EP0012309B1 - Fuel injection system for diesel engines, especially for automotive diesel engines - Google Patents

Fuel injection system for diesel engines, especially for automotive diesel engines Download PDF

Info

Publication number
EP0012309B1
EP0012309B1 EP79104834A EP79104834A EP0012309B1 EP 0012309 B1 EP0012309 B1 EP 0012309B1 EP 79104834 A EP79104834 A EP 79104834A EP 79104834 A EP79104834 A EP 79104834A EP 0012309 B1 EP0012309 B1 EP 0012309B1
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
fuel
injection
air
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
Application number
EP79104834A
Other languages
German (de)
French (fr)
Other versions
EP0012309A3 (en
EP0012309A2 (en
Inventor
Erich Ing. Jäger
Werner Ing. Faupel
Heinz Ing. Kuschmierz
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
Priority to AT79104834T priority Critical patent/ATE7417T1/en
Publication of EP0012309A2 publication Critical patent/EP0012309A2/en
Publication of EP0012309A3 publication Critical patent/EP0012309A3/en
Application granted granted Critical
Publication of EP0012309B1 publication Critical patent/EP0012309B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • 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
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
    • 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
    • F02M41/128—Varying injection timing by angular adjustment of the face-cam or the rollers support
    • 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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention is based on a fuel injection system according to the preamble of the independent claim.
  • fuel injection systems which are provided in particular for vehicle diesel engines, have a speed-dependent spray timing adjustment device which automatically compensates for the delayed start of injection at the injection nozzle at high speeds due to the long line paths.
  • This injection timing adjustment device which is also referred to as an automatic spray adjuster, ensures that the cheapest combustion and thus the greatest output of the diesel engine are retained even at rapidly changing speeds. It has now been found that this only fully applies if the air pressure conditions remain the same. However, if the diesel engines are operated at high altitudes, the ability to ignite is impaired by the reduced air filling (lower compression end temperatures) and the ignition delay is greater, especially with no load and part load. This results in steep pressure rises and thus a hard gear of the engine as well as misfires that lead to Blaurach.
  • a fuel injection system of the generic type with a fuel injection pump designed as a distributor injection pump is already known (with distributor injection pump VE..F .: from Robert Bosche GmbH, Stuttgart, see, for example, technical customer service notification VDT-1-460 / 1, 2. Addendum dated 5th 1977 or SAE-Paper No. 760127 from the Automotive Engineering Congress in Detroit, Michigan, from 23rd to 27th February 1976), in which the position of a VolIastansch determining the maximum permissible delivery quantity! A-.
  • the speed controller integrated in the pump housing is corrected as a function of the boost pressure or atmospheric pressure of the combustion air supplied to the engine.
  • the hydraulic and / or load-dependent hydraulic spray adjuster integrated in this injection pump does not take into account the changed air pressure conditions of the combustion air, so that the disadvantages mentioned at the beginning are not eliminated despite the correction of the delivery rate.
  • the fuel injection system according to the invention with the characterizing features of independent claim 1 has the advantage that the ignition conditions during operation of diesel engines at high altitudes or when the air weight changes as a result of the air quantity-dependent correction of the change in the start of delivery, which is otherwise at least speed-dependent.
  • the emission of hydrocarbons and therefore of blue smoke is reduced under the conditions mentioned and the engine's gear is avoided.
  • FIG. 1 shows a simplified sectional illustration of a known distributor injection pump with a spray adjustment device and a smoke control device
  • FIG. 2 shows a section through part of this distributor injection pump with the configuration according to the invention.
  • the injection pump shown in greatly simplified form in FIG. 1 is the known piston-type distributor injection pump of the VE..F .. type from Robert Bosch GmbH, Stuttgart, which is manufactured in large quantities and is known from the publications mentioned in the introduction to the description.
  • a pump piston works in a housing 10 in a cylinder bore 11. 12, which is set in a manner known per se by a cam drive consisting of a roller ring 13 and a front cam disk 14 into a reciprocating and simultaneously rotating movement.
  • a pump work chamber 15 acted upon by the pump piston 12 is filled during the suction stroke of the pump piston 12 via a suction bore 16 and control grooves 17 of the pump piston 12 and during the pressure stroke of the pump piston 12 with a closed suction bore 16 via a longitudinal bore 18 and a delivery groove 19 connected to it, via a pressure valve 21 and a Druckleitug 22 conveyed to an injection nozzle, not shown, on the engine cylinder.
  • a transverse bore 23 of the pump piston 12 connected to the longitudinal bore 18 is opened by a ring slide 24.
  • the fuel supplied to the pump working chamber 15 via the suction bore 16 is taken from an interior 25 of the injection pump which serves as a suction chamber and into which the fuel which is deflected from the transverse bore 23 by the ring valve 24 can flow back.
  • the interior 25 is supplied by a pre-feed pump 26 fuel from a reservoir 27, the delivery pressure by a pressure control valve 28 speed. is controlled dependent.
  • Parallel to the overflow quantity flowing back into the reservoir 27 via the pressure control valve 28, the interior 25 is preferably provided at its highest point with a throttle point 29 which determines the continuous outflow of a partial quantity, to which a return line 31, indicated only by an arrow, is connected, which is not shown in FIG returns to the reservoir 27 in a manner shown.
  • the interior of the pump 25 is cooled by this continuously flowing portion.
  • the interior 25 not only houses the cam drive 13, 14 of the pump piston 12 but also a centrifugal mechanical speed controller 32.
  • a centrifugal weight controller 33 which is rotated in a manner not shown by a drive shaft 34, which also drives the front cam disk 14 of the cam drive, actuates via a regulator sleeve 35 and a regulating lever 36. whose axial position controlled by a control lever 36 controls the delivery end and thus the injection quantity of the pump.
  • the control lever 36 ′ rests on a tensioning lever 37, the position of which is determined by the position of a full-load stop 38.
  • the pretensioning force of a control spring 39 holding the tensioning lever 37 in contact with the full load stop 38 determines the regulation speed.
  • the full-load stop 38 is formed by the crowned end of a lever arm 41a of a double-arm stop lever 41, the second lever arm 41b of which is supported on a scanning pin 42.
  • the sensing pin 42 which is guided in the wall of the pump housing 10 by means of a narrow sliding fit preventing the passage of fuel, is in turn supported on a cam surface 43 of a smoke control device 44.
  • the cam surface 43 is worked into the surface of a control slide 45 which is guided in a bore 46 of the pump housing 10 and can be actuated by a diaphragm socket set 49 against the force of a return spring 47 as part of an actuator 48 of the smoke control device 44.
  • the space designated 51 and surrounding the diaphragm socket set 49 is connected to the ambient air pressure via a bore 52 or to the intake manifold of the engine via a charge air line indicated by an arrow 53.
  • the smoke limitation device 44 operates as a function of the absolute air pressure and this device can be used both for an atmospheric pressure-dependent correction of the full load delivery rate and for a boost pressure-dependent correction.
  • the fuel fed into the interior 25 by the pre-feed pump 26 and under a speed-dependent feed pressure also actuates an actuating piston 55 of a hydraulic injection adjuster 56 serving as a spray adjustment device, via a pressure chamber 54 connected to the interior 25.
  • the actuating piston 55 works against the force of a return spring 57 for this purpose articulated to the roller ring 13, and rotates this with increasing pre-feed pump pressure in the inner space 25 in the sense of an early adjustment of the start of delivery.
  • the pre-feed pump 26 driven by the drive shaft 34 which is drawn outside the pump housing 10 for the sake of clarity, serves as a control pump for the spray adjustment device 56 and the associated pressure control valve 28 is of course also installed in the pump housing 10 in practice.
  • FIG. 2 shows the configuration of the smoke control device according to the invention.
  • a smoke limitation device 44 ' is attached to the pump housing 10, the pressure socket set 49 of which is combined with a control slide 45' working against the force of the return spring 47 to form an actuator 48 '.
  • the control slide 45 ' is brought together in a guide bush 65, which is screwed into the pump housing 10 and fastened by means of a ring nut 66.
  • the bore 46 in the guide bushing 65 which receives the control slide 45 'is closed towards the interior 25 of the injection pump, so that the pre-feed pump pressure prevailing in the interior 25 cannot act on the control slide 45':
  • the space 51 of the smoke control device 44 ′ surrounding the diaphragm box set 49 is connected to the ambient air via a pipe screw connection 166 screwed into the bore 52, so that this smoke control device 44 ′ serves as a full-load stop operating in dependence on the atmospheric pressure, the full-load stop controlled by the cam surface 43 and via the tracer pin 42 and the stop lever 41 on the full load stop 38 transmitted travel of the clamping lever 37 determined.
  • This tensioning lever 37 is the tensioning lever of the speed controller 32 shown in more detail in FIG. 1.
  • the pipe screw connection 166 enables the supply of the air under atmospheric pressure via line 53 from the air filter or intake pipe of the internal combustion engine or, in the short version shown, prevents it the penetration of dirt into the space 51. If the line 53 is connected to the intake pipe of a supercharged engine, this device can also work as a boost pressure-dependent full-load stop.
  • the smoke limitation device 44 ' also contains the control device designated here 58', and a part 45a 'of the control slide 45' serves as a correction actuator of this control device 58 'and is thus actuated by the same diaphragm dose set 49 which also controls the delivery rate correction via the cam surface 43.
  • the part 45a 'of the control slide 45' serving as a correction actuator is provided with an annular groove 68 which, together with a slot throttle 67 in the wall of the guide bush 65, forms the control device 58 ', the effective throttle cross-section being dependent on the axial position controlled by the diaphragm socket set 49 the annular groove 68 depends.
  • the throttle cross section of the slit throttle 67 controlled by the control slide 45 ′ controls the outflow of a portion of the fuel in the interior 25 under speed-dependent pressure into the return line 31 returning to the reservoir 27, so that the speed-dependent pressure in the interior 25 undergoes a correction depending on the air volume and the start of the delivery, which is dependent on the feed pump pressure in the interior 25, is adapted accordingly to the air volume by the injection adjuster.
  • the stroke of the control slide 45 ' is coordinated such that the slot throttle 67 can never be closed', so that a portion of the fuel required for cooling the interior 25 always flows out.
  • the slot throttle 67 which acts as a variable throttle point, is via a bore 69 in the wall of the pump housing 10 with the interior 25 and via the annular groove 68 on the control slide 45 'and a bore 71 in the wall of the guide bush 65 and a bore 71 in the wall the guide bushing 65 and a bore 72 in the wall of the pump housing 10 are connected to the return line 31.
  • the described air pressure-dependent and thus air volume-dependent correction of the otherwise at least speed-dependent change in the start of delivery can be applied analogously to any other type of fuel timing device, including electrically controlled or regulated.

Landscapes

  • 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)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

A fuel injection system is proposed for Diesel type internal combustion engines, by means of which the ignition conditions of a Diesel engine are kept optimal even during operation at high altitudes despite a reduced air charge. The system includes a fuel injection pump equipped with an injection timing adjustment apparatus which functions in accordance with rpm and a control apparatus functions in accordance with the air quantity supplied to the engine. By means of the control apparatus, a correction controlled in accordance with air pressure and therefore dependent on air quantity is superimposed on the change in the onset of the fuel supply controlled by the injection adjuster at least in accordance with rpm. When a hydraulic injection adjuster is used, the supply pressure of a control pump is increased by a correcting final control element of the control apparatus when the air quantity is decreasing in the direction toward an early adjustment of the onset of supply.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffspritzanlage nach der Gattung des unabhängigen Patentanspruches. Solche, insbesondere für Fahrzeug-Dieselmotoren vorgesehenen Kraftstoffeinspritzanlagen weisen eine drehzahlabhängig arbeitende Spritzzeitpunktverstelleinrichtung auf, die den bei hohen Drehzahlen durch die langen Leitungswege auftretenden Spritzbeginnverzug an der Einspritzdüse automatisch ausgleicht. Durch den Einsatz dieser auch als automatischer Spritzversteller bezeichneten Spritzzeitpunktverstelleinrichtung wird erreicht, dass die günstigste Verbrennung und damit die grösste Leistung des Dieselmotors auch bei sich stark ändernden Drehzahlen erhalten bleibt. Nun hat es sich herausgestellt, dass dies nur bei gleichbleibenden Luftdruckverhältnissen voll zutrifft. Werden die Dieselmotoren jedoch in grossen Höhen betrieben, so ist die Zündwilligkeit durch die verminderte Luftfüllung (niedrigere Kompressions-Endtemparaturen) beeinträchtigt und der Zündverzug wird, vor allem bei Nullast und Teillast grösser. Dies hat sowohl steile Druckanstiege und damit einen harten Gang des Motors als auch Zündaussetzer zur Folge, die zu Blaurach führen.The invention is based on a fuel injection system according to the preamble of the independent claim. Such fuel injection systems, which are provided in particular for vehicle diesel engines, have a speed-dependent spray timing adjustment device which automatically compensates for the delayed start of injection at the injection nozzle at high speeds due to the long line paths. The use of this injection timing adjustment device, which is also referred to as an automatic spray adjuster, ensures that the cheapest combustion and thus the greatest output of the diesel engine are retained even at rapidly changing speeds. It has now been found that this only fully applies if the air pressure conditions remain the same. However, if the diesel engines are operated at high altitudes, the ability to ignite is impaired by the reduced air filling (lower compression end temperatures) and the ignition delay is greater, especially with no load and part load. This results in steep pressure rises and thus a hard gear of the engine as well as misfires that lead to Blaurach.

Es ist bereits eine Kraftstoffeinspritzanlage der gattungsgemässen Bauart mit einer als Verteiler- einspritzpumpe ausgebildeten Kraftstoffeinspritzpumpe bekannt (mit Verteiler-Einspritzpumpe VE..F.: der Robert Bosche GmbH, Stuttgart, siehe z. B. technische Kundendienstmitteilung VDT-1-460/1, 2. Nachtrag vom 5. 1977 oder SAE-Paper Nr. 760127 vom Automotive Engineering Congress in Detroit, Michigan, vom 23. bis 27. Februar 1976), bei der die, die maximal zulässige Fördermenge bestimmende Lage eines VolIastansch!a- . ges des in das Pumpengehäuse integrierten Drehzahlreglers in Abhängigkeit vom Lädedruck oder Atmosphärendruck der dem Motor zugeführten Verbrennungsluft korrigiert wird. Der in diese Einspritzpumpe integrierte drehzahl- und/oder lastabhängig arbeitende hydraulische Spritzversteller berücksichtigt jedoch nicht die veränderten Luftdruckverhältnisse der Verbrennungsluft, so dass die eingangs genannten Nachteile trotz der Fördermengenkorrektur nicht behoben sind.A fuel injection system of the generic type with a fuel injection pump designed as a distributor injection pump is already known (with distributor injection pump VE..F .: from Robert Bosche GmbH, Stuttgart, see, for example, technical customer service notification VDT-1-460 / 1, 2. Addendum dated 5th 1977 or SAE-Paper No. 760127 from the Automotive Engineering Congress in Detroit, Michigan, from 23rd to 27th February 1976), in which the position of a VolIastansch determining the maximum permissible delivery quantity! A-. The speed controller integrated in the pump housing is corrected as a function of the boost pressure or atmospheric pressure of the combustion air supplied to the engine. The hydraulic and / or load-dependent hydraulic spray adjuster integrated in this injection pump does not take into account the changed air pressure conditions of the combustion air, so that the disadvantages mentioned at the beginning are not eliminated despite the correction of the delivery rate.

Bei einer durch die DE-A-26 48 043 bekannt gewordenen Verteilereinspritzpumpe mit hydraulischem Spritzenversteller wird durch temperaturabhängig gesteuertes Ändern des Stellkolben des Spritzverstellers beaufschlagenden Vorförderpumpendrucks der drehzahlabhängig gesteuerten Spritzbeginnverstellung eine temperaturabhängig gesteuerte Frühverstellung überlagert, die aber nur vom Startbeginn bis zum Warmlauf der Brennkraftmaschine wirksam ist. Diese Einrichtung ist bei warmer Brennkraftmaschine unwirksam und die eingangs genannten Nachteile werden durch diese Steuereinrichtung nicht behoben.In a distributor injection pump with hydraulic syringe adjuster that has become known from DE-A-26 48 043, a temperature-dependent early adjustment is superimposed on a temperature-dependent early adjustment by changing the actuating piston of the injection adjuster acting on the adjusting piston of the injection adjuster, but this is only effective from the start of the start to the warming up of the internal combustion engine . This device is ineffective when the internal combustion engine is warm and the disadvantages mentioned at the outset are not eliminated by this control device.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemässe Kraftstoffeinspritzanlage mit den kennzeichnenden Merkmalen des unabhängigen Patentanspruchs 1 hat demgegenüber den Vorteil, dass durch die luftmengenabhängig gesteuerte Korrektur der ansonsten mindestens drehzahlabhängig gesteuerten Förderbeginnänderung die Zündbedingungen beim Betrieb von Dieselmotoren in grossen Höhen oder bei durch Aufladung verändertem Luftgewicht verbessert werden. Die Emmission von Kohlenwasserstoffen und damit von Blaurauch wird unter den erwähnten Bedingungen reduziert und ein zu harter Gang des Motors vermieden.The fuel injection system according to the invention with the characterizing features of independent claim 1 has the advantage that the ignition conditions during operation of diesel engines at high altitudes or when the air weight changes as a result of the air quantity-dependent correction of the change in the start of delivery, which is otherwise at least speed-dependent. The emission of hydrocarbons and therefore of blue smoke is reduced under the conditions mentioned and the engine's gear is avoided.

Durch die in den abhängigen Patentansprüchen aufgeführten Massnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im unabhängigen Patentanspruch 1 angebenen Kraftstoffeinspritzanlage möglich. Durch die nach Patentanspruch 3 in die Rauchbegrenzungsvorrichtung integrierte Steuervorrichtung ist sowohl für die Anpassung der Vollastfördermenge an den Luftdruck der dem Motor zugeführten Verbrennungsluft als auch für die Förderbeginnkorrektur nur ein einziges vom Luftdruck abhängig arbeitendes Stellglied notwendig und beide Korrekturen werden parallel gesteuert. Da kein zusätzliches Stellglied notwendig ist, kommt man auch mit dem gleichen Bauraum aus, der für eine Einspritzpumpe erforderlich ist, die lediglich mit einer Rauchbegrenzungsvorrichtung ausgestattet ist.The measures listed in the dependent claims allow advantageous developments and improvements of the fuel injection system specified in independent claim 1. Due to the control device integrated into the smoke limitation device according to claim 3, only a single actuator that works as a function of the air pressure is necessary both for adapting the full-load delivery rate to the air pressure of the combustion air supplied to the engine and for the start of delivery correction, and both corrections are controlled in parallel. Since no additional actuator is required, the same installation space is required that is required for an injection pump that is only equipped with a smoke control device.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine vereinfachte Schnittdarstellung einer bekannten Verteilereinspritzpumpe mit einer Spritzverstelleinrichtung und einer Rauchbegrenzungseineinrichtung und Figur 2 einen Schnitt durch einen Teil dieser Verteilereinspritzpumpe mit der erfindungsgemässen Ausgestaltung.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. FIG. 1 shows a simplified sectional illustration of a known distributor injection pump with a spray adjustment device and a smoke control device, and FIG. 2 shows a section through part of this distributor injection pump with the configuration according to the invention.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Bei der in Figur 1 stark vereinfacht dargestellten Einpritzpumpe handelt es sich um die bekannte Hubkolben-Verteilereinspritzpumpe der Bauart VE..F.. der Robert Bosch GmbH, Stuttgart, die in Grosserie gefertigt wird und aus-den in der Beschreibunseinleitung genannten Druckschriften bekannt ist.The injection pump shown in greatly simplified form in FIG. 1 is the known piston-type distributor injection pump of the VE..F .. type from Robert Bosch GmbH, Stuttgart, which is manufactured in large quantities and is known from the publications mentioned in the introduction to the description.

In einem Gehäuse 10 arbeitet in einer Zylinderbohrung 11 ein Pumpenkolben. 12, der in an sich bekannter Weise von einem aus einem Rollenring 13 und einer Stirnnockenscheibe 14 bestehenden Nockentrieb in eine sowohl hin- und hergehende als auch gleichzeitig rotierende Bewegung versetzt wird. Ein vom Pumpenkolben 12 beaufschlagter Pumpenarbeitsraum 15 wird beim Saughub des Pumpenkolbens 12 über eine Saugbohrung 16 und Steuernuten 17 des Pumpenkolbens 12 gefüllt und beim Druckhub des Pumpenkolbens 12 bei abgeschlossener Saugbohrung 16 über eine Längsbohrung 18 und eine mit dieser verbundenen Fördernut 19, über ein Druckventil 21 und eine Druckleitug 22 zu einer nicht näher dargestellten Einspritzdüse am Motorzylinder gefördert. Bei Förderende wird eine mit der Längsbohrung 18 verbundene Querbohrung 23 des Pumpenkolbens 12 von einem Ringschieber 24 aufgesteuert.A pump piston works in a housing 10 in a cylinder bore 11. 12, which is set in a manner known per se by a cam drive consisting of a roller ring 13 and a front cam disk 14 into a reciprocating and simultaneously rotating movement. A pump work chamber 15 acted upon by the pump piston 12 is filled during the suction stroke of the pump piston 12 via a suction bore 16 and control grooves 17 of the pump piston 12 and during the pressure stroke of the pump piston 12 with a closed suction bore 16 via a longitudinal bore 18 and a delivery groove 19 connected to it, via a pressure valve 21 and a Druckleitug 22 conveyed to an injection nozzle, not shown, on the engine cylinder. At the end of the delivery, a transverse bore 23 of the pump piston 12 connected to the longitudinal bore 18 is opened by a ring slide 24.

Der über die Saugbohrung 16 dem Pumpenarbeitsraum 15 zugeführte Kraftstoff wird einem als Saugraum dienenden Innenraum 25 der Einspritzpumpe entnommen, in den auch der vom Ringschieber 24 aus der Querbohrung 23 abgesteuerte Kraftstoff zurückfliessen kann. Dem Innenraum 25 wird von einer Vorföderpumpe 26 Kraftstoff aus einem Vorratsbehälter 27 zugeführt, dessen Förderdruck durch ein Drucksteuerventil 28 drehzahl. abhängig gesteuert wird. Paralell zu der über das Drucksteuerventil 28 in den Vorratsbehälter 27 zurückfliessenden Überströmmenge ist der Innenraum 25 vorzugsweise an seiner höchsten Stelle mit einer dem dauernden Abfluss einer Teilmenge bestimmenden Drosselstelle 29 versehen, an die eine nur durch einen Pfeil angedeutete Rückflussleitung 31 angeschlossen ist, die in nicht näher dargestellter Weise zum Vorratsbehälter 27 zurückführt. Durch diese dauernd abfliessende Teilmenge wird der Innenraum der Pumpe 25 gekühlt. Dies ist notwendig, da der Innenraum 25 nicht nur den Nockentrieb 13, 14 des Pumpenkolbens 12 sondern auch einen fliehkraftbetätigten mechanischen Drehzahlregler 32 aufnimmt. Ein Fliehgewichtsregler 33, der in nicht näher dargestellter Weise von einer auch die Stirnockenscheibe 14 des Nockentriebs antreibenden Antriebswelle 34 in Drehbewegung versetzt wird, betätigt über eine Reglermuffe 35 und einen Regelhebel 36. in bekannter Weise den als Fördermengenverstellglied der Hubkolben-Verteilerspritzpumpe dienenden Ringschieber 24, dessen von einem Regelhbel 36 gesteuerte axiale Lage das Förderende und damit die Einspritzmenge der Pumpe steuert. In der gezeichneten Vollaststellung der Reglerteile liegt der Regelhebel 36'an einem Spannhebel 37 an, dessen Lage durch die Stellung eines Vollastanschlags 38 bestimmt ist. Die Vorspannkraft einer den Spannhebel 37 in Anlage mit dem Vollastanschlag 38 haltenden Regelfeder 39 bestimmt die Abregeldrehzahl.The fuel supplied to the pump working chamber 15 via the suction bore 16 is taken from an interior 25 of the injection pump which serves as a suction chamber and into which the fuel which is deflected from the transverse bore 23 by the ring valve 24 can flow back. The interior 25 is supplied by a pre-feed pump 26 fuel from a reservoir 27, the delivery pressure by a pressure control valve 28 speed. is controlled dependent. Parallel to the overflow quantity flowing back into the reservoir 27 via the pressure control valve 28, the interior 25 is preferably provided at its highest point with a throttle point 29 which determines the continuous outflow of a partial quantity, to which a return line 31, indicated only by an arrow, is connected, which is not shown in FIG returns to the reservoir 27 in a manner shown. The interior of the pump 25 is cooled by this continuously flowing portion. This is necessary because the interior 25 not only houses the cam drive 13, 14 of the pump piston 12 but also a centrifugal mechanical speed controller 32. A centrifugal weight controller 33, which is rotated in a manner not shown by a drive shaft 34, which also drives the front cam disk 14 of the cam drive, actuates via a regulator sleeve 35 and a regulating lever 36. whose axial position controlled by a control lever 36 controls the delivery end and thus the injection quantity of the pump. In the drawn full-load position of the controller parts, the control lever 36 ′ rests on a tensioning lever 37, the position of which is determined by the position of a full-load stop 38. The pretensioning force of a control spring 39 holding the tensioning lever 37 in contact with the full load stop 38 determines the regulation speed.

Der Vollastanschlag 38 ist vom balligen Ende eines Hebelarmes 41a eines doppelarmigen Anschlaghebeis 41 gebildet, dessen zweiter Hebelarm 41b sich an einem Abtaststift 42 abstützt. Der mittels einer engen und den Durchtritt von Kraftstoff verhindernden Gleitpassung in der Wand des Pumpengehäuses 10 geführte Abtaststift 42 stützt sich seinerseits an einer Nockenfläche 43 einer Rauchbegrenzungsvorrichtung 44 ab. Die Nockenfläche 43 ist in die Oberfläche eines Steuerschiebers 45 eingearbeitet, der in einer Bohrung 46 des Pumpengehäuses 10 geführt ist und als.Teil eines Stellgliedes 48 der Rauchbegrenzungsvorrichtung 44 entgegen der Kraft einer Rückstellfeder 47 von einem Membrandosensatz 49 betätigbar ist. Der mit 51 bezeichnete, den Membrandosensatz 49 umgebende Raum ist über eine Bohrung 52 an den Umgebungsluftdruck oder über eine durch einen Pfeil 53 angedeutete Ladeluftleitung an das Saugrohr des Motors angeschlossen. Durch den Mebrandosensatz 49 arbeitet die Rauchbegrenzungsvorrichtung 44 in Abängigkeit vom absoluten Luftdruck und diese Vorrichtung kann sowohl für eine atmosphärendruckabhängige Korrektur der Vollastfödermenge als auch für eine ladedruckabhängige Korrektur verwendet werden.The full-load stop 38 is formed by the crowned end of a lever arm 41a of a double-arm stop lever 41, the second lever arm 41b of which is supported on a scanning pin 42. The sensing pin 42, which is guided in the wall of the pump housing 10 by means of a narrow sliding fit preventing the passage of fuel, is in turn supported on a cam surface 43 of a smoke control device 44. The cam surface 43 is worked into the surface of a control slide 45 which is guided in a bore 46 of the pump housing 10 and can be actuated by a diaphragm socket set 49 against the force of a return spring 47 as part of an actuator 48 of the smoke control device 44. The space designated 51 and surrounding the diaphragm socket set 49 is connected to the ambient air pressure via a bore 52 or to the intake manifold of the engine via a charge air line indicated by an arrow 53. By means of the diaphragm can set 49, the smoke limitation device 44 operates as a function of the absolute air pressure and this device can be used both for an atmospheric pressure-dependent correction of the full load delivery rate and for a boost pressure-dependent correction.

Der in den Innenraum 25 von der Vorförderpumpe 26 zugeführte, unter drehzahlabhängig gesteuertem Vorförderpumpendruck stehende Kraftstoff betätigt auch über einen an den Innenraum 25 angeschlossenen Druckraum 54 einen Stellkolben 55 eines als Spritzverstelleinrichtung dienenden hydraulischen Spritzverstellers 56. Der entgegen der Kraft einer Rückstellfeder 57 arbeitende Stellkolben 55 ist dazu an den Rollenring 13 angelenkt, und verdreht diesen bei steigendem Vorförderpumpendruck im Inneraum 25 im Sinne einer Frühverstellung des Fördebeginns. Die von der Antriebswelle 34 angetriebene Vorförderpumpe 26, die nur der Übersicht halber ausserhalb des Pumpengehäuses 10 gezeichnet ist, dient dabei als Steuerpumpe der Spritzverstelleinrichtung 56 und das zugehörige Drucksteuerventil 28 ist in der Praxis selbstverständlich ebenfalls in das Pumpengehäuse 10 eingebaut.The fuel fed into the interior 25 by the pre-feed pump 26 and under a speed-dependent feed pressure also actuates an actuating piston 55 of a hydraulic injection adjuster 56 serving as a spray adjustment device, via a pressure chamber 54 connected to the interior 25. The actuating piston 55 works against the force of a return spring 57 for this purpose articulated to the roller ring 13, and rotates this with increasing pre-feed pump pressure in the inner space 25 in the sense of an early adjustment of the start of delivery. The pre-feed pump 26 driven by the drive shaft 34, which is drawn outside the pump housing 10 for the sake of clarity, serves as a control pump for the spray adjustment device 56 and the associated pressure control valve 28 is of course also installed in the pump housing 10 in practice.

Am Beispiel der oben beschriebenen Einspritzpumpe zeigt Figur 2 die erfindungsgemässe Ausgestaltung der Rauchbegrenzungseinrichtung.Using the example of the injection pump described above, FIG. 2 shows the configuration of the smoke control device according to the invention.

An das Pumpengehäuse 10 ist eine Rauchbegrenzungsvorrichtung 44' angebaut, deren Druckdosensatz 49 mit einem entgegen der Kraft der Rückstellfeder 47 arbeitenden Steuerschieber 45' zu einem Stellglied 48' zusammengefasst ist. Der Steuerschieber 45' ist in einer Führungsbuchse 65 zusammengeführt, die in das Pumpengehäuse 10 eingeschraubt und mittels einer Ringmutter 66 befestigt ist. Die den Steuerschieber 45' aufnehmende Bohrung 46 in der Führungsbuchse 65 ist zum Innenraum 25 der Einspritzpumpe hin geschlossen, so dass der im Innenraum 25 herrschende Vorförderpumpendruck nicht auf den Steuerschieber 45' einwirken kann:A smoke limitation device 44 'is attached to the pump housing 10, the pressure socket set 49 of which is combined with a control slide 45' working against the force of the return spring 47 to form an actuator 48 '. The control slide 45 'is brought together in a guide bush 65, which is screwed into the pump housing 10 and fastened by means of a ring nut 66. The bore 46 in the guide bushing 65 which receives the control slide 45 'is closed towards the interior 25 of the injection pump, so that the pre-feed pump pressure prevailing in the interior 25 cannot act on the control slide 45':

Der den Membrandosensatz 49 umgebende Raum 51 der Rauchbegrenzungsvorrichtung 44' ist über eine in die Bohrung 52 eingeschraubte Rohrverschraubung 166 mit der Umgebungsluft verbunden, so dass diese Rauchbegrenzungsvorrichtung- 44' als atmosphärendruckabhängig arbeitender Vollastanschlag dient, dessen von der Nockenfläche 43 gesteuerter und über den Abtaststift 42 und den Anschlaghebel 41 auf den Vollastanschlag 38 übertragener Stellweg des Spannhebels 37 bestimmt. Bei diesem Spannhebel 37 handelt es sich um den in Figur 1 näher dargestellten Spannhebel des Drehzahlreglers 32.,Die Rohrverschraubung 166 ermöglicht die Zufuhr der unter Atmosphärendruck stehender Luft über die Leitung 53 vom Luftfilter oder Ansaugrohr der Brennkraftmaschine her oder in der gezeichneten kurzen Ausführung verhindert sie das Eindringen von Schmutz in den Raum 51. Wird die Leitung 53 an das Ansaugrohr eines aufgeladenen Motors angeschlossen, dann kann diese Vorrichtung auch als ladedruckabhängiger Vollastanschlag arbeiten.The space 51 of the smoke control device 44 ′ surrounding the diaphragm box set 49 is connected to the ambient air via a pipe screw connection 166 screwed into the bore 52, so that this smoke control device 44 ′ serves as a full-load stop operating in dependence on the atmospheric pressure, the full-load stop controlled by the cam surface 43 and via the tracer pin 42 and the stop lever 41 on the full load stop 38 transmitted travel of the clamping lever 37 determined. This tensioning lever 37 is the tensioning lever of the speed controller 32 shown in more detail in FIG. 1. The pipe screw connection 166 enables the supply of the air under atmospheric pressure via line 53 from the air filter or intake pipe of the internal combustion engine or, in the short version shown, prevents it the penetration of dirt into the space 51. If the line 53 is connected to the intake pipe of a supercharged engine, this device can also work as a boost pressure-dependent full-load stop.

Bei diesem Ausführungsbeispiel nach Figur 2 enthält die Rauchbegrenzungsvorrichtung 44' auch die hier mit 58' bezeichnete Steuervorrichtung, und ein Teil 45a' des Steuerschiebers 45' dient dabei als Korrekturstellglied dieser Steuervorrichtung 58' und wird somit vom gleichen Membrandosensatz 49 betätigt, der auch die Fördermengenkorrektur über die Nockenfläche 43 steuert. Der als Korrekturstellglied dienende Teil 45a' des Steuerschiebers 45' ist mit einer Ringnut 68 versehen, die zusammen mit einer Schlitzdrossel 67 in der Wand der Führungsbüchse 65 die Steuervorrichtung 58' bildet, wobei der wirksame Drosselquerschnitt von der durch den Membrandosensatz 49 luftdruckabhängig gesteuerten axialen Lage der Ringnut 68 abhängt. Durch den vom Steuerschieber 45' gesteuerten Drosselquerschnitt der Schlitzdrossel 67 wird der Abfluss einer Teilmenge des im Innenraum 25 unter drehzahlabhängigem Druck stehenden Kraftstoffs in die zum Vorratsbehälter 27 zurückführende Rückflussleitung 31 luftmengenabhängig gesteuert, so dass der drehzahlabhängig gesteuerte Druck im Innenraum 25 eine luftmengenabhängig gesteuerte Korrektur erfährt und die vom Vorförderpumpendruck im Innenraum 25 abhängige Förderbeginnähderung durch den Spritzversteller entsprechend an die Luftmenge angepasst wird. Der Hub des Steuerschiebers 45' ist so abgestimmt, dass die Schlitzdrossel 67 niemals verschlossen werden'kann, so das immer eine für die Kühlung des Innenraums 25 erforderliche Teilmenge des Kraftstoffes abströmt. Die als veränderliche- Drosselstelle wirkende Schlitzdrossel 67 ist über.eine Bohrung 69 in der Wand des Pumpengehäuses 10 mit dem Innenraum 25 und über die Ringnut 68 am Steuerschieber 45' und eine Bohrung 71 in der Wand der Führungsbüchse 65 sowie eine Bohrung 71 in der Wand der Führungsbüchse 65 sowie eine Bohrung 72 in der Wand des Pumpengehäuses 10 mit der Rückflussleitüng 31 verbunden.In this exemplary embodiment according to FIG. 2 The smoke limitation device 44 'also contains the control device designated here 58', and a part 45a 'of the control slide 45' serves as a correction actuator of this control device 58 'and is thus actuated by the same diaphragm dose set 49 which also controls the delivery rate correction via the cam surface 43. The part 45a 'of the control slide 45' serving as a correction actuator is provided with an annular groove 68 which, together with a slot throttle 67 in the wall of the guide bush 65, forms the control device 58 ', the effective throttle cross-section being dependent on the axial position controlled by the diaphragm socket set 49 the annular groove 68 depends. The throttle cross section of the slit throttle 67 controlled by the control slide 45 ′ controls the outflow of a portion of the fuel in the interior 25 under speed-dependent pressure into the return line 31 returning to the reservoir 27, so that the speed-dependent pressure in the interior 25 undergoes a correction depending on the air volume and the start of the delivery, which is dependent on the feed pump pressure in the interior 25, is adapted accordingly to the air volume by the injection adjuster. The stroke of the control slide 45 'is coordinated such that the slot throttle 67 can never be closed', so that a portion of the fuel required for cooling the interior 25 always flows out. The slot throttle 67, which acts as a variable throttle point, is via a bore 69 in the wall of the pump housing 10 with the interior 25 and via the annular groove 68 on the control slide 45 'and a bore 71 in the wall of the guide bush 65 and a bore 71 in the wall the guide bushing 65 and a bore 72 in the wall of the pump housing 10 are connected to the return line 31.

Durch den die Steuervorrichtung 58' beinhaltenden, in das Pumpengehäuse 10 hinein verlängerten Teil der Rauchbegrenzungsvorrichtung 44' hat sich die Aussenkontur der Pumpe gegenüber einersolchen mit einer nur luftdruckabhängig arbeitenden Rauchbegrenzungsvorrichtungen nicht geändert, denn die Funktion der luftabhängigen Korrektur der Förderbeginnänderung wird auf einfache Weise vom Stellglied 48' mit übernommen.As a result of the part of the smoke control device 44 'which includes the control device 58' and which is extended into the pump housing 10, the outer contour of the pump has not changed compared to those with smoke control devices which only work as a function of air pressure, since the function of the air-dependent correction of the change in the start of delivery is easily performed by the actuator 48 'taken over.

Die beschriebene luftdruckabhängig gesteuerte und damit luftmengenabhängige Korrektur der ansonsten mindestens drehzahlabhängigen Förderbeginnänderung kann bei jeder anderen Bauart von Sprittzeitpunktverstelleinrichtungen, auch bei elektrisch gesteuerten oder geregelten, sinngemäss angewendet werden.The described air pressure-dependent and thus air volume-dependent correction of the otherwise at least speed-dependent change in the start of delivery can be applied analogously to any other type of fuel timing device, including electrically controlled or regulated.

Claims (3)

1. Fuel-injection pump for diesel-type internal combustion engines, in particular for motor vehicles, with a pump suciton-chamber (25) which is supplied with fuel by means of a fuel feed pump (26), with a pressure control valve (28) which controls a pump suction-chamber (25) outflow cross-section as a function of the pressure in the suction chamber (25), with a start of injection adjustment piston (55) which the suction-chamber pressure can displace counter to the force of a return spring (57), with a device for varying a supplementary pump suction-chamber (25) outflow cross-section (67) as a funciton of the rate at which air is being supplied to the internal combustion engine, and, in additiorr, with a speed governor (32) for adjusting the positon of a feed-rate regulating element (37, 24), the travel of which is limited by the position of a full-load stop (38), this position defining the maximum permissible full-load feed rate, characterised in that the supplementary outflow crossection (67) can at the same time be varied by means of a correcting servo element (48') of a smoke-limiting device (58') which defines, via this element (48'), the position of the full-load stop (38), as a function of the pressure of the air which is being supplied to the engine.
2. Fuel-injection unit according to Patent Claim 1, characterised in that the correcting servo element is formed by a portion (45a') of the servo element (48') of the smoke-limiting device (44').
3. Fuel-injection unit with a control slider which belongs to the servo element of the smoke-limiting device according to Patent Claims 1, and which is mounted in a guide bush, characterised in that that portion (45a') of the servo element (48') which forms the correcting-servo element possesses an annular channel (68) which is machined into the control slider (45') and which, with a slit-type restrictor (67), machined into the wall of the guide bush (65) and serving as a restriction point, forms the control device (58'), it being possible to vary the effective cross-section or the restrictor by means of the axial position of the annular channel (68), this position being controlled as a function of the air pressure.
EP79104834A 1978-12-16 1979-12-03 Fuel injection system for diesel engines, especially for automotive diesel engines Expired EP0012309B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT79104834T ATE7417T1 (en) 1978-12-16 1979-12-03 FUEL INJECTION SYSTEM FOR DIESEL ENGINES, ESPECIALLY FOR VEHICLE DIESEL ENGINES.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19782854422 DE2854422A1 (en) 1978-12-16 1978-12-16 FUEL INJECTION SYSTEM FOR DIESEL INTERNAL COMBUSTION ENGINES, ESPECIALLY FOR VEHICLE DIESEL ENGINES
DE2854422 1978-12-16

Publications (3)

Publication Number Publication Date
EP0012309A2 EP0012309A2 (en) 1980-06-25
EP0012309A3 EP0012309A3 (en) 1980-07-09
EP0012309B1 true EP0012309B1 (en) 1984-05-09

Family

ID=6057400

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79104834A Expired EP0012309B1 (en) 1978-12-16 1979-12-03 Fuel injection system for diesel engines, especially for automotive diesel engines

Country Status (6)

Country Link
US (1) US4384560A (en)
EP (1) EP0012309B1 (en)
JP (1) JPS5584824A (en)
AT (1) ATE7417T1 (en)
BR (1) BR7908187A (en)
DE (2) DE2854422A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4128754A1 (en) * 1990-08-29 1992-03-05 Zexel Corp DISTRIBUTION TYPE FUEL INJECTION PUMP

Families Citing this family (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2931938A1 (en) * 1979-08-07 1981-02-26 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
JPS5644795U (en) * 1979-09-14 1981-04-22
JPS5650226A (en) * 1979-09-29 1981-05-07 Mazda Motor Corp Fuel injection device for diesel engine
JPS5773335U (en) * 1980-10-22 1982-05-06
SE439950B (en) * 1980-12-16 1985-07-08 Volvo Ab DEVICE FOR CONTINUOUS SAFETY OF A TURBOLED DIESEL ENGINE WORKING STATE WITH REGARD TO SPEED AND LOADING
JPS6128028Y2 (en) * 1981-05-14 1986-08-20
JPS57200621A (en) * 1981-06-05 1982-12-08 Diesel Kiki Co Ltd Fuel injection amount regulating device in fuel injection pump
DE3138606A1 (en) * 1981-09-29 1983-04-14 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3139789A1 (en) * 1981-10-07 1983-04-21 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3146132A1 (en) * 1981-11-21 1983-06-01 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3146499A1 (en) * 1981-11-24 1983-06-01 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3212524A1 (en) * 1982-04-03 1983-10-13 Spica S.p.A., Livorno IMPROVEMENT OF THE SPRAY TIME ADJUSTMENT SYSTEM WITH AN INJECTION PUMP, IN PARTICULAR WITH A PISTON PUMP
JPS58204938A (en) * 1982-05-24 1983-11-29 Toyota Motor Corp Controller of fuel injection timing in diesel engine with supercharger
DE3234049A1 (en) * 1982-09-14 1984-03-15 Diesel Kiki Co. Ltd., Tokyo Injection time adjustment compensation device for a fuel injection pump
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
DE3242108A1 (en) * 1982-11-13 1984-05-17 Robert Bosch Gmbh, 7000 Stuttgart DISTRIBUTOR INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3243349A1 (en) * 1982-11-24 1984-05-24 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP
DE3245947A1 (en) * 1982-12-11 1984-06-14 Robert Bosch Gmbh, 7000 Stuttgart Fuel injection pump for internal combustion engines
DE3307265A1 (en) * 1983-03-02 1984-09-06 Volkswagenwerk Ag, 3180 Wolfsburg Control device for injection pumps
DE3430141A1 (en) * 1984-08-16 1986-02-27 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION SYSTEM FOR DIESEL INTERNAL COMBUSTION ENGINES, ESPECIALLY FOR VEHICLE DIESEL ENGINES
US4643155A (en) * 1984-10-05 1987-02-17 Olin Corporation Variable stroke, electronically controlled fuel injection control system
GB2173923B (en) * 1985-04-15 1989-01-05 Ricardo Consulting Eng Fuel supply system for turbocharged internal combustion engine
JPH0444825Y2 (en) * 1985-06-24 1992-10-22
US4889092A (en) * 1985-07-18 1989-12-26 Ail Corporation Fuel viscosity/density compensation device
US4869219A (en) * 1986-07-14 1989-09-26 Cummins Engine Company, Inc. Dual spring air fuel control for the PT fuel system
JPH01105733U (en) * 1988-01-08 1989-07-17
DE3912624A1 (en) * 1989-04-18 1990-10-25 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3919064A1 (en) * 1989-06-10 1990-12-13 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
ES2045568T3 (en) * 1990-01-04 1994-01-16 Bosch Gmbh Robert REVOLUTION NUMBER REGULATOR OF A 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
US6158416A (en) * 1998-11-16 2000-12-12 General Electric Company Reduced emissions elevated altitude speed control for diesel engines
US6234149B1 (en) 1999-02-25 2001-05-22 Cummins Engine Company, Inc. Engine control system for minimizing turbocharger lag including altitude and intake manifold air temperature compensation
DE102010003539A1 (en) * 2010-03-31 2011-10-06 Robert Bosch Gmbh Method and circuit arrangement for determining position-minus time

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1251243A (en) * 1959-01-14 1961-01-20 Cie Crouzet Method and device for automatic injection advance control in combustion engines

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1932600C3 (en) * 1969-06-27 1978-07-27 Robert Bosch Gmbh, 7000 Stuttgart Fuel injection system for compression ignition engines with a change in the start of injection
ZA711668B (en) * 1970-03-18 1971-12-29 Cav Ltd Liquid fuel pumping apparatus
JPS5339528B1 (en) * 1971-03-06 1978-10-21
US3742925A (en) * 1971-07-19 1973-07-03 Caterpillar Tractor Co Timing mechanism for engines
US3795233A (en) * 1972-05-19 1974-03-05 Caterpillar Tractor Co Fuel-air ratio control for supercharged engines
JPS544449B2 (en) * 1973-08-31 1979-03-07
US3968779A (en) * 1975-02-11 1976-07-13 Stanadyne, Inc. Fuel injection pump and injection control system therefor
DE2648043C2 (en) * 1976-10-23 1984-05-24 Robert Bosch Gmbh, 7000 Stuttgart Fuel injection pump for internal combustion engines
US4197059A (en) * 1978-07-26 1980-04-08 Ford Motor Company Fuel injection pump having means for retarding the fuel injection timing schedule

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1251243A (en) * 1959-01-14 1961-01-20 Cie Crouzet Method and device for automatic injection advance control in combustion engines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
BUSSIEN "Automobiltechnisches Handbuch", Seite 61 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4128754A1 (en) * 1990-08-29 1992-03-05 Zexel Corp DISTRIBUTION TYPE FUEL INJECTION PUMP

Also Published As

Publication number Publication date
BR7908187A (en) 1980-07-22
EP0012309A3 (en) 1980-07-09
DE2854422A1 (en) 1980-07-03
JPS63611B2 (en) 1988-01-07
DE2966972D1 (en) 1984-06-14
EP0012309A2 (en) 1980-06-25
ATE7417T1 (en) 1984-05-15
JPS5584824A (en) 1980-06-26
US4384560A (en) 1983-05-24

Similar Documents

Publication Publication Date Title
EP0012309B1 (en) Fuel injection system for diesel engines, especially for automotive diesel engines
DE2558699C2 (en) Pump nozzle for fuel injection into an internal combustion engine
DE2942010C2 (en)
DE2326083C2 (en) Device for controlling the fuel-air ratio for a supercharged internal combustion engine
GB1580150A (en) Fuel injection pump for internal combustion engines
DE3150805A1 (en) Fuel injection system
EP0733160B1 (en) Fuel-injection system for a two-stroke internal-combustion engine
EP0204117B1 (en) Fuel injection pump for internal-combustion engines
DE3121108C2 (en)
DE3242108C2 (en)
EP0168586B1 (en) Fuel injection pump
EP0386175B1 (en) Fuel injection pump for internal combustion engines
DE2946557A1 (en) DEVICE FOR CONTROLLING AN EXHAUST GAS RECIRCULATION DEVICE IN INTERNAL COMBUSTION ENGINES
DE2812246A1 (en) FUEL CORRECTION DEVICE OF A FUEL INJECTION PUMP FOR COMBUSTION ENGINE
EP0354399B1 (en) Fuel injection pump for internal-combustion engines
US4387683A (en) Fuel injection pump for internal combustion engines
US5263457A (en) Fuel injection pump for internal combustion engines
DE3019218A1 (en) DISTRIBUTION TYPE FUEL INJECTION PUMP
EP0341243B1 (en) Fuel injection pumps for internal combustion engines
EP0318714B1 (en) Exhaust gas recirculation device for internal combustion engines
DE2903551A1 (en) Fuel injection pump for Diesel engine - has insert with auxiliary piston to vary start of injection according to engine load
EP0454803B1 (en) Fuel-injection pump for internal-combustion engines
DE3704580A1 (en) FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
EP0456772B1 (en) Fuel injection pump for internal combustion engines
US2016619A (en) Fuel injection system for internal combustion engines

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

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): AT DE FR GB IT

AK Designated contracting states

Designated state(s): AT DE FR GB IT

17P Request for examination filed

Effective date: 19791203

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): AT DE FR GB IT

REF Corresponds to:

Ref document number: 7417

Country of ref document: AT

Date of ref document: 19840515

Kind code of ref document: T

REF Corresponds to:

Ref document number: 2966972

Country of ref document: DE

Date of ref document: 19840614

ET Fr: translation filed
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: AT

Payment date: 19851128

Year of fee payment: 7

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

Ref country code: AT

Effective date: 19861203

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

Ref country code: GB

Payment date: 19941123

Year of fee payment: 16

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

Ref country code: FR

Payment date: 19941230

Year of fee payment: 16

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

Ref country code: DE

Payment date: 19950222

Year of fee payment: 16

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

Ref country code: GB

Effective date: 19951203

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

Effective date: 19951203

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

Ref country code: FR

Effective date: 19960830

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

Ref country code: DE

Effective date: 19960903

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST