EP0012309A2 - 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

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Publication number
EP0012309A2
EP0012309A2 EP79104834A EP79104834A EP0012309A2 EP 0012309 A2 EP0012309 A2 EP 0012309A2 EP 79104834 A EP79104834 A EP 79104834A EP 79104834 A EP79104834 A EP 79104834A EP 0012309 A2 EP0012309 A2 EP 0012309A2
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EP
European Patent Office
Prior art keywords
pressure
pump
control device
control
fuel injection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP79104834A
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German (de)
French (fr)
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EP0012309B1 (en
EP0012309A3 (en
Inventor
Erich Ing. Jäger
Werner Ing. Faupel
Heinz Ing. Kuschmierz
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Robert Bosch GmbH
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Robert Bosch GmbH
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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

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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 main 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.
  • this injection timing adjustment device which is also referred to as an automatic spray adjuster, it is achieved that the cheapest combustion and thus the greatest output of the diesel engine even at rapidly changing speeds lasts. Now it has been found that this only fully applies if the air pressure conditions remain the same.
  • the diesel engines are operated at high altitudes, the willingness to ignite is impaired by the reduced air filling (lower compression end temperatures) and the ignition delay is greater, especially at zero load and part load. This results in both steep pressure increases and thus a hard gear of the engine as well as misfires that lead to blue smoke.
  • 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 Bosch GmbH, Stuttgart, see, for example, technical customer service notification VDT-I-46O / 1, 2nd supplement from 5.1977 or SAE Paper No. 760127 from the Automotive Engineering Congress in Detroit, Michigan, from February 23 to 27, 1976), in which the position of a full-load stop of the speed controller integrated in the pump housing, which determines the maximum permissible delivery quantity, as a function of the boost pressure or atmospheric pressure of the engine supplied combustion air is corrected.
  • the hydraulic spray adjuster which is integrated in this injection pump as a function of the speed and / or load, does not take into account the changed air pressure conditions of the combustion air, so that the disadvantages mentioned at the outset are not eliminated despite the correction of the delivery rate.
  • the fuel injection system according to the invention with the characterizing features of the main claim has the advantage that the ignition conditions during operation of diesel engines at high altitudes or when the air weight changes due to supercharging are improved by the air quantity-dependent correction of the otherwise at least speed-dependent controlled start of delivery change.
  • the emission of hydrocarbons and thus of blue smoke is reduced under the conditions mentioned and the engine running too hard is avoided.
  • the measures listed in the subclaims enable advantageous developments and improvements of the fuel injection system specified in the main claim.
  • the necessary air quantity-dependent correction can be achieved in a simple manner in that the delivery pressure of the control pump is increased by a correction actuator of the control device with a decreasing amount of air in the sense of an advance (early shift) of the start of delivery.
  • the necessary correction is achieved in that the correction actuator of the control device engages on the pressure control valve. If the fuel injection system is equipped with a throttle point which, in addition to the pressure control valve, influences the delivery pressure of the control pump and determines the outflow of a partial quantity, the necessary correction can also be achieved without influencing the pressure control valve by changing the flow cross section of the throttle point through the correction actuator of the control device.
  • a particularly advantageous and space-saving design results in a fuel injection system designed according to the preamble of claim 5 in that the throttle point has a throttle cross-section that can be changed by the correction actuator of the control device and that the correction actuator can be actuated by the actuator of the smoke limitation device that also includes the control device.
  • Further simplifications and improvements to this system result from the features of claims 6 and 7.
  • the control device integrated in the smoke control device according to claim 7 means that only one adjustment is made both for adapting the full-load delivery volume to the air pressure of the combustion air supplied to the engine and for the delivery start correction Actuator dependent on air pressure necessary and both corrections are made in parallel controlled. 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.
  • FIG. 1 shows a simplified sectional illustration of the first exemplary embodiment designed as a distributor injection pump
  • FIG. 2 shows a section through the part of the second exemplary embodiment that is essential to the invention due to its space-saving design.
  • the first exemplary embodiment shown in greatly simplified form in FIG. 1 is a piston-type distributor injection pump of the VE..F .. type from Robert Bosch GmbH, Stuttgart, which is manufactured in large series and is known from the publications mentioned in the introduction to the description.
  • a pump piston 12 works in a cylinder bore 11, 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 in a reciprocating and simultaneously rotating movement.
  • a pump working chamber 15 acted upon by the pump piston 12 is in the suction stroke of the pump piston 12 via a suction bore 16 and Control grooves 17 of the pump piston 12 are filled and, during the pressure stroke of the pump piston 12 with the suction bore 16 closed, are conveyed via a longitudinal bore 18 and a conveying groove 19 connected thereto, via a pressure valve 21 and a pressure line 22 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.
  • Fuel is supplied to the interior 24 by a pre-feed pump 26 from a reservoir 27, the feed pressure of which is controlled by a pressure control valve 28 as a function of the speed.
  • 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 discharge 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 24 of the cam drive, be actuates via a regulator sleeve 35 and a regulating lever 34 in a known manner the ring slide 24 serving as the delivery quantity adjusting element of the reciprocating-piston distributor injection pump, the axial position of which, controlled by a regulating lever 36, controls the end of delivery and thus the injection quantity of the pump.
  • control lever 36 bears against 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 tracer pin 42.
  • the scanning 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 incorporated 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-limiting device 44 operates in response to the absolute air pressure and this device can be used both for an atmospheric pressure-dependent correction of the Full load delivery rate as well as for a boost pressure-dependent correction can be used.
  • 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 prefeed pump pressure in the interior 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 injection adjustment device lu, and the associated pressure control valve 28 is of course also built into the pump housing 10 in practice.
  • the pressure in the interior 25 of the pump controlled by the pressure control valve 28 is controlled by a control device 58 depending on the air pressure of the combustion air supplied to the engine corrected in the sense of an early shift occurring when the air pressure falls and thus pressure increase in the interior 25.
  • this is done by changing the bias of a pressure control spring 59 of the pressure control valve 28 gers 61 for the pressure control spring 59 can be changed by a correction actuator 62 depending on the air pressure.
  • the correction actuator 62 similar to the actuator 48 of the smoke control device 44, is provided with a diaphragm can set 63, which is shown here simply by a single pressure can.
  • a space 64 surrounding the diaphragm socket set 63 is connected either to the ambient air pressure or to the suction line of the engine via a line indicated by an arrow 53a.
  • This arrangement enables a correction of the start of spraying which can be controlled completely independently of the smoke limitation device 44.
  • This control device 58 can also act in the same way by influencing the outflow quantity of the pressure control valve 28 or by controlling a counter pressure acting on the side of the pressure control spring 59.
  • the fuel pressure in the interior 25 must experience the pressure change required for the air flow-dependent correction of the start of delivery.
  • 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 guided 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 bush 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 66 screwed into the bore 52, so that this smoke control device 44' serves as a full-load stop, which is controlled by the cam surface 43 and is operated by the cam pressure Via the tracer pin 42 and the stop lever 41 to the full load stop 38, the travel path determines the position of the clamping lever 37 which determines the full load delivery rate of the injection pump.
  • This tensioning lever 37 is the tensioning lever of the speed controller 32 shown in more detail in FIG. 1.
  • the pipe screw connection 66 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 this Ingress of dirt into the space 51. If the line 53 is connected to the intake pipe of a supercharged engine, then 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 box set 49 which also corrects the delivery quantity controls over 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.
  • Control slide 45 By the from Control slide 45 'controlled throttle cross-section of the slot throttle 67, the outflow of a portion of the fuel in the interior 25 under speed-dependent pressure into the return pipe 31 returning to the reservoir 27 is controlled depending on the air quantity, so that the speed-dependent pressure in the interior 25 undergoes an air-quantity-controlled correction and that of Pre-feed pump pressure in the interior 25 dependent change in delivery start is adjusted accordingly by the spray adjuster to the amount of air.
  • the stroke of the control slide 45 ' is adjusted so 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 72 in the wall of the pump housing 10 connected to the return line 31.
  • the described air pressure-dependent and thus air volume-dependent correction of the otherwise at least speed-dependent delivery start change can be applied analogously to any other type of spray timing adjustment device, including electrically controlled or regulated ones.

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

Die Erfindung geht aus von einer Kraftstoffeinspritzanlage nach der Gattung des Hauptanspruchs. 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-Endtemperaturen) 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 Blaurauch führen.The invention is based on a fuel injection system according to the preamble of the main 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. Through the use of this injection timing adjustment device, which is also referred to as an automatic spray adjuster, it is achieved that the cheapest combustion and thus the greatest output of the diesel engine even at rapidly changing speeds lasts. Now it has 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 willingness to ignite is impaired by the reduced air filling (lower compression end temperatures) and the ignition delay is greater, especially at zero load and part load. This results in both steep pressure increases and thus a hard gear of the engine as well as misfires that lead to blue smoke.

Es ist bereits eine Kraftstoffeinspritzanlage der gattungsgemäßen Bauart mit einer als Verteilereinspritzpumpe ausgebildeten Kraftstoffeinspritzpumpe bekannt (mit VerteilerEinspritzpumpe VE..F.. der Robert Bosch GmbH, Stuttgart, siehe z.B. technische Kundendienstmitteilung VDT-I-46O/1, 2. Nachtrag vom 5.1977 oder SAE-Paper Nr. 760127 vom Automotive Engineering Congressin Detroit, Michigan, vom 23. bis 27. Februar 1976), bei der die, die maximal zulässige Fördermenge bestimmende Lage eines Vollastanschlages des in das Pumpengehäuse integrierten Drehzahlreglers in Abhängigkeit vom Ladedruck 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 Bosch GmbH, Stuttgart, see, for example, technical customer service notification VDT-I-46O / 1, 2nd supplement from 5.1977 or SAE Paper No. 760127 from the Automotive Engineering Congress in Detroit, Michigan, from February 23 to 27, 1976), in which the position of a full-load stop of the speed controller integrated in the pump housing, which determines the maximum permissible delivery quantity, as a function of the boost pressure or atmospheric pressure of the engine supplied combustion air is corrected. However, the hydraulic spray adjuster, which is integrated in this injection pump as a function of the speed and / or load, does not take into account the changed air pressure conditions of the combustion air, so that the disadvantages mentioned at the outset are not eliminated despite the correction of the delivery rate.

Bei einer durch die DE-OS 26 48 043 bekannt gewordenen Verteilereinspritzpumpe mit hydraulischem Spritzversteller wird durch temperaturabhängig gesteuertes Ändern des den 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 injection adjuster which has become known from DE-OS 26 48 043, the position is controlled by changing the temperature as a function of temperature piston of the injection adjuster acting on the pre-feed pump pressure of the speed-dependent injection start adjustment is superimposed on a temperature-dependent early adjustment, which is only effective from the start until the engine warms up. 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.

Vorte_le der ErfindungVorte_le the invention

Die erfindungsgemäße Kraftstoffeinspritzanlage mit den kennzeichnenden Merkmalen des Hauptanspruchs 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 Emission 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 the main claim has the advantage that the ignition conditions during operation of diesel engines at high altitudes or when the air weight changes due to supercharging are improved by the air quantity-dependent correction of the otherwise at least speed-dependent controlled start of delivery change. The emission of hydrocarbons and thus of blue smoke is reduced under the conditions mentioned and the engine running too hard is avoided.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Kraftstoffeinspritzanlage möglich. So kann in besonders vorteilhafter Weise bei einer Kraftstoffeinspritzanlage mit einem in den Nockenantrieb der Einspritzpumpe eingebauten, als Spritzzeitpunktverstelleinrichtung dienenden und von einem drehzahlabhängigen Förderdruck einer Steuerpumpe betätigbaren hydraulischen Spritzversteller die notwendige luftmengenabhängige Korrektur auf einfache Weise dadurch erreicht werden, daß der Förderdruck der Steuerpumpe durch ein Korrekturstellglied der Steuervorrichtung bei sich verringernder Luftmenge im Sinne einer Vorverlegung (Frühverschiebung) des Förderbeginns erhöht wird. Bei einer Kraftstoffeinspritzanlage, bei der der Förderdruck der Steuerpumpe durch ein Drucksteuerventil drehzahlabhängig steuerbar ist, wird die notwendige Korrektur dadurch erreicht, daß das Korrekturstellglied der Steuervorrichtung am Drucksteuerventil eingreift. Ist die Kraftstoffeinspritzanlage mit einer zusätzlich zum Drucksteuerventil den Förderdruck der Steuerpumpe beeinflussenden und den Abfluß einer Teilmenge bestimmenden Drosselstelle ausgestattet, ist auch ohne Beeinflussung des Drucksteuerventils die notwendige Korrektur dadurch erreichbar, daß der Durchflußquerschnitt der Drosselstelle durch das Korrekturstellglied der Steuervorrichtung verändert wird.The measures listed in the subclaims enable advantageous developments and improvements of the fuel injection system specified in the main claim. In a particularly advantageous manner, in a fuel injection system with a hydraulic injection adjuster built into the cam drive of the injection pump and serving as the injection timing adjustment device and which can be actuated by a speed-dependent delivery pressure of a control pump, the necessary air quantity-dependent correction can be achieved in a simple manner in that the delivery pressure of the control pump is increased by a correction actuator of the control device with a decreasing amount of air in the sense of an advance (early shift) of the start of delivery. In a fuel injection system in which the delivery pressure of the control pump can be controlled in a speed-dependent manner by a pressure control valve, the necessary correction is achieved in that the correction actuator of the control device engages on the pressure control valve. If the fuel injection system is equipped with a throttle point which, in addition to the pressure control valve, influences the delivery pressure of the control pump and determines the outflow of a partial quantity, the necessary correction can also be achieved without influencing the pressure control valve by changing the flow cross section of the throttle point through the correction actuator of the control device.

Eine besonders vorteilhafte und raumsparende Bauweise ergibt sich bei einer nach dem Oberbegriff des Anspruchs 5 ausgebildeten Kraftstoffeinspritzanlage dadurch, daß die Drosselstelle einen durch das Korrekturstellglied der Steuervorrichtung veränderbaren Drosselquerschnitt aufweist und daß das Korrekturstellglied vom Stellglied der zugleich die Steuervorrichtung umfassenden Rauchbegrenzungsvorrichtung betätigbar ist. Weitere Vereinfachungen und Verbesserungen dieser Anlage ergeben sich durch die Merkmale der Ansprüche 6 und 7. Durch die nach Anspruch 7 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.A particularly advantageous and space-saving design results in a fuel injection system designed according to the preamble of claim 5 in that the throttle point has a throttle cross-section that can be changed by the correction actuator of the control device and that the correction actuator can be actuated by the actuator of the smoke limitation device that also includes the control device. Further simplifications and improvements to this system result from the features of claims 6 and 7. The control device integrated in the smoke control device according to claim 7 means that only one adjustment is made both for adapting the full-load delivery volume to the air pressure of the combustion air supplied to the engine and for the delivery start correction Actuator dependent on air pressure necessary and both corrections are made in parallel controlled. 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

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine vereinfachte Schnittdarstellung des als Verteilereinspritzpumpe ausgebildeten ersten Ausführungsbeispiels und Figur 2 einen Schnitt durch den erfindungswesentlichen Teil des zweiten, durch seine raumsparende Bauweise bevorzugten Ausführungsbeispiels.Two embodiments of the invention are shown in the drawing and explained in more detail in the following description. FIG. 1 shows a simplified sectional illustration of the first exemplary embodiment designed as a distributor injection pump, and FIG. 2 shows a section through the part of the second exemplary embodiment that is essential to the invention due to its space-saving design.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Bei dem in Figur 1 stark vereinfacht dargestellten ersten Ausführungsbeispiel handelt es sich um eine Hubkolben-Verteilereinspritzpumpe der Bauart VE..F.. der Robert Bosch GmbH, Stuttgart, die in Großserie gefertigt wird und aus den in der Beschreibungseinleitung genannten Druckschriften bekannt ist.The first exemplary embodiment shown in greatly simplified form in FIG. 1 is a piston-type distributor injection pump of the VE..F .. type from Robert Bosch GmbH, Stuttgart, which is manufactured in large series 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 Druckleitung 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.In a housing 10, a pump piston 12 works in a cylinder bore 11, 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 in a reciprocating and simultaneously rotating movement. A pump working chamber 15 acted upon by the pump piston 12 is in the suction stroke of the pump piston 12 via a suction bore 16 and Control grooves 17 of the pump piston 12 are filled and, during the pressure stroke of the pump piston 12 with the suction bore 16 closed, are conveyed via a longitudinal bore 18 and a conveying groove 19 connected thereto, via a pressure valve 21 and a pressure line 22 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 24 wird von einer Vorförderpumpe 26 Kraftstoff aus einem Vorratsbehälter 27 zugeführt, dessen Förderdruck durch ein Drucksteuerventil 28 drehzahlabhängig gesteuert wird. Parallel 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 Vcrratsbehälter 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 Stirnnockenscheibe 24 des Nockentriebs antreibenden Antriebswelle 34 in Drehbewegung versetzt wird, betätigt über eine Reglermuffe 35 und einen Regelhebel 34 in bekannter Weise den als Fördermengenverstellglied der Hubkolben-Verteilereinspritzpumpe dienenden Ringschieber 24, dessen von einem Regelhebel 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. Fuel is supplied to the interior 24 by a pre-feed pump 26 from a reservoir 27, the feed pressure of which is controlled by a pressure control valve 28 as a function of the speed. 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 discharge 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 24 of the cam drive, be actuates via a regulator sleeve 35 and a regulating lever 34 in a known manner the ring slide 24 serving as the delivery quantity adjusting element of the reciprocating-piston distributor injection pump, the axial position of which, controlled by a regulating lever 36, controls the end of delivery and thus the injection quantity of the pump. In the drawn full load position of the controller parts, the control lever 36 bears against 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 Anschlaghebels 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 Mem- brandosensatz 49 arbeitet die Rauchbegrenzungsvorrichtung 44 in Abhängigkeit vom absoluten Luftdruck und diese Vorrichtung kann sowohl für eine atmosphärendruckabhängige Korrektur der Vollastfördermenge 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 tracer pin 42. The scanning 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 incorporated 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 Mem - brandosensatz 49, the smoke-limiting device 44 operates in response to the absolute air pressure and this device can be used both for an atmospheric pressure-dependent correction of the Full load delivery rate as well as for a boost pressure-dependent correction can be used.

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 Innenraum 25 im Sinne einer Frühverstellung des Förderbeginns. Die von der Antriebswelle 34 angetriebene Vorförderpumpe 26, die nur der Übersicht halber außerhalb des Pumpengehäuses 10 gezeichnet ist, dient dabei als Steuerpumpe der Spritzverstelleinrichtungelu,nd 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 prefeed pump pressure in the interior 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 injection adjustment device lu, and the associated pressure control valve 28 is of course also built into the pump housing 10 in practice.

Um neben der luftdruckabhängig gesteuerten Fördermengenkorrektur mittels der Rauchbegrenzungsvorrichtung 44 eine für den Betrieb des Motors ebenfalls luftdruckabhängig gesteuerte Korrektur der Förderbeginnänderung zu erhalten, wird der vom Drucksteuerventil 28 gesteuerte Druck im Innenraum 25 der Pumpe durch eine Steuervorrichtung 58 in Abhängigkeit vom Luftdruck der dem Motor zugeführten Verbrennungsluft im Sinne einer bei fallendem Luftdruck erfolgenden Frühverschiebung und damit Drucksteigerung im Innenraum 25 korrigiert. Dies geschieht bei dem in Figur 1 dargestellten Ausführungsbeispiels mittels einer Vorspannungsänderung einer Drucksteuerfeder 59 des Drucksteuerventils 28. Dazu ist die Lage eines Federwiderlagers 61 für die Drucksteuerfeder 59 durch ein Korrekturstellglied 62 in Abhängigkeit vom Luftdruck änderbar. Das Korrekturstellglied 62 ist dazu, ähnlich wie das Stellglied 48 der Rauchbegrenzungsvorrichtung 44, mit einem hier vereinfacht nur durch eine einzige Druckdose dargestellten Membrandosensatz 63 versehen. Ein den Membrandosensatz 63 umgebender Raum 64 ist dabei entweder an den Umgebungsluftdruck oder über eine durch einen Pfeil 53a angedeutete Leitung an die Saugleitung des Motors angeschlossen. Diese Anordnung ermöglicht eine vollkommen unabhängig von der Rauchbegrenzungsvorrichtung 44 steuerbare Korrektur des Spritzbeginns. Ein gleichwirkender Eingriff dieser Steuervorrichtung 58 kann auch durch Beeinflussung der Abströmmenge des Drucksteuerventils 28 oder durch Steuerung eines auf der Seite der Drucksteuerfeder 59 wirksamen Gegendrucks erfolgen. Durch alle möglichen und von der Erfindung umfaßten Varianten muß jedoch der Kraftstoffdruck im Innenraum 25 die zur luftmengenabhängigen Korrektur des Förderbeginns erforderliche Druckänderung erfahren.In order to obtain a correction of the start of delivery change, which is also dependent on the air pressure and controlled for the operation of the engine, in addition to the air pressure-dependent delivery rate correction by means of the smoke limitation device 44, the pressure in the interior 25 of the pump controlled by the pressure control valve 28 is controlled by a control device 58 depending on the air pressure of the combustion air supplied to the engine corrected in the sense of an early shift occurring when the air pressure falls and thus pressure increase in the interior 25. In the embodiment shown in FIG. 1, this is done by changing the bias of a pressure control spring 59 of the pressure control valve 28 gers 61 for the pressure control spring 59 can be changed by a correction actuator 62 depending on the air pressure. For this purpose, the correction actuator 62, similar to the actuator 48 of the smoke control device 44, is provided with a diaphragm can set 63, which is shown here simply by a single pressure can. A space 64 surrounding the diaphragm socket set 63 is connected either to the ambient air pressure or to the suction line of the engine via a line indicated by an arrow 53a. This arrangement enables a correction of the start of spraying which can be controlled completely independently of the smoke limitation device 44. This control device 58 can also act in the same way by influencing the outflow quantity of the pressure control valve 28 or by controlling a counter pressure acting on the side of the pressure control spring 59. However, due to all possible variants included in the invention, the fuel pressure in the interior 25 must experience the pressure change required for the air flow-dependent correction of the start of delivery.

Bei dem in Figur 2 nur ausschnittweise dargestellten Ausführungsbeispiel sind gegenüber Figur 1 gleiche Teile gleich bezichnet und abweichende Teile mit einem Indexstrich versehen. 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 Führungsbüchse 65 geführt, die in das Pumpengehäuse 10 eingeschraubt und mittels einer Ringmutter 66 befestigt ist. Die den Steuerschieber 45' aufnehmende Bohrung 46 in der Führungsbüchse 65 ist zum Innenraum 25 der Einspritzpumpe hin geschlossen, so daß der im Innenraum 25 herrschende Vorförderpumpendruck nicht auf den Steuerschieber 45' einwirken kann.In the exemplary embodiment shown only in detail in FIG. 2, the same parts as in FIG. 1 are identified in the same way and different parts are provided with an index line. 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 guided 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 bush 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 Rauchbegren- zungsvorrichtung 44' ist über eine in die Bohrung 52 eingeschraubte Rohrverschraubung 66 mit der Umgebungsluft verbun- den, 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 die die Vollastfördermenge der Einspritzpumpe bestimmende Stellung des Spannhebels 37 bestimmt. Bei diesem Spannhebel 37 handelt es sich um den in Figur 1 näher dargestellten Spannhebel des Drehzahlreglers 32. Die Rohrverschraubung 66 ermöglicht die Zufuhr der unter Atmosphärendruck stehenden Luft über die Leitung 53 vom Luftfilter oder Ansaugrohr der Brennkraftmaschine her oder in der gezeichneten kurzzen 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 66 screwed into the bore 52, so that this smoke control device 44' serves as a full-load stop, which is controlled by the cam surface 43 and is operated by the cam pressure Via the tracer pin 42 and the stop lever 41 to the full load stop 38, the travel path determines the position of the clamping lever 37 which determines the full load delivery rate of the injection pump. This tensioning lever 37 is the tensioning lever of the speed controller 32 shown in more detail in FIG. 1. The pipe screw connection 66 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 this Ingress of dirt into the space 51. If the line 53 is connected to the intake pipe of a supercharged engine, then this device can also work as a boost pressure-dependent full-load stop.

Bei diesem Ausführungsbeispl 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 Förderbeginnänderung 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 daß immer eine für die Kühlung des Innenraums 25 erforderliche Teilmenge des Kraftstoffs 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 72 in der Wand des Pumpengehäuses 10 mit der Rückflußleitung 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 box set 49 which also corrects the delivery quantity controls over 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. By the from Control slide 45 'controlled throttle cross-section of the slot throttle 67, the outflow of a portion of the fuel in the interior 25 under speed-dependent pressure into the return pipe 31 returning to the reservoir 27 is controlled depending on the air quantity, so that the speed-dependent pressure in the interior 25 undergoes an air-quantity-controlled correction and that of Pre-feed pump pressure in the interior 25 dependent change in delivery start is adjusted accordingly by the spray adjuster to the amount of air. The stroke of the control slide 45 'is adjusted so 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 72 in the wall of the pump housing 10 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 einer solchen mit einer nur luftdruckabhängig arbeitenden Rauchbegrenzungsvorrichtung 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 that with a smoke control device which only works as a function of air pressure, since the function of the air-dependent correction of the change in the start of delivery is in a simple manner by Actuator 48 'adopted.

Die beschriebene luftdruckabhängig gesteuerte und damit luftmengenabhängige Korrektur der ansonsten mindestens drehzahlabhängigen Förderbeginnänderung kann bei jeder anderen Bauart von Spritzzeitpunktverstelleinrichtungen, 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 delivery start change can be applied analogously to any other type of spray timing adjustment device, including electrically controlled or regulated ones.

Claims (7)

1. Kraftstoffeinspritzanlage für Diesel-Brennkraftmaschinen, insbesondere für Fahrzeug-Dieselmotoren, mit einer den Förderbeginn mindestens eines Pumpenkolbens einer Kraftstoffeinspritzpumpe in Abhängigkeit von mindestens einer Betriebskenngröße, vorzugsweise der Drehzahl, steuernden, Spritzzeitpunktverstelleinrichtung, dadurch gekennzeichnet, daß die von der Spritzzeitpunktverstelleinrichtung (56) gesteuerte Förderbeginnänderung durch eine in Abhängigkeit von der dem Motor zugeführten Luftmenge arbeitende Steuervorrichtung (58, 58') zusätzlich korrigierbar ist.1.Fuel injection system for diesel internal combustion engines, in particular for vehicle diesel engines, with a start of delivery of at least one pump piston of a fuel injection pump as a function of at least one operating parameter, preferably the speed, which controls the spray timing adjustment device, characterized in that the spray timing adjustment device (56) controls it Change in the start of delivery can be additionally corrected by a control device (58, 58 ') which operates as a function of the amount of air supplied to the engine. 2. Kraftstoffeinspritzanlage mit einem in den Nockenantrieb der Einspritzpumpe eingebauten, als Spritzzeitpunktverstelleinrichtung dienenden und von einem drehzahlabhängigen Förderdruck einer Steuerpumpe betätigbaren hydraulischen Spritzversteller, nach Anspruch 1, dadurch gekennzeichnet, daß der Förderdruck der Steuerpumpe (26) durch ein Korrekturstellglied (62, 45a') der Steuervorrichtung (58, 58') bei sich verringender Luftmenge im Sinne einer Vorverlegung (Frühverschiebung) des Förderbeginns erhöht wird.2. Fuel injection system with a hydraulic injection adjuster built into the cam drive of the injection pump, serving as the injection timing adjustment device and actuable by a speed-dependent delivery pressure of a control pump, according to claim 1, characterized in that the delivery pressure of the control pump (26) by a correction actuator (62, 45a ') the control device (58, 58 ') is increased as the amount of air decreases in the sense of an advance (early shift) of the start of delivery. 3. Kraftstoffeinspritzanlage, bei der der Förderdruck der Steuerpumpe durch ein Drucksteuerventil mindestens drehzahlabängig steuerbar ist, nach Anspruch 2, dadurch gekennzeichnet, daß das Korrekturstellglied (62) der Steuervorrichtung (58) am Drucksteuerventil (28) eingreift (Figur 1).3. Fuel injection system, in which the delivery pressure of the control pump can be controlled at least as a function of speed by a pressure control valve, according to claim 2, characterized in that the correction actuator (62) of the control device (58) engages on the pressure control valve (28) (Figure 1). 4. Kraftstoffeinspritzanlage mit einer zusätzlich zum Drucksteuerventil den Förderdruck der Steuerpumpe beeinflussenden und den Abfluß einer Teilmenge bestimmenden Drosselstelle, nach Anspruch 3, dadurch gekennzeichnet, daß der Durchflußquerschnitt der Drosselstelle (67) durch das Korrekturstellglied (45a') der Steuervorrichtung (58') veränderbar ist (Figur 2).4. Fuel injection system with an additional to the pressure control valve influencing the delivery pressure of the control pump and determining the outflow of a portion of the throttle point, according to claim 3, characterized in that the flow cross section of the throttle point (67) by the correction actuator (45a ') of the control device (58') can be changed is (Figure 2). 5. Kraftstoffeinspritzanlage nach Anspruch 2, bei der der als Saugraum ausgebildete Innenraum der Einspritzpumpe, insbesondere einer Verteilereinspritzpumpe, mit unter mindestens drehzahlabhängig gesteuertem Vorförderpumpendruck stehendem Kraftstoff gefüllt ist und einen Drehzahlregler aufnimmt, bei dem der Weg eines mit dem Fördermengenverstellglied der Einspritzpumpe verbundenen Regelhebels durch die die maximal zulässige Vollastfördermenge bestimmende Lage eines Vollastanschlags begrenzt ist, welche von einem in Abhängigkeit vom Druck der dem Motor zugeführten Luft arbeitenden Stellglied einer Rauchbegrenzungsvorrichtung festlegbar und änderbar ist, und bei der die Vorförderpumpe als Steuerpumpe des hydraulischen Spritzverstellers dient, wobei der Vorförderpumpendruck außer durch ein Drucksteuerventil durch eine den dauernden Abfluß einer Teilmenge aus dem Innenraum bestimmende Drosselstelle in eine Rückflußleitung steuerbar ist, dadurch gekennzeichnet, daß die Drosselstelle (67) einen durch das Korrekturstellglied (45a') der Steuervorrichung (58') veränderbaren Drosselquerschnitt aufweist und daß das Korrekturstellglied (45a') vom Stellglied (45') der zugleich die Steuervorrichtung (58') umfassenden Rauchbegrenzungsvorrichtung (44') betätigbar ist (Figur 2).5. The fuel injection system according to claim 2, in which the interior of the injection pump, in particular a distributor injection pump, which is designed as a suction space, is filled with fuel standing under at least speed-dependent pre-feed pump pressure and accommodates a speed controller in which the path of a control lever connected to the delivery quantity adjustment element of the injection pump is controlled by the the maximum permissible full-load delivery position of a full-load stop is limited, which can be determined and changed by an actuator of a smoke control device that works as a function of the pressure of the air supplied to the engine, and in which the pre Feed pump serves as a control pump of the hydraulic injection adjuster, the pre-feed pump pressure being controllable in addition to a pressure control valve by a throttle point which determines the continuous outflow of a partial quantity from the interior into a return line, characterized in that the throttle point (67) is controlled by the correction actuator (45a '). the control device (58 ') has a variable throttle cross-section and that the correction actuator (45a') can be actuated by the actuator (45 ') of the smoke control device (44') which also comprises the control device (58 ') (Figure 2). 6. Kraftstoffeinspritzanlage nach Anspruch 5, dadurch gekennzeichnet, daß das Korrekturstellglied von einem Teil (45a') des Stellglieds (48') der Rauchbegrenzungsvorrichtung (44') gebildet ist.6. Fuel injection system according to claim 5, characterized in that the correction actuator of a part (45 a ') of the actuator (48') of the smoke control device (44 ') is formed. 7. Kraftstoffeinspritzanlage mit einem in einer Führungsbüchse geführten Steuerschieber des Stellglieds der Rauchbegrenzungsvorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß der das Korrekturstellglied bildende Teil (45a') des Stellglieds (48') eine in den Steuerschieber (45') eingearbeitete Ringnut (68) aufweist und mit einer in die Wand der Führungsbüchse (65) eingearbeiteten und als Drosselstelle dienenden Schlitzdrossel (67) die Steuervorrichtung (58') bildet, wobei der wirksame Drosselquerschnitt durch die luftdruckabhängig gesteuerte axiale Lage der Ringnut (68) veränderbar ist.7. Fuel injection system with a control slide of the actuator of the smoke control device guided in a guide bush, according to claim 6, characterized in that the part (45a ') of the actuator (48') forming the correction actuator has an annular groove (68) incorporated in the control slide (45 '). and forms the control device (58 ') with a slot throttle (67) which is worked into the wall of the guide bush (65) and serves as a throttle point, the effective one Throttle cross section can be changed by the axial position of the annular groove (68), which is controlled as a function of 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 true EP0012309A2 (en) 1980-06-25
EP0012309A3 EP0012309A3 (en) 1980-07-09
EP0012309B1 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)

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EP0076458A1 (en) * 1981-10-07 1983-04-13 Robert Bosch Gmbh Fuel injection pump for internal-combustion engines
FR2516981A1 (en) * 1981-11-21 1983-05-27 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
EP0080113A1 (en) * 1981-11-24 1983-06-01 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
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
WO1990012957A1 (en) * 1989-04-18 1990-11-01 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
EP0436054A1 (en) * 1990-01-04 1991-07-10 Robert Bosch Gmbh Speed governor for the fuel injection pump of an internal combustion engine

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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
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
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
DE3919064A1 (en) * 1989-06-10 1990-12-13 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
US5144926A (en) * 1990-08-29 1992-09-08 Zexel Corporation Fuel injection pump of distribution type
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

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0076458A1 (en) * 1981-10-07 1983-04-13 Robert Bosch Gmbh Fuel injection pump for internal-combustion engines
FR2516981A1 (en) * 1981-11-21 1983-05-27 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
EP0080113A1 (en) * 1981-11-24 1983-06-01 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
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
WO1990012957A1 (en) * 1989-04-18 1990-11-01 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
EP0436054A1 (en) * 1990-01-04 1991-07-10 Robert Bosch Gmbh Speed governor for the fuel injection pump of an internal combustion engine

Also Published As

Publication number Publication date
BR7908187A (en) 1980-07-22
DE2966972D1 (en) 1984-06-14
JPS5584824A (en) 1980-06-26
EP0012309B1 (en) 1984-05-09
JPS63611B2 (en) 1988-01-07
DE2854422A1 (en) 1980-07-03
ATE7417T1 (en) 1984-05-15
US4384560A (en) 1983-05-24
EP0012309A3 (en) 1980-07-09

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