EP0318714B1 - Exhaust gas recirculation device for internal combustion engines - Google Patents

Exhaust gas recirculation device for internal combustion engines Download PDF

Info

Publication number
EP0318714B1
EP0318714B1 EP88118278A EP88118278A EP0318714B1 EP 0318714 B1 EP0318714 B1 EP 0318714B1 EP 88118278 A EP88118278 A EP 88118278A EP 88118278 A EP88118278 A EP 88118278A EP 0318714 B1 EP0318714 B1 EP 0318714B1
Authority
EP
European Patent Office
Prior art keywords
pressure
gas recirculation
fuel
valve
fuel injection
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
EP88118278A
Other languages
German (de)
French (fr)
Other versions
EP0318714A3 (en
EP0318714A2 (en
Inventor
Klaus Dipl.-Ing. Krieger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0318714A2 publication Critical patent/EP0318714A2/en
Publication of EP0318714A3 publication Critical patent/EP0318714A3/en
Application granted granted Critical
Publication of EP0318714B1 publication Critical patent/EP0318714B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/06—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture adding lubricant vapours
    • 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
    • F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/59—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor
    • F02M26/62—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor in response to fuel pressure
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/55—Systems for actuating EGR valves using vacuum actuators

Definitions

  • the invention relates to an exhaust gas recirculation device for internal combustion engines according to the preamble of patent claim 1.
  • a distributor injection pump serves as the fuel injection system, in which the start of delivery takes place via a speed-dependent hydraulic pressure prevailing in the pump suction chamber and at which this pressure is caused by a position of the sleeve of the aerodynamic speed regulator dependent drain opening is affected.
  • the position of the control sleeve is determined depending on the speed and load, since on the one hand the purely speed-dependent flying forces act on the control sleeve and in the opposite direction the forces which can be changed arbitrarily via the adjusting lever and which are entered by a control spring and correspond to the load.
  • the discharge opening is opened by the control sleeve when the desired load and speed for exhaust gas recirculation has been reached.
  • the fuel flowing out through the discharge opening is blocked by a throttle, this dynamic pressure acting via a servomotor on a directional control valve via which a pneumatically operated exhaust gas recirculation valve is controlled.
  • This type of control has the disadvantage that the throttling valve has a certain cross-section, which from a certain outflow quantity causes the required switching pressure, but this means that with larger outflow quantities per time, i.e. at high speeds and open discharge opening, the throttle acts as a closure, so that the change in the pressure curve in the suction space provided for the adjustment of the start of delivery stops.
  • the exhaust gas recirculation device according to the invention with the characterizing features of claim 1 has the advantage that the direct implementation of the hydraulic pressure for switching the directional control valve saves costs while reducing sources of interference.
  • An embodiment of the object of the invention is shown in the drawing and described in more detail below. It is a distributor injection pump in the Shown longitudinal section, which is used to control a schematically shown exhaust gas recirculation system.
  • a pump and distributor piston 1 is set into a reciprocating and at the same time rotating movement by a drive shaft 2 and with the aid of a cam gear 3. With each pressure stroke of the pump piston 1, fuel is conveyed from a pump work chamber 4 via a longitudinal distribution groove 5 to one of a plurality of pressure channels 6, which are arranged around the pump and distributor piston 1 at uniform angular intervals and each lead to a combustion chamber (not shown) of an internal combustion engine.
  • the pump working chamber 4 is supplied with fuel via a suction channel 7 from a suction chamber 8 which is present in the housing of the injection pump and is filled with fuel, in that during the suction stroke of the pumping and distributing piston 1 the suction channel 7 is opened by longitudinal control grooves 9 provided in the pump piston 1.
  • the number of control grooves 9 corresponds to the number of pressure channels 6 and thus the number of pressure strokes carried out with one revolution of the pump piston.
  • a solenoid valve 10 is arranged, which closes the suction channel 7 at the end of the injection, so that no fuel can get from the suction chamber 8 into the pump working chamber 4 during the suction stroke of the pump piston 1.
  • the quantity to be injected into the pressure channel 6 per stroke is determined by the axial position of a control slide 11 arranged around the pump piston 1. This axial position is determined by a speed controller 12 and an arbitrarily actuable adjusting lever 13, evaluating the respective speed and load (the load can correspond, for example, to the position of the accelerator pedal of the motor vehicle).
  • the suction chamber 8 is supplied with fuel by a feed pump 14, which is driven by the drive shaft 2 and supplies fuel from a fuel tank 15 and a suction line 16.
  • the output pressure of the feed pump 14 and thus the pressure in the suction chamber 8 are controlled by a pressure control valve 17, this pressure also increasing with increasing speed in accordance with a desired function.
  • the cam mechanism 3 and the speed controller 12 are arranged in the suction chamber 8 and are thus acted upon on all sides by this pressure and are lubricated by this fuel.
  • the cam drive 3 which is driven by the drive shaft 2, has a roller ring 19 which carries rollers 18, which is rotatably mounted in the housing by a certain angle and in the U-shaped cross section of which the rollers 18 are mounted.
  • This roller ring 19 is coupled with an injection adjusting piston 22 in a rotationally locking manner via an adjusting bolt 21, this injection adjusting piston 22 being shown rotated by 90 ° in the drawing, ie actually perpendicular to the plane of the illustration is adjustable.
  • this roller ring 19 there is a claw coupling in which the claws 23 on the output side of the drive shaft 2 mesh with the claws 24 on the drive side of the pumping and distributing piston 1 so that the pumping and distributing piston 1 independently of the drive shaft 2 exert a lifting movement while rotating can.
  • An end cam disk 25 is arranged on the pump piston 1 and runs with its end cam 26 on the rollers 18, the number of end cams in turn corresponding to the number of pressure channels 6. The end cam disk 25 is pressed with its track onto the rollers 20 by springs 27, only one of which is shown.
  • the direction of displacement of the injection adjustment piston is chosen so that when the fuel pressure in the suction chamber 8 increases with increasing speed, the injection adjustment piston 22 is displaced counter to the return spring 28 and rotates the roller ring 19 so that the end cams 26 of the end cam disk 25 come into engagement with the rollers 18 earlier , whereby the start of the stroke of the pump piston 1 and thus the start of delivery of the fuel with respect to the rotational position of the drive shaft 2 is brought forward. So the higher the speed, the earlier the start of delivery (start of spraying).
  • the speed controller 12 is driven via a gear wheel 32, which is connected to the drive shaft 2 and drives a speed sensor 33 with flyweights 34, which act on a control sleeve 35 on the one hand, which is mounted axially displaceably on an axis 36 and on the other hand through a control spring 37 attacks the control lever system 38, which articulates the control slide 11 for its stroke position.
  • the control lever system 38 is pivotally mounted on an axis 39 for this purpose.
  • the bias of the control spring 37 can be changed by the adjusting lever 13 in such a way that when the adjusting lever 13 is moved in the direction of increasing load, the bias of the control spring 37 also increases, so that the control slide 11 is pushed further up, which is due to a given later opening of a relief channel 41 of the pump work space 4 during the pressure stroke of the pump piston 1, an increase in the injection quantity results.
  • the control of the amount of fuel still in the pump work chamber 4 is always given when the orifices 42 of the relief channel 1 emerge from the control slide 11 during the pressure stroke of the pump piston 1 and the further fuel delivery of the pump piston 1 into the suction chamber 8 takes place.
  • the drain channel 44 is connected via a drain line 45 to the fuel tank 15, in which Drain line a pressure control valve 46 is arranged. Upstream of this pressure-maintaining valve 46, a hydraulic servomotor 47 of a pneumatic 3/2-way valve 48 is connected to the discharge line 45.
  • the directional control valve 48 controls a vacuum line 49, which leads from an exhaust gas recirculation valve 51 to a vacuum source 52.
  • the exhaust gas recirculation valve 51 which is loaded in the closing direction by a spring 53, is arranged in an exhaust gas recirculation line 54 of an engine 55, which is supplied with fuel via an injection line 56 from the pressure channel 6, which is delivered in the manner described above, with appropriate regulation of the quantity and the start of delivery .
  • the drain line 45 has a bypass 57, in which a dam throttle 58 is arranged.
  • the exhaust gas recirculation control takes place in such a way that below a certain load, at which the control bore 43 opens the drain channel 44, the fuel flowing there out of the suction chamber 8 and into the drain line 45 is stowed there by the throttling throttle 58 until the pressure holding valve is reached after reaching a certain pressure 46 opens and allows the fuel to flow into the fuel tank 15 while maintaining this discharge pressure.
  • the pneumatic directional valve 48 is opened by the hydraulic servomotor 47, so that the exhaust gas recirculation valve 51 is opened by the vacuum source 52 against the force of the closing spring 53 via the vacuum line 49 and exhaust gas by the exhaust gas recirculation line 54 from the exhaust side of the engine can flow to the suction side.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)

Description

Die Erfindung geht aus von einer Abgasrückführeinrichtung für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1.The invention relates to an exhaust gas recirculation device for internal combustion engines according to the preamble of patent claim 1.

Bekanntlich können die schädlichen Emissionen einer Brennkraftmaschine durch die Optimierung des Brennraumes und der Einspritzanlage nur bis zu einer bestimmten Grenze verringert werden. Die Kohlenwasserstoffemission wird durch die Spritzbeginnfrühverschiebung minimiert, wodurch die NOx-Emission ansteigt. Um diese NOx-Emission wieder zu reduzieren, wird bekanntlich die Abgasrückführung vorgenommen, wofür verschiedene Methoden bekannt sind. Diese speziell für die Verringerung der Kohlenwasserstoffemission durchgeführte Früherverstellung des Förderbeginns ist teilweise überlagert mit der ohnehin in der Einspritzanlage vorhandenen last- sowie drehzahlabhängigen Spritzbeginnregelung. Bekanntlich muß mit zunehmender Drehzahl der Förderbeginn auf früher verstellt werden, insbesondere um die natürliche Spritzbeginnspätverstellung mit zunehmender Drehzahl, die durch die winkelmäßig zunehmende Laufzeit der Druckwellen in der Einspritzleitung bedingt ist, auszugleichen. Eine Abgasrückführung darf nur unterhalb einer bestimmten Last erfolgen, d.h. unterhalb einer bestimmten Einspritzmenge, wobei sich dieser Wert mit der Drehzahl in etwa entsprechend den Lastkurven des Reglerkennfelds ändert.It is known that the harmful emissions of an internal combustion engine can only be reduced to a certain limit by optimizing the combustion chamber and the injection system. The hydrocarbon emission is minimized by the injection begin early shift, which increases NOx emissions. As is known, the exhaust gas recirculation is carried out to reduce this NO x emission again, for which various methods are known. This early adjustment of the start of delivery, which is carried out specifically for reducing the hydrocarbon emission, is partially superimposed on the load and load already present in the injection system speed-dependent spray start control. As is known, the start of delivery must be adjusted to earlier with increasing speed, in particular in order to compensate for the natural late injection start with increasing speed, which is caused by the angularly increasing duration of the pressure waves in the injection line. Exhaust gas recirculation may only take place below a certain load, ie below a certain injection quantity, this value changing with the speed approximately in accordance with the load curves of the control map.

Bei einer bekannten Abgasrückführeinrichtung für Brennkraftmaschinen der gattungsgemäßen Art (DE-A-2855 027) dient als Kraftstoffeinspritzanlage eine Verteilereinspritzpumpe, bei der der Förderbeginn über einen im Pumpensaugraum herrschenden drehzahlabhängigen hydraulischen Druck erfolgt und bei der dieser Druck durch eine von der Lage der Muffe des Fliegkraftdrehzahlreglers abhängige Abflußöffnung beeinflußt wird. Die Lage der Regelmuffe ist drehzahl- und lastabhängig bestimmt, da einerseits an der Regelmuffe die rein drehzahlabhängigen Fliegkräfte angreifen und in entgegengesetzter Richtung die über den Verstellhebel willkürlich änderbaren und durch eine Regelfeder eingegebenen der Last entsprechenden Kräfte. Die Abflußöffnung wird durch die Regelmuffe dann aufgesteuert, wenn die für eine Abgasrückführung gewünschte Last und Drehzahl erreicht ist. Der durch die Abflußöffnung abströmende Kraftstoff wird durch eine Drossel gestaut, wobei dieser Staudruck über einen Stellmotor auf ein Wegeventils wirkt, über das ein pneumatisch betätigtes Abgasrückführuentil gesteuert wird.In a known exhaust gas recirculation device for internal combustion engines of the generic type (DE-A-2855 027), a distributor injection pump serves as the fuel injection system, in which the start of delivery takes place via a speed-dependent hydraulic pressure prevailing in the pump suction chamber and at which this pressure is caused by a position of the sleeve of the aerodynamic speed regulator dependent drain opening is affected. The position of the control sleeve is determined depending on the speed and load, since on the one hand the purely speed-dependent flying forces act on the control sleeve and in the opposite direction the forces which can be changed arbitrarily via the adjusting lever and which are entered by a control spring and correspond to the load. The discharge opening is opened by the control sleeve when the desired load and speed for exhaust gas recirculation has been reached. The fuel flowing out through the discharge opening is blocked by a throttle, this dynamic pressure acting via a servomotor on a directional control valve via which a pneumatically operated exhaust gas recirculation valve is controlled.

Diese Art der Steuerung hat den Nachteil, daß die Staudrossel einen bestimmten Querschnitt aufweist, der ab einer bestimmten Abströmmenge zwar den erforderlichen Schaltdruck bewirkt, was jedoch dazu führt, daß bei größeren Abströmmengen pro Zeit, also bei hohen Drehzahlen und geöffneter Abflußöffnung, sich die Drossel wie ein Verschluß auswirkt, so daß die für die Angleichung des Förderbeginns vorgesehene Änderung des Druckverlaufs im Saugraum aussetzt.This type of control has the disadvantage that the throttling valve has a certain cross-section, which from a certain outflow quantity causes the required switching pressure, but this means that with larger outflow quantities per time, i.e. at high speeds and open discharge opening, the throttle acts as a closure, so that the change in the pressure curve in the suction space provided for the adjustment of the start of delivery stops.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Abgasrückführeinrichtung mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß durch die direkte Umsetzung des hydraulischen Druckes zur Schaltung des Wegeventils Kosten gespart werden bei gleichzeitigem Vermindern von Störquellen.The exhaust gas recirculation device according to the invention with the characterizing features of claim 1 has the advantage that the direct implementation of the hydraulic pressure for switching the directional control valve saves costs while reducing sources of interference.

Dadurch, daß parallel zur Staudrossel ein Druckhalteventil für die abströmende Menge vorhanden ist, über das der erforderliche Stelldruck des Stellmotors des Wegeventils erzielbar ist, wird vor allem erreicht, daß der Querschnitt der Staudrossel sehr eng gehalten werden kann, da die Staudrossel nun nur noch die Aufgabe hat, bei geschlossener Abflußöffnung an der Regelmuffe den hydraulischen Druck am hydraulischen Stellmotor so weit abzubauen, daß das Wegeventil wieder schließen kann. Das Druckhalteventil hingegen hält bei abfließendem Kraftstoff gerade einen Druck aufrecht, wie er zum Betätigen des Stellmotors notwendig ist, der jedoch so gering ist, daß er keinen Einfluß auf den Druck im Saugraum hat, so daß die lastabhängige Förderbeginnsteuerung nicht beeinträchtigt ist.The fact that there is a pressure control valve for the outflowing quantity parallel to the throttling valve, via which the required actuating pressure of the servomotor of the directional control valve can be achieved, the main result is that the cross section of the throttling valve can be kept very narrow, since the throttling valve is now only the The task is to reduce the hydraulic pressure on the hydraulic servomotor so far that the directional control valve can close again when the drain opening on the control sleeve is closed. The pressure control valve, on the other hand, maintains a pressure when the fuel is flowing away, as is necessary to actuate the servomotor, which is however so low that it has no influence on the pressure in the suction chamber, so that the load-dependent delivery start control is not impaired.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the invention can be found in the following description, the drawing and the claims.

Zeichnungdrawing

Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist in der Zeichnung dargestellt und im folgenden näher beschrieben. Es ist eine Verteilereinspritzpumpe im Längsschnitt dargestellt, die zur Steuerung einer schematisch dargestellten Abgasrückführanlage dient.An embodiment of the object of the invention is shown in the drawing and described in more detail below. It is a distributor injection pump in the Shown longitudinal section, which is used to control a schematically shown exhaust gas recirculation system.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Bei der Verteilereinspritzpumpe wird ein Pump- und Verteilerkolben 1 durch eine Antriebswelle 2 und mit Hilfe eines Nockengetriebes 3 in eine hin- und hergehende und gleichzeitig rotierende Bewegung versetzt. Bei jedem Druckhub des Pumpenkolbens 1 wird dabei aus einem Pumpenarbeitsraum 4 über eine Verteilerlängsnut 5 Kraftstoff zu einem von mehreren Druckkanälen 6 gefördert, die um den Pump- und Verteilerkolben 1 herum in gleichmäßigen Drehwinkelabständen angeordnet sind und jeweils zu einem nicht dargestellten Brennraum einer Brennkraftmaschine führen. Der Pumpenarbeitsraum 4 wird über einen Saugkanal 7 aus einem im Gehäuse der Einspritzpumpe vorhandenen und mit Kraftstoff gefüllten Saugraum 8 mit Kraftstoff versorgt, indem während des Saughubs des Pump- und Verteilerkolbens 1 der Saugkanal 7 durch im Pumpenkolben 1 vorgesehene Steuerlängsnuten 9 aufgesteuert wird. Die Anzahl der Steuernuten 9 enspricht der Anzahl der Druckkanäle 6 und damit der Anzahl der bei einer Umdrehung des Pumpenkolbens ausgeführten Druckhübe. In dem Saugkanal 7 ist ein Magnetventil 10 angeordnet, das zur Beendigung der Einspritzung den Saugkanal 7 sperrt, so daß während des Saughubs des Pumpenkolbens 1 kein Kraftstoff aus dem Saugraum 8 in den Pumpenarbeitsraum 4 gelangen kann.In the case of the distributor injection pump, a pump and distributor piston 1 is set into a reciprocating and at the same time rotating movement by a drive shaft 2 and with the aid of a cam gear 3. With each pressure stroke of the pump piston 1, fuel is conveyed from a pump work chamber 4 via a longitudinal distribution groove 5 to one of a plurality of pressure channels 6, which are arranged around the pump and distributor piston 1 at uniform angular intervals and each lead to a combustion chamber (not shown) of an internal combustion engine. The pump working chamber 4 is supplied with fuel via a suction channel 7 from a suction chamber 8 which is present in the housing of the injection pump and is filled with fuel, in that during the suction stroke of the pumping and distributing piston 1 the suction channel 7 is opened by longitudinal control grooves 9 provided in the pump piston 1. The number of control grooves 9 corresponds to the number of pressure channels 6 and thus the number of pressure strokes carried out with one revolution of the pump piston. In the suction channel 7, a solenoid valve 10 is arranged, which closes the suction channel 7 at the end of the injection, so that no fuel can get from the suction chamber 8 into the pump working chamber 4 during the suction stroke of the pump piston 1.

Die pro Hub in den Druckkanal 6 geförderte einzuspritzende Menge wird durch die axiale Lage eines um den Pumpenkolben 1 angeordneten Regelschiebers 11 bestimmt. Diese axiale Lage wird durch einen Drehzahlregler 12 und einen willkürlich betätigbaren Verstellhebel 13 bestimmt unter Auswertung der jeweiligen Drehzahl und Last (die Last kann beispielsweise der Stellung des Gaspedals des Kraftfahrzeugs entsprechen).The quantity to be injected into the pressure channel 6 per stroke is determined by the axial position of a control slide 11 arranged around the pump piston 1. This axial position is determined by a speed controller 12 and an arbitrarily actuable adjusting lever 13, evaluating the respective speed and load (the load can correspond, for example, to the position of the accelerator pedal of the motor vehicle).

Der Saugraum 8 wird von einer Förderpumpe 14 her mit Kraftstoff versorgt, die durch die Antriebswelle 2 angetrieben wird und aus einem Kraftstoffbehälter 15 und einer Saugleitung 16 Kraftstoff zuführt. Durch ein Drucksteuerventil 17 wird der Ausgangsdruck der Förderpumpe 14 und damit der Druck im Saugraum 8 gesteuert, wobei dieser Druck mit zunehmender Drehzahl entsprechend einer gewünschten Funktion ebenfalls zunimmt. Im Saugraum 8 sind der Nockentrieb 3 sowie der Drehzahlregler 12 angeordnet, die somit allseitig von diesem Druck beaufschlagt sind und von diesem Kraftstoff geschmiert werden.The suction chamber 8 is supplied with fuel by a feed pump 14, which is driven by the drive shaft 2 and supplies fuel from a fuel tank 15 and a suction line 16. The output pressure of the feed pump 14 and thus the pressure in the suction chamber 8 are controlled by a pressure control valve 17, this pressure also increasing with increasing speed in accordance with a desired function. The cam mechanism 3 and the speed controller 12 are arranged in the suction chamber 8 and are thus acted upon on all sides by this pressure and are lubricated by this fuel.

Der durch die Antriebswelle 2 angetriebene Nockentrieb 3 weist einen Rollen 18 tragenden Rollenring 19 auf, der um einen bestimmten Winkel verdrehbar im Gehäuse gelagert ist und in dessen U-förmigen Querschnitt die Rollen 18 gelagert sind. Dieser Rollenring 19 ist über einen Verstellbolzen 21 mit einem Spritzverstellkolben 22 verdrehschlüssig gekoppelt, wobei in der Zeichnung dieser Spritzverstellkolben 22 um 90° verdreht dargestellt ist, d.h. tatsächlich senkrecht zur Darstellungsebene verstellbar ist. In der Innenbohrung dieses Rollenrings 19 ist eine Klauenkupplung vorhanden, bei der abtriebsseitige Klauen 23 der Antriebswelle 2 mit antriebsseitigen Klauen 24 des Pump- und Verteilerkolbens 1 ineinandergreifen, so daß der Pump- und Verteilerkolben 1 unabhängig von der Antriebswelle 2 eine Hubbewegung während des Rotierens ausüben kann. Am Pumpenkolben 1 ist eine Stirnnockenscheibe 25 angeordnet, die mit ihrer Stirnnocken 26 aufweisenden Stirnfläche auf den Rollen 18 abläuft, wobei die Zahl der Stirnnocken wiederum der Anzahl der Druckkanäle 6 entspricht. Die Stirnnockenscheibe 25 wird durch Federn 27, von denen nur eine dargestellt ist, mit ihrer Laufbahn auf die Rollen 20 gepresst.The cam drive 3, which is driven by the drive shaft 2, has a roller ring 19 which carries rollers 18, which is rotatably mounted in the housing by a certain angle and in the U-shaped cross section of which the rollers 18 are mounted. This roller ring 19 is coupled with an injection adjusting piston 22 in a rotationally locking manner via an adjusting bolt 21, this injection adjusting piston 22 being shown rotated by 90 ° in the drawing, ie actually perpendicular to the plane of the illustration is adjustable. In the inner bore of this roller ring 19 there is a claw coupling in which the claws 23 on the output side of the drive shaft 2 mesh with the claws 24 on the drive side of the pumping and distributing piston 1 so that the pumping and distributing piston 1 independently of the drive shaft 2 exert a lifting movement while rotating can. An end cam disk 25 is arranged on the pump piston 1 and runs with its end cam 26 on the rollers 18, the number of end cams in turn corresponding to the number of pressure channels 6. The end cam disk 25 is pressed with its track onto the rollers 20 by springs 27, only one of which is shown.

Der tangential zum Rollenring axial verschiebbare Spritzverstellkolben 22 ist in der einen Verstellrichtung durch eine Rückstellfeder 28 belastet und in der anderen Verstellrichtung durch den in einem Raum 29 herrschenden Druck des Saugraums 8, welcher durch einen im Spritzverstellkolben 22 vorhandenen Drosselkanal 31 übertragen wird. Die Verschieberichtung des Spritzverstellkolbens ist dabei so gewählt, daß wenn der Kraftstoffdruck im Saugraum 8 mit zunehmender Drehzahl steigt, der Spritzverstellkolben 22 entgegen der Rückstellfeder 28 verschoben den Rollenring 19 so verdreht, daß die Stirnnocken 26 der Stirnnockenscheibe 25 früher mit den Rollen 18 in Eingriff gelangen, wodurch der Hubbeginn des Pumpenkolbens 1 und damit der Förderbeginn des Kraftstoffes in bezug auf die Drehlage der Antriebswelle 2 vorverlegt wird. Je höher also die Drehzahl ist, desto früher ist der Förderbeginn (Spritzbeginn).The injection adjustment piston 22, which is axially displaceable tangentially to the roller ring, is loaded in one adjustment direction by a return spring 28 and in the other adjustment direction by the pressure of the suction space 8 prevailing in a space 29, which is transmitted through a throttle channel 31 present in the injection adjustment piston 22. The direction of displacement of the injection adjustment piston is chosen so that when the fuel pressure in the suction chamber 8 increases with increasing speed, the injection adjustment piston 22 is displaced counter to the return spring 28 and rotates the roller ring 19 so that the end cams 26 of the end cam disk 25 come into engagement with the rollers 18 earlier , whereby the start of the stroke of the pump piston 1 and thus the start of delivery of the fuel with respect to the rotational position of the drive shaft 2 is brought forward. So the higher the speed, the earlier the start of delivery (start of spraying).

Der Antrieb des Drehzahlreglers 12 erfolgt über ein Zahnrad 32, das mit der Antriebswelle 2 verbunden ist und einen Drehzahlgeber 33 mit Fliehgewichten 34 antreibt, welche an einer Reglermuffe 35 einerseits angreifen, die axial verschiebbar auf einer Achse 36 gelagert ist und an der andererseits das durch eine Regelfeder 37 belastete Regelhebelsystem 38 angreift, welches den Regelschieber 11 für seine Hublage anlenkt. Das Regelhebelsystem 38 ist auf einer Achse 39 hierfür schwenkbar gelagert. Die Vorspannung der Regelfeder 37 ist durch den Verstellhebel 13 änderbar und zwar in der Art, daß bei Verstellung des Verstellhebels 13 in Richtung zunehmender Last auch die Vorspannung der Regelfeder 37 zunimmt, so daß der Regelschieber 11 weiter nach oben geschoben wird, was aufgrund eines dadurch gegebenen späteren Aufsteuerns eines Entlastungskanals 41 des Pumpenarbeitsraums 4 während des Druckhubs des Pumpenkolbens 1 eine Zunahme der Einspritzmenge zur Folge hat. Die Absteuerung der noch im Pumpenarbeitsraum 4 befindlichen Kraftstoffmenge ist immer dann gegeben, wenn während des Druckhubs des Pumpenkolbens 1 die Mündungen 42 des Entlastungskanals 1 aus dem Regelschieber 11 austauchen und so die weitere Kraftstoffförderung des Pumpenkolbens 1 in den Saugraum 8 erfolgt.The speed controller 12 is driven via a gear wheel 32, which is connected to the drive shaft 2 and drives a speed sensor 33 with flyweights 34, which act on a control sleeve 35 on the one hand, which is mounted axially displaceably on an axis 36 and on the other hand through a control spring 37 attacks the control lever system 38, which articulates the control slide 11 for its stroke position. The control lever system 38 is pivotally mounted on an axis 39 for this purpose. The bias of the control spring 37 can be changed by the adjusting lever 13 in such a way that when the adjusting lever 13 is moved in the direction of increasing load, the bias of the control spring 37 also increases, so that the control slide 11 is pushed further up, which is due to a given later opening of a relief channel 41 of the pump work space 4 during the pressure stroke of the pump piston 1, an increase in the injection quantity results. The control of the amount of fuel still in the pump work chamber 4 is always given when the orifices 42 of the relief channel 1 emerge from the control slide 11 during the pressure stroke of the pump piston 1 and the further fuel delivery of the pump piston 1 into the suction chamber 8 takes place.

Um den Förderbeginn, der wie bisher beschrieben nur drehzahlabhängig geändert wird, auch lastabhängig zu steuern, ist in der Verstellmuffe 35 eine Steuerbohrung 43 vorhanden, die mit einem in der Achse 39 verlaufenden Abflußkanal 44 zusammenwirkt, wodurch entweder in bestimmten Lastzuständen, die sich über den Verstellhebel 13, die Regelfeder 37 und das Regelhebelsystem 38 auf die Regelmuffe 35 auswirken oder in bestimmten Fällen der Belastung des Motors, die sich auf die Drehzahl auswirkt, indem über die Fliehgewichte 34 eine Verstellung der Regelmuffe 35 erfolgt, durch das Aufsteuern des Abflußkanals 44 durch die Steuerbohrung 43 der Druck im Saugraum 8 verringert und damit der Förderbeginn auf später gestellt wird.In order to control the start of delivery, which, as previously described, is only changed as a function of speed, also as a function of load, there is a control bore in the adjusting sleeve 35 43 available, which cooperates with a drain channel 44 extending in the axis 39, which either in certain load conditions, which affect the control sleeve 35 via the adjusting lever 13, the control spring 37 and the control lever system 38, or in certain cases the load on the engine, the affects the speed of rotation by adjusting the control sleeve 35 via the centrifugal weights 34, the pressure in the suction chamber 8 is reduced by opening the drain channel 44 through the control bore 43 and the delivery start is thus set to later.

Dieses Aufsteuern des Abflußkanals findet immer unterhalb einer bestimmten Last statt. Aus diesem Grunde wird der abfließende Kraftstoff zur Steuerung der Abgasrückführung verwendet, die ebenfalls unterhalb einer bestimmten Last eingeschaltet werden soll. Diese Spritzbeginnspätverstellung bei niederer Last dient unter anderem auch dazu, die NOx-Emission zu reduzieren, was allerdings zur Folge hat, daß die Kohlenwasserstoff-Emission (HC) ansteigt. Die NOx-Emission wird zusätzlich durch die Abgasrückführung reduziert. Die Folge sind allerdings eine leichte Verschlechterung des Kraftstoffverbrauchs der Brennkraftmaschine und der HC-Emission, sowie die Gefahr von Schwarzrauchbildung. Aus diesen Gründen wird die Abgasrückführung nur unterhalb einer bestimmten Last (Einspritzmenge pro Hub) durchgeführt.This opening of the drain channel always takes place below a certain load. For this reason, the outflowing fuel is used to control the exhaust gas recirculation, which should also be switched on below a certain load. This late start of spraying at low load is also used, among other things, to reduce NO x emissions, but this has the consequence that the hydrocarbon emission (HC) increases. The NO x emission is further reduced by the exhaust gas recirculation. However, the result is a slight deterioration in the fuel consumption of the internal combustion engine and HC emissions, and the risk of black smoke formation. For these reasons, exhaust gas recirculation is only carried out below a certain load (injection quantity per stroke).

Der Abflußkanal 44 ist über eine Abflußleitung 45 mit dem Kraftstoffbehälter 15 verbunden, wobei in dieser Abflußleitung ein Druckhalteventil 46 angeordnet ist. Stromauf dieses Druckhalteventils 46 ist mit der Abflußleitung 45 ein hydraulischer Stellmotor 47 eines pneumatischen 3/2-Wegeventils 48 verbunden. Das Wegeventil 48 steuert eine Unterdruckleitung 49, die von einem Abgasrückführventil 51 zu einer Unterdruckquelle 52 führt. Das in Schließrichtung durch eine Feder 53 belastete Abgasrückführventil 51 ist in einer Abgasrückführleitung 54 eines Motors 55 angeordnet, der über eine Einspritzleitung 56 vom Druckkanal 6 her mit Kraftstoff versorgt wird, der in der oben beschriebenen Art gefördert wird bei entsprechender Regelung der Menge und des Förderbeginns. Die Abflußleitung 45 weist einen Bypass 57 auf, in dem eine Staudrossel 58 angeordnet ist.The drain channel 44 is connected via a drain line 45 to the fuel tank 15, in which Drain line a pressure control valve 46 is arranged. Upstream of this pressure-maintaining valve 46, a hydraulic servomotor 47 of a pneumatic 3/2-way valve 48 is connected to the discharge line 45. The directional control valve 48 controls a vacuum line 49, which leads from an exhaust gas recirculation valve 51 to a vacuum source 52. The exhaust gas recirculation valve 51, which is loaded in the closing direction by a spring 53, is arranged in an exhaust gas recirculation line 54 of an engine 55, which is supplied with fuel via an injection line 56 from the pressure channel 6, which is delivered in the manner described above, with appropriate regulation of the quantity and the start of delivery . The drain line 45 has a bypass 57, in which a dam throttle 58 is arranged.

Die Abgasrückführsteuerung findet so statt, daß unterhalb einer bestimmten Last, bei der die Steuerbohrung 43 den Abflußkanal 44 aufsteuert, der dort aus dem Saugraum 8 und in die Abflußleitung 45 abfließende Kraftstoff dort durch die Staudrossel 58 gestaut wird bis ab Erreichen eines bestimmten Druckes das Druckhalteventil 46 öffnet und unter Halten dieses Abflußdruckes den Kraftstoff in den Kraftstoffbehälter 15 abströmen läßt. Kurz vor Erreichen dieses Abflußdruckes wird durch den hydraulischen Stellmotor 47 das pneumatische Wegeventil 48 geöffnet, so daß über die Unterdruckleitung 49 das Abgasrückführventil 51 durch die Unterdruckquelle 52 entgegen der Kraft der Schließfeder 53 geöffnet wird und Abgas über die Abgasrückführleitung 54 von der Abgasseite des Motors zur Saugseite strömen kann. Sobald dann bei Überschreiten des erforderlichen Lastzustandes durch die Regelmuffe 35 wieder der Abflußkanal 44 geschlossen wird, baut sich über die Staudrossel 58 der Abflußdruck in der Abflußleitung 45 wieder ab, so daß der hydraulische Stellmotor 47 das Wegeventil 48 und damit das Abgasrückführventil 51 sperrt.The exhaust gas recirculation control takes place in such a way that below a certain load, at which the control bore 43 opens the drain channel 44, the fuel flowing there out of the suction chamber 8 and into the drain line 45 is stowed there by the throttling throttle 58 until the pressure holding valve is reached after reaching a certain pressure 46 opens and allows the fuel to flow into the fuel tank 15 while maintaining this discharge pressure. Shortly before this discharge pressure is reached, the pneumatic directional valve 48 is opened by the hydraulic servomotor 47, so that the exhaust gas recirculation valve 51 is opened by the vacuum source 52 against the force of the closing spring 53 via the vacuum line 49 and exhaust gas by the exhaust gas recirculation line 54 from the exhaust side of the engine can flow to the suction side. As soon as the discharge channel 44 is closed again when the required load state is exceeded by the control sleeve 35, the discharge pressure in the discharge line 45 builds up again via the throttle throttle 58, so that the hydraulic servomotor 47 blocks the directional control valve 48 and thus the exhaust gas recirculation valve 51.

Claims (3)

  1. Exhaust-gas recirculation system for internal combustion engines, with an exhaust-gas recirculation valve (51) which is arranged in an exhaust-gas recirculation line (54) connecting an exhaust line of an internal combustion engine to an intake line of the internal combustion engine and is actuated by a pneumatic servomotor to which air from a vacuum source (52) can be fed as the actuating medium via a directional valve (48) having a servomotor (47); with a fuel injection system, in which, in a characteristic-map range for a minimum load and rotational speed, a hydraulic control pressure is available, this fuel injection system having a fuel injection pump in which a hydraulic control pressure which controls the variation in the beginning of delivery of the fuel injection pump is available as this hydraulic control pressure, this pressure being the pressure of fuel which is pumped by a feed pump (14) into a pressure space (8) of the fuel injection pump and with an outflow passage (45) of the pressure space (8), through which part of the fuel fed to the pressure space (8) flows off via a valve (35, 43) controlled as a function of load and rotational speed, and with a restrictor (58) which is arranged in the outflow passage (45) and upstream of which the servomotor (47) for controlling the directional valve (48) is connected to the outflow passage (45), the feed pump pumping fuel at a rotational speed-dependent pressure into the pressure space, characterized in that the feed pump (14) is driven by a drive shaft (2) of the fuel injection pump, and in that arranged in parallel with the restrictor (58) is a pressure-maintaining valve (46) via which the pressurized fluid flows off while a back pressure is maintained which is, at the same time, the actuating pressure for the servomotor of the directional valve (48).
  2. Exhaust-gas recirculation system with a fuel injection pump according to Claim 1, characterized in that as the valve controlled as a function of load and rotational speed use is made of a governor sleeve (35) which is displaceable by flyweight (34) counter to the force of a governor spring (37) with a prestress variable as a function of load and allows the control fluid to escape into an outflow passage (44) via a control hole (43).
  3. Exhaust-gas recirculation system according to Claim 2, characterized in that the fuel injection pump is a distributor-type injection pump, the pumping and distributing plunger (1) of which is rotationally adjustable relative to the drive shaft (2) by means of an injection adjustment device for varying the beginning of delivery, and in that this relative rotation is effected by means of a hydraulically actuated injection adjustment piston (22) which engages in a cam drive (3) arranged between the drive shaft (2) and the pumping and distributing plunger (1) and is acted upon by a fuel pressure present in the housing of the distributor-type injection pump, in a suction space (8), and controlled as a function of rotational speed.
EP88118278A 1987-12-03 1988-11-03 Exhaust gas recirculation device for internal combustion engines Expired - Lifetime EP0318714B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3740968A DE3740968C1 (en) 1987-12-03 1987-12-03 Exhaust gas recirculation device for internal combustion engines
DE3740968 1987-12-03

Publications (3)

Publication Number Publication Date
EP0318714A2 EP0318714A2 (en) 1989-06-07
EP0318714A3 EP0318714A3 (en) 1990-02-14
EP0318714B1 true EP0318714B1 (en) 1994-02-23

Family

ID=6341803

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88118278A Expired - Lifetime EP0318714B1 (en) 1987-12-03 1988-11-03 Exhaust gas recirculation device for internal combustion engines

Country Status (5)

Country Link
US (1) US4907560A (en)
EP (1) EP0318714B1 (en)
JP (1) JP2690335B2 (en)
KR (1) KR970003154B1 (en)
DE (2) DE3740968C1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2583895Y2 (en) * 1991-02-19 1998-10-27 三菱自動車工業株式会社 diesel engine
JPH05133286A (en) * 1991-11-12 1993-05-28 Nissan Motor Co Ltd Exhaust recirculation device for diesel engine
US5865156A (en) * 1997-12-03 1999-02-02 Caterpillar Inc. Actuator which uses fluctuating pressure from an oil pump that powers a hydraulically actuated fuel injector
US6050248A (en) * 1997-12-03 2000-04-18 Caterpillar Inc. Exhaust gas recirculation valve powered by pressure from an oil pump that powers a hydraulically actuated fuel injector
US6148805A (en) * 1998-12-15 2000-11-21 Caterpillar Inc. Engine with hydraulic fuel injection and EGR valve using a single high pressure pump

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2855027A1 (en) * 1976-12-22 1980-07-10 Bosch Gmbh Robert DEVICE FOR ACTUATING AN ACTUATING ELEMENT IN A COMBUSTION ENGINE ON AN EXHAUST GAS RECIRCULATION CONTROL DEVICE
DE2658051A1 (en) * 1976-12-22 1978-07-06 Bosch Gmbh Robert DEVICE FOR REGULATING THE COMPOSITION OF THE OPERATING MIXTURE OF A COMBUSTION MACHINE
DE2658052A1 (en) * 1976-12-22 1978-07-06 Bosch Gmbh Robert DEVICE FOR LOAD-DEPENDENT ACTIVATION OF A CONTROL ORGAN
GB1599648A (en) * 1977-12-01 1981-10-07 Lucas Industries Ltd Engine system including a diesel engine having exhaust gas recirculation
GB2031515B (en) * 1978-10-12 1982-12-08 Lucas Industries Ltd Compression ignition engine with exhaust gas recirculation
JPS5627058A (en) * 1979-08-13 1981-03-16 Toyota Motor Corp Exhaust gas recycling controller in internal combustion engine
DE2904906A1 (en) * 1979-02-09 1980-08-14 Bosch Gmbh Robert DEVICE FOR REGULATING THE COMPOSITION OF THE OPERATING MIXTURE PUT INTO THE COMBUSTION ROOM OF AN INTERNAL COMBUSTION ENGINE
JPS5656958A (en) * 1979-10-17 1981-05-19 Nippon Soken Inc Exhaust gas recycling method and device for diesel engine
DE2946557A1 (en) * 1979-11-17 1981-05-27 Robert Bosch Gmbh, 7000 Stuttgart DEVICE FOR CONTROLLING AN EXHAUST GAS RECIRCULATION DEVICE IN INTERNAL COMBUSTION ENGINES
JPS57137644A (en) * 1981-02-19 1982-08-25 Mazda Motor Corp Exhaust gas recirculation device for diesel engine
US4373496A (en) * 1981-04-01 1983-02-15 Robert Bosch Gmbh Apparatus for controlling an exhaust recirculation device in internal combustion engines
DE3135234A1 (en) * 1981-09-05 1983-03-17 Robert Bosch Gmbh, 7000 Stuttgart DEVICE FOR THE LOAD-RELATED OPERATION OF AN ACTUATOR OF AN INTERNAL COMBUSTION ENGINE
DE3138606A1 (en) * 1981-09-29 1983-04-14 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
JPS5956338A (en) * 1982-09-27 1984-03-31 沖電気工業株式会社 Method of cutting fuse
DE3612068A1 (en) * 1986-04-10 1987-10-15 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES WITH EXHAUST GAS RECIRCULATION

Also Published As

Publication number Publication date
KR970003154B1 (en) 1997-03-14
KR890010409A (en) 1989-08-08
EP0318714A3 (en) 1990-02-14
DE3887966D1 (en) 1994-03-31
JP2690335B2 (en) 1997-12-10
DE3740968C1 (en) 1988-12-15
US4907560A (en) 1990-03-13
EP0318714A2 (en) 1989-06-07
JPH025750A (en) 1990-01-10

Similar Documents

Publication Publication Date Title
EP0455762B1 (en) Electro-hydraulic control device for an internal-combustion engine valve
DE2503346C2 (en) Fuel distributor injection pump for internal combustion engines
DE3001155A1 (en) FUEL INJECTION SYSTEM FOR SELF-IGNITIONING INTERNAL COMBUSTION ENGINE
DE2115169A1 (en) Fuel injection device for internal combustion engines with compression ignition
EP1446559A1 (en) Device for the control of at least one gas exchange valve
DE1258187B (en) Fuel injection pump for internal combustion engines
EP0281580B1 (en) Fuel injection device for a diesel engine
DE3416392C2 (en)
EP0319707B1 (en) Fuel injection pump for internal-combustion engines, particularly for diesel engines
EP0318714B1 (en) Exhaust gas recirculation device for internal combustion engines
EP0273225B1 (en) Fuel injection pump for internal-combustion engines
DE3121108C2 (en)
DE4310457A1 (en) Fuel injection pump for internal combustion engines
EP0168586B1 (en) Fuel injection pump
DE2240289A1 (en) FUEL INJECTION DEVICE
DE3026896C2 (en)
DE1224987B (en) Fuel injection pump for internal combustion engines
DE3612700A1 (en) FUEL FEEDING SYSTEM FOR A TURBOCHARGED MACHINE WITH INTERNAL COMBUSTION
EP0354399B1 (en) Fuel injection pump for internal-combustion engines
EP0341243B1 (en) Fuel injection pumps for internal combustion engines
WO1991002897A1 (en) Fuel injection pump for internal combustion engines
DE2448693C2 (en) Speed controller for a distributor injection pump
DE3644148A1 (en) FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3704580A1 (en) FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
EP0461211B1 (en) Fuel injection pump

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19900703

17Q First examination report despatched

Effective date: 19910117

RAP3 Party data changed (applicant data changed or rights of an application transferred)

Owner name: ROBERT BOSCH GMBH

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19940218

REF Corresponds to:

Ref document number: 3887966

Country of ref document: DE

Date of ref document: 19940331

ET Fr: translation filed
ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20011227

Year of fee payment: 14

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20021023

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20021123

Year of fee payment: 15

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20031103

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20031103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040730

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051103