EP0080113A1 - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines Download PDF

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Publication number
EP0080113A1
EP0080113A1 EP82110388A EP82110388A EP0080113A1 EP 0080113 A1 EP0080113 A1 EP 0080113A1 EP 82110388 A EP82110388 A EP 82110388A EP 82110388 A EP82110388 A EP 82110388A EP 0080113 A1 EP0080113 A1 EP 0080113A1
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EP
European Patent Office
Prior art keywords
pressure
injection pump
fuel injection
control
space
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
EP82110388A
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German (de)
French (fr)
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EP0080113B1 (en
Inventor
Franz Eheim
Gerald Höfer
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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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/447—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means specially adapted to limit fuel delivery or to supply excess of fuel temporarily, e.g. for starting of the engine
    • 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
    • F02D1/06—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 by means dependent on pressure of engine working fluid
    • F02D1/065—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 by means dependent on pressure of engine working fluid of intake of air
    • 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
    • F02D1/12—Transmission of control impulse to pump control, e.g. with power drive or power assistance non-mechanical, e.g. hydraulic

Definitions

  • the invention is based on a fuel injection pump according to the preamble of the main claim.
  • an injection pump of this type known from DE-PS 19 12 919
  • the full-load injection quantity is limited with the aid of an adjustable stop which, designed as an angle lever, scans a contour on an adjusting piston which, depending on the speed-dependent fuel pressure in the suction space of the injection pump, is adjustable against a spring .
  • an adjustable stop which, designed as an angle lever, scans a contour on an adjusting piston which, depending on the speed-dependent fuel pressure in the suction space of the injection pump, is adjustable against a spring .
  • only a speed-dependent adjustment of the full-load injection quantity is possible.
  • Other operating parameters of the internal combustion engine cannot be taken into account.
  • the full-load injection quantity is limited with the aid of an adjustable stop which, depending on the pressure of the air supplied to the combustion chambers of the internal combustion engine, for. B. from boost pressure in supercharged internal combustion engines is adjustable.
  • a pressure cell exposed to the boost pressure displaces a control piston provided with a contour on the lateral surface, the contour of which is mechanically scanned.
  • Such a boost pressure-dependent correction of the injection quantity has the disadvantage that it can only follow the dynamic changes in the load relatively slowly, particularly in the case of devices operated with exhaust gas for air compression of the intake air, since the change in the exhaust gas volume follows a change in the fuel quantity only with delay. If the quantity adjustment element that comes into contact with the stopper is exposed to high forces, high frictional forces occur when the stopper is adjusted, which leads to a pronounced hysteresis behavior when setting the full load. This behavior is all the more disadvantageous in the case of injection with charge pressure-dependent adjustment, since setting errors increase considerably with increasing engine speed and load. The reason for this is that the charging characteristics, delivery pressure as a function of the load, become ever flatter with increasing speed and include increasingly small angles with the adjustment characteristic resulting from the requirements of the internal combustion engine, adjustment quantity via boost pressure.
  • a space cam which determines the position of the full load stop, is shifted on the one hand by the speed-dependent suction chamber pressure of the injection pump and, on the other hand, rotated depending on the boost pressure.
  • a pressure cell acted upon by the boost pressure is used as an actuator and the space curve on the space cam is mechanically scanned and transferred to the full load stop.
  • This also has the disadvantage that hysteresis errors occur in particular during the scanning when the control spring forces are transmitted to the space cam via the scanning device.
  • the torque that can be applied from the control box shown there is
  • Means must be provided which further increase the actuating force.
  • the actuating device according to the invention with the characterizing features of the main claim has the advantage that, depending on the operating parameters of the internal combustion engine, in particular the density of the air supplied to the internal combustion engine, a pressure is modulated which influences the adjustment of the adjusting piston. The forces required to modulate a pressure are then no longer dependent on the forces which occur when the actuating piston is mechanically scanned.
  • the z. B. existing from pressure sockets control signal transmitters have relatively small dimensions. With these, actuating forces are generated without great expenditure of energy, which easily overcome the friction on the actuating piston without the risk of excessive hysteresis.
  • the device is suitable for injection pumps in which the forces transmitted to the actuating piston are already kept very low during the mechanical scanning of the contour, because, for. B. not the entire force of the control spring arrangement acts on the actuating piston.
  • Fig. 1 shows a first embodiment of an adjustment of the actuating piston with a pressure control valve which is adjusted directly by a pressure transducer
  • Fig. 2 a variant of the embodiment according to Fig. * 1 in which the pressure transducer changes the bias force acting on the spool return spring .
  • the z. B. can be a distributor injection pump.
  • the latter has a fuel quantity adjusting element 2 designed as a lever, which actuates a ring slide (not shown) to control the fuel injection quantity. It is at full load, possibly with the interposition of an angle lever 3, against an adjustable stop 5 which is guided in the form of a tracer pin in a bore 8 and projects at right angles into a cylinder 9 arranged in the housing.
  • An actuating piston 11 is guided in this and encloses a working space 14 on its one end face 12 in the cylinder 9.
  • this is constantly connected via a throttle bore 16 located on the end face 15 of the cylinder 9 to a space which is filled with pressure medium, the pressure of which is controlled as a function of the speed.
  • this space is the fuel-filled suction space 17 of the fuel injection pump, the fuel being supplied by a fuel pump 18, which draws fuel from a fuel reservoir 19 and whose delivery side can be relieved via a pressure control valve 20.
  • This arrangement results in a speed-dependent pressure in the suction chamber 17 in a known manner.
  • the actuating piston 11 has a contour 21 on its outer surface by which the position of the stylus is determined when the actuating piston is displaced.
  • the rear side 22 of the actuating piston 11 encloses a pressure chamber 23 in the cylinder 9, in which a return spring 24 is arranged which acts on the rear side 22 of the actuating piston 11.
  • a pressure line 25 leads from the pressure chamber 23 and opens into a cylinder bore 27.
  • a control slide 28 is slidably arranged, which has an annular groove 29 in the region of the confluence of the pressure line 25. This is so long that, taking into account the displaceability of the control slide 28, the pressure line 25 remains in constant connection with the annular groove 29.
  • the control slide in the cylinder bore 27 closes a space 31 which relieves pressure via a relief line 32 and in which a compression spring 33 acting on the first end face 30 is clamped.
  • the cylinder bore 27 opens at the end opposite the space 31 into a relief space 34 of larger diameter, so that a control edge 35 forms at the transition from the cylinder bore 27 to the relief space 34.
  • a relief line 32 ', z. B. to the suction side of the feed pump 18.
  • a recess 37 is formed in the lateral surface, which is substantially triangular and extends from the annular groove 29.
  • the tip of the recess 37 points in the direction of the relief chamber 34 and comes into overlap if the control slide 28 is deflected accordingly the control edge 35.
  • a more or less large outflow cross-section 39 is released between the boundary edge of the recess 37 and the control edge 35, as shown in dashed lines in the drawing.
  • an adjusting pin 40 projects into the relief space 34 from the opposite side, which can be actuated by an actuating device 41 and comes to rest on the other end face 38 of the control slide 28.
  • the actuating device 41 consists of an actuating membrane 42 to which the actuating pin 40 is articulated and which separates a control pressure chamber 43 from a reference pressure chamber 44.
  • the reference pressure space can either be the atmospheric pressure or a constant pressure, e.g. B. the vacuum in a barometer box.
  • the control pressure in the control pressure chamber is the pressure that determines the density of the air supplied to the combustion chambers of the internal combustion engine. This can e.g. B. the boost pressure or, in the case of uncharged internal combustion engines, the ambient pressure, in accordance with which the control slide is displaced and the outflow cross-section 39 is changed.
  • the unit actuator 41 with control slide 28 thus represents a pressure control valve 45, with the aid of which the pressure in the pressure chamber 23 is controlled as a function of operating parameters, in particular the boost pressure or the air pressure.
  • the pressure source 46 for providing the outlet pressure is connected to the pressure line 25 via a connecting line 47, in which a decoupling throttle 48 is arranged. By draining pressure medium downstream of the decoupling throttle With the help of the pressure control valve 45, a pressure can be set which is lower than the outlet pressure of the pressure source 46.
  • the pressure source 46 in the example shown is realized in that a fuel line 49 branches off from the suction chamber 17, in which a second throttle 50 is arranged and which leads to the decoupling throttle 48. Between the decoupling throttle 48 and the second throttle 50, a relief line 51 branches off from the fuel line, a pressure relief valve 52 being arranged in the relief line 51. This has the effect that a constant pressure prevails in the area between the decoupling throttle 48 and the second throttle 50, provided that the pressure supply from the suction space 17 is sufficient.
  • the speed-dependent pressure is built up in the working space 14 when the internal combustion engine starts operating, so that the actuating piston 11 is deflected in accordance with this pressure against the force of the return spring 24.
  • the stylus 5 is shifted according to the contour 21.
  • a hydraulic pressure acts on the rear side 22, which is determined by the pressure control valve 45 and counteracts the pressure in the working space 14.
  • This pressure quasi limits the deflectability of the actuating piston 11, so that the actuating piston 11 is adjustable depending on the speed, but at most only within the limits given by the boost pressure.
  • the high working capacity of the suction chamber pressure can be used for the adjustment of the full load stop, the resulting signal pressure being modified with little energy expenditure.
  • the pressure control valve 45 ' according to FIG. 2 shows a variant of the pressure control valve 45 according to FIG. 2.
  • the control slide 28 encloses a space 31 in the cylinder bore 27 with its one end face 30, which is now directly connected to the pressure line 25 and in which the input pressure prevails.
  • the spring returning the control slide 28 against this pressure is now arranged as a control spring 53 in the relief chamber 34 and acts on the other end face 38 of the control slide 28.
  • the control spring 53 is supported on the end of an adjusting pin 40 'provided with a spring plate 54, which, as in FIG first executed example of an actuating membrane 42 is adjustable.
  • the moving mass acting on the actuating diaphragm 42 and the influence of frictional forces are lower, so that a lower hysteresis behavior when controlling the pressure in the pressure chamber 24 is to be expected here.

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

Abstract

Es wird eine Kraftstoffeinspritzpumpe vorgeschlagen, deren Mengenverstellglied eine Wegbegrenzung in Form eines verstellbaren Anschlags (5) aufweist, der entsprechend der Verschiebung eines Stellkolbens (11) gemäß einer diesem aufgeprägten Kontur (21) eingestellt wird. Die Verschiebung des Stellkolbens erfolgt mit dem drehzahlabhängigen Druck des Saugraumes (17) entgegen der Kraft einer Rückstellfeder (24) und entgegen einem mit Hilfe eines Drucksteuerventils (45) entsprechend Betriebsparametern einstellbaren Druck. Damit erfolgt die Verstellung des Anschlags mit dem hohen Arbeitsvermögen des Saugraumdrucks, wobei die Begrenzung der Verstellung mit Hilfe des vom Saugraumdruck abgezweigten, modulierten Drucks erzielt wird.A fuel injection pump is proposed, the quantity adjustment element of which has a travel limitation in the form of an adjustable stop (5), which is adjusted according to the displacement of an actuating piston (11) according to a contour (21) impressed on it. The control piston is displaced with the speed-dependent pressure of the suction chamber (17) against the force of a return spring (24) and against a pressure that can be adjusted with the aid of a pressure control valve (45) according to operating parameters. The stop is thus adjusted with the high working capacity of the suction chamber pressure, the limitation of the adjustment being achieved with the aid of the modulated pressure diverted from the suction chamber pressure.

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzpumpe nach der Gattung des Hauptanspruchs aus. Bei einer durch die DE-PS 19 12 919 bekannten Einspritzpumpe dieser Art wird die Vollasteinspritzmenge mit Hilfe eines verstellbaren Anschlags begrenzt, der als Winkelhebel ausgestaltet eine Kontur an einem Verstellkolben abtastet, welcher in Abängigkeit vom drehzahlabhängigen Kraftstoffdruck im Saugraum der Einspritzpumpe gegen eine Feder verstellbar ist. Bei dieser Ausgestaltung ist lediglich eine drehzahlabhängige Angleichung der Vollasteinspritzmenge möglich. Weitere Betriebsparameter der Brennkraftmaschine können nicht berücksichtigt werden.The invention is based on a fuel injection pump according to the preamble of the main claim. In an injection pump of this type known from DE-PS 19 12 919, the full-load injection quantity is limited with the aid of an adjustable stop which, designed as an angle lever, scans a contour on an adjusting piston which, depending on the speed-dependent fuel pressure in the suction space of the injection pump, is adjustable against a spring . In this embodiment, only a speed-dependent adjustment of the full-load injection quantity is possible. Other operating parameters of the internal combustion engine cannot be taken into account.

Bei einer anderen durch die DE-OS 28 54 422 bekannten Einspritzpumpe wird die Vollasteinspritzmenge mit Hilfe eines verstellbaren Anschlags begrenzt, der in Abhängigkeit von dem Druck der den Brennräumen der Brennkraftmaschine zugeführten Luft, z. B. vom Ladedruck bei aufgeladenen Brennkraftmaschinen, verstellbar ist. Dazu verschiebt eine dem Ladedruck ausgesetzte Druckdose einen mit einer Kontur an der Mantelfläche versehenen Stellkolben, dessen Kontur mechanisch abgetastet wird.In another injection pump known from DE-OS 28 54 422, the full-load injection quantity is limited with the aid of an adjustable stop which, depending on the pressure of the air supplied to the combustion chambers of the internal combustion engine, for. B. from boost pressure in supercharged internal combustion engines is adjustable. For this purpose, a pressure cell exposed to the boost pressure displaces a control piston provided with a contour on the lateral surface, the contour of which is mechanically scanned.

Eine solche ladedruckabhängige Korrektur der Einspritzmenge hat den Nachteil, daß sie den dynamischen Änderungen der Last nur relativ langsam folgen kann, insbesondere bei mit Abgas betriebenen Einrichtungen zur Luftverdichtung der Ansaugluft, da die Abgasvolumenänderung nur verzögernd einer Kraftstoffmengenänderung folgt. Ist das Mengenverstellorgan, das auf den Anschlag zur Anlage kommt, hohen Kräften ausgesetzt, so treten bei der Verstellung des Anschlags hohe Reibungskräfte auf, was zu einem ausgeprägten Hystereseverhalten bei der Vollasteinstellung führt. Dieses Verhalten ist bei Einspritzung mit ladedruckabhängiger Angleichung umso nachteiliger als sich Einstellfehler bei zunehmender Drehzahl und Last ganz beträchtlich verstärken. Der Grund dafür liegt darin, daß die Laderkennlinien, Förderdruck in Abhängigkeit von der Last, mit steigender Drehzahl immer flacher werden und mit der sich aus den Erfordernissen der Brennkraftmaschine ergebenden Angleichkennlinie, Angleichmenge über Ladedruck, zunehmend kleiner Winkel einschließen.Such a boost pressure-dependent correction of the injection quantity has the disadvantage that it can only follow the dynamic changes in the load relatively slowly, particularly in the case of devices operated with exhaust gas for air compression of the intake air, since the change in the exhaust gas volume follows a change in the fuel quantity only with delay. If the quantity adjustment element that comes into contact with the stopper is exposed to high forces, high frictional forces occur when the stopper is adjusted, which leads to a pronounced hysteresis behavior when setting the full load. This behavior is all the more disadvantageous in the case of injection with charge pressure-dependent adjustment, since setting errors increase considerably with increasing engine speed and load. The reason for this is that the charging characteristics, delivery pressure as a function of the load, become ever flatter with increasing speed and include increasingly small angles with the adjustment characteristic resulting from the requirements of the internal combustion engine, adjustment quantity via boost pressure.

Bei der durch die DE-OS 28 47 572 bekannten Kraftstoffeinspritzpumpe wird ein Raumnocken, der die Lage des Vollastanschlags bestimmt, einerseits durch den drehzahlabhängigen Saugraumdruck der Einspritzpumpe verschoben und andererseits in Abhängigkeit vom Ladedruck verdreht. Dabei wird eine vom Ladedruck beaufschlagte Druckdose als Stellglied verwendet und die Raumkurve auf dem Raumnocken mechanisch abgetastet und auf den Vollastanschlag übertragen. Dies hat ebenfalls den Nachteil, daß durch die Reibung bei der Abtastung Hysteresefehler insbesondere dann auftreten, wenn die Regelfederkräfte über die Abtastvorrichtung auf den Raumnocken übertragen werden. Ferner ist das von der dort gezeigten Stelldose aufbringbare Drehmoment beiIn the fuel injection pump known from DE-OS 28 47 572, a space cam, which determines the position of the full load stop, is shifted on the one hand by the speed-dependent suction chamber pressure of the injection pump and, on the other hand, rotated depending on the boost pressure. In this case, a pressure cell acted upon by the boost pressure is used as an actuator and the space curve on the space cam is mechanically scanned and transferred to the full load stop. This also has the disadvantage that hysteresis errors occur in particular during the scanning when the control spring forces are transmitted to the space cam via the scanning device. Furthermore, the torque that can be applied from the control box shown there is

vertretbaren Abmessungen nur gering. Es müssen Mittel vorgesehen werden, die die Stellkraft noch weiter verstärken.justifiable dimensions. Means must be provided which further increase the actuating force.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Stelleinrichtung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß in Abhängigkeit von Betriebsparametern der Brennkraftmaschine, insbesondere von der Dichte der der Brennkraftmaschine zugeführten Luft ein Druck moduliert wird, der die Verstellung des Verstellkolbens beeinflußt. Die zur Modulation eines Drucks benötigten Kräfte sind dann nicht mehr abhängig von den Kräften, die bei der mechanischen Abtastung des Stellkolbens auftreten. Somit kann der z. B. aus Druckdosen bestehende Steuersignalgeber relativ kleine Abmessungen besitzen. Mit diesen werden ohne großen Energieaufwand Stellkräfte erzeugt, die die Reibung an dem Stellkolben leicht überwinden, ohne daß die Gefahr einer zu großen Hysterese auftritt. Insbesondere ist die Einrichtung für Einspritzpumpen geeignet, bei denen die auf den Stellkolben übertragenen Kräfte bei der mechanischen Abtastung der Kontur bereits sehr gering gehalten werden, weil z. B. nicht die gesamte Kraft der Regelfederanordnung auf den Stellkolben wirkt.The actuating device according to the invention with the characterizing features of the main claim has the advantage that, depending on the operating parameters of the internal combustion engine, in particular the density of the air supplied to the internal combustion engine, a pressure is modulated which influences the adjustment of the adjusting piston. The forces required to modulate a pressure are then no longer dependent on the forces which occur when the actuating piston is mechanically scanned. Thus, the z. B. existing from pressure sockets control signal transmitters have relatively small dimensions. With these, actuating forces are generated without great expenditure of energy, which easily overcome the friction on the actuating piston without the risk of excessive hysteresis. In particular, the device is suitable for injection pumps in which the forces transmitted to the actuating piston are already kept very low during the mechanical scanning of the contour, because, for. B. not the entire force of the control spring arrangement acts on the actuating piston.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Lösung gekennzeichnet,Advantageous further developments and improvements of the solution specified in the main claim are characterized by the measures listed in the subclaims,

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden in der nachfolgenden Beschreibung näher erläutert. Es zeigen Fig. 1 ein erstes Ausführungsbeispiel einer Verstelleinrichtung des Stellkolbens mit einem Drucksteuerventil, das unmittelbar durch einen Druckgeber verstellt wird und Fig. 2 eine Variante zum Ausführungsbeispiel nach Fig.*1, bei dem der Druckgeber die Vorspannung einer auf den Steuerschieber wirkenden Rückstellfeder verändert.Two embodiments of the invention are shown in the drawing and are described in the following description exercise explained in more detail. In the drawings Fig. 1 shows a first embodiment of an adjustment of the actuating piston with a pressure control valve which is adjusted directly by a pressure transducer, and Fig. 2 a variant of the embodiment according to Fig. * 1 in which the pressure transducer changes the bias force acting on the spool return spring .

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Fig. 1 ist ein Teil einer Kraftstoffeinspritzpumpe dargestellt, die z. B. eine Verteilereinspritzpumpe sein kann. Diese weist in bekannter Weise ein als Hebel ausgestaltetes Kraftstoffmengenverstellglied 2 auf, das einen nicht weiter gezeichneten Ringschieber zur Steuerung der Kraftstoffeinspritzmenge betätigt. Es liegt bei Vollaststellung, ggf. unter Zwischenschaltung eines Winkelhebels 3, an einen verstellbaren Anschlag 5, der in Form eines Abtaststiftes in einer Bohrung 8 geführt ist und rechtwinklig in einen im Gehäuse angeordneten Zylinder 9 hineinragt. In diesem ist ein Stellkolben 11 geführt, der auf seiner einen Stirnseite 12 in dem Zylinder 9 einen Arbeitsraum 14 einschließt. Dieser ist über einen an der Stirnseite 15 des Zylinders 9 befindliche Drosselbohrung 16 ständig mit einem Raum verbunden, der mit Druckmittel gefüllt ist, dessen Druck drehzahlabhängig gesteuert wird. Dieser Raum ist im ausgeführten Beispiel der mit Kraftstoff gefüllte Saugraum 17 der Kraftstoffeinspritzpumpe, wobei die Versorgung mit Kraftstoff durch eine Kraftstoffpumpe 18 erfolgt, die aus einem Kraftstoffvorratsbehälter 19 Kraftstoff ansaugt und deren Förderseite über ein Drucksteuerventil 20 entlastbar ist. Durch diese Anordnung stellt sich in bekannter Weise im Saugraum 17 ein drehzahlabhängiger Druck ein.In Fig. 1, a part of a fuel injection pump is shown, the z. B. can be a distributor injection pump. In a known manner, the latter has a fuel quantity adjusting element 2 designed as a lever, which actuates a ring slide (not shown) to control the fuel injection quantity. It is at full load, possibly with the interposition of an angle lever 3, against an adjustable stop 5 which is guided in the form of a tracer pin in a bore 8 and projects at right angles into a cylinder 9 arranged in the housing. An actuating piston 11 is guided in this and encloses a working space 14 on its one end face 12 in the cylinder 9. This is constantly connected via a throttle bore 16 located on the end face 15 of the cylinder 9 to a space which is filled with pressure medium, the pressure of which is controlled as a function of the speed. In the example shown, this space is the fuel-filled suction space 17 of the fuel injection pump, the fuel being supplied by a fuel pump 18, which draws fuel from a fuel reservoir 19 and whose delivery side can be relieved via a pressure control valve 20. This arrangement results in a speed-dependent pressure in the suction chamber 17 in a known manner.

Der Stellkolben 11 weist im Bereich des Eindringens des Abtaststiftes 5 in den Zylinder 9 an seiner Mantelfläche eine Kontur 21 auf, durch die die Stellung des Abtaststiftes bei Verschieben des Stellkolbens bestimmt wird. Die Rückseite 22 des Stellkolbens 11 schließt in Zylinder 9 einen Druckraum 23 ein, in dem eine Rückstellfeder 24 angeordnet ist, die die Rückseite 22 des Stellkolbens 11 beaufschlagt. Vom Druckraum 23 führt eine Druckleitung 25 ab, die in eine Zylinderbohrung 27 mündet. Dort ist ein Steuerschieber 28 verschiebbar angeordnet, der im Bereich der Einmündung der Druckleitung 25 eine Ringnut 29 aufweist. Diese ist dabei so lang, daß unter Berücksichtigung der Verschiebbarkeit des Steuerschiebers 28 die Druckleitung 25 ständig in Verbindung mit der Ringnut 29 bleibt. Mit der ersten Stirnseite 30 schließt der Steuerschieber in der Zylinderbohrung 27 einen Raum 31, der über eine Entlastungsleitung 32 entlastet und in den eine die erste Stirnseite 30 beaufschlagende Druckfeder 33 eingespannt ist.In the area of penetration of the stylus 5 into the cylinder 9, the actuating piston 11 has a contour 21 on its outer surface by which the position of the stylus is determined when the actuating piston is displaced. The rear side 22 of the actuating piston 11 encloses a pressure chamber 23 in the cylinder 9, in which a return spring 24 is arranged which acts on the rear side 22 of the actuating piston 11. A pressure line 25 leads from the pressure chamber 23 and opens into a cylinder bore 27. There, a control slide 28 is slidably arranged, which has an annular groove 29 in the region of the confluence of the pressure line 25. This is so long that, taking into account the displaceability of the control slide 28, the pressure line 25 remains in constant connection with the annular groove 29. With the first end face 30, the control slide in the cylinder bore 27 closes a space 31 which relieves pressure via a relief line 32 and in which a compression spring 33 acting on the first end face 30 is clamped.

Die Zylinderbohrung 27 mündet an dem dem Raum 31 gegenüber liegenden Ende in einen Entlastungsraum 34 größeren Durchmessers, so daß sich am Übergang von Zylinderbohrung 27 zum Entlastungsraum 34 eine Steuerkante 35 bildet. Vom Entlastungsraum 34 führt eine Entlastungsleitung 32' ab, z. B. zur Saugseite der Förderpumpe 18. An dem sich an die Ringnut 29 in Richtung Entlastungsraum 34 angrenzenden Kolbenteil 36 des Steuerschiebers 28 ist in der Mantelfläche eine Ausnehmung 37 eingeformt, die im wesentlichen dreieckig ist und von der Ringnut 29 ausgeht. Die Spitze der Ausnehmung 37 weist in der Richtung zum Entlastungsraum 34 und kommt bei entsprechender Auslenkung des Steuerschiebers 28 in Überdeckung mit der Steuerkante 35. An dieser Stelle wird je nach Auslenkung des Steuerschiebers 28 ein mehr oder weniger großer Abströmquerschnitt 39 zwischen der Begrenzungskante der Ausnehmung 37 und der Steuerkante 35 freigegeben, wie das gestrichelt in der Zeichnung dargestellt ist.The cylinder bore 27 opens at the end opposite the space 31 into a relief space 34 of larger diameter, so that a control edge 35 forms at the transition from the cylinder bore 27 to the relief space 34. From the relief space 34 leads a relief line 32 ', z. B. to the suction side of the feed pump 18. On the adjacent to the annular groove 29 in the direction of the relief chamber 34 piston part 36 of the spool 28, a recess 37 is formed in the lateral surface, which is substantially triangular and extends from the annular groove 29. The tip of the recess 37 points in the direction of the relief chamber 34 and comes into overlap if the control slide 28 is deflected accordingly the control edge 35. At this point, depending on the deflection of the control slide 28, a more or less large outflow cross-section 39 is released between the boundary edge of the recess 37 and the control edge 35, as shown in dashed lines in the drawing.

Koaxial zum Steuerschieber ragt in den Entlastungsraum 34 von der gegenüber liegenden Seite ein Stellstift 40 hinein, der von einer Stelleinrichtung 41 betätigbar ist und zur Anlage an der anderen Stirnseite 38 des Steuerschiebers 28 kommt. Die Stelleinrichtung 41 besteht im gezeigten Beispiel aus einer Stellmembran 42, an die der Stellstift 40 angelenkt ist und die einen Steuerdruckraum 43 von einem Referenzdruckraum 44 trennt. Der Referenzdruckraum kann dabei entweder der atmosphärische Druck sein oder ein konstanter Druck, z. B. das Vakuum in einer Barometerdose. Der Steuerdruck im Steuerdruckraum ist der Druck, der die Dichte der den Brennräumen der Brennkraftmaschine zugeführten Luft bestimmt. Dies kann z. B. der Ladedruck oder bei nicht aufgeladenen Brennkraftmaschinen der Umgebungsdruck sein, entsprechend dem der Steuerschieber verschoben und der Abströmquerschnitt 39 verändert wird.Coaxially to the control slide, an adjusting pin 40 projects into the relief space 34 from the opposite side, which can be actuated by an actuating device 41 and comes to rest on the other end face 38 of the control slide 28. In the example shown, the actuating device 41 consists of an actuating membrane 42 to which the actuating pin 40 is articulated and which separates a control pressure chamber 43 from a reference pressure chamber 44. The reference pressure space can either be the atmospheric pressure or a constant pressure, e.g. B. the vacuum in a barometer box. The control pressure in the control pressure chamber is the pressure that determines the density of the air supplied to the combustion chambers of the internal combustion engine. This can e.g. B. the boost pressure or, in the case of uncharged internal combustion engines, the ambient pressure, in accordance with which the control slide is displaced and the outflow cross-section 39 is changed.

Die Einheit Stelleinrichtung 41 mit Steuerschieber 28 stellt also ein Drucksteuerventil 45 dar, mit dessen Hilfe der Druck im Druckraum 23 in Abhängigkeit von Betriebsparametern, insbesondere vom Ladedruck oder vom Luftdruck, gesteuert wird. Die Druckquelle 46 zur Bereitstellung des Ausgangsdrucks ist mit der Druckleitung 25 über eine Verbindungsleitung 47 verbunden, in der eine Abkoppeldrossel 48 angeordnet ist. Durch Abströmenlassen von Druckmittel stromabwärts der Abkoppeldrossel kann mit Hilfe des Drucksteuerventils 45 ein Druck eingestellt werden, der kleiner ist als der Ausgangsdruck der Druckquelle 46.The unit actuator 41 with control slide 28 thus represents a pressure control valve 45, with the aid of which the pressure in the pressure chamber 23 is controlled as a function of operating parameters, in particular the boost pressure or the air pressure. The pressure source 46 for providing the outlet pressure is connected to the pressure line 25 via a connecting line 47, in which a decoupling throttle 48 is arranged. By draining pressure medium downstream of the decoupling throttle With the help of the pressure control valve 45, a pressure can be set which is lower than the outlet pressure of the pressure source 46.

Die Druckquelle 46 im ausgeführten Beispiel wird dadurch realisiert, daß von dem Saugraum 17 eine Kraftstoffleitung 49 abzweigt, in der eine zweite Drossel 50 angeordnet ist und die zur Abkoppeldrossel 48 führt. Zwischen Abkoppeldrossel 48 und zweiter Drossel 50 zweigt ferner eine Entlastungsleitung 51 von der Kraftstoffleitung ab, wobei in der Entlastungsleitung 51 ein Druckbegrenzungsventil 52 angeordnet ist. Dieses bewirkt, daß im Bereich zwischen Abkoppeldrossel 48 und zweiter Drossel 50 ein konstanter Druck herrscht, sofern die Druckversorgung von Saugraum 17 her ausreichend ist.The pressure source 46 in the example shown is realized in that a fuel line 49 branches off from the suction chamber 17, in which a second throttle 50 is arranged and which leads to the decoupling throttle 48. Between the decoupling throttle 48 and the second throttle 50, a relief line 51 branches off from the fuel line, a pressure relief valve 52 being arranged in the relief line 51. This has the effect that a constant pressure prevails in the area between the decoupling throttle 48 and the second throttle 50, provided that the pressure supply from the suction space 17 is sufficient.

Bei der beschriebenen Einrichtung wird bei Betriebsaufnahme der Brennkraftmaschine der drehzahlabhängige Druck in den Arbeistraum 14 aufgebaut, so daß der Stellkolben 11 entsprechend diesem Druck entgegen der Kraft der Rückstellfeder 24 ausgelenkt wird. Der Abtaststift 5 wird dabei entsprechend der Kontur 21 verschoben. Weiterhin wirkt jedoch auf die Rückseite 22 ein hydraulischer Druck, der durch das Drucksteuerventil 45 bestimmt ist und dem Druck im Arbeitsraum 14 entgegen wirkt. Dieser Druck begrenzt quasi die Auslenkbarkeit des Stellkolbens 11, so daß der Stellkolben 11 abhängig von der Drehzahl, maximal jedoch nur in den durch den Ladedruck gegebenen Grenzen, verstellbar ist. Es kann hier das hohe Arbeitsvermögen des Saugraumdrucks für die Verstellung des Vollastanschlages verwendet werden, wobei mit geringem Energieaufwand der resultierende Stelldruck modifiziert wird.In the device described, the speed-dependent pressure is built up in the working space 14 when the internal combustion engine starts operating, so that the actuating piston 11 is deflected in accordance with this pressure against the force of the return spring 24. The stylus 5 is shifted according to the contour 21. Furthermore, however, a hydraulic pressure acts on the rear side 22, which is determined by the pressure control valve 45 and counteracts the pressure in the working space 14. This pressure quasi limits the deflectability of the actuating piston 11, so that the actuating piston 11 is adjustable depending on the speed, but at most only within the limits given by the boost pressure. The high working capacity of the suction chamber pressure can be used for the adjustment of the full load stop, the resulting signal pressure being modified with little energy expenditure.

Eine Variante zum Drucksteuerventil 45 nach Fig. 1 zeigt das Drucksteuerventil 45' nach Fig. 2. Auch dort schließt der Steuerschieber 28 in der Zylinderbohrung 27 mit seiner einen Stirnseite 30 einen Raum 31 ein, der nun jedoch unmittelbar mit der Druckleitung 25 verbunden ist und in dem also der eingesteuerte Druck vorherrscht. Die den Steuerschieber 28 entgegen diesem Druck rückstellende Feder ist nun als Steuerfeder 53 im Entlastungsraum 34 angeordnet und beaufschlagt die andere Stirnseite 38 des Steuerschiebers 28. Die Steuerfeder 53 stützt sich dabei an dem mit einem Federteller 54 versehenen Ende eines Stellstifts 40', der wie im ersten ausgeführten Beispiel von einer Stellmembran 42 verstellbar ist.The pressure control valve 45 'according to FIG. 2 shows a variant of the pressure control valve 45 according to FIG. 2. Here too, the control slide 28 encloses a space 31 in the cylinder bore 27 with its one end face 30, which is now directly connected to the pressure line 25 and in which the input pressure prevails. The spring returning the control slide 28 against this pressure is now arranged as a control spring 53 in the relief chamber 34 and acts on the other end face 38 of the control slide 28. The control spring 53 is supported on the end of an adjusting pin 40 'provided with a spring plate 54, which, as in FIG first executed example of an actuating membrane 42 is adjustable.

Bei dieser Ausgestaltung ist die auf die Stellmembran 42 wirkende bewegte Masse und der Einfluß von Reibungskräften geringer, so daß hier mit einem geringeren Hystereseverhalten beim Steuern des Drucks im Druckraum 24 zu rechnen ist.In this embodiment, the moving mass acting on the actuating diaphragm 42 and the influence of frictional forces are lower, so that a lower hysteresis behavior when controlling the pressure in the pressure chamber 24 is to be expected here.

Claims (7)

1. Kraftstoffeinspritzpumpe für Brennkraftmaschinen mit einem Kraftstoffmengenverstellglied und einer diesem zugeordnetem Einrichtung zur Veränderung des möglichen Weges des Mengenverstellgliedes bestehend aus einer Verstelleinrichtung, die einen entgegen einer Rückstellfeder verstellbaren Stellkolben aufweist, entsprechend dessen Stellung mittels einer Übertragungseinrichtung der mögliche Weg des Mengenverstellgliedes veränderbar ist, wobei der Stellkolben einen Arbeitsraum begrenzt, der mit einer Druckquelle verbindbar ist, dessen Druck abhängig von der Drehzahl der Kraftstoffeinspritzpumpe verändert wird, dadurch gekennzeichnet, daß die andere, dem Arbeitsraum (14) abgewandte Stirnseite (22) des Stellkolbens (11) einen Druckraum (23) begrenzt, der in Unterstützung der Rückstellfeder (24) von einem in Abhängigkeit von Betriebsparametern der Brennkraftmaschine, insbesondere von der Dichte der den Brennräumen der Brennkraftmaschine zugeführten Luft, steuerbaren Druck beaufschlagt ist.1.Fuel injection pump for internal combustion engines with a fuel quantity adjusting element and a device associated therewith for changing the possible path of the quantity adjusting element consisting of an adjusting device which has an adjusting piston which is adjustable against a return spring, the position of the quantity adjusting element being changeable according to its position by means of a transmission device, the Adjusting piston delimits a working space that can be connected to a pressure source, the pressure of which is changed depending on the speed of the fuel injection pump, characterized in that the other end face (22) of the adjusting piston (11) facing away from the working space (14) has a pressure space (23) limited, which, in support of the return spring (24), is acted upon by a pressure which is controllable as a function of operating parameters of the internal combustion engine, in particular of the density of the air supplied to the combustion chambers of the internal combustion engine. 2. Kraftstoffeinspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß der Druckraum (23) über eine Abkoppeldrossel (48) mit einer Druckquelle (17; 46) und zudem über ein Drucksteuerventil (45, 45') mit einem Entlastungsraum (34) verbindbar ist, wobei die Steuerkraft des Drucksteuerventils abhängig von Betriebsparametern ist.2. Fuel injection pump according to claim 1, characterized in that the pressure chamber (23) via a decoupling throttle (48) with a pressure source (17; 46) and also via a pressure control valve (45, 45 ') with a relief chamber (34) can be connected, the control force of the pressure control valve being dependent on operating parameters. 3. Kraftstoffeinspritzpumpe nach Anspruch 2, dadurch gekennzeichnet, daß das Drucksteuerventil einen Steuerschieber (28) aufweist, der von einem Stellglied (42, 40, 40') in Abhängigkeit von Betriebsparametern entgegen der Kraft einer Rückstellfeder (33, 53) verschiebbar ist und dabei einen Abströmquerschnitt (39) steuert.3. Fuel injection pump according to claim 2, characterized in that the pressure control valve has a control slide (28) which is displaceable by an actuator (42, 40, 40 ') in dependence on operating parameters against the force of a return spring (33, 53) and thereby controls an outflow cross section (39). 4. Kraftstoffeinspritzpumpe nach Anspruch 2, dadurch gekennzeichnet, daß das Drucksteuerventil einen Steuerschieber (28) aufweist, der in einer Bohrung (27) dicht verschiebbar mit der einen, ersten Stirnseite (30) einen mit dem Druckraum (23) verbundenen Raum (31) einschließt und auf der anderen Stirnseite (38) von der Kraft einer Feder (53) belastet ist, deren Vorspannung abhängig von Betriebsparametern änderbar ist und an dem Steuerschieber eine Steuerkante (35) zugeordnet ist, die einem Abströmquerschnitt (39) steuert.4. Fuel injection pump according to claim 2, characterized in that the pressure control valve has a control slide (28) which is displaceably displaceable in a bore (27) with the one, first end face (30) a space (31) connected to the pressure space (23) encloses and is loaded on the other end face (38) by the force of a spring (53), the pretension of which can be changed depending on operating parameters and on the control slide a control edge (35) is assigned which controls an outflow cross section (39). 5. Kraftstoffeinspritzpumpe nach einem der vorstehenden Ansprüche 3 oder 4, dadurch gekennzeichnet, daß der Steuerschieber (28) eine Ringnut (29) aufweist, die ständig mit dem Druckraum (23) über eine Druckleitung (25) verbunden ist und deren eine Begrenzungskante (37) zusammen mit der Steuerkante (35) den Abströmquerschnitt (39) bildet.5. Fuel injection pump according to one of the preceding claims 3 or 4, characterized in that the control slide (28) has an annular groove (29) which is constantly connected to the pressure chamber (23) via a pressure line (25) and whose one boundary edge (37 ) forms the outflow cross section (39) together with the control edge (35). 6. Kraftstoffeinspritzpumpe nach Anspruch 5, dadurch gekennzeichnet, daß die Begrenzungskante eine von der Ringnut (28) an der Mantelfläche des Steuerschiebers abzweigende Ausnehmung (37) begrenzt, die mit einer am Übergang der Bohrung (27) in einen Entlastungsraum (34) mit größerem Durchmesser gebildete Steuerkante (35) zusammenarbeitet.6. A fuel injection pump according to claim 5, characterized in that the boundary edge delimits a recess (37) branching off from the annular groove (28) on the lateral surface of the control slide valve, which has a larger one at the transition of the bore (27) into a relief chamber (34) Diameter formed control edge (35) works together. 7. Kraftstoffeinspritzpumpe nach einem der vorstehenden Ansprüche 2 bis 6, dadurch gekennzeichnet, daß von der Druckquelle, von der der Arbeitsraum (14) mit Druck versorgt wird, eine Druckleitung (49) führt, in der eine zweite Drossel (50) und eine Abkoppeldrossel (48) in Reihe nacheinander angeordnet sind und zum Druckraum (23) führt und daß ferner von der Druckleitung (49) zwischen der zweiten Drossel (50) und der Abkoppeldrossel (48) eine Entlastungsleitung (51) abführt, die ein Druckbegrenzungsventil (52) enthält, durch das der Druck zwischen den beiden Drosseln auf einen konstanten Wert bei Betrieb der Kraftstoffeinspritzpumpe haltbar ist.7. Fuel injection pump according to one of the preceding claims 2 to 6, characterized in that from the pressure source from which the working space (14) is supplied with pressure, a pressure line (49) leads, in which a second throttle (50) and a decoupling throttle (48) are arranged in series one after the other and leads to the pressure chamber (23) and that furthermore, from the pressure line (49) between the second throttle (50) and the decoupling throttle (48), a relief line (51) leads away, which is a pressure relief valve (52) contains, by means of which the pressure between the two throttles can be maintained at a constant value during operation of the fuel injection pump.
EP82110388A 1981-11-24 1982-11-11 Fuel injection pump for internal combustion engines Expired EP0080113B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19813146499 DE3146499A1 (en) 1981-11-24 1981-11-24 FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3146499 1981-11-24

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EP0080113A1 true EP0080113A1 (en) 1983-06-01
EP0080113B1 EP0080113B1 (en) 1986-03-12

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EP (1) EP0080113B1 (en)
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DE (2) DE3146499A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0204117A1 (en) * 1985-05-18 1986-12-10 Robert Bosch Gmbh Fuel injection pump for internal-combustion engines
FR2592917A1 (en) * 1986-01-16 1987-07-17 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES WHERE THE ADJUSTMENT PISTON IS MOVED ACCORDING TO THE PRESSURE.
WO1990015233A1 (en) * 1989-06-10 1990-12-13 Robert Bosch Gmbh Fuel injection pump for internal combustion engines

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5958146A (en) * 1982-09-24 1984-04-03 Diesel Kiki Co Ltd Device for compensating fuel injection volume of fuel injection pump of distributing type
JPS5958147A (en) * 1982-09-24 1984-04-03 Diesel Kiki Co Ltd Device for compensating fuel injection amount of fuel injection pump of distributing type
DE3506041A1 (en) * 1985-02-21 1986-08-21 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3609758A1 (en) * 1986-03-22 1987-09-24 Bosch Gmbh Robert METHOD FOR CONTROLLING THE MAXIMUM FUEL INJECTION AMOUNT IN FUEL INJECTION PUMPS FOR INTERNAL COMBUSTION ENGINES
DE3709366A1 (en) * 1987-03-21 1988-09-29 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE19728110A1 (en) * 1997-07-02 1999-01-07 Bosch Gmbh Robert Fuel injection pump for internal combustion engines

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH194671A (en) * 1936-09-30 1937-12-15 Scintilla Ag Control device on fuel injection pumps of internal combustion engines.
DE941879C (en) * 1941-09-12 1956-04-19 Daimler Benz Ag With a pressure medium, in particular a special fluid circuit, e.g. Lubricating oil, working control device for injection pumps of internal combustion engines
DE1912919A1 (en) * 1969-03-14 1970-09-24 Bosch Gmbh Robert Speed regulator for fuel injection pump
GB2034814A (en) * 1978-11-02 1980-06-11 Bosch Gmbh Robert Fuel injection pump for super charged diesel internal combustion engines
EP0012309A2 (en) * 1978-12-16 1980-06-25 Robert Bosch Gmbh Fuel injection system for Diesel engines, especially for automotive Diesel engines

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3795233A (en) * 1972-05-19 1974-03-05 Caterpillar Tractor Co Fuel-air ratio control for supercharged engines
US4037575A (en) * 1975-08-25 1977-07-26 Caterpillar Tractor Co. Altitude compensated fuel control system
JPS5410830A (en) * 1977-06-27 1979-01-26 Mitsubishi Motors Corp Fuel injection amount controller
JPS5410831A (en) * 1977-06-27 1979-01-26 Mitsubishi Motors Corp Injected idling fuel regulator
DE2731107A1 (en) * 1977-07-09 1979-01-25 Bosch Gmbh Robert CONTROL DEVICE FOR CHARGED INJECTION COMBUSTION ENGINES
JPS6041213B2 (en) * 1979-09-12 1985-09-14 トヨタ自動車株式会社 Destruction prevention device for turbocharged internal combustion engines

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH194671A (en) * 1936-09-30 1937-12-15 Scintilla Ag Control device on fuel injection pumps of internal combustion engines.
DE941879C (en) * 1941-09-12 1956-04-19 Daimler Benz Ag With a pressure medium, in particular a special fluid circuit, e.g. Lubricating oil, working control device for injection pumps of internal combustion engines
DE1912919A1 (en) * 1969-03-14 1970-09-24 Bosch Gmbh Robert Speed regulator for fuel injection pump
GB2034814A (en) * 1978-11-02 1980-06-11 Bosch Gmbh Robert Fuel injection pump for super charged diesel internal combustion engines
EP0012309A2 (en) * 1978-12-16 1980-06-25 Robert Bosch Gmbh Fuel injection system for Diesel engines, especially for automotive Diesel engines

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0204117A1 (en) * 1985-05-18 1986-12-10 Robert Bosch Gmbh Fuel injection pump for internal-combustion engines
FR2592917A1 (en) * 1986-01-16 1987-07-17 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES WHERE THE ADJUSTMENT PISTON IS MOVED ACCORDING TO THE PRESSURE.
WO1990015233A1 (en) * 1989-06-10 1990-12-13 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US5233957A (en) * 1989-06-10 1993-08-10 Robert Bosch Gmbh Fuel injection pump for internal combustion engines

Also Published As

Publication number Publication date
JPS5893941A (en) 1983-06-03
DE3146499A1 (en) 1983-06-01
DE3269883D1 (en) 1986-04-17
US4450805A (en) 1984-05-29
EP0080113B1 (en) 1986-03-12

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