injection devices for injection internal combustion engines, each of which is designed as a pump-nozzle assembly associated with a motor cylinder, and in which the change in the amount of fuel injected during operation by rotating the with an oblique control edge provided pump piston is effected via a crank arranged on the piston foot and a common control rod, and on an injection device of the type mentioned at the outset for carrying out this method.
  • Pump-nozzle assemblies formed from the injection pump and nozzle have a variable delivery capacity depending on the position of the inclined control edge. With a certain rotational position of the pump piston, the maximum delivery length of the pump-nozzle assembly or the maximum delivery rate permitted for a particular injection engine is reached.
  • the invention now aims to provide a particularly simple method for adjusting and equalizing the delivery rates of the individual pump-nozzle assemblies, with which the desired equality can be achieved without further ado using complex measuring instruments and special tools.
  • the method according to the invention essentially consists in that the control rod common to the pump-nozzle units is fixed in a preselected displacement position, that the cranks of the individual pump-nozzle assemblies are set in a relative to a predetermined individual delivery rate of each individual pump -The nozzle assembly is brought to the selected rotational position and held in this, and that the coupling elements connecting the crank to the control rod are non-positively connected to the control rod after setting the said rotational position of the cranks, whereupon the displacement movement of the control rod is released again.
  • the setting of the control rod common to the pump-nozzle units in a preselected displacement position can be made in a simple manner by means of a plug-in bolt with which the control rod is held in a certain length relative to the engine block.
  • the individual pump-nozzle assemblies can be measured on a test bench before installation and the rotational position of the crank corresponding to a predetermined individual delivery quantity can be specified in a simple manner, for example as a limit stop, during the measurement on the test bench.
  • Chen injection quantity corresponds and in this rotational position via coupling elements with the control rod non-positively.
  • the coupling element can be slidably guided, for example, via an elongated hole in the common control rod relative to the longitudinal direction of the control rod, and is non-positively connected to the control rod in the preselected rotational position of the cranks, for example by bolts and nuts. If the determination of the displacement movement of the control rod is subsequently canceled, a displacement of the control rod leads to an adjustment of the delivery rate that is the same for all pump-nozzle units, since the starting point for this adjustment, that is, the angle of rotation of the crank, also contributes which determined the coupling elements on the control rod, was chosen the same in relation to the flow rate of the individual pump-nozzle units.
  • the rotational position of the cranks can be set at a preselected angle to an end position, in particular the maximum delivery rate of the pump-nozzle assemblies, this rotational position either by an individual stop of the individual pump-nozzle units, or with the aid a simple teaching can be set at a predetermined angular distance from such an end position.
  • An injection device suitable for carrying out the method according to the invention for injection internal combustion engines in which the injection pump and injection nozzle are assembled to form a pump-nozzle assembly, each associated with a motor cylinder, and in which the change in the amount of fuel injected during operation is caused by rotation of the pump piston provided with an oblique control edge a crank arranged on the piston foot is effected in a particularly simple manner Characterized in that within the turning path of the crank there is provided a stop for the crank which is adjustable in its rotational position relative to the pump piston liner or to the housing of the pump-nozzle assembly and is fixed in rotation during operation.
  • Such a stop can initially be arranged in an adjustable manner in its rotational position for the measurement of the delivery quantity parameters of the individual pump-nozzle assemblies and can already be rigidly fixed on the test bench after a predetermined delivery quantity has been determined.
  • a certain delivery rate of the pump-nozzle assemblies is directly predetermined by the stop and the above-described setting and equalization of a plurality of such injection devices can be carried out in a particularly simple manner.
  • the training can be made so that the stop is connected to a non-rotatably guided slide or guide piece for the pump piston, the guide piece preferably being designed as a spring plate.
  • a stop which is particularly easy to adjust and which is rigid in the operating position is formed by an adjusting screw crossing the axis of the pump piston.
  • the design can also be such that the stop is rigidly connected to the upper spring plate of the pump piston spring, in particular is formed integrally therewith, and that the spring plate is rotationally fixed to the guide piece in a selected rotational position, in particular by plastic deformation is connected for the pump piston.
  • the slide preferably has a groove, so that a rotation lock is achieved by embossing on the circumference of the spring plate which carries the stop.
  • the An Impact can, however, be formed by a clamping ring fixed to the housing or a guide sleeve, the clamping ring preferably being designed as a guide and rotation lock for the spring plate carrying the stop or the guide piece carrying the stop.
  • FIG. 1 shows a cross section through the crank-side end of a pump-nozzle assembly according to the invention
  • FIG. 2 shows a plan view in the direction of arrow II of FIG. 1
  • FIG. 3 shows a modified embodiment analogous to the illustration according to FIG. 1
  • FIG 4 shows a plan view in the direction of arrow IV in FIG. 3
  • FIG. 5 shows a further embodiment in a section analogous to FIG. 1
  • FIG. 6 shows a section along the line in the direction of arrow VI-VI in FIG. 5
  • FIG 7 a modified design in section analogous to FIG.
  • FIG. 8 a plan view in the direction of arrow VIII in FIG. 7,
  • FIG. 9 a modified design in section analogous to FIG.
  • FIG. 10 a plan view in the direction of FIG Arrow X of FIG. 9
  • FIG. 11 is an illustration of the setting process of the pump-nozzle assembly according to FIG. 1 with the aid of an adjusting gauge
  • FIG. 12 is a plan view in the direction of arrow XII of FIG. 11.
  • the pump element piston is designated 1 and rotatably arranged by means of a crank 2.
  • the crank 2 is brought into a position in the test bench run, for example, in which the pump element piston 1 delivers the fuel delivery quantity that is required for the full-load operation of the internal combustion engine.
  • a spring plate 4 is first rotatably arranged, which consists of a plate 5 and a sheet metal ring 6.
  • the sheet metal ring 6 carries a stop 8 for the crank 2.
  • the spring plate 4 is now rotated until the stop 8 bears against the crank 2.
  • the sheet metal ring 6 is stamped with the guide piece 3 in this rotational position in the region of a groove 9 provided on the guide piece 3.
  • the pump-nozzle assembly is provided with a rigid stop 8, which now corresponds to the largest fuel delivery quantity required for full-load operation of the internal combustion engine.
  • the stop can also easily be provided in a rotational position which corresponds to a quantity which exceeds the largest delivery quantity during operation. If the subsequent equalization of the individual injection devices is to take place at a partial delivery rate of the amount required for teaching operation or the zero delivery rate, the crank can be brought into a certain angle of rotation 8 by means of a teaching.
  • crank 2 After installing the pump-nozzle assembly in the internal combustion engine, the crank 2 is now held in a rotational position at the stop 8 as shown in FIGS. 1 and 2.
  • the control rod or the delivery rate adjustment member 10 is fixed in its displacement position by a bolt 11.
  • a coupling element 12 is brought into engagement with the crank 2 and can be displaced in the longitudinal direction thereof in a slot 15 of the control rod 10 by means of a screw bolt 13 and a not yet tightened nut 14.
  • the coupling element is non-positively connected by tightening the nut 14 to the control rod 10 when the predetermined rotational position of the crank in the illustration according to FIG. 2 is the position in which the crank rests against the stop 8.
  • the slider can be displaced by the pin 16 in the axial direction of the pump element piston 1 and, in the event of change relative to the axis 17, is guided in an elongated hole 18 thereof.
  • the pump piston spring is designated 19.
  • FIGS. 1 and 2 have been retained for the same components.
  • the spring plate 20 is formed separately from the sheet metal ring 21 carrying the stop 8, so that a play S between the guide piece 3 and the sheet metal ring 21 carrying the stop 8 is maintained.
  • the sheet metal ring 21 is easily rotatable relative to the guide piece 22 in the non-embossed state and is secured against rotation in the desired rotational position in an analogous manner to that shown in FIG. 2.
  • a guide piece 22 is provided, which is designed directly as a spring plate for the spring 19.
  • the head of this guide piece carries a stop screw 23, which limits the rotation path of the crank 2. The limitation in turn takes place, for example, in the position of the maximum delivery rate required for the full load range.
  • the stop screw 23 can act together with a bolt 24 as a transport lock for the pressure piece 25.
  • a guide tube 26 which serves to support the lateral forces caused by the pump nozzle drive outside the pump spring 19.
  • An adjusting ring 27 is mounted on the guide tube 26 and, as in the previous embodiments, is rotated until the stop 28 connected to this adjusting ring 27 bears against the crank 2 brought into the desired rotational position. In this rotational position, the adjusting ring 27 is fixed and clamped by tightening the screw 29.
  • the setting or clamping ring 27 serves at the same time as a guide and rotation lock for the guide sleeve 31 carrying the stop 30, which is designed as a spring plate.
  • a pin 32 is welded to the adjusting or clamping ring 27, which engages in a recess 33 in the guide sleeve 31.
  • a transport lock can also be provided in the embodiment according to FIG. 7.
  • cranks 2 can be equated with respect to the control rod 10 in the full-load range, in the idling range or with zero delivery rate, for which purpose as in FIG. 11 and 12, can be used.
  • the pump-nozzle unit shown in FIG. 1 can again be seen in the illustration according to FIG. 11.
  • the crank 2 is now brought into a position on the test bench in which the pump element piston 1 delivers, for example, a fuel delivery quantity that is required for the idle operation of the internal combustion engine.
  • the An Beat 8 is now set at a predetermined distance A from this position as crank 2, for which a gauge 34 is used. It must be ensured that, depending on the position of the stop 8 or 8 a, the crank can reach both the position for the full load and the zero delivery rate.
  • the crank 2 is now held with the aid of the teaching 34 at a distance from the stop 8 in FIG. 12 and is coupled in this position to the control rod 10 via the coupling element 12. This process is repeated for the individual pump-nozzle assemblies which are to be operated with the same control rod 10. In this way, the pump-nozzle assemblies can be assimilated for any given delivery quantities, which must be the same for the individual pump-nozzle units.

Abstract

1. Injection device for internal-combustion engines having fuel injection, comprising unit injectors adjoined to each engine cylinder, in which the variation of the injected amount of fuel in operation in effected by rotation of the plunger (1) having an inclined control edge via a crank (2) mainted at the foot of the plunger by means of a common reciprocable control rod (10) having coupling elements (12) frictionally connected thereto and coacting with said cranks (2), whereat for adjusting and coordinating the unit injectors the control rod (10) is lockable in a preselected sliding position, while the cranks (2) of the separate unit injectors, with the coupling elements (12) being disconnected from the control rod (10) for free shifting, are set in a rotational position each which for all unit injectors corresponds to the same predetermined amount of fuel to be injected, whereupon the coupling elements (12) are frictionally connected to the control rod (10), characterised in that a per se known stop means (8, 28) is provided for the rotational position of each crank (2) corresponding to the predetermined amount of fuel to be injected and that each stop means is a stop means (8, 28) for the crank whose rotational position is adjustable within the rotational range of the adjoined crank (2) with respect to the pump barrel or the body of the unit injector, resp., for adjusting and coordinating the predetermined amount of fuel to be injected and in operation is non-rotatably locked.

Description

Die Erfindung bezieht sich auf ein Verfahren zur Einstellung und Gleichstellung einer Mehrzahl von Einspritzeinrichtungen für Einspritzbrennkraftmaschinen, welche jeweils als einem Motorzylinder zugeordnete Pumpe-Düse-Baueinheit ausgebildet sind, und bei welchen die Veränderung der eingespritzten Kraftstoffmenge während des Betriebes durch Verdrehung des mit einer schrägen Steuerkante versehenen Pumpenkolbens über eine am Kolbenfuß angeordnete Kurbel und eine gemeinsame Regelstange bewirkt wird, sowie auf eine Einspritzeinrichtung der eingangs genannten Art zur Durchführung dieses Verfahrens. Aus Einspritzpumpe und Düse gebildete Pumpe-Düse-Baueinheiten weisen eine in Abhängigkeit von der Stellung der schrägen Steuerkante veränderliche Förderleistung auf. Bei einer bestimmten Drehstellung des Pumpenkolbens wird hiebei die maximale Förderlänge der Pumpe-Düse-Baueinheit oder aber die maximale für eine bestimmte Einspritzbrennkraftmaschine zulässige Fördermenge, erreicht. Bei mehrzylindrigen Einspritzbrennkraftmaschinen wird nun eine Mehrzahl derartiger Einspritzeinrichtungen angeordnet, welche gemeinsam von einem Regler über eine gemeinsame Regelstange verstellt werden sollen. Ein für die einwandfreie Funktion derartiger Einspritzbrennkraftmaschinen wesentliches Problem liegt darin, daß die gemeinsame Verstellung mehrerer Pumpe-Düse-Baueinheiten jeweils zur gleichen Veränderung der Einspritzmenge der einzelnen Pumpe-Düse-Einheiten führen soll.The invention relates to a method for adjusting and equating a plurality of injection devices for injection internal combustion engines, each of which is designed as a pump-nozzle assembly associated with a motor cylinder, and in which the change in the amount of fuel injected during operation by rotating the with an oblique control edge provided pump piston is effected via a crank arranged on the piston foot and a common control rod, and on an injection device of the type mentioned at the outset for carrying out this method. Pump-nozzle assemblies formed from the injection pump and nozzle have a variable delivery capacity depending on the position of the inclined control edge. With a certain rotational position of the pump piston, the maximum delivery length of the pump-nozzle assembly or the maximum delivery rate permitted for a particular injection engine is reached. In the case of multi-cylinder injection internal combustion engines, a plurality of such injection devices are now arranged, which are to be adjusted jointly by a controller via a common control rod. A problem that is essential for the proper functioning of such injection internal combustion engines is that the joint adjustment of several pump-nozzle construction units should lead to the same change in the injection quantity of the individual pump-nozzle units.

Die Erfindung zielt nun darauf ab, ein besonders einfaches Verfahren zur Einstellung und Gleichstellung der Fördermengen der einzelnen Pumpe-Düse-Baueinheiten zu schaffen, mit welchem ohne Zuhilfenahme aufwendiger Meßinstrumente und Spezialwerkzeuge die gewünschte Gleichstellung ohne weiteres erzielt werden kann. Zur Lösung dieser Aufgabe besteht das erfindungsgemäße Verfahren im wesentlichen darin, daß die den Pumpe-Düse-Einheiten gemeinsame Regelstange in einer vorgewählten Verschiebelage festgelegt wird, daß die Kurbeln der einzelnen Pumpe-Düse-Baueinheiten in eine relativ zu einer vorgegebenen individuellen Fördermenge jeder einzelnen Pumpe-Düse-Baueinheit gewählte Drehlage gebracht und in dieser gehalten werden, und daß die die Kurbel mit der Regelstange verbindenden Kuppelglieder nach Einstellen der genannten Drehlage der Kurbeln mit der Regelstange kraftschlüssig verbunden werden, worauf die Verschiebebewegung der Regelstange wiederum freigegeben wird. Die Festlegung, der den Pumpe-Düse-Einheiten gemeinsamen Regelstange in einer vorgewählten Verschiebelage kann hiebei in einfacher Weise durch einen Steckbolzen vorgenommen werden, mit welchem die Regelstange relativ zum Motorblock in einer bestimmten Länge festgehalten wird. Die einzelnen Pumpe-Düse-Baueinheiten können vor dem Einbau auf einem Prüfstand ausgemessen werden und die einer vorgegebenen individuellen Fördermenge entsprechende Drehlage der Kurbel kann in einfacher Weise, beispielsweise als Begrenzungsanschlag, bei der Messung auf dem Prüfstand vorgegeben werden. Für die Einstellung und Gleichstellung der einzelnen Pumpen ist es nun lediglich erforderlich, die einzelnen Pumpe-Düse-Baueinheiten in eine Drehlage zu verstellen und in dieser festzuhalten, welche bei allen Pumpe-Düse-Einheiten der gleichen Einspritzmenge entspricht und in dieser Drehlage über Kuppelglieder mit der Regelstange kraftschlüssig zu verbinden. Das Kuppelglied kann hiebei beispielsweise über ein Langloch der gemeinsamen Regelstange relativ zur Längsrichtung der Regelstange verschieblich geführt sein, und wird in der vorgewählten Drehlage der Kurbeln beispielsweise durch Schraubenbolzen und Muttern mit der Regelstange kraftschlüssig verbunden. Wenn in der Folge die Festlegung der Verschiebebewegung der Regelstange wieder aufgehoben wird, führt eine Verschiebung der Regelstange zu einer für alle Pumpe-Düse-Einheiten gleichen Verstellung der Fördermenge, da auch der Ausgangspunkt für diese Verstellung, das heißt, derjenige Drehwinkel der Kurbel, bei welcher die Festlegung der Kuppelglieder an der Regelstange erfolgte, in bezug auf die Fördermenge der einzelnen Pumpe-Düse-Einheiten gleich gewählt wurde.The invention now aims to provide a particularly simple method for adjusting and equalizing the delivery rates of the individual pump-nozzle assemblies, with which the desired equality can be achieved without further ado using complex measuring instruments and special tools. To achieve this object, the method according to the invention essentially consists in that the control rod common to the pump-nozzle units is fixed in a preselected displacement position, that the cranks of the individual pump-nozzle assemblies are set in a relative to a predetermined individual delivery rate of each individual pump -The nozzle assembly is brought to the selected rotational position and held in this, and that the coupling elements connecting the crank to the control rod are non-positively connected to the control rod after setting the said rotational position of the cranks, whereupon the displacement movement of the control rod is released again. The setting of the control rod common to the pump-nozzle units in a preselected displacement position can be made in a simple manner by means of a plug-in bolt with which the control rod is held in a certain length relative to the engine block. The individual pump-nozzle assemblies can be measured on a test bench before installation and the rotational position of the crank corresponding to a predetermined individual delivery quantity can be specified in a simple manner, for example as a limit stop, during the measurement on the test bench. For the adjustment and equality of the individual pumps, it is now only necessary to adjust the individual pump-nozzle assemblies in a rotational position and to hold them in this position, which is the same for all pump-nozzle units Chen injection quantity corresponds and in this rotational position via coupling elements with the control rod non-positively. The coupling element can be slidably guided, for example, via an elongated hole in the common control rod relative to the longitudinal direction of the control rod, and is non-positively connected to the control rod in the preselected rotational position of the cranks, for example by bolts and nuts. If the determination of the displacement movement of the control rod is subsequently canceled, a displacement of the control rod leads to an adjustment of the delivery rate that is the same for all pump-nozzle units, since the starting point for this adjustment, that is, the angle of rotation of the crank, also contributes which determined the coupling elements on the control rod, was chosen the same in relation to the flow rate of the individual pump-nozzle units.

In bevorzugter Weise kann die Drehlage der Kurbeln in vorgewähltem Winkel zu einer Endlage, insbesondere der maximalen Fördermenge der Pumpe-Düse-Baueinheiten, eingestellt werden, wobei diese Drehlage entweder durch einen individuellen Anschlag der einzelnen Pumpe-Düse-Einheiten,-oder aber unter Zuhilfenahme einer einfachen Lehre in vorbestimmtem Winkelabstand von einer derartigen Endlage eingestellt werden kann.In a preferred manner, the rotational position of the cranks can be set at a preselected angle to an end position, in particular the maximum delivery rate of the pump-nozzle assemblies, this rotational position either by an individual stop of the individual pump-nozzle units, or with the aid a simple teaching can be set at a predetermined angular distance from such an end position.

Eine zur Durchführung des erfindungsgemäßen Verfahrens geeignete Einspritzeinrichtung für Einspritzbrennkraftmaschinen, bei welcher Einspritzpumpe und Einspritzdüse zu einer jeweils einem Motorzylinder zugeordneten Pumpe-Düse-Baueinheit zusammengebaut sind und bei welcher die Veränderung der eingespritzten Kraftstoffmenge während des Betriebes durch Verdrehung des mit einer schrägen Steuerkante versehenen Pumpenkolbens über eine am Kolbenfuß angeordnete Kurbel bewirkt wird, ist in besonders einfacher Weise dadurch gekennzeichnet, daß innerhalb des Verdrehweges der Kurbel ein relativ zur Pumpenkolbenbüchse bzw. zum Gehäuse der Pumpe-Düse-Baueinheit in seiner Drehlage einstellbarer und im Betrieb drehfest festgelegter Anschlag für die Kurbel vorgesehen ist. Ein derartiger Anschlag kann für die Messung der Fördermengenkenngrößen der einzelnen Pumpe-Düse-Baueinheiten zunächst in seiner Drehlage einstellbar angeordnet sein und bereits am Prüfstand nach Ermittlung einer vorbestimmten Fördermenge starr festgelegt werden. Beim nachfolgenden Einbau derartiger, einen starren Anschlag für die Kurbel aufweisender Einspritzeinrichtungen ist eine bestimmte Fördermenge der Pumpe-Düse-Baueinheiten durch den Anschlag unmittelbar vorgegeben und es kann die oben beschriebene Einstellung und Gleichstellung einer Mehrzahl solcher Einspritzeinrichtungen in besonders einfacher Weise vorgenommen werden. Die Ausbildung kann hiebei so getroffen sein, daß der Anschlag mit einem drehfest geführten Gleit- bzw. Führungsstück für den Pumpenkolben verbunden ist, wobei vorzugsweise das Führungsstück als Federteller ausgebildet ist. Ein besonders einfach verstellbarer und in der Betriebslage starrer Anschlag ist von einer die Achse des Pumpenkolbens kreuzenden Stellschraube gebildet. Zur Erzielung eines starren Anschlages kann aber auch die Ausbildung so getroffen sein, daß der Anschlag mit dem oberen Federteller der Pumpenkolbenfeder starr verbunden, insbesondere einstückig mit diesem ausgebildet ist, und daß der Federteller in einer gewählten Drehlage, insbesondere durch plastische Verformung drehfest mit dem Führungsstück für den Pumpenkolben verbunden ist. Um eine derartige drehfeste Verriegelung des den Anschlag tragenden Bauteiles mit dem Gleitstück sicherzustellen, weist das Gleitstück vorzugsweise eine Nut auf, sodaß durch Prägung am Umfang des Federtellers, welcher den Anschlag trägt, eine Drehsicherung erzielt wird. Der Anschlag kann aber von einem am Gehäuse oder einer Führungshülse festgelegten Klemmring gebildet sein, wobei vorzugsweise der Klemmring als Führungs- und Drehsicherung für den den Anschlag tragenden Federteller bzw. das den Anschlag tragende Führungsstück ausgebildet ist.An injection device suitable for carrying out the method according to the invention for injection internal combustion engines, in which the injection pump and injection nozzle are assembled to form a pump-nozzle assembly, each associated with a motor cylinder, and in which the change in the amount of fuel injected during operation is caused by rotation of the pump piston provided with an oblique control edge a crank arranged on the piston foot is effected in a particularly simple manner Characterized in that within the turning path of the crank there is provided a stop for the crank which is adjustable in its rotational position relative to the pump piston liner or to the housing of the pump-nozzle assembly and is fixed in rotation during operation. Such a stop can initially be arranged in an adjustable manner in its rotational position for the measurement of the delivery quantity parameters of the individual pump-nozzle assemblies and can already be rigidly fixed on the test bench after a predetermined delivery quantity has been determined. In the subsequent installation of such a rigid stop for the crank-type injection devices, a certain delivery rate of the pump-nozzle assemblies is directly predetermined by the stop and the above-described setting and equalization of a plurality of such injection devices can be carried out in a particularly simple manner. The training can be made so that the stop is connected to a non-rotatably guided slide or guide piece for the pump piston, the guide piece preferably being designed as a spring plate. A stop which is particularly easy to adjust and which is rigid in the operating position is formed by an adjusting screw crossing the axis of the pump piston. To achieve a rigid stop, however, the design can also be such that the stop is rigidly connected to the upper spring plate of the pump piston spring, in particular is formed integrally therewith, and that the spring plate is rotationally fixed to the guide piece in a selected rotational position, in particular by plastic deformation is connected for the pump piston. In order to ensure such a rotationally fixed locking of the component carrying the stop with the slide, the slide preferably has a groove, so that a rotation lock is achieved by embossing on the circumference of the spring plate which carries the stop. The An Impact can, however, be formed by a clamping ring fixed to the housing or a guide sleeve, the clamping ring preferably being designed as a guide and rotation lock for the spring plate carrying the stop or the guide piece carrying the stop.

Die Erfindung wird nachfolgend an Hand von Ausführungsbeispielen der erfindungsgemäßen Einspritzeinrichtung näher erläutert. In diesen zeigen Fig. 1 einen Querschnitt durch das kurbelseitige Ende einer erfindungsgemäßen Pumpe-Düse-Baueinheit, Fig. 2 eine Draufsicht im Sinne des Pfeiles II der Fig. 1, Fig. 3 eine abgewandelte Ausführungsform analog der Darstellung nach Fig. 1, Fig. 4 eine Draufsicht in Richtung des Pfeiles IV der Fig. 3, Fig. 5 eine weitere Ausgestaltung in einem Schnitt analog der Fig. 1, Fig. 6 einen Schnitt längs der Linie in Richtung des Pfeiles VI-VI der Fig. 5, Fig. 7 eine abgewandelte Ausbildung im Schnitt analog der Fig. 1, Fig. 8 eine Draufsicht in Richtung des Pfeiles VIII der Fig. 7, Fig. 9 eine abgewandelte Ausbildung im Schnitt analog der Fig. 1, Fig. 10 eine Draufsicht in Richtung des Pfeiles X der Fig. 9, Fig. 11 eine Illustration des Einstellvorganges der Pumpe-Düse-Baueinheit nach Fig. 1 unter Zuhilfenahme einer Einstellehre, und Fig. 12 eine Draufsicht in Richtung des Pfeiles XII der Fig. 11.The invention is explained in more detail below on the basis of exemplary embodiments of the injection device according to the invention. 1 shows a cross section through the crank-side end of a pump-nozzle assembly according to the invention, FIG. 2 shows a plan view in the direction of arrow II of FIG. 1, FIG. 3 shows a modified embodiment analogous to the illustration according to FIG. 1, FIG 4 shows a plan view in the direction of arrow IV in FIG. 3, FIG. 5 shows a further embodiment in a section analogous to FIG. 1, FIG. 6 shows a section along the line in the direction of arrow VI-VI in FIG. 5, FIG 7 a modified design in section analogous to FIG. 1, FIG. 8 a plan view in the direction of arrow VIII in FIG. 7, FIG. 9 a modified design in section analogous to FIG. 1, FIG. 10 a plan view in the direction of FIG Arrow X of FIG. 9, FIG. 11 is an illustration of the setting process of the pump-nozzle assembly according to FIG. 1 with the aid of an adjusting gauge, and FIG. 12 is a plan view in the direction of arrow XII of FIG. 11.

In Fig. 1 ist der Pumpenelementkolben mit 1 bezeichnet und unter Vermittlung einer Kurbel 2 drehbar angeordnet. Die.Kurbel 2 wird beim Prüfstandslauf beispielsweise in eine Stellung gebracht, bei welcher der Pumpenelementkolben 1 diejenige Kraftstoffördermenge liefert, die für den Vollastbetrieb der Brennkraftmaschine erforderlich ist. Relativ zu einem Führungsstück 3 für den Pumpenelementkolben 1 ist ein Federteller 4 zunächst drehbar angeordnet, welcher aus einer Platte 5 und einem Blechring 6 besteht.In Fig. 1, the pump element piston is designated 1 and rotatably arranged by means of a crank 2. The crank 2 is brought into a position in the test bench run, for example, in which the pump element piston 1 delivers the fuel delivery quantity that is required for the full-load operation of the internal combustion engine. Relative to a guide piece 3 for the pump element piston 1, a spring plate 4 is first rotatably arranged, which consists of a plate 5 and a sheet metal ring 6.

Die Platte 5 und der Blechring 6 sind über Schweißpunkte 7 miteinander verbunden. Wie aus Fig. 2 ersichtlich ist, trägt der Blechring 6 einen Anschlag 8 für die Kurbel 2. Bei einer vorgewählten Drehlage der Kurbel 2 wird nun der Federteller 4 so weit verdreht, bis der Anschlag 8 an der Kurbel 2 anliegt. Wie aus Fig. 2 ersichtlich, wird der Blechring 6 mit dem Führungsstück 3 in dieser Drehlage im Bereich einer am Führungsstück 3 angebrachten Nut 9 verprägt. Auf diese Weise ist die Pumpe-Düse-Baueinheit mit einem starren Anschlag 8 versehen, welcher nun der größten, für den Vollastbetrieb der Brennkraftmaschine erforderlichen Kraftstoffördermenge entspricht. Der Anschlag kann ohne weiteres auch in einer Drehlage vorgesehen sein, welche einer, die größte Fördermenge im Betrieb übersteigenden Menge entspricht. Wenn die nachfolgende Gleichstellung der einzelnen Einspritzeinrichtungen bei einer Teilfördermenge der für den Lehrlaufbetrieb erforderlichen Menge oder der Nullfördermenge erfolgen soll, kann die Kurbel unter Vermittlung einer Lehre in einen bestimmten Drehwinkel zum Anschlag 8 gebracht werden.The plate 5 and the sheet metal ring 6 are connected to one another via welding spots 7. As can be seen from FIG. 2, the sheet metal ring 6 carries a stop 8 for the crank 2. With a preselected rotational position of the crank 2, the spring plate 4 is now rotated until the stop 8 bears against the crank 2. As can be seen from FIG. 2, the sheet metal ring 6 is stamped with the guide piece 3 in this rotational position in the region of a groove 9 provided on the guide piece 3. In this way, the pump-nozzle assembly is provided with a rigid stop 8, which now corresponds to the largest fuel delivery quantity required for full-load operation of the internal combustion engine. The stop can also easily be provided in a rotational position which corresponds to a quantity which exceeds the largest delivery quantity during operation. If the subsequent equalization of the individual injection devices is to take place at a partial delivery rate of the amount required for teaching operation or the zero delivery rate, the crank can be brought into a certain angle of rotation 8 by means of a teaching.

Nach Einbau der Pumpe-Düse-Baueinheit in die Brennkraftmaschine wird nun wie in Fig. 1 und 2 dargestellt, die Kurbel 2 in einer Drehstellung am Anschlag 8 gehalten. Die Regelstange bzw. das Fördermengenverstellglied 10 wird über einen Bolzen 11 in ihrer Verschiebelage festgelegt. Ein Kuppelglied 12 wird in Eingriff mit der Kurbel 2 gebracht und ist über einen Schraubenbolzen 13, sowie eine noch nicht festgezogene Mutter 14 in einem Langloch 15 der Regelstange 10 in Längsrichtung derselben verschieblich. Das Kuppelglied wird durch Festziehen der Mutter 14 mit der Regelstange 10 kraftschlüssig verbunden, wenn die vorbestimmte Drehlage der Kurbel bei der Darstellung nach Fig. 2 diejenige Lage, bei welcher die Kurbel am Anschlag 8 anliegt, erreicht ist. In analoger Weise wird für weitere Pumpe-Düse-Baueinheiten entsprechend Fig. 1 vorgegangen, sodaß eine Gleichstellung der Mengenförderung aller Pumpe-Düse-Baueinheiten erfolgt. Nach Entfernung des Bolzens 11 werden alle Pumpe-Düse-Baueinheiten in gleicher Weise durch die Regelstange 10 verstellt, wobei die Kraftstoffördermengen der einzelnen Pumpe-Düse-Einheiten bezogen auf die Regelstange 10 gleichgestellt sind. Wie aus Fig. 1 ersichtlich, ist das Gleitstück durch den Zapfen 16 in Achsrichtung des Pumpenelementkolbens 1 verschiebbar und gegen Veränderung relativ zur Achse 17 in einem Langloch 18 desselben geführt. Die Pumpenkolbenfeder ist mit 19 bezeichnet.After installing the pump-nozzle assembly in the internal combustion engine, the crank 2 is now held in a rotational position at the stop 8 as shown in FIGS. 1 and 2. The control rod or the delivery rate adjustment member 10 is fixed in its displacement position by a bolt 11. A coupling element 12 is brought into engagement with the crank 2 and can be displaced in the longitudinal direction thereof in a slot 15 of the control rod 10 by means of a screw bolt 13 and a not yet tightened nut 14. The coupling element is non-positively connected by tightening the nut 14 to the control rod 10 when the predetermined rotational position of the crank in the illustration according to FIG. 2 is the position in which the crank rests against the stop 8. In an analogous manner, for white tere pump-nozzle assemblies according to FIG. 1, so that the quantity delivery of all pump-nozzle assemblies is equal. After the bolt 11 has been removed, all the pump-nozzle assemblies are adjusted in the same way by the control rod 10, the fuel delivery quantities of the individual pump-nozzle units being equal in relation to the control rod 10. As can be seen from FIG. 1, the slider can be displaced by the pin 16 in the axial direction of the pump element piston 1 and, in the event of change relative to the axis 17, is guided in an elongated hole 18 thereof. The pump piston spring is designated 19.

Bei der Ausbildung nach Fig. 3 und 4 sind für die gleichen Bauteile die Bezugszeichen der Fig. 1 und 2 beibehalten worden. Zum Unterschied von der Ausbildung nach Fig. 1 ist jedoch hier der Federteller 20 gesondert von dem den Anschlag 8 tragenden Blechring 21 ausgebildet, sodaß ein Spiel S zwischen dem Führungsstück 3 und dem den Anschlag 8 tragenden Blechring 21 aufrecht erhalten wird. Der Blechring 21 ist in unverprägtem Zustand leicht relativ zum Führungsstück 22 drehbar und wird in der gewünschten Drehlage in analoger Weise wie in Fig. 2 dargestellt, durch Verprägen gegen Drehung gesichert.3 and 4, the reference numerals of FIGS. 1 and 2 have been retained for the same components. In contrast to the design according to FIG. 1, however, the spring plate 20 is formed separately from the sheet metal ring 21 carrying the stop 8, so that a play S between the guide piece 3 and the sheet metal ring 21 carrying the stop 8 is maintained. The sheet metal ring 21 is easily rotatable relative to the guide piece 22 in the non-embossed state and is secured against rotation in the desired rotational position in an analogous manner to that shown in FIG. 2.

Bei der Ausbildung nach Fig. 5 und 6 ist ein Führungsstück 22 vorgesehen, welches unmittelbar als Federteller für die Feder 19 ausgebildet ist. Der Kopf dieses Führungsstückes trägt, wie in Fig. 6 deutlich dargestellt ist, eine Anschlagschraube 23, welche den Drehweg der Kurbel 2 begrenzt. Die Begrenzung erfolgt wiederum beispielsweise in der Stellung der für den Vollastbereich maximal erforderlichen Fördermenge. Die Anschlagschraube 23 kann hiebei zusammen mit einem Bolzen 24 als Transportsicherung für das Druckstück 25 wirken.5 and 6, a guide piece 22 is provided, which is designed directly as a spring plate for the spring 19. As is clearly shown in FIG. 6, the head of this guide piece carries a stop screw 23, which limits the rotation path of the crank 2. The limitation in turn takes place, for example, in the position of the maximum delivery rate required for the full load range. The stop screw 23 can act together with a bolt 24 as a transport lock for the pressure piece 25.

Bei der Fig. 7 ist ein Führungsrohr 26 vorgesehen, welches der Abstützung der durch den Pumpen-Düsen-Antrieb bedingten Seitenkräfte außerhalb der Pumpenfeder 19 dient. Am Führungsrohr 26 ist ein Einstellring 27 gelagert, der wie bei den vorangehenden Ausbildungen, so weit verdreht wird, bis der mit diesem Einstellring 27 verbundene Anschlag 28 an der in die gewünschte Drehstellung gebrachten Kurbel 2 anliegt. In dieser Drehstellung wird der Einstellring 27 durch Festziehen der Schraube 29 festgelegt und geklemmt.7, a guide tube 26 is provided which serves to support the lateral forces caused by the pump nozzle drive outside the pump spring 19. An adjusting ring 27 is mounted on the guide tube 26 and, as in the previous embodiments, is rotated until the stop 28 connected to this adjusting ring 27 bears against the crank 2 brought into the desired rotational position. In this rotational position, the adjusting ring 27 is fixed and clamped by tightening the screw 29.

Bei der Ausbildung nach den Fig. 9 und 10 dient der Einstell- bzw. Klemmring 27 gleichzeitig als Führungs- und Drehsicherung für die den Anschlag 30 tragende Führungshülse 31, welche als Federteller ausgebildet ist. Zu diesem Zweck ist am Einstell- bzw. Klemmring 27 ein Zapfen 32 angeschweißt, welcher in eine Ausnehmung 33 der Führungshülse 31 eingreift. In analoger Weise kann auch bei der Ausbildung nach Fig. 7 eine Transportsicherung vorgesehen sein.In the embodiment according to FIGS. 9 and 10, the setting or clamping ring 27 serves at the same time as a guide and rotation lock for the guide sleeve 31 carrying the stop 30, which is designed as a spring plate. For this purpose, a pin 32 is welded to the adjusting or clamping ring 27, which engages in a recess 33 in the guide sleeve 31. In an analogous manner, a transport lock can also be provided in the embodiment according to FIG. 7.

Bei allen, in den Fig. 1 bis 10 erläuterten Varianten, kann neben der dargestellten Einstellung auf jeweils maximale Fördermenge eine Gleichstellung der Kurbeln 2 in bezug auf die Regelstange 10 im Vollastbereich, im Leerlaufbereich oder bei Nullfördermenge vorgenommen werden, wofür wie in Fig. 11 und 12 dargestellt, vorgegangen werden kann.In all of the variants explained in FIGS. 1 to 10, in addition to the setting shown for the maximum delivery rate in each case, the cranks 2 can be equated with respect to the control rod 10 in the full-load range, in the idling range or with zero delivery rate, for which purpose as in FIG. 11 and 12, can be used.

Bei der Darstellung nach Fig. 11 ist wiederum die in Fig. 1 dargestellte .Pumpe-Düse-Einheit ersichtlich. Die Kurbel 2 wird nun am Prüfstand in eine Stellung gebracht, bei der der Pumpenelementkolben 1 beispielsweise eine Kraftstoffördermenge liefert, die für den Leerlaufbetrieb der Brennkraftmaschine erforderlich ist. Der Anschlag 8 wird nun in vorgegebenem Abstand A von dieser Stellung als Kurbel 2 festgelegt, wofür eine Lehre 34 verwendet wird. Dabei muß gewährleistet sein, daß je nach Lage des Anschlages 8 bzw. 8 a die Kurbel sowohl die Stellung für die Vollast- als auch die Nullfördermenge erreichen kann. Beim Einbau der Pumpe-Düse-Einheit in die Brennkraftmaschine wird nun die Kurbel 2 unter Zuhilfenahme der Lehre 34 im in Fig. 12 mit A bezeichnetem Abstand zum Anschlag 8 gehalten und in dieser Stellung mit der Regelstange 10 über das Kuppelglied 12 gekuppelt. Dieser Vorgang wird für die einzelnen Pumpe-Düse-Baueinheiten, welche mit der gleichen Regelstange 10 betätigt werden sollen, weiderholt. Auf diese Weise kann die Gleichstellung der Pumpe-Düse-Baueinheiten bei beliebigen vorgegebenen Fördermengen, welche jeweils für die einzelnen Pumpe-Düse-Einheiten gleich sein müssen, erfolgen.The pump-nozzle unit shown in FIG. 1 can again be seen in the illustration according to FIG. 11. The crank 2 is now brought into a position on the test bench in which the pump element piston 1 delivers, for example, a fuel delivery quantity that is required for the idle operation of the internal combustion engine. The An Beat 8 is now set at a predetermined distance A from this position as crank 2, for which a gauge 34 is used. It must be ensured that, depending on the position of the stop 8 or 8 a, the crank can reach both the position for the full load and the zero delivery rate. When installing the pump-nozzle unit in the internal combustion engine, the crank 2 is now held with the aid of the teaching 34 at a distance from the stop 8 in FIG. 12 and is coupled in this position to the control rod 10 via the coupling element 12. This process is repeated for the individual pump-nozzle assemblies which are to be operated with the same control rod 10. In this way, the pump-nozzle assemblies can be assimilated for any given delivery quantities, which must be the same for the individual pump-nozzle units.

Claims (9)

1. Verfahren zur Einstellung und Gleichstellung einer Mehrzahl von Einspritzeinrichtungen für Einspritzbrennkraftmaschinen, welche jeweils als einem Motorzylinder zugeordnete Pumpe-Düse-Baueinheit ausgebildet sind, und bei welchem die Veränderung der eingespritzten Kraftstoffmenge während des Betriebes durch Verdrehung des mit einer schrägen Steuerkante versehenen Pumpenkolbens über eine am Kolbenfuß angeordnete Kurbel und eine gemeinsame Regelstange bewirkt wird, dadurch gekennzeichnet, daß die den Pumpe-Düse-Einheiten gemeinsame Regelstange in einer vorgewählten Verschiebelage festgelegt wird, daß die Kurbeln der einzelnen Pumpe-Düse-Baueinheiten in eine relativ zu einer vorgegebenen individuellen Fördermenge jeder einzelnen Pumpe-Düse-Baueinheit gewählte Drehlage gebracht und in dieser gehalten werden, und daß die die Kurbel mit der Regelstange verbindenden Kuppelglieder nach Einstellen der genannten Drehlage der Kurbeln mit der Regelstange kraftschlüssig verbunden werden, worauf die Verschiebebewegung der Regelstange wiederum freigegeben wird.1. A method for adjusting and equating a plurality of injection devices for injection internal combustion engines, each of which is designed as a pump-nozzle assembly assigned to a motor cylinder, and in which the change in the amount of fuel injected during operation by rotating the pump piston provided with an oblique control edge via one arranged on the piston foot crank and a common control rod is effected, characterized in that the common control rod of the pump-nozzle units is fixed in a preselected displacement position, that the cranks of the individual pump-nozzle assemblies in a relative to a predetermined individual flow rate each individual pump-nozzle assembly selected rotational position are brought and held in this, and that the coupling elements connecting the crank to the control rod are non-positively connected to the control rod after setting the said rotational position of the cranks, whereupon di e Sliding movement of the control rod is released again. 2. Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß die Drehlage der Kurbeln in vorgewähltem Winkel zu einer Endlage, insbesondere der maximalen Fördermenge der Pumpe-Düse-Baueinheiten, eingestellt wird.2. The method according to claim 1, characterized in that the rotational position of the cranks is set at a preselected angle to an end position, in particular the maximum delivery rate of the pump-nozzle assemblies. 3. Einspritzeinrichtung für Einspritzbrennkraftmaschinen, bei welcher Einspritzpumpe und Einspritzdüse zu einer jeweils einem Motorzylinder zugeordneten Pumpe-Düse-Baueinheit zusammengebaut sind und bei welcher die Veränderung der eingespritzten Kraftstoffmenge während des Betriebes durch Verdrehung des mit einer schrägen Steuerkante versehenen Pumpenkolbens (1) über eine am Kolbenfuß angeordnete Kurbel (2) bewirkt wird, zur Durchführung des Verfahrens nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, daß innerhalt des Verdrehweges der Kurbel (2) ein relativ zur Pumpenkolbenbüchse bzw. zum Gehäuse der Pumpe-Düse-Baueinheit in seiner Drehlage einstellbarer und im Betrieb drehfest festgelegter Anschlag (8, 28) für die Kurbel vorgesehen ist.3.Injection device for injection internal combustion engines, in which the injection pump and injection nozzle are assembled to form a pump-nozzle assembly, each associated with a motor cylinder, and in which the change in the quantity of fuel injected during operation by rotating the pump piston (1) provided with an oblique control edge via an am Piston base arranged crank (2) is effected to carry out the method according to one of claims 1 or 2, characterized in that within the rotation of the crank (2) a relative to Pump piston sleeve or to the housing of the pump nozzle assembly in its rotational position adjustable and rotatably fixed stop (8, 28) is provided for the crank. 4. Einspritzeinrichtung nach Anspruch 3, dadurch gekennzeichnet, daß der Anschlag (8, 28) mit einem drehfest geführten Gleit- bzw. Führungsstück (3) für den Pumpenkolben (1) verbunden ist.4. Injection device according to claim 3, characterized in that the stop (8, 28) with a rotationally guided slide or guide piece (3) for the pump piston (1) is connected. 5. Einspritzeinrichtung nach Anspruch 4, dadurch gekennzeichnet, daß das Führungsstück (3) als Federteller ausgebildet ist.5. Injection device according to claim 4, characterized in that the guide piece (3) is designed as a spring plate. 6. Einspritzeinrichtung nach einem der Ansprüche 3, 4 oder 5, dadurch gekennzeichnet, daß der Anschlag von einer die Achse des Pumpenkolbens kreuzenden Stellschraube (23) gebildet ist.6. Injection device according to one of claims 3, 4 or 5, characterized in that the stop is formed by an adjusting screw (23) crossing the axis of the pump piston. 7. Einspritzeinrichtung nach einem der Ansprüche 3 bis 6, dadurch gekennzeichnet, daß der Anschlag (8) mit dem oberen Federteller (4) der Pumpenkolbenfeder (19) starr verbunden, insbesondere einstückig mit diesem ausgebildet ist, und daß der Federteller (4) in einer gewählten Drehlage, insbesondere durch plastische Verformung drehfest mit dem Führungsstück (3) für den Pumpenkolben (1) verbunden ist.7. Injection device according to one of claims 3 to 6, characterized in that the stop (8) with the upper spring plate (4) of the pump piston spring (19) rigidly connected, in particular is integrally formed therewith, and that the spring plate (4) in a selected rotational position, in particular by means of plastic deformation, is connected in a rotationally fixed manner to the guide piece (3) for the pump piston (1). 8. Einspritzeinrichtung nach einem der Ansprüche 3 bis 7, dadurch gekennzeichnet, daß der Anschlag (28) von einem am Gehäuse oder einem Führungsrohr (26) festgelegten Klemmring .(27) gebildet ist.8. Injection device according to one of claims 3 to 7, characterized in that the stop (28) is formed by a clamping ring (27) fixed to the housing or a guide tube (26). 9. Einspritzeinrichtung nach Anspruch 8, dadurch gekennzeichnat, daß der Klemmring (27) als Führungs- und Drehsicherung für den Anschlag (30) tragenden Federteller bzw. die den Anschlag tragende Führungshülse (31) ausgebildet ist.9. Injection device according to claim 8, characterized gekennzeichnat that the clamping ring (27) as a guide and rotation for the stop (30) carrying spring plate or the stop carrying guide sleeve (31) is formed.
EP19810890198 1980-12-18 1981-12-10 Device for adjusting and coordinating a plurality of injection devices Expired EP0055245B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT6185/80 1980-12-18
AT618580A AT381148B (en) 1980-12-18 1980-12-18 INJECTION DEVICE FOR INJECTION INTERNAL COMBUSTION ENGINES

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EP0055245A2 true EP0055245A2 (en) 1982-06-30
EP0055245A3 EP0055245A3 (en) 1983-10-05
EP0055245B1 EP0055245B1 (en) 1986-03-05

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Cited By (18)

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GB2128268A (en) * 1982-10-11 1984-04-26 Same Spa Delivery-regulation unit for in-line injection pumps
GB2140098A (en) * 1983-05-16 1984-11-21 Yanmar Diesel Engine Co Fuel injection pump quantity control device
FR2546235A1 (en) * 1983-05-16 1984-11-23 Yanmar Diesel Engine Co DEVICE FOR ADJUSTING THE QUANTITY OF INJECTED FUEL, FOR A DIESEL ENGINE WITH VERTICAL CRANKSHAFT
AU569861B2 (en) * 1983-05-16 1988-02-25 Yanmar Diesel Engine Co. Ltd. Diesel engine fuel injection control device
US4603811A (en) * 1983-06-06 1986-08-05 Steyr-Daimler-Puch Ag Injection unit associated with each cylinder of a multicylinder diesel engine
AT386255B (en) * 1983-06-06 1988-07-25 Steyr Daimler Puch Ag INJECTION UNIT ASSIGNED PER CYLINDER OF A MULTI-CYLINDER DIESEL ENGINE
AT390125B (en) * 1984-11-27 1990-03-26 Steyr Daimler Puch Ag DEVICE FOR COUPLING A SLIDING ACTUATOR ROD WITH A CONTROL UNIT, IN PARTICULAR A CONTROL ROD OF AN INJECTION UNIT OF AN INTERNAL COMBUSTION ENGINE
DE3539963A1 (en) * 1984-11-27 1986-06-05 Steyr-Daimler-Puch Ag, Wien DEVICE FOR COUPLING A SLIDING ACTUATOR ROD WITH A CONTROL UNIT, IN PARTICULAR WITH THE CONTROL ROD OF AN INJECTION UNIT OF AN INTERNAL COMBUSTION ENGINE
US4677952A (en) * 1984-11-27 1987-07-07 Steyr- Daimler-Puch Ag Unit for coupling a displaceable operating bar or shaft with a regulating member, in particular with an adjusting rod of a fuel injection aggregate in an internal combustion engine
AT387823B (en) * 1984-12-11 1989-03-28 Steyr Daimler Puch Ag Auxiliary device for an actuating rod of the regulating members provided on pump/nozzle assemblies of fuel- injection internal combustion engines
EP0288669A1 (en) * 1987-04-30 1988-11-02 GebràœDer Sulzer Aktiengesellschaft Fuel injection pump for a diesel engine
CH672005A5 (en) * 1987-04-30 1989-10-13 Sulzer Ag
DE4207702A1 (en) * 1992-03-11 1993-09-16 Kloeckner Humboldt Deutz Ag Method of setting fuel injection system of IC engine - involves controlling piston rotation by levers with pins attached which engage slot in control rod, equal torque is applied to each piston
GB2304829A (en) * 1995-09-02 1997-03-26 Bosch Gmbh Robert Fuel-injection pump for internal combustion engines
GB2304829B (en) * 1995-09-02 1997-11-05 Bosch Gmbh Robert Fuel injection pump for internal combustion engines
EP1298315A1 (en) * 2000-05-26 2003-04-02 Yanmar Co., Ltd. Fuel injection pump
EP1298315A4 (en) * 2000-05-26 2005-01-05 Yanmar Co Ltd Fuel injection pump
US6953022B1 (en) 2000-05-26 2005-10-11 Yanmar Co., Ltd. Fuel injection pump

Also Published As

Publication number Publication date
EP0055245B1 (en) 1986-03-05
ATA618580A (en) 1986-01-15
AT381148B (en) 1986-08-25
DE3174018D1 (en) 1986-04-10
EP0055245A3 (en) 1983-10-05

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