EP0480173B1 - Fuel injection pump for internal combustion engine - Google Patents

Fuel injection pump for internal combustion engine Download PDF

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Publication number
EP0480173B1
EP0480173B1 EP91114895A EP91114895A EP0480173B1 EP 0480173 B1 EP0480173 B1 EP 0480173B1 EP 91114895 A EP91114895 A EP 91114895A EP 91114895 A EP91114895 A EP 91114895A EP 0480173 B1 EP0480173 B1 EP 0480173B1
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EP
European Patent Office
Prior art keywords
fuel injection
pump
injection pump
stationary part
piston
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.)
Expired - Lifetime
Application number
EP91114895A
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German (de)
French (fr)
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EP0480173A1 (en
Inventor
Wolfgang Ing. Fehlmann
Wolfgang Dipl.-Ing. Braun (Fh)
Dieter Dipl.-Ing. Junger (Fh)
Werne Ing. Naumann
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/121—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor with piston arranged axially to driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages

Definitions

  • the invention relates to a fuel injection pump for internal combustion engines according to the preamble of claim 1.
  • Such a fuel injection pump is known from DE-A-39 13 764.
  • This fuel injection pump has a pump piston which is set into a rotary-stroke movement by a cam drive.
  • the cam drive consists of an essentially stationary part, which is designed as a roller ring, and a rotating part driven by a drive shaft, which is designed as a lifting disk.
  • the essentially stationary part can be rotated relative to the rotating part by means of an adjusting device, as a result of which the assignment of the stroke movement of the pump piston to the angle of rotation of the drive shaft can be changed.
  • the pump piston delimits a pump working space, which can be relieved via an electrically controlled valve during the pump stroke of the pump piston to control the injection-effective pump piston stroke.
  • a bolt engages radially in the essentially stationary part of the cam drive, which is, on the other hand, mounted in a slide in a piston.
  • the piston is arranged in a fuel-filled cylinder and can be displaced by the fuel pressure against the force of a spring tangentially to the stationary part, which is rotated here.
  • the start of injection is determined by the point in time at which the valve closes, but the essentially fixed part is nevertheless rotated by means of the adjusting device.
  • a fuel injection pump which has a pump piston driven by a cam drive in a rotary-stroke movement.
  • the cam drive consists of an essentially stationary part in the form of a roller ring and a rotating part driven by a drive shaft in the form of a lifting disk.
  • a bolt engages radially in the essentially stationary part, which on the other hand engages in a slot in a piston.
  • the piston is guided in a fuel-filled cylinder with little tangential play with respect to the essentially stationary part.
  • the piston is displaceable in the cylinder by the fuel pressure against the force of a spring approximately parallel to the longitudinal axis of the fuel injection pump.
  • the slot in the piston extends obliquely to its direction of displacement, so that when the piston is displaced, the essentially stationary part is twisted and the injection begins to change.
  • the aim is to determine the start of spraying depending on different operating parameters of the internal combustion engine operated by the fuel injection pump by means of the electrically controlled valve, for which purpose a rotation of the essentially stationary part is no longer necessary.
  • the fuel injection pump according to the invention with the features of claim 1 has the advantage that the substantially stationary part of the cam drive is blocked using components of known fuel injection pumps with spray adjustment device in a single rotational position, so that only a few changes are required based on known fuel injection pumps. Due to the free axial displaceability of the slider, it can be easily installed and it is possible to compensate for different axial positions of the stationary part due to tolerances. The small play of the slide in the tangential direction with respect to the stationary part prevents the slide from deflecting in the receptacle.
  • FIG. 1 shows a fuel injection pump in longitudinal section with a first exemplary embodiment
  • FIG. 2 shows a detail of the fuel injection pump designated II in FIG. 1 with a second exemplary embodiment.
  • a distributor-type fuel injection pump shown in FIG. 1 has a pump piston 13 operating in a cylinder bore 10 in a bushing 12 inserted into a pump housing 11.
  • the pump piston 13 is set in a reciprocating and at the same time rotating movement by a cam drive 14.
  • the cam drive 14 consists of a lifting disk 17, coupled to a drive shaft 16 of the fuel injection pump, as a rotating part and a roller ring 18 as a stationary part.
  • the lifting disk 17 has a cam track with end cam elevations 19, which rests on rollers 20 held in the roller ring 18.
  • the pump piston 13 on the one hand and an electrically controlled valve 22 inserted into the pump housing 11 on the other hand delimit a pump work chamber 23 in the cylinder bore 10.
  • the interior 24 of the fuel injection pump is filled with fuel by a feed pump 25 integrated in the fuel injection pump and serves as a suction chamber from which the Pump work space is supplied.
  • the roller ring 18 has a cylindrical outer circumference 26, via which it is mounted radially in a bore 27 in the pump housing 11.
  • a bolt 30 engages radially in the roller ring 18 and is secured in the roller ring by a pin 31.
  • the end of the bolt 30 protruding from the roller ring 18 is supported in a radial bore 32 in a sliding block 33 serving as a sliding piece.
  • the sliding block 33 is arranged in an axially displaceable manner in a longitudinal groove 36 which extends approximately parallel to the longitudinal axis 34 of the drive shaft 16 or fuel injection pump and is open to the interior 24, in the inside of the pump housing 11.
  • the sliding block 33 is guided between the bottom 37 of the longitudinal groove 36 and the outer circumference 26 of the roller ring 18 with little play.
  • the sliding block 33 is arranged in the longitudinal groove 36 with as little play as possible in order to block and to prevent a rotational movement of the roller ring to prevent the sliding block from knocking out in the longitudinal groove under impacts acting on the roller ring and supported by the sliding block.
  • the bolt 30 is pivotably arranged with little play and can be displaced along its longitudinal axis 38.
  • roller ring 18 and the bolt 30 can be adopted unchanged from known fuel injection pumps with an adjustable roller ring. An additional sealing point is not necessary when the roller ring is blocked.
  • a connection of the interior 24 to the pump work space 23 is controlled by the valve 22.
  • the valve 22 is opened and fuel flows from the interior 24 through a channel 40 and the valve 22 into the pump working space 23.
  • the valve 22 is closed and over for the duration of the selected high-pressure delivery of the pump piston a distributor opening 41 on the circumference of the pump piston 13, the fuel brought to high pressure is conveyed with corresponding rotation of the pump piston into delivery channels 42 shown in broken lines, which are connected to the injection points of the internal combustion engine via injection lines.
  • the closing time and thus the high-pressure injection quantity and the closing time of the valve 22 which determines the start of the high-pressure injection phase is determined by a control unit (not shown).
  • a rotary encoder 43 which is connected to the control unit, is provided for detecting the rotational speed and the rotational position of the drive shaft 16 of the fuel injection pump.
  • the control unit can take into account further operating parameters such as, for example, load, temperature etc. of the internal combustion engine operated with the fuel injection pump.
  • the roller ring 18 and the bolt 30 are designed as described in the first exemplary embodiment.
  • the sliding block 46 is arranged in a blind bore 47 in the pump housing 11 which extends approximately parallel to the longitudinal axis 34 of the pump.
  • the bolt 30 protrudes through an opening 48 in the pump housing 11 between the interior 24 and the blind bore 47 into the bore 49 in the sliding block 46.
  • the sliding block 46 is axially displaceable in the blind bore 47, but is arranged transversely to its longitudinal axis with as little play as possible.
  • the blind bore 47 has a threaded section 50 to the outside of the pump housing 11, into which a screw plug 51 is screwed, which closes the blind bore 47, a sealing ring 52 being clamped between the pump housing 11 and the screw plug 51.
  • the sliding block 46 can be inserted into the bore 47 from the outside of the pump housing 11.
  • the roller ring 18, the bolt 30 and the sliding block 46 can be taken over essentially unchanged from known fuel injection pumps with an adjustable roller ring.
  • the position of the blind bore 47 for the sliding block 46 is preferably selected so that it can be drilled with little effort in an automated production of the pump housing 11.
  • the locking screw 51 and the sealing ring 52 are standard parts, so that the blocking of the roller ring 18 is achieved with simple means.

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

Description

Die Erfindung betrifft eine Kraftstoffeinspritzpumpe für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1.The invention relates to a fuel injection pump for internal combustion engines according to the preamble of claim 1.

Eine solche Kraftstoffeinspritzpumpe ist durch die DE-A-39 13 764 bekannt. Diese Kraftstoffeinspritzpumpe weist einen Pumpenkolben auf, der von einem Nockenantrieb in eine Dreh-Hub-Bewegung versetzt wird. Der Nockenantrieb besteht aus einem im wesentlichen ortsfesten Teil, der als Rollenring ausgebildet ist, und einem von einer Antriebswelle angetriebenen rotierenden Teil, der als eine Hubscheibe ausgebildet ist. Der im wesentlichen ortsfeste Teil ist mittels einer Verstelleinrichtung gegenüber dem rotierenden Teil verdrehbar, wodurch die Zuordnung der Hubbwegung des Pumpenkolbens zum Drehwinkel der Antriebswelle änderbar ist. Der Pumpenkolben begrenzt einen Pumpenarbeitsraum, der über ein elektrisch gesteuertes Ventil während des Pumphubs des Pumpenkolbens zur Steuerung des einspritzwirksamen Pumpenkolbenhubs entlastbar ist. In den im wesentlichen ortsfesten Teil des Nockenantriebs greift radial ein Bolzen ein, der andererseits in einem Gleitstück in einem Kolben gelagert ist. Der Kolben ist in einem kraftstoffgefüllten Zylinder angeordnet und vom Kraftstoffdruck beaufschlagt gegen die Kraft einer Feder tangential zum ortsfesten Teil verschiebbar, der hierbei verdreht wird. Der Spritzbeginn wird bei dieser Kraftstoffeinspritzpumpe zwar durch den Zeitpunkt des Schließens des Ventils bestimmt, jedoch ist trotzdem eine Verdrehung des im wesentlichen ortsfesten Teils mittels der Verstelleinrichtung vorgesehen.Such a fuel injection pump is known from DE-A-39 13 764. This fuel injection pump has a pump piston which is set into a rotary-stroke movement by a cam drive. The cam drive consists of an essentially stationary part, which is designed as a roller ring, and a rotating part driven by a drive shaft, which is designed as a lifting disk. The essentially stationary part can be rotated relative to the rotating part by means of an adjusting device, as a result of which the assignment of the stroke movement of the pump piston to the angle of rotation of the drive shaft can be changed. The pump piston delimits a pump working space, which can be relieved via an electrically controlled valve during the pump stroke of the pump piston to control the injection-effective pump piston stroke. A bolt engages radially in the essentially stationary part of the cam drive, which is, on the other hand, mounted in a slide in a piston. The piston is arranged in a fuel-filled cylinder and can be displaced by the fuel pressure against the force of a spring tangentially to the stationary part, which is rotated here. In this fuel injection pump, the start of injection is determined by the point in time at which the valve closes, but the essentially fixed part is nevertheless rotated by means of the adjusting device.

Durch die DE-C-963 825 ist weiterhin eine Kraftstoffeinspritzpumpe bekannt, die einen durch einen Nockenantrieb in einer Dreh-Hub-Bewegung angetriebenen Pumpenkolben aufweist. Der Nockenantrieb besteht aus einem im wesentlichen ortsfesten Teil in Form eines Rollenrings und einem von einer Antriebswelle angetriebenen rotierenden Teil in Form einer Hubscheibe. In den im wesentlichen ortsfesten Teil greift radial ein Bolzen ein, der andererseits in einen Schlitz in einem Kolben eingreift. Der Kolben ist in einem kraftstoffgefüllten Zylinder mit geringem tangentialem Spiel bezüglich des im wesentlichen ortsfesten Teils geführt. Der Kolben ist im Zylinder durch den Kraftstoffdruck gegen die Kraft einer Feder etwa parallel zur Längsachse der Kraftstoffeinspritzpumpe verschiebbar. Der Schlitz im Kolben verläuft schräg zu dessen Verschieberichtung, so daß bei einer Verschiebung des Kolbens eine Verdrehung des im wesentlichen ortsfesten Teils und damit eine Änderung des Spritzbeginns erfolgt.From DE-C-963 825 a fuel injection pump is also known which has a pump piston driven by a cam drive in a rotary-stroke movement. The cam drive consists of an essentially stationary part in the form of a roller ring and a rotating part driven by a drive shaft in the form of a lifting disk. A bolt engages radially in the essentially stationary part, which on the other hand engages in a slot in a piston. The piston is guided in a fuel-filled cylinder with little tangential play with respect to the essentially stationary part. The piston is displaceable in the cylinder by the fuel pressure against the force of a spring approximately parallel to the longitudinal axis of the fuel injection pump. The slot in the piston extends obliquely to its direction of displacement, so that when the piston is displaced, the essentially stationary part is twisted and the injection begins to change.

Es wird jedoch angestrebt, den Spritzbeginn in Äbhängigkeit von unterschiedlichen Betriebsparametern der mit der Kraftstoffeinspritzpumpe betriebenen Brennkraftmaschine durch das elektrisch gesteuerte Ventil zu bestimmen, wozu eine Verdrehung des im wesentlichen ortsfesten Teils nicht mehr erforderlich ist.However, the aim is to determine the start of spraying depending on different operating parameters of the internal combustion engine operated by the fuel injection pump by means of the electrically controlled valve, for which purpose a rotation of the essentially stationary part is no longer necessary.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe mit den Merkmalen des Patentanspruchs 1 hat den Vorteil, daß der im wesentlichen ortsfeste Teil des Nockenantriebs unter Verwendung von Bauteilen bekannter Kraftstoffeinspritzpumpen mit Spritzverstelleinrichtung in einer einzigen Drehstellung blockiert ist, so daß ausgehend von bekannten Kraftstoffeinspritzpumpen nur wenige Änderungen erforderlich sind. Durch die freie axiale Verschiebbarkeit des Gleitstücks kann dieses einfach montiert werden und es ist ein Ausgleich von toleranzbedingten unterschiedlichen axialen Stellungen des ortsfesten Teils möglich. Durch das geringe Spiel des Gleitstücks in tangentialer Richtung bezüglich des ortsfesten Teils wird ein Ausschlagen des Gleitstücks in der Aufnahme vermieden.The fuel injection pump according to the invention with the features of claim 1 has the advantage that the substantially stationary part of the cam drive is blocked using components of known fuel injection pumps with spray adjustment device in a single rotational position, so that only a few changes are required based on known fuel injection pumps. Due to the free axial displaceability of the slider, it can be easily installed and it is possible to compensate for different axial positions of the stationary part due to tolerances. The small play of the slide in the tangential direction with respect to the stationary part prevents the slide from deflecting in the receptacle.

In den Unteransprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzpumpe gekennzeichnet. Bei der Ausbildung der Aufnahme nach Anspruch 2 erfordert diese keine zusätzliche Dichtstelle am Pumpengehäuse. Durch die Ausbildung gemäß Anspruch 3 ist ein Verschieben des Gleitstücks zum Ausgleich von Toleranzen ermöglicht, ein Ausschlagen der Aufnahme durch auf das Gleitstuck wirkende Stöße jedoch verhindert. Durch die Ausbildung der Aufnahme nach Anspruch 5 ist eine Montage des Gleitstucks von der Außenseite des Pumpengehäuses ermöglicht.Advantageous refinements and developments of the fuel injection pump according to the invention are characterized in the subclaims. In the formation of the receptacle according to claim 2, this does not require an additional sealing point on the pump housing. The embodiment according to claim 3 enables the sliding piece to be displaced to compensate for tolerances, but prevents the receptacle from knocking out due to impacts acting on the sliding piece. The design of the receptacle according to claim 5 enables the sliding piece to be mounted from the outside of the pump housing.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Kraftstoffeinspritzpumpe im längsschnitt mit einem ersten Ausführungsbeispiel und Figur 2 einen in Figur 1 mit II bezeichneten Ausschnitt der Kraftstoffeinspritzpumpe mit einem zweiten Ausführungsbeispiel.Two embodiments of the invention are shown in the drawing and explained in more detail in the following description. FIG. 1 shows a fuel injection pump in longitudinal section with a first exemplary embodiment, and FIG. 2 shows a detail of the fuel injection pump designated II in FIG. 1 with a second exemplary embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Eine in der Figur 1 dargestellte Kraftstoffeinspritzpumpe der Verteilerbauart weist einen in einer Zylinderbohrung 10 in einer in ein Pumpengehäuse 11 eingesetzten Buchse 12 arbeitenden Pumpenkolben 13 auf. Der Pumpenkolben 13 wird durch einen Nockenantrieb 14 in eine hin- und hergehende und zugleich rotierende Bewegung versetzt. Der Nockenantrieb 14 besteht aus einer mit einer Antriebswelle 16 der Kraftstoffeinspritzpumpe gekoppelten Hubscheibe 17, als rotierendem Teil und einem Rollenring 18 als ortsfestem Teil. Die Hubscheibe 17 weist eine Nockenbahn mit Stirnnockenerhebungen 19 auf, die auf im Rollenring 18 gehaltenen Rollen 20 aufliegt. Der Pumpenkolben 13 einerseits sowie ein in das Pumpengehäuse 11 eingesetztes elektrisch gesteuertes Ventil 22 andererseits begrenzen in der Zylinderbohrung 10 einen Pumpenarbeitsraum 23. Der Innenraum 24 der Kraftstoffeinspritzpumpe wird durch eine in der Kraftstoffeinspritzpumpe integrierte Förderpumpe 25 mit Kraftstoff gefüllt und dient als Saugraum, aus dem der Pumpenarbeitsraum versorgt wird.A distributor-type fuel injection pump shown in FIG. 1 has a pump piston 13 operating in a cylinder bore 10 in a bushing 12 inserted into a pump housing 11. The pump piston 13 is set in a reciprocating and at the same time rotating movement by a cam drive 14. The cam drive 14 consists of a lifting disk 17, coupled to a drive shaft 16 of the fuel injection pump, as a rotating part and a roller ring 18 as a stationary part. The lifting disk 17 has a cam track with end cam elevations 19, which rests on rollers 20 held in the roller ring 18. The pump piston 13 on the one hand and an electrically controlled valve 22 inserted into the pump housing 11 on the other hand delimit a pump work chamber 23 in the cylinder bore 10. The interior 24 of the fuel injection pump is filled with fuel by a feed pump 25 integrated in the fuel injection pump and serves as a suction chamber from which the Pump work space is supplied.

Der Rollenring 18 weist einen zylinderförmigen AuBenumfang 26 auf, über den er in einer Bohrung 27 im Pumpengehäuse 11 radial gelagert ist. In den Rollenring 18 greift radial ein Bolzen 30 ein, der im Rollenring durch einen Stift 31 gesichert ist. Das aus dem Rollenring 18 ragende Ende des Bolzens 30 ist in einer radialen Bohrung 32 in einem als Gleitstuck dienenden Gleitstein 33 gelagert. Der Gleitstein 33 ist in einer sich etwa parallel zur Längsachse 34 der Antriebswelle 16 bzw. Kraftstoffeinspritzpumpe erstreckenden, zum Innenraum 24 offenen Längsnut 36 in der Innenseite des Pumpengehäuses 11 axial verschiebbar angeordnet. Der Gleitstein 33 ist zwischen dem Boden 37 der Längsnut 36 und dem AuBenumfang 26 des Rollenrings 18 mit geringem Spiel geführt. Tangential zum Rollenring 18 ist der Gleitstein 33 in der Längsnut 36 mit möglichst geringem Spiel angeordnet, um eine Drehbewegung des Rollenrings zu blockieren und um ein Ausschlagen des Gleitsteins in der Längsnut unter auf den Rollenring wirkenden und sich über den Gleitstein abstützenden Stößen zu verhindern. In der Bohrung 32 im Gleitstein 33 ist der Bolzen 30 mit kleinem Spiel schwenkbar angeordnet und entlang seiner Längsachse 38 verschiebbar.The roller ring 18 has a cylindrical outer circumference 26, via which it is mounted radially in a bore 27 in the pump housing 11. A bolt 30 engages radially in the roller ring 18 and is secured in the roller ring by a pin 31. The end of the bolt 30 protruding from the roller ring 18 is supported in a radial bore 32 in a sliding block 33 serving as a sliding piece. The sliding block 33 is arranged in an axially displaceable manner in a longitudinal groove 36 which extends approximately parallel to the longitudinal axis 34 of the drive shaft 16 or fuel injection pump and is open to the interior 24, in the inside of the pump housing 11. The sliding block 33 is guided between the bottom 37 of the longitudinal groove 36 and the outer circumference 26 of the roller ring 18 with little play. Tangential to the roller ring 18, the sliding block 33 is arranged in the longitudinal groove 36 with as little play as possible in order to block and to prevent a rotational movement of the roller ring to prevent the sliding block from knocking out in the longitudinal groove under impacts acting on the roller ring and supported by the sliding block. In the bore 32 in the sliding block 33, the bolt 30 is pivotably arranged with little play and can be displaced along its longitudinal axis 38.

Hierdurch ist ein Ausgleich von Abstands- und Winkelfehlern zwischen dem Rollenring 18 und dem Gleitstein 33 ermöglicht, ohne daß dies zu einer Verspannung des Bolzens 30 führt. Von bekannten Kraftstoffeinspritzpumpen mit verstellbarem Rollenring können der Rollenring 18 sowie der Bolzen 30 unverändert übernommen werden. Eine zusätzliche Dichtstelle ist bei der Blockierung des Rollenrings nicht erforderlich.This makes it possible to compensate for distance and angle errors between the roller ring 18 and the sliding block 33, without this leading to the bolt 30 being braced. The roller ring 18 and the bolt 30 can be adopted unchanged from known fuel injection pumps with an adjustable roller ring. An additional sealing point is not necessary when the roller ring is blocked.

Durch das Ventil 22 wird eine Verbindung des Innenraums 24 mit dem Pumpenarbeitsraum 23 gesteuert. Beim Saughub des Pumpenkolbens 13 ist das Ventil 22 geöffnet und Kraftstoff strömt aus dem Innenraum 24 durch einen Kanal 40 sowie das Ventil 22 in den Pumpenarbeitsraum 23. Beim Druckhub des Pumpenkolbens 13 wird das Ventil 22 für die Dauer der gewählten Hochdruckförderung des Pumpenkolbens geschlossen und über eine Verteileröffnung 41 am Umfang des Pumpenkolbens 13 wird der auf Hochdruck gebrachte Kraftstoff bei entsprechender Drehung des Pumpenkolbens in strichliniert dargestellte Förderkanäle 42 gefördert, die über Einspritzleitungen mit den Einspritzstellen der Brennkraftmaschine verbunden sind. Die Schließdauer und damit die Hochdruckeinspritzmenge sowie der den Beginn der Hochdruckeinspritzphase bestimmende Schließzeitpunkt des Ventils 22 wird durch ein nicht dargestelltes Steuergerät bestimmt. Zur Erfassung der Drehzahl sowie Drehlage der Antriebswelle 16 der Kraftstoffeinspritzpumpe ist ein Drehgeber 43 vorgesehen, der mit dem Steuergerät verbunden ist. Durch das Steuergerät können weitere Betriebsparameter wie beispielsweise Last, Temperatur etc. der mit der Kraftstoffeinspritzpumpe betriebenen Brennkraftmaschine berücksichtigt werden.A connection of the interior 24 to the pump work space 23 is controlled by the valve 22. During the suction stroke of the pump piston 13, the valve 22 is opened and fuel flows from the interior 24 through a channel 40 and the valve 22 into the pump working space 23. During the pressure stroke of the pump piston 13, the valve 22 is closed and over for the duration of the selected high-pressure delivery of the pump piston a distributor opening 41 on the circumference of the pump piston 13, the fuel brought to high pressure is conveyed with corresponding rotation of the pump piston into delivery channels 42 shown in broken lines, which are connected to the injection points of the internal combustion engine via injection lines. The closing time and thus the high-pressure injection quantity and the closing time of the valve 22 which determines the start of the high-pressure injection phase is determined by a control unit (not shown). A rotary encoder 43, which is connected to the control unit, is provided for detecting the rotational speed and the rotational position of the drive shaft 16 of the fuel injection pump. The control unit can take into account further operating parameters such as, for example, load, temperature etc. of the internal combustion engine operated with the fuel injection pump.

Bei einem in Figur 2 dargestellten zweiten Ausführungsbeispiel sind der Rollenring 18 und der Bolzen 30 wie beim ersten Ausführungsbeispiel beschrieben, ausgebildet. Der Gleitstein 46 ist jedoch abweichend vom ersten Ausführungsbeispiel in einer sich etwa parallel zur Pumpenlängsachse 34 erstreckenden Sackbohrung 47 im Pumpengehäuse 11 angeordnet. Der Bolzen 30 ragt durch eine Öffnung 48 im Pumpengehäuse 11 zwischen Innenraum 24 und Sackbohrung 47 in die Bohrung 49 im Gleitstein 46. Der Gleitstein 46 ist in der Sackbohrung 47 axial verschiebbar, quer zu seiner Längsachse jedoch mit möglichst geringem Spiel angeordnet. Die Sackbohrung 47 weist zur Außenseite des Pumpengehäuses 11 einen Gewindeabschnitt 50 auf, in den eine Verschlußschraube 51 eingeschraubt ist, die die Sackbohrung 47 verschließt, wobei zwischen dem Pumpengehäuse 11 und der Verschlußschraube 51 ein Dichtring 52 eingespannt ist. Der Gleitstein 46 ist von der Außenseite des Pumpengehäuses 11 in die Bohrung 47 einsetzbar. Beim zweiten Ausführungsbeispiel können der Rollenring 18, der Bolzen 30 sowie der Gleitstein 46 im wesentlichen unverändert von bekannten Kraftstoffeinspritzpumpe mit verstellbarem Rollenring übernommen werden. Die Lage der Sackbohrung 47 für den Gleitstein 46 ist vorzugsweise so gewählt, daß diese bei einer automatisierten Fertigung des Pumpengehäuses 11 mit geringem Aufwand gebohrt werden kann. Die Verschlußschraube 51 sowie der Dichtring 52 sind Normteile, so daß die Blockierung des Rollenrings 18 mit einfachen Mitteln erreicht ist.In a second exemplary embodiment shown in FIG. 2, the roller ring 18 and the bolt 30 are designed as described in the first exemplary embodiment. In contrast to the first exemplary embodiment, the sliding block 46 is arranged in a blind bore 47 in the pump housing 11 which extends approximately parallel to the longitudinal axis 34 of the pump. The bolt 30 protrudes through an opening 48 in the pump housing 11 between the interior 24 and the blind bore 47 into the bore 49 in the sliding block 46. The sliding block 46 is axially displaceable in the blind bore 47, but is arranged transversely to its longitudinal axis with as little play as possible. The blind bore 47 has a threaded section 50 to the outside of the pump housing 11, into which a screw plug 51 is screwed, which closes the blind bore 47, a sealing ring 52 being clamped between the pump housing 11 and the screw plug 51. The sliding block 46 can be inserted into the bore 47 from the outside of the pump housing 11. In the second embodiment, the roller ring 18, the bolt 30 and the sliding block 46 can be taken over essentially unchanged from known fuel injection pumps with an adjustable roller ring. The position of the blind bore 47 for the sliding block 46 is preferably selected so that it can be drilled with little effort in an automated production of the pump housing 11. The locking screw 51 and the sealing ring 52 are standard parts, so that the blocking of the roller ring 18 is achieved with simple means.

Claims (5)

  1. Fuel injection pump for internal combustion engines, having at least one pump piston (13) which is moved in a rotating and simultaneously reciprocating manner by a cam drive (14), which consists of an essentially stationary part (18) and a rotating part (17) driven by a drive shaft (16), a pin (30) engaging radially in the essentially stationary part (18), on the one hand, and being supported in a sliding piece (33; 46), on the other, and having a pump working space (23) bounded by the pump piston (13), which pump working space (23) can be relieved by means of an electrically controlled valve (22) during the pumping stroke of the pump piston (13) in order to control the pump piston stroke which effects injection, the beginning of injection being determined by the instant when the valve (22) closes, which is controlled as a function of operating parameters of the internal combustion engine, characterized in that the sliding piece (33; 46) is arranged in a recess (36; 47) in a housing part (11) of the fuel injection pump and guided so that it can be displaced freely in the axial direction approximately parallel to the longitudinal centre line (34) of the fuel injection pump but with little clearance tangential to the stationary part (18), in order to block a rotational motion of the stationary part (18).
  2. Fuel injection pump according to Claim 1, characterized in that the recess is configured as a longitudinal groove (36) open towards the internal space (11) of the fuel injection pump.
  3. Fuel injection pump according to Claim 2, characterized in that the sliding piece (33) is arranged with little clearance between the bottom (37) of the longitudinal groove (36) and the external periphery (26) of the stationary part (18).
  4. Fuel injection pump according to Claim 1, characterized in that the recess is configured as a pocket hole (47) in the housing part (11) with a side opening (48) to the pump internal space (11).
  5. Fuel injection pump according to Claim 4, characterized in that the pocket hole (47) is open towards the outside of the housing part (11) and has a threaded section (50) there, into which a screw plug (51) can be screwed.
EP91114895A 1990-10-10 1991-09-04 Fuel injection pump for internal combustion engine Expired - Lifetime EP0480173B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9014068U 1990-10-10
DE9014068U DE9014068U1 (en) 1990-10-10 1990-10-10 Fuel injection pump for internal combustion engines

Publications (2)

Publication Number Publication Date
EP0480173A1 EP0480173A1 (en) 1992-04-15
EP0480173B1 true EP0480173B1 (en) 1994-12-28

Family

ID=6858234

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91114895A Expired - Lifetime EP0480173B1 (en) 1990-10-10 1991-09-04 Fuel injection pump for internal combustion engine

Country Status (4)

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EP (1) EP0480173B1 (en)
JP (1) JP3119908B2 (en)
DE (2) DE9014068U1 (en)
ES (1) ES2067107T3 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4232741A1 (en) * 1992-09-30 1994-03-31 Bosch Gmbh Robert Fuel injection pump for internal combustion engines
JP3355681B2 (en) * 1993-02-15 2002-12-09 東ソー株式会社 Column with built-in filter for liquid chromatography
DE4344865A1 (en) * 1993-12-29 1995-07-06 Bosch Gmbh Robert Fuel injection pump

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE963825C (en) * 1954-09-12 1957-05-16 Bosch Gmbh Robert Fuel injection pump for multi-cylinder internal combustion engines
DE1943674A1 (en) * 1969-07-23 1971-03-11 Orange Einspritzgeraete Kg Injection timing adjustment device for distributor injection pumps
JPS637276U (en) * 1986-07-01 1988-01-18
US5000668A (en) * 1988-04-27 1991-03-19 Diesel Kiki Co., Ltd. Distribution-type fuel injection pump

Also Published As

Publication number Publication date
EP0480173A1 (en) 1992-04-15
DE59104054D1 (en) 1995-02-09
DE9014068U1 (en) 1992-02-13
JP3119908B2 (en) 2000-12-25
ES2067107T3 (en) 1995-03-16
JPH04262054A (en) 1992-09-17

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