EP0910739A1 - Fuel injection system - Google Patents

Fuel injection system

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Publication number
EP0910739A1
EP0910739A1 EP98912246A EP98912246A EP0910739A1 EP 0910739 A1 EP0910739 A1 EP 0910739A1 EP 98912246 A EP98912246 A EP 98912246A EP 98912246 A EP98912246 A EP 98912246A EP 0910739 A1 EP0910739 A1 EP 0910739A1
Authority
EP
European Patent Office
Prior art keywords
injection
cam
pump
valve
area
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
EP98912246A
Other languages
German (de)
French (fr)
Other versions
EP0910739B1 (en
Inventor
Stuart-William Nicol
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0910739A1 publication Critical patent/EP0910739A1/en
Application granted granted Critical
Publication of EP0910739B1 publication Critical patent/EP0910739B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • F02M45/063—Delivery stroke of piston being divided into two or more parts, e.g. by using specially shaped cams

Definitions

  • the invention is based on a fuel injection system according to the preamble of claim 1.
  • a distributor injection pump is provided as the fuel injection pump, with a reciprocatingly driven and at the same time rotating pump piston, each of one of a plurality of injection lines during its rotary movement and its pumping stroke lead to one fuel injection valve each, supplied with fuel brought to the injection pressure.
  • the electrically controlled valve which is a solenoid valve
  • the electrically controlled valve is opened briefly in order to relieve the pump work space and to briefly reduce the fuel pressure achieved.
  • a very fast switching solenoid valve is required, which requires considerable effort in the electrical control and in the construction of the valve.
  • the fact that the injection is interrupted is particularly disadvantageous must be time-controlled by a solenoid valve. As a result, an increasing part of the available cam stroke for interrupting the injection is used with increasing speed.
  • High-pressure fuel delivery to the fuel injector opens in the direction of delivery and closes when the injection is ended and which is suitable for reducing pressure waves between the pressure valve and the fuel injection valve and for maintaining a desired constant stand pressure in this area during the injection breaks.
  • the solution according to the invention ensures a safe interruption of the injection between the pre-injection and the main injection with low demands on the speed of a time-controlled valve.
  • the constructionally supported interruption of the injection ensures that a safe interruption of the injection between the pre-injection and the main injection can be maintained even at a higher speed, without there being a loss of the cam stroke that can be provided for high-pressure delivery.
  • the speed-independent influence of the switching time is compensated by the second part of the cam, so that there are no overly high demands on the speed of the electrically controlled valve.
  • FIG. 1 shows a schematic diagram of a fuel injection pump that is controlled by a solenoid valve
  • FIG. 2 shows a course of the cam track according to the invention in the form of a cam elevation curve over the angle of rotation with a first control sequence of the valve at low engine speed
  • FIG. 3 shows a course of the cam track according to the invention the angle of rotation with a second control sequence of the valve at high engine speed.
  • the solution according to the invention is implemented using a distributor injection pump, as is shown schematically in FIG. 1. It is a distribution unit Injection pump of the axial piston type, although the object of the invention can also be used in other fuel injection pumps, such as, for. B. Distributor injection pumps of the radial piston pump type or single pumps with only one pump piston for supplying a single cylinder
  • a pump piston 1 is provided in the distributor injection pump of the type shown in FIG.
  • the pump piston is provided with a cam 6, which has axially downward facing cams 5 of the embodiment according to the invention, for. B. coupled via a spring, not shown.
  • the cam disk is rotating, in particular synchronously with the speed of the internal combustion engine supplied by the injection pump, from a drive shaft, not shown, in a known manner
  • the cam disc runs under the influence of the spring on a known axially fixed roller ring and subsequently sets the rotating pump and distributor piston in a reciprocating conveying and suctioning movement.
  • the timing or angle of rotation of the rollers on the cam flank thus determines the stroke position of the pump piston.
  • the pump piston comes into connection with one of several injection lines 7 via a distributor groove 8 in the outer surface of the pump and distributor piston.
  • the distributor groove is continuously connected to the pump work space via a longitudinal channel 9.
  • the injection line introduces via Pressure valve 12 to a fuel injection valve 13 which is assigned to the respective cylinder of an internal combustion engine.
  • the pump working chamber 10 is supplied with fuel via a suction line 15, which is supplied by a suction chamber 17, which is essentially only shown in broken lines and is enclosed within the housing of the fuel injection pump.
  • the suction chamber receives fuel from a fuel delivery pump 18, which is synchronous with the fuel injection pump, eg. B. is driven by the drive shaft and thus promotes fuel in speed-dependent amounts in the suction chamber.
  • a fuel delivery pump 18 which is synchronous with the fuel injection pump, eg. B. is driven by the drive shaft and thus promotes fuel in speed-dependent amounts in the suction chamber.
  • an additional pressure control valve 19 the pressure in the suction chamber is usually controlled as a function of speed, if with the help of this
  • Fuel continuously flows back to the reservoir 23 via an overflow throttle 22, so that cooling of the injection pump or degassing of the suction chamber is thereby ensured.
  • the suction line 15 leads via a check valve 16 into the pump work space, the check valve opening in the direction of the pump work space.
  • an electrically controlled valve 24 is provided, which controls a bypass line 21 to the pressure valve 16 and with the aid of which a connection is made between the pump work chamber 10 and the suction chamber 17 when the valve is opened and the pump work chamber 10 is closed when the valve is closed.
  • the electrically controlled valve 24 symbolized as a solenoid valve is controlled by a control device 25 according to operating parameters in a manner known per se. With a sufficiently large flow cross section of the valve 24, the check valve 16 can also be omitted. In this case the Pump work space during the suction stroke is filled exclusively via the electrically controlled valve.
  • the start of the high pressure delivery of the pump piston is controlled.
  • the start of spraying can also be controlled with the valve.
  • the injection start can be adjusted by a separate injection start adjustment device, which is known to have a cam drive part that can be rotated relative to the pump piston that scans the cam.
  • the high-pressure delivery sides of the cam flanks of the cams 5 are designed in such a way that, as shown in FIG. 2 or 3, they produce a stroke profile of the pump piston over time, which is divided into a first region V which begins after the delivery stroke of the piston after a small one Delivery stroke ends, in a second area P in which the piston is then not moved at all or only so slightly in the conveying direction that it is not effective for high-pressure delivery in this area and an injection break occurs, and finally in a third area H, in which the The cam flank rises again and shifts the pump piston further for further delivery of the main injection quantity.
  • area P the cam can be right, slightly rising or also slightly falling.
  • the pre-injection is still controlled by the electrically controlled valve in such a way that it is closed when the rollers come into the second area P.
  • the electrically controlled valve e.g. a solenoid valve or a valve actuated by a piezo, for controlling the start of the pre-injection quantity delivery in U.T., i.e. is closed from a base circle before the cam curve rises and is opened again in the cam area V before the cam area P is reached.
  • valve 24 After a pause in spraying in region P, valve 24 then re-closes with the start of high-pressure delivery for the main injection in the subsequent cam flank part H, where the high-pressure delivery is then interrupted again by opening valve 24 and the main injection is ended.
  • the requirements for the exactness of the control point are lower than with any other control of a spray start.
  • valve 24 is controlled so that it is only closed in the region of the cam flank P, so that it is securely closed when the Fuel delivery for the now main injection takes place in the area of the cam flank part H adjoining the area P.
  • the end of the injection is in turn controlled by opening the valve, which usually takes place before the top dead center of the cam of the injection pumps.
  • This control has the advantage that at high speeds the pump working space of the injection pump can be sufficiently filled with fuel, since the filling phase is now extended compared to the control at low speed and the piston movement in the filling direction, i.e. during the suction stroke only has to reach the stroke area on which the second area P is located. Because the high-pressure pumping only takes place from area P, the required filling quantity of the pumping work space is reduced.
  • the electrically controlled valve therefore closes only in the region P of the cam flank, so that the suction stroke can be fully utilized for the suction of fuel via the cam flank V running down.
  • the inflow filling effect has an effect in the beginning of the cam flank in front of area P as long as the valve is not yet closed.

Abstract

The invention relates to a fuel injection system having a fuel injection pump, the high-pressure delivery of which is determined by an electrically operated valve (24) which controls a discharge channel (21). The high-pressure delivery phase is determined by closing this valve (24). In order to carry out an injection, sub-divided into a pre-injection and a main injection, and in order to simplify control of the electrically operated valve (24), the cam (5) driving the pump piston (1) is so designed as to create an area in which the pump piston (1), in order to interrupt injection between pre-injection and main injection, maintains the position attained, moves backward, or moves forward more slowly, and the valve (24) is controlled in such a way that, at low rotational speed, the pump working area (10) is closed when the pump piston (1) is in front of the beginning of the cam area (V) preceding the area (P), and open when the pump piston (1) is in the cam area (V), and is closed again at the beginning of the cam area (H) following the area (P), before being opened again in order to complete injection; whereas at high rotational speed the first closing of the valve (24) per delivery stroke takes place in the area (P) without prior pre-injection.

Description

KraftstoffeinspritzsystemFuel injection system
Stand der TechnikState of the art
Die Erfindung geht von einem Kraftstoffeinspritzsystem gemäß der Gattung des Patentanspruchs 1 aus. Bei einem solchen, durch die DE-A-36 44 257 bekannten System ist als Kraft- Stoffeinspritzpumpe eine Verteilereinspritzpumpe vorgesehen, mit einem hin- und hergehend angetriebenen und zugleich rotierenden Pumpenkolben, der bei seiner Drehbewegung und seinem Pumphub jeweils eine von mehreren Einspritzleitungen, die zu je einem Kraftstoffeinspritzventil führen, mit auf Einspritzdruck gebrachtem Kraftstoff versorgt. ZurThe invention is based on a fuel injection system according to the preamble of claim 1. In such a system known from DE-A-36 44 257, a distributor injection pump is provided as the fuel injection pump, with a reciprocatingly driven and at the same time rotating pump piston, each of one of a plurality of injection lines during its rotary movement and its pumping stroke lead to one fuel injection valve each, supplied with fuel brought to the injection pressure. to
Unterteilung der Einspritzung in eine Voreinspritzung und eine Haupteinspritzung wird das elektrisch gesteuerte Ventil, das ein Magnetventil ist, kurzzeitig geöffnet, um so den Pumpenarbeitsraum zu entlasten und den erzielten Kraft- Stoffdruck kurzzeitig abzubauen. Dies bedeutet, daß ein sehr schnell schaltendes Magnetventil erforderlich ist, das einen erheblichen Aufwand an die elektrische Steuerung und an die Konstruktion des Ventils erfordert. Besonders nachteilig ist dabei die Tatsache, daß die Unterbrechung der Einspritzung durch ein Magnetventil zeitgesteuert erfolgen muß. Dadurch wird mit zunehmender Drehzahl ein immer größer werdender Teil des verfügbaren Nockenhubes für die Unterbrechung der Einspritzung in Anspruch genommen. Bei einer Verteilerein- spritzpumpe steht ein gegenüber den Möglichkeiten einer Reiheneinspritzpumpe, bei der ein Nocken allein jeweils einen Pumpenkolben antreibt ein wesentlich geringerer Hub pro Einispritzvorgang zur Verfügung, weil der hier verfügbare Nockenhub wegen der begrenzten Länge der Nockenbahn beschränkt ist. Eine zeitgesteuerte Unterbrechung der Einspritzung durch Zwischenentlastung des Pumpenarbeitsraumes mittels eines Magnetventils bedeutet daher eine wesentliche Einschränkung der durch die Kraftstoffeinspritzpumpe bereitgestellte Leistung. Weiterhin ist auch ein spezielles Druck- ventil in der Verbindung zwischen Pumpenarbeitsraum und Einspritzventil vorgesehen, das beiDividing the injection into a pre-injection and a main injection, the electrically controlled valve, which is a solenoid valve, is opened briefly in order to relieve the pump work space and to briefly reduce the fuel pressure achieved. This means that a very fast switching solenoid valve is required, which requires considerable effort in the electrical control and in the construction of the valve. The fact that the injection is interrupted is particularly disadvantageous must be time-controlled by a solenoid valve. As a result, an increasing part of the available cam stroke for interrupting the injection is used with increasing speed. In the case of a distributor injection pump, there is a much smaller stroke per injection process compared to the possibilities of an in-line injection pump, in which one cam alone drives one pump piston, because the cam stroke available here is limited due to the limited length of the cam track. A time-controlled interruption of the injection by means of an intermediate relief of the pump work space by means of a solenoid valve therefore means a substantial restriction of the power provided by the fuel injection pump. Furthermore, a special pressure valve is also provided in the connection between the pump work space and the injection valve
Kraftstoffhochdruckförderung zur Kraftstoffeinspritzdüse in Förderrichtung öffnet und bei Beendigung der Einspritzung schließt und das geeignet ist, Druckwellen zwischen dem Druckventil und dem Kraftstoffeinspritzventil abzubauen und in diesem Bereich einen angestrebten konstanten Standdruck während der Einspritzpausen zu halten. Vorteilhaft ist es bei einer unterteilten Kraftstoffeinspritzung mit einer Voreinspritzung und einer Haupteinspritzung pro Arbeitstakt des jeweiligen zu versorgenden Zylinders der Brennkraftmaschine für einen konstanten Standdruck in den Einspritzpausen zu sorgen.High-pressure fuel delivery to the fuel injector opens in the direction of delivery and closes when the injection is ended and which is suitable for reducing pressure waves between the pressure valve and the fuel injection valve and for maintaining a desired constant stand pressure in this area during the injection breaks. In the case of a divided fuel injection with a pre-injection and a main injection per work cycle of the respective cylinder of the internal combustion engine to be supplied, it is advantageous to ensure a constant stand pressure in the injection breaks.
Vorteile der ErfindungAdvantages of the invention
Durch die erfindungsgemäße Lösung erfolgt eine sichere Unterbrechung der Einspritzung zwischen Vor- und Haupteinspritzung bei geringen Anforderungen an die Schnelligkeit eines zeitgesteuerten Ventils. Dabei wird während der Unter- brechung der Einspritzung zwischen Vor- und Haupteinspritzung kein oder nur ein sehr geringe Teil des verfügbaren Nockenhubes in Anspruch genommen. Durch die konstruktiv über die Nockenform unterstütze Unterbrechung der Einspritzung wird erreicht, daß selbst bei höherer Drehzahl eine sichere Unterbrechung der Einspritzung zwischen Vor- und Haupteinspritzung einhaltbar ist, ohne, daß es zu einer Einbuße an für die Hochdruckförderung bereitstellbaren Nockenhub kommt. Der drehzahlunabhängige Einfluß der Schalt- zeit wird durch durch den zweiten Teilbereich des Nocken kompensiert, so daß auch keine allzugroße Anforderungen an die Schnelligkeit des elektrisch gesteuerten Ventils gestellt werden müssen.The solution according to the invention ensures a safe interruption of the injection between the pre-injection and the main injection with low demands on the speed of a time-controlled valve. During the sub No or only a very small part of the available cam stroke was used to break the injection between the pre-injection and the main injection. The constructionally supported interruption of the injection ensures that a safe interruption of the injection between the pre-injection and the main injection can be maintained even at a higher speed, without there being a loss of the cam stroke that can be provided for high-pressure delivery. The speed-independent influence of the switching time is compensated by the second part of the cam, so that there are no overly high demands on the speed of the electrically controlled valve.
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Prinzipdarstellung einer Kraftstoffeinspritzpumpe, die von einem Magnetventil gesteuert wird, Figur 2 einen Verlauf der erfindungsgemäßen Nockenbahn in Form einer Nockenerhebungskurve über den Drehwinkel mit einer ersten Steuerungssequenz des Ventils bei niedriger Drehzahl der Brennkraftmaschine und Figur 3 einen Verlauf der erfindungsgemäßen Nockenbahn über den Drehwinkel mit einer zweiten Steuerungssequenz des Ventils bei hoher Drehzahl der Brennkraftmaschine.An embodiment of the invention is shown in the drawing and is explained in more detail in the following description. FIG. 1 shows a schematic diagram of a fuel injection pump that is controlled by a solenoid valve, FIG. 2 shows a course of the cam track according to the invention in the form of a cam elevation curve over the angle of rotation with a first control sequence of the valve at low engine speed, and FIG. 3 shows a course of the cam track according to the invention the angle of rotation with a second control sequence of the valve at high engine speed.
Beschreibungdescription
Die erfindungsgemäße Lösung ist beim nachfolgend beschriebenen Ausführungsbeispiel anhand einer Verteilereinspritzpumpe realisiert, wie sie schematisch in der Figur 1 dargestellt ist. Es handelt sich dort um eine Verteilerein- spritzpumpe der Axialkolbenbauart, wenn auch der Gegenstand der Erfindung auch bei anderen Kraftstoffeinspritzpumpen verwendbar ist, wie z. B. Verteilereinspritzpumpen der Ra- dialkolbenpumpenbauart oder Einzelpumpen mit nur einem Pum- penkolben zur Versorgung eines einzelnen Zylinders einerIn the exemplary embodiment described below, the solution according to the invention is implemented using a distributor injection pump, as is shown schematically in FIG. 1. It is a distribution unit Injection pump of the axial piston type, although the object of the invention can also be used in other fuel injection pumps, such as, for. B. Distributor injection pumps of the radial piston pump type or single pumps with only one pump piston for supplying a single cylinder
Brennkraftmaschine oder Reihenpumpen.- Besonders vorteilhaft ist die Erfindung aber bei einer Verteilereinspritzpumpe verwirklichbar, weil hier der verfügbare Nockenhub wegen der begrenzten Länge der Nockenbahn kleiner ist als bei z.B. einer Reiheneinpritzpumpe . Bei der Verteilereinspritzpumpe der in der Figur 1 gezeigten Art ist ein Pumpenkolben 1 vorgesehen, der in einer Zylinderbohrung 2 verschieb- und verdrehbar angeordnet ist und dort stirnseitig einen Pumpenarbeitsraum 10 einschließt. Der Pumpenkolben ist dabei mit einer Nockenscheibe 6, die axial nach unten weisende Nocken 5 der erfindungsgemäßen Ausgestaltung aufweist, z. B. über eine nicht weiter gezeigte Feder, gekoppelt. Die Nockenscheibe wird rotierend, insbesondere synchron zur Drehzahl der von der Einspritzpumpe versorgten Brennkraftmaschine von einer nicht weiter gezeigten Antriebswelle in bekannterInternal combustion engine or in-line pumps. However, the invention can be implemented particularly advantageously in a distributor injection pump, because here the available cam stroke is smaller than in e.g. due to the limited length of the cam track. an in-line injection pump. A pump piston 1 is provided in the distributor injection pump of the type shown in FIG. The pump piston is provided with a cam 6, which has axially downward facing cams 5 of the embodiment according to the invention, for. B. coupled via a spring, not shown. The cam disk is rotating, in particular synchronously with the speed of the internal combustion engine supplied by the injection pump, from a drive shaft, not shown, in a known manner
Weise angetrieben, wobei die Nockenscheibe unter Einfluß der Feder auf einem bekannten axial feststehenden Rollenring abläuft und in der Folge den rotierenden Pumpen- und Verteilerkolben in eine hin- und hergehende fördernden und ansaugende Bewegung versetzt. Der zeitliche bzw. drehwin- kelabhängige Ablauf der Rollen auf der Nockenflanke bestimmt also die Hublage des Pumpenkolbens . Bei seiner Drehbewegung in Zuordnung zu einem Pumpenförderhub, bei dem aus dem Pumpenarbeitsraum 10 Kraftstoff unter Hochdruck verdrängt wird, kommt der Pumpenkolben mit einer von mehreren Einspritzleitungen 7 über eine Verteilernut 8 in der Mantelfläche des Pump- und Verteilerkolbens in Verbindung. Die Verteilernut ist dabei über einen Längskanal 9 ständig mit dem Pumpenarbeitsraum verbunden. Die Einspritzleitung führt über ein Druckventil 12 zu einem Kraftstoffeinspritzventil 13, das dem jeweiligen Zylinder einer Brennkraftmaschine zugeordnet ist .Driven in a manner whereby the cam disc runs under the influence of the spring on a known axially fixed roller ring and subsequently sets the rotating pump and distributor piston in a reciprocating conveying and suctioning movement. The timing or angle of rotation of the rollers on the cam flank thus determines the stroke position of the pump piston. During its rotational movement in association with a pump delivery stroke, in which fuel is displaced from the pump work space 10 under high pressure, the pump piston comes into connection with one of several injection lines 7 via a distributor groove 8 in the outer surface of the pump and distributor piston. The distributor groove is continuously connected to the pump work space via a longitudinal channel 9. The injection line introduces via Pressure valve 12 to a fuel injection valve 13 which is assigned to the respective cylinder of an internal combustion engine.
Die Versorgung des Pumpenarbeitsraumes 10 mit Kraftstoff erfolgt über eine Saugleitung 15, die von einem Saugraum 17, der im wesentlichen nur noch gestrichelt dargestellt ist und innerhalb des Gehäuses der Kraftstoffeinspritzpumpe eingeschlossen ist, versorgt. Der Saugraum erhält Kraftstoff von einer Kraftstofförderpumpe 18, die synchron zur Kraft- stoffeinspritzpumpe, z. B. von der Antriebswelle her, angetrieben wird und somit Kraftstoff in drehzahlabhängigen Mengen in den Saugraum fördert. Mit Hilfe eines zusätzlichen Drucksteuerventils 19 wird der Druck im Saugraum üblicher- weise drehzahlabhängig gesteuert, wenn mit Hilfe diesesThe pump working chamber 10 is supplied with fuel via a suction line 15, which is supplied by a suction chamber 17, which is essentially only shown in broken lines and is enclosed within the housing of the fuel injection pump. The suction chamber receives fuel from a fuel delivery pump 18, which is synchronous with the fuel injection pump, eg. B. is driven by the drive shaft and thus promotes fuel in speed-dependent amounts in the suction chamber. With the help of an additional pressure control valve 19, the pressure in the suction chamber is usually controlled as a function of speed, if with the help of this
Drucks Zusatzfunktionen der Kraftstoffeinspritzpumpe gesteuert werden sollen. Über eine Überlaufdrossel 22 fließt beständig Kraftstoff zum Vorratsbehälter 23 zurück, so daß dadurch für Kühlung der Einspritzpumpe bzw. Entgasung des Saugraumes gesorgt ist. Die Saugleitung 15 führt über ein Rückschlagventil 16 in den Pumpenarbeitsraum, wobei das Rückschlagventil in Richtung Pumpenarbeitsraum öffnet. Parallel zu diesem Rückschlagventil ist ein elektrisch gesteuertes Ventil 24 vorgesehen, das eine Bypassleitung 21 zum Druckventil 16 steuert und mit dessen Hilfe beim Öffnen des Ventils eine Verbindung zwischen Pumpenarbeitsraum 10 und Saugraum 17 hergestellt ist und beim Schließen des Ventils der Pumpenarbeitsraum 10 verschlossen ist. Das als Magnetventil symbolisierte elektrisch gesteuerte Ventil 24 wird von einer Steuereinrichtung 25 entsprechend Betriebsparametern in an sich bekannter Weise gesteuert. Bei genügend großem Durchflußquerschnitt des Ventils 24 kann jedoch das Rückschlagventil 16 auch entfallen. In diesem Falle wird der Pumpenarbeitsraum beim Saughub ausschließlich über das elektrischgesteuerte Ventil gefüllt.Pressure additional functions of the fuel injection pump to be controlled. Fuel continuously flows back to the reservoir 23 via an overflow throttle 22, so that cooling of the injection pump or degassing of the suction chamber is thereby ensured. The suction line 15 leads via a check valve 16 into the pump work space, the check valve opening in the direction of the pump work space. In parallel to this check valve, an electrically controlled valve 24 is provided, which controls a bypass line 21 to the pressure valve 16 and with the aid of which a connection is made between the pump work chamber 10 and the suction chamber 17 when the valve is opened and the pump work chamber 10 is closed when the valve is closed. The electrically controlled valve 24 symbolized as a solenoid valve is controlled by a control device 25 according to operating parameters in a manner known per se. With a sufficiently large flow cross section of the valve 24, the check valve 16 can also be omitted. In this case the Pump work space during the suction stroke is filled exclusively via the electrically controlled valve.
Mit Hilfe dieses elektrisch gesteuerten Ventils, wird der Beginn der Hochdruckförderung des Pumpenkolbens gesteuert . Mit dem Ventil kann letztendlich auch der Spritzbeginn gesteuert werden. Neben dieser Möglichkeit kann der Spritzbe- gin durch eine separate Spritzbeginnverstelleinrichtung verstellt werden, die bekannterweise einen relativ zum den Nocken abtastenden Pumpenkolben verdrehbarer Nockenantriebs- teil aufweist. Beim Verschließen des Ventils baut sich im Pumpenarbeitsraum 10 aufgrund der Förderbewegung des Pumpenkolbens ein für einen Einspritzvorgang erforderlicher Druck auf . Der so auf Einspritzdruck gebrachte Kraftstoff wird über den Längskanal 9 und die Verteilernut 8 einer der Einspritzleitungen 7 zugeführt. Mit dem Wiederöffnen des elektrisch gesteuerten Ventils wird die Hochdruckförderung unterbrochen. Die Schließdauer des Ventils bestimmt die Einspritzmenge, ggf. kann, wie oben gesagt, mit diesem auch der Spritzzeitpunkt gesteuert werden.With the help of this electrically controlled valve, the start of the high pressure delivery of the pump piston is controlled. Ultimately, the start of spraying can also be controlled with the valve. In addition to this possibility, the injection start can be adjusted by a separate injection start adjustment device, which is known to have a cam drive part that can be rotated relative to the pump piston that scans the cam. When the valve is closed, a pressure required for an injection process builds up in the pump work chamber 10 due to the conveying movement of the pump piston. The fuel thus brought to the injection pressure is supplied to one of the injection lines 7 via the longitudinal channel 9 and the distributor groove 8. When the electrically controlled valve is reopened, the high pressure delivery is interrupted. The closing time of the valve determines the injection quantity; if necessary, the injection timing can also be controlled with this, as mentioned above.
Erfindungsgemäß sind die Hochdruckförderseiten der Nockenflanken der Nocken 5, so ausgebildet, daß sie wie in der Figur 2 oder 3 dargestellt über die Zeit einen Hubverlauf des Pumpenkolbens erzeugen, der unterteilt ist in einen ersten Bereich V der beginnend mit den Förderhub des Kolbens nach einem kleinen Förderhub endet, in einen zweiten Bereich P in dem der Kolben dann gar nicht oder nur so geringfügig in Förderrichtung bewegt wird, daß er in diesem Bereich für eine Hochdruckförderung nicht wirksam ist und eine Einspritzpause entsteht und schließlich in einen dritten Bereich H, in dem die Nockenflanke wieder ansteigt und den Pumpenkolben zwecks weiterer Förderung der Haupteinspritz- menge weiter verschiebt. Im Bereich P kann der Nocken waage- recht, leicht steigend oder auch leicht fallend verlaufen. Die Voreinspritzung wird dabei weiterhin durch das elektrisch gesteuerte Ventil gesteuert und zwar so, daß es geschlossen ist, wenn die Rollen in den zweiten Bereich P kommen .According to the invention, the high-pressure delivery sides of the cam flanks of the cams 5 are designed in such a way that, as shown in FIG. 2 or 3, they produce a stroke profile of the pump piston over time, which is divided into a first region V which begins after the delivery stroke of the piston after a small one Delivery stroke ends, in a second area P in which the piston is then not moved at all or only so slightly in the conveying direction that it is not effective for high-pressure delivery in this area and an injection break occurs, and finally in a third area H, in which the The cam flank rises again and shifts the pump piston further for further delivery of the main injection quantity. In area P the cam can be right, slightly rising or also slightly falling. The pre-injection is still controlled by the electrically controlled valve in such a way that it is closed when the rollers come into the second area P.
Für einen Betrieb bei niedriger Drehzahl ist dem Diagramm in Figur 2 entnehmbar, daß das elektrisch gesteuerte Ventil, z.B. ein Magnetventil oder auch ein von einem Piezo betätigtes Ventil, zur Steuerung des Beginns der Vorein- spritzmengenförderung in U.T., d.h. vor dem Anstieg der Nockenkurve aus einem Grundkreis geschlossen wird und in dem Nockenbereich V vor Erreichen des Nockenbereichs P wieder geöffnet wird. Nach einer Spritzpause im Bereich P folgt dann ein Wiederschließen des Ventils 24 mit Beginn der Hochdruckförderung für die Haupteinspritzung im anschließenden Nockenflankenteil H, wo danach durch Öffnen des Ventils 24 die Hochdruckförderung wiederum unterbrochen und die Haupt- einspritzung beendet wird. Im Punkt des Wiedeerschließens sind die Anforderungen an die Exaktheit des Steuerpunktes niedriger als bei einer sonstigen Steuerung eines Spritzbeginns .For operation at low speed it can be seen from the diagram in Figure 2 that the electrically controlled valve, e.g. a solenoid valve or a valve actuated by a piezo, for controlling the start of the pre-injection quantity delivery in U.T., i.e. is closed from a base circle before the cam curve rises and is opened again in the cam area V before the cam area P is reached. After a pause in spraying in region P, valve 24 then re-closes with the start of high-pressure delivery for the main injection in the subsequent cam flank part H, where the high-pressure delivery is then interrupted again by opening valve 24 and the main injection is ended. At the point of reclosing, the requirements for the exactness of the control point are lower than with any other control of a spray start.
Für den Betrieb bei hoher Drehzahl ist eine Unterterteilung in Vor- und Haupteinsprizung nicht so dringend erforderlich, da hier auf Grund der im wesentlichen zeitkonstant ablaufenden Verbrennungsvorgängen eine Verschiebung der Verbrennung in Drehrichtung nach dem oberen Totpunkt des Brennkraftmaschinenkolbens erfolgt und sich hier Zündverzüge bei eingespritzten Kraaftstoffmengen nicht mehr so nachteilig auf die Geräuschbildung bemerkbar machen, für diesen Fall, der in Figur 3 gezeigt ist, wird das Ventil 24 so angesteuert, daß es erst im Bereich des Nockenflankenteils P geschlossen wird, so daß es sicher geschlossen ist, wenn die Kraftstoffförderung für die nun alleinige Haupteinspritzung im Bereich des sich dem Bereich P anschließenden Nockenflankenteils H erfolgt. Das Ende der Einspritzung wird wiederum durch Öffnen des Ventils gesteuert, was dann in der Regel noch vor dem oberen Totpunkt des Nocken der Einspritzpumpen erfolgt .For operation at high speed, a subdivision into pre-injection and main injection is not so urgently necessary, since the combustion processes are shifted in the direction of rotation after top dead center of the internal combustion engine piston due to the essentially time-constant combustion processes and there are no ignition delays with injected fuel quantities make more noticeable on the noise, in this case, which is shown in Figure 3, the valve 24 is controlled so that it is only closed in the region of the cam flank P, so that it is securely closed when the Fuel delivery for the now main injection takes place in the area of the cam flank part H adjoining the area P. The end of the injection is in turn controlled by opening the valve, which usually takes place before the top dead center of the cam of the injection pumps.
Diese Ansteuerung hat den Vorteil, daß bei hohen Drehzahlen der Pumpenarbeitsraum der Einspritzpumpe ausreichend mit Kraftstoff gefüllt werden kann, da die Füllphase nun gegen über der Steuerung bei niedriger Drehzahl verlängert ist und die Kolbenbewegung in Füllrichtung, d.h. beim Saughub nur bis inden Hubbereich gelangen muß auf dem sich der zweite Berreich P befindet. Wegen der erst ab dem Bereich P erfol- genden Hochdruckförderung ist die erforderliche Füllmenge des Pumpemnarbeitsraumes reduziert. Das elektrisch gesteuerte Ventil schließt also erst im Bereich P der Nockenflanke, so daß der Saughub zum Angesaugen von Kraftstoff über die ablaufende Nockenflanke V voll ausgenutzt werden kann. Der Einströmfüllungseffekt wirkt sich noch im beginnenden Teil der Nockenflanke vor dem Bereich P aus solange das Ventil noch nicht geschlossen ist.This control has the advantage that at high speeds the pump working space of the injection pump can be sufficiently filled with fuel, since the filling phase is now extended compared to the control at low speed and the piston movement in the filling direction, i.e. during the suction stroke only has to reach the stroke area on which the second area P is located. Because the high-pressure pumping only takes place from area P, the required filling quantity of the pumping work space is reduced. The electrically controlled valve therefore closes only in the region P of the cam flank, so that the suction stroke can be fully utilized for the suction of fuel via the cam flank V running down. The inflow filling effect has an effect in the beginning of the cam flank in front of area P as long as the valve is not yet closed.
In Einzelfällen ist es möglich, die Nockenform zu modifizieren, im Sinne einer gewollten unterteilten Einspritzung und in Unterstützung der Steuerarbeit des Ventils. Statt eine rückläufigen Hubbewegung des Kolben zu erzeugen, kann dieser auch lediglich in seiner Stellung verharren oder nur so geringfügig weiterbewegt werden, daß seine Bewegung nicht ausreicht, eine Einspritzung nennenswerter Art zu ermöglichen, derart, daß auch schon ohne dem Einfluß des Ventils eine wirksame Spritzpause konstruktiv vorgegebener Länge auftreten kann, die die Kraftstoffzufuhr in den Brennraum der Brennkraftmaschine reduziert, so daß der Druckan- stieg im Brennraum kleiner wird und eine geräuscharme Verbrennung erzielt werden kann. In individual cases, it is possible to modify the cam shape, in the sense of a deliberate split injection and in support of the control work of the valve. Instead of generating a declining stroke movement of the piston, it can only remain in its position or can only be moved so slightly that its movement is not sufficient to enable an appreciable type of injection, such that an effective spray pause even without the influence of the valve constructive predetermined length can occur, which reduces the fuel supply to the combustion chamber of the internal combustion engine, so that the pressure rose in the combustion chamber becomes smaller and quiet combustion can be achieved.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzsystem mit einer Kraftstoffeinspritz- pumpe mit einem Pumpenkolben, der von einem mit wenigstens einem Nocken versehenen Nockenantrieb angetrieben wird und einen Pumpenarbeitsraum (10) begrenzten, der zur Versorgung wenigstens eines Kraftstoffeinspritzventiles (13) mit auf Einspritzdruck gebrachtem Kraftstoffeinspritzmengen dient, sowie mit einem elektrisch gesteuerten Ventil (24) , über das der Pumpenarbeitsraum (10) der Kraftstoffeinspritzpumpe zur Steuerung der Einspritzung mit einem Entlastungraum (17) , verbunden oder geschlossen wird, und mit Unterbrechung der Einspritzung zwischen einer Vor- und einer Haupteinspritzung pro Einspritzvorgang dadurch gekennzeichnet, daß der wenigstens eine Nocken so ausgebildet ist, daß er auf seiner den Pumpenkolben zu seinem Förderhub bewegenden Nockenflankeseite einen ersten Teilbereich (V) aufweist, in dem der Pumpenkolben einen Förderhub zur Durchführung einer Voreinspritzung durchführt, einen zweiten Teilbereich (P) aufweist, in dem der Kolben (1) nach der Beendigung der Voreinspritzung im wesentlichen in seiner dort erreichten Stellung verharrt oder nur gerinfügig in Förderrichtung oder gegen Förderrichtung bewegt wird und anschließend zur Durchführung des Förderhubes für die Haupteinspritzung einen dritten Teilbereich (H) aufweist, wobei das elektrisch gesteuerte Ventil (24) so angesteuert wird, daß es bei niedriger Drehzahl vor dem Beginn des ersten Teilbereichs (V) geschlossen ist und im ersten Teilbereich (V) zur Beendigung der Voreinspritzung geöffnet wird und anschließend zur Durchführung der Haupteinspritzung zu Beginn des dritten Teilbereiches wieder geschlossen wird und in diesem dritten Teilbereich des Nockens vor Erreichen des oberen Totpunktes des Nockens wieder geöffnet wird und daß bei hoher Drehzahl das Ventil zur Einleitung einer Haupteinspritzung ohne vorhergehender Voreinspritzung innerhalb des zweiten Teilbereichs (P) geschlossen wird und innerhalb des dritten Teilbereiches zur Beendigung der Haupteinspritzung vor Erreichen des oberen Totpunktes wieder göffnet wird. 1. Fuel injection system with a fuel injection pump with a pump piston which is driven by a cam drive provided with at least one cam and a pump working space (10) which serves to supply at least one fuel injection valve (13) with fuel injection quantities brought to injection pressure, and with one Electrically controlled valve (24), via which the pump work chamber (10) of the fuel injection pump for controlling the injection is connected or closed with a relief chamber (17), and with the interruption of the injection between a pre-injection and a main injection per injection process, characterized in that the at least one cam is designed such that it has a first partial area (V) on its cam flank side that moves the pump piston to its delivery stroke, in which the pump piston carries out a delivery stroke for performing a pre-injection, a second partial area ( P) in which the piston (1) remains after the end of the pre-injection essentially in its position reached there or only slightly in the delivery direction or is moved against the direction of delivery and then has a third section (H) for carrying out the delivery stroke for the main injection, the electrically controlled valve (24) being controlled so that it is closed at low speed before the start of the first section (V) and is opened in the first section (V) to terminate the pre-injection and then closed again to carry out the main injection at the beginning of the third section and is opened again in this third section of the cam before reaching the top dead center of the cam and that at high speed the valve to initiate a main injection without previous pre-injection within the second section (P) and is opened within the third section to end the main injection before reaching top dead center.
EP98912246A 1997-04-25 1998-02-17 Fuel injection system Expired - Lifetime EP0910739B1 (en)

Applications Claiming Priority (3)

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DE19717493 1997-04-25
DE19717493A DE19717493A1 (en) 1997-04-25 1997-04-25 Fuel injection system
PCT/DE1998/000452 WO1998049442A1 (en) 1997-04-25 1998-02-17 Fuel injection system

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EP0910739A1 true EP0910739A1 (en) 1999-04-28
EP0910739B1 EP0910739B1 (en) 2001-10-04

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JP (1) JP2000513783A (en)
CN (1) CN1089854C (en)
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DE10101107A1 (en) * 2001-01-12 2002-07-25 Bosch Gmbh Robert Fuel injection system
JP2003343396A (en) * 2002-05-22 2003-12-03 Mitsubishi Electric Corp High pressure fuel supply equipment
FI119120B (en) * 2004-01-23 2008-07-31 Waertsilae Finland Oy Apparatus and Method for Modifying Fuel Injection Pressure
DE102010027745A1 (en) * 2010-04-14 2011-10-20 Robert Bosch Gmbh high pressure pump

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US3690768A (en) * 1969-02-28 1972-09-12 Mitsubishi Motors Corp Diesel fuel injection system with improved starting performance
US4838232A (en) * 1984-08-14 1989-06-13 Ail Corporation Fuel delivery control system
JPS62110566U (en) 1985-12-27 1987-07-14
JPS635140A (en) * 1986-06-24 1988-01-11 Diesel Kiki Co Ltd Injection control method for fuel injection pump
DE3629751C2 (en) * 1986-09-01 1998-07-02 Bosch Gmbh Robert Pre-injection device for internal combustion engines
DE3929747A1 (en) * 1989-09-07 1991-03-14 Bosch Gmbh Robert METHOD AND DEVICE FOR CONTROLLING FUEL INJECTION
US5325837A (en) * 1992-11-19 1994-07-05 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
EP0805270A3 (en) * 1993-04-09 1998-02-11 Zexel Corporation Fuel injection system
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Title
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US6079388A (en) 2000-06-27
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EP0910739B1 (en) 2001-10-04
JP2000513783A (en) 2000-10-17
WO1998049442A1 (en) 1998-11-05
DE59801622D1 (en) 2001-11-08
CN1224484A (en) 1999-07-28
RU2196246C2 (en) 2003-01-10
CN1089854C (en) 2002-08-28

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