EP0391366B1 - Fuel injection apparatus - Google Patents

Fuel injection apparatus Download PDF

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Publication number
EP0391366B1
EP0391366B1 EP90106394A EP90106394A EP0391366B1 EP 0391366 B1 EP0391366 B1 EP 0391366B1 EP 90106394 A EP90106394 A EP 90106394A EP 90106394 A EP90106394 A EP 90106394A EP 0391366 B1 EP0391366 B1 EP 0391366B1
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EP
European Patent Office
Prior art keywords
bore
fuel
valve
control valve
high pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90106394A
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German (de)
French (fr)
Other versions
EP0391366A2 (en
EP0391366A3 (en
Inventor
Wolfgang Dr.-Ing. Köhler
Reda Rizk
Hans-Gottfried Michels
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Kloeckner Humboldt Deutz AG
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Kloeckner Humboldt Deutz AG
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Priority to AT90106394T priority Critical patent/ATE99386T1/en
Publication of EP0391366A2 publication Critical patent/EP0391366A2/en
Publication of EP0391366A3 publication Critical patent/EP0391366A3/en
Application granted granted Critical
Publication of EP0391366B1 publication Critical patent/EP0391366B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • 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
    • 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
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • the invention relates to a fuel injection device for diesel engines according to the preamble of claim 1.
  • Fuel injection pumps of this type can draw in the fuel via a suction hole in the plunger bushing and / or via a suction valve, which is located in the region of the delivery chamber.
  • the fuel is drawn in via a seat valve which is arranged in the region of the high-pressure chamber and can be actuated by means of an electromagnetic adjusting device.
  • the fuel is pumped from the pump plunger into the injection line via a pressure or relief valve.
  • the function of the pressure or relief valve is to lower the pressure in the injection line to a certain level after the injection process has ended and to prevent the injection line from being sucked empty when the fuel is subsequently drawn in. This is intended to achieve both a rapid, spatter-free closing of the injection valve and cavitation-free operation of the injection system.
  • EP-A-0 174 261 describes an injection system for diesel internal combustion engines which is controlled by electromagnetic control valves.
  • the advantage of this solution is that no relief valve is provided and each control valve has only one electromagnet.
  • the position of the electromagnetic control valve in the vicinity of the fuel injection valve is disadvantageous. As a result, when the electromagnetic control valve is opened, the inertia of the fuel column in the injection line partially empties it, which can lead to cavitation.
  • EP-A-0 114 375 describes a fuel injection device for diesel engines with a control by an electromagnetic control valve, each having two actuating magnets.
  • relief valves are provided in this fuel injection device.
  • the invention has for its object to improve fuel injection and thus the combustion in diesel engines.
  • the simple construction of the fuel injector means that the maintenance effort is low and the dimensions and costs are kept small.
  • the elimination of the pressure valve means that the injection element is simplified and less expensive.
  • the overall height and maintenance requirements of the injection device are reduced by eliminating a wearing part.
  • the harmful space is also kept small, since the flow connection between the high-pressure chamber and the injection valve has a practically constant flow cross section despite the electromagnetically operated seat valve installed in this flow connection. This is possible because a high-pressure annulus is also provided as a bypass line with a constant flow cross-section in the area of the electromagnetically actuated seat valve.
  • the harmful space is minimized by cutting the stepped bore and the high-pressure bore at right angles.
  • the high pressure area is acted upon by the admission pressure prevailing in the low pressure chamber during the suction.
  • This so-called stand pressure the level of which is ensured according to the invention by a pressure-maintaining valve in the suction chamber, advantageously ensures the stability of the start of delivery and the delivery rate of the injection pump and reduces the risk of cavitation in the system.
  • the solution according to the invention offers the advantage that the arrangement of the injection elements can be optimally adapted to the respective structural conditions of the engine housing.
  • An advantageous development of the invention prevents the fuel injection pump from running dry when the engine is not running, since according to the invention a tightly closing inlet valve closes off the low-pressure chamber from the fuel inlet.
  • the solution according to the invention offers the advantage that the arrangement of the injection pump elements can be optimally adapted to the respective structural conditions of the engine housing.
  • the injection line is particularly short and thus the harmful space is particularly small, so that the injection pressure can be particularly high.
  • An advantageous embodiment of the invention ensures that separate manufacture and testing and individual replacement of the injection pump element and control valve or electromagnetic actuating device is possible.
  • An advantageous development of the invention reduces the dead space of the fuel injection device.
  • This installation clearance is advantageously bridged by two sealing elements which, in addition to their function as a high-pressure seal, also take over the bearing of the control valve in the stepped bore of the plunger bush.
  • the high-pressure fuel when it is driven off by the control valve body, is returned to the low-pressure chamber through a hole in the plunger sleeve. This avoids expensive external connection lines with their risk of leakage.
  • a further advantageous development of the invention is the arrangement of the elements parallel to the axis of the control valve body, with which the control valve is fastened to the plunger sleeve. This arrangement prevents the bracing and thus jamming of the control valve body in the control valve sleeve.
  • An advantageous design of the pump plunger with a diverter groove ensures that the delivery of the injection pump is interrupted regardless of the serviceability of the control valve before the delivery runs into the tip radius of the injection pump cam.
  • the arrangement of the anchor plate according to the invention in a vented and fuel-filled space with appropriate adjustment of the gap between the attracted anchor and the electromagnetic actuating device to the various design parameters of the control valve, enables a rebound-free closing and thus an exact control of the start of delivery and the delivery rate of the fuel .
  • the inventive design of the outer contour of the injection pump element makes it possible to replace a normal element with the injection pump element with a control valve without any reworking.
  • the position of the high-pressure chamber and the suction or discharge borehole according to the invention enables a minimal harmful space in the high-pressure region, which is comparable to the harmful space of a normal element.
  • the fuel injection device consists of an injection pump element 1 and a control valve 2, the injection pump element 1 also being the carrier of the control valve 2.
  • the injection pump element is composed of a pump plunger 4, a plunger sleeve 5, the control valve 2 consists of a seat valve 3 and an electromagnetic actuator 7.
  • the plunger 4 which is sealingly guided in a plunger sleeve 5, forms a high-pressure chamber 11 together with the plunger sleeve.
  • the high-pressure chamber 11 is connected to the low-pressure chamber 13 via a suction or discharge bore 14.
  • the low-pressure chamber 13 is acted upon by a fuel feed pump, not shown, via an inlet valve 51.
  • the pressure in the low pressure chamber 13 is kept constant by a pressure maintaining valve 52.
  • the plunger 1 is moved axially via a roller tappet 54 by a cam 55 against the force of a compression spring 53.
  • the fuel is conveyed into a high-pressure bore 12 after completion of the suction or discharge bore 14.
  • the seat valve 3 is open, the delivered fuel flows back into the low-pressure chamber 13 via the high-pressure annulus 26, the control valve seat 25, the low-pressure annulus 27 and the return bore 15.
  • the high-pressure delivery is ended by opening the seat valve 3.
  • the connection thus created to the low-pressure chamber 13 relieves the high-pressure region 50, which is under the pressure of the low-pressure chamber 13 until the seat valve 3 is closed again. This prevents the formation of cavities during the downward movement of the pump plunger and ensures constant pressure conditions at the beginning of the next injection, which lead to a stable start of delivery and quantity characteristics.
  • the inlet valve 51 and the pressure holding valve 52 which are designed as particularly tightly closing valves, prevent the low-pressure chamber 13 and the high-pressure region 50 from running dry when the engine is at a standstill, thereby avoiding difficulties when starting the engine.
  • the high-pressure chamber 11 is pulled up to just below a stepped bore 19, which is used to hold the control valve 2. As a result, the harmful volume in the high-pressure chamber 11 is minimized, which proves to be particularly advantageous with high injection pressures.
  • the high-pressure chamber 11 has no end cover, since the injection pump element 1 is designed as a so-called "mono element".
  • the design as a mono element advantageously increases the high-pressure capability of the fuel injection device by minimizing the expansion of the pressure space.
  • a suction or discharge bore 14 which connects the high-pressure chamber 11 to a low-pressure chamber 13, which in turn is connected to the suction chamber of the injection pump housing, not shown.
  • the suction or discharge bore 14 is drilled obliquely from the low pressure chamber 13 in the direction of the high pressure chamber 11 in order to take into account the position of the high pressure chamber 11.
  • the low-pressure chamber 13 is also connected via a return bore 15 to an annular space 16 of a control valve sleeve 17 of the seat valve 3. This avoids an external return line, which means construction costs and leakage risk.
  • the seat valve 3 sits with a clearance fit in the stepped bore 19 of the plunger sleeve 5 and is mounted in two high-pressure sealing elements 20. It is connected by screws, not shown, which are inserted through bores in an end cover 21 and the plunger sleeve 5 and screwed into the control valve sleeve 17, to form a firm bond with the plunger sleeve 5 without the seat valve 3 being tensioned. Due to the installation clearance between the control valve sleeve 17 and the stepped bore 19, tensioning and consequently jamming of the seat valve 3, caused by the tightening of the injection line 48, is also avoided.
  • a particular advantage of this arrangement is that an independent exchange of control valve 2 and injection pump element 1 as well as the electromagnetic actuating device 7 is ensured.
  • This modular structure enables cost-effective production and repair of the fuel injection device.
  • the seat valve 3 has a control valve sleeve 17 and a control valve body 22, which is guided so that it can move axially in the control valve sleeve 17, specifically in a high-pressure guide 23 and a low-pressure guide 24.
  • the control valve body 22 separates a high-pressure annulus 26 from a low-pressure annulus 27 with a control valve seat 25.
  • the high-pressure annulus 26 is via a high-pressure control bore 28 and the high pressure bore 12 connected to the high pressure chamber 11.
  • the low-pressure annular space 27 is connected to the low-pressure space 13 via the control bore 29, the annular space 16 and the return bore 15.
  • the control valve body 22 has a leak oil longitudinal bore 42 and a leak oil transverse bore 43, which create a connection between a leak oil chamber 44 and a spring chamber 34.
  • an anchor plate 30 is fastened, which is moved by the electromagnetic actuating device 7.
  • the anchor plate 30 is fastened by means of a countersunk screw 31 screwed into the control valve body 22, which axially clamps the anchor plate 30 and a stop ring 32 against the control valve body 22.
  • the anchor plate 30 is located in a fuel-filled damping space 33 which is delimited by an intermediate piece 41 and the electromagnetic actuating device 7.
  • the volume of the damping space 33 is dimensioned such that no significant flow resistances occur between the anchor plate 30 and the walls of the intermediate piece 41 during the axial movement of the anchor plate 30.
  • the damping chamber 33 is connected to a spring chamber 34, which is also fuel-filled.
  • a spring 36 In the spring chamber 34 there is a spring 36, the force of which acts on the stop ring 32 in the direction of the stop 35.
  • the stop 35 serves to limit the stroke of the control valve body 22.
  • the damping chamber 33 and the spring chamber 34 are connected to the control bore 29 via a throttle bore 37.
  • a threaded bore 38 is provided, to which a ventilation or fuel return line 39 is connected, which leads to the fuel tank (not shown).
  • a pressure holding valve 40 is arranged, the cut-off pressure of which is lower than the delivery pressure of the fuel delivery pump, not shown.
  • the electromagnetic adjusting device 7 is clamped against the control valve sleeve 17 by screws (not shown), acting parallel to the axis of the control valve body 22, with the intermediate piece 41, without bracing the latter.
  • the entire low-pressure area of the control valve 2 is sealed by O-rings 45.
  • the fuel injector works as follows:
  • the pump plunger 4 is moved from its bottom dead center position in the direction of the control valve 2. After passing through a preliminary stroke, it first closes the suction and discharge bore 14. The plunger 4 then delivers fuel into the high-pressure bore 12 and into the high-pressure control bore 28.
  • the spring 36 When the anchor plate 30 is tightened, the spring 36 is also preloaded. As soon as the electromagnetic adjusting device 7 is de-energized, the spring 36 lifts the control valve body 22 from its seat 25. As a result, the fuel flows back into the low-pressure chambers and the fuel injection is ended.
  • a prerequisite for the precise function of the seat valve 3 and thus for reproducible delivery start and fluctuation-free delivery quantity is a rebound-free placement of the control valve body 22 on the control valve seat 25.
  • This is achieved according to the invention by a finely tuned damping of the movement of the control valve body 22.
  • the displacement flow is between Anchor plate 30 and the electromagnetic actuator 7 used.
  • the armature plate 30 is designed without open, axial bores in order to effect the most effective squeezing flow at the stroke end between the armature plate 30 and the electromagnetic actuating device 7.
  • the amount of damping required depends, among other things, on the moving mass, i. H. from the mass of the control valve body 22 + anchor plate 30 + countersunk screw 31 + stop ring 32 + proportion of the mass of the spring 36. Another factor relevant to damping is the spring stiffness of the control valve seat 25.
  • the damping itself depends, among other things, on the fuel viscosity, the geometry of the anchor plate 30 and the minimum distance 46 between the anchor plate 30 and the electromagnetic actuating device 7 and the pressure in the damping space 33. These influencing factors have to be coordinated. The optimal adjustment is achieved when the control valve body 22 is placed on the control valve seat 25 without kickback and the damping-related slowdown in the movement of the control valve body 22 is minimized.
  • the supply of the damping chamber 33 with damping liquid, for. B. damping oil can be done via a separate damping oil circuit.
  • fuel is taken from the low-pressure area, specifically from the control bore 29 of the seat valve 3, specifically via the throttle bore 37. The latter prevents the pressure surges in the control bore 29 from reaching the damping chamber 33.
  • damping space 33 For proper functioning of the damping, it is important that there is no air in the damping space 33, since this affects the viscosity and compressibility of the damping medium. It is also important that the damping fluid is renewed continuously as it warms up and ages.
  • the venting of the damping space 33 is accomplished via the threaded bore 38, which is provided in such a way that it is in the installed position of the control valve 2 in the region of the highest point of the damping space 33.
  • the vent or fuel return line 39 is connected to the threaded bore 38, through which the fuel does not return to the pressure holding valve 40 shown fuel tank flows.
  • the pressure holding valve 40 ensures a certain liquid pressure in the damping chamber 33, which is lower than the maximum delivery pressure of the low-pressure pump, not shown, and lower than the pressure in the low-pressure chambers of the fuel injector. This ensures a flow through the damping chamber 33 and thus renewal of the damping medium fuel and cooling of the control valve 2.
  • the pressure control valve 40 has the effect that the damping chamber 33 cannot run empty when the engine is at a standstill, which leads to undamped lifting movement and thus to bouncing of the control valve 3. Among other things, this would result in an incorrect start of delivery when the engine is restarted.
  • the leak oil from the leak oil chamber 44 is guided via the leak oil longitudinal bore 42 and the leak oil cross bore 43 in the control valve body 22 to the spring chamber 34 and thus into the damping oil circuit.
  • This solution according to the invention saves a separate leakage oil return line.
  • control groove 8 of the pump plunger 4 ensures that the fuel is directed into the suction or control bore 14 at the end of the delivery stroke.
  • the fuel injection is ended in any case before the delivery into the tip area of the injection pump cam arrives and overloaded it.
  • the pump plunger 4 of the injection pump element 1 is considerably easier to manufacture than that of the normal element 1a, since the rotating device and the precise control edges are eliminated.
  • the fuel injection device allows an exact determination of the start of delivery and metering of the fuel injection quantity by the rebound-free placement of the control valve body 22 on the control valve seat 25.
  • it is easy to manufacture and service since the main components of injection pump element 1, control valve 2 and electromagnetic actuating device 7 are to be manufactured, checked and exchanged individually and independently of one another are.

Abstract

1. Fuel injection device for diesel internal combustion engines with a minimum of one pump plunger 4, which is carried and forms a seal in a plunger sleeve 5 and together with the plunger sleeve 5 forms a high-pressure chamber 11, which during the downward movements of the plunger caused by fuel is connected by a control element to a low-pressure chamber 13, the high-pressure chamber 11 being flow- connected to an injection valve 49 via an injection line 48. <??>2.1 The object of the invention is to design the clearance of the fuel injection device as small as possible in order thereby to achieve high injection pressures. <??>2.2 This object is met according to the invention by a permanently open flow connection between the high-pressure chamber 11 and the injection valve 49. <IMAGE>

Description

Die Erfindung betriffl eine Brennstoffeinspritzvorrichtung für Dieselbrennkraftmaschinen nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injection device for diesel engines according to the preamble of claim 1.

Brennstoffeinspritzpumpen dieser Bauart können den Brennstoff über eine Saugbohrung in der Plungerbüchse und/oder über ein Saugventil, das sich im Bereich des Förderraumes befindet, ansaugen.Fuel injection pumps of this type can draw in the fuel via a suction hole in the plunger bushing and / or via a suction valve, which is located in the region of the delivery chamber.

Bei einer anderen Bauart der Brennstoff-Einspritzpumpen wird der Brennstoff über ein im Bereich des Hochdruckraumes angeordnetes, mittels elektromagnetischer Stellvorrichtung betätigbares Sitzventil angesaugt.In another type of fuel injection pump, the fuel is drawn in via a seat valve which is arranged in the region of the high-pressure chamber and can be actuated by means of an electromagnetic adjusting device.

Bei beiden Bauarten wird der Brennstoff nach dem Ansaugen von dem Pumpenplunger über ein Druck- bzw. Entlastungsventil in die Einspritzleitung gefördert.In both types, the fuel is pumped from the pump plunger into the injection line via a pressure or relief valve.

Das Druck- bzw. Entlastungsventil hat die Aufgabe, den Druck in der Einspritzleitung nach Abschluß des Einspritzvorganges auf ein bestimmtes Maß abzusenken und beim anschließenden Ansaugen des Brennstoffes ein Leersaugen der Einspritzleitung zu verhindern. Dadurch sollen sowohl ein rasches, nachspritzerfreies Schließen des Einspritzventils als auch ein kavitationsfreies Arbeiten des Einspritzsystems verwirklicht werden.The function of the pressure or relief valve is to lower the pressure in the injection line to a certain level after the injection process has ended and to prevent the injection line from being sucked empty when the fuel is subsequently drawn in. This is intended to achieve both a rapid, spatter-free closing of the injection valve and cavitation-free operation of the injection system.

Die EP-A-0 174 261 beschreibt eine Einspritzanlage für Dieselbrennkraftmaschinen, die durch elektromagnetische Steuerventile gesteuert wird. Vorteilhaft an dieser Lösung ist, daß kein Entlastungsventil vorgesehen ist und jedes Steuerventil nur einen Elektromagneten aufweist. Von Nachteil ist die Lage des elektromagnetischen Steuerventils in der Nähe des Kraftstoffeinspritzventils. Dadurch wird beim Öffnen des elektromagnetischen Steuerventils durch die Trägheit der Kraftstoffsäule in der Einspritzleitung diese zum Teil entleert, was zu Kavitation führen kann.EP-A-0 174 261 describes an injection system for diesel internal combustion engines which is controlled by electromagnetic control valves. The advantage of this solution is that no relief valve is provided and each control valve has only one electromagnet. The position of the electromagnetic control valve in the vicinity of the fuel injection valve is disadvantageous. As a result, when the electromagnetic control valve is opened, the inertia of the fuel column in the injection line partially empties it, which can lead to cavitation.

Die EP-A-0 114 375 beschreibt eine Kraftstoffeinspritzvorrichtung für Dieselbrennkraftmaschinen mit einer Steuerung durch ein elektromagnetisches Steuerventil, das jeweils zwei Betätigungsmagnete aufweist. Außerdem sind bei dieser Kraftstoffeinspritzvorrichtung Entlastungsventile vorgesehen.EP-A-0 114 375 describes a fuel injection device for diesel engines with a control by an electromagnetic control valve, each having two actuating magnets. In addition, relief valves are provided in this fuel injection device.

Der Erfindung liegt die Aufgabe zugrunde, die Brennstoff-Einspritzung und damit die Verbrennung in Dieselbrennkraftmaschinen zu verbessern. Außerdem sollen durch einfachen Aufbau der Brennstoff-Einspritzvorrichtung der Wartungsaufwand gering und die Abmessungen und Kosten klein gehalten werden.The invention has for its object to improve fuel injection and thus the combustion in diesel engines. In addition, the simple construction of the fuel injector means that the maintenance effort is low and the dimensions and costs are kept small.

Diese Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst. Es hat sich nämlich in überraschender Weise gezeigt, daß auf ein Druck- bzw. Entlastungsventil verzichtet werden kann, wenn in dem Zeitintervall zwischen Förderende und Förderbeginn eine dauernde Strömungsverbindung zwischen Hochdruckraum und Niederdruckraum besteht. Dadurch wird der Hochdruckbereich in den Niederdruckraum hinein entlastet, ohne ein Druck- bzw. Entlastungsventil zu benötigen. Da andererseits der Hochdruckbereich in dem Zeitintervall zwischen Förderende und Förderbeginn unter dem Druck des Niederdruckraumes steht, wird im Hochdruckbereich eine Hohlraumbildung durch die Abwärtsbewegung des Pumpenplungers sicher vermieden. Durch das Fehlen des Druck- bzw. Entlastungsventils vermindert sich der schädliche Raum erheblich, da sich nun ein konstanter oder in etwa konstanter Strömungsquerschnitt zwischen dem Förderraum und dem Einspritzventil realisieren läßt. Auf diese Weise wird die Steifheit des Hochdrucksystems vergrößert, so daß bei gleichen Förderraten der Einspritzpumpe höhere Einspritzdrücke erreicht werden können. Höhere Einspritzdrücke führen aber zu verbesserter Verbrennung mit geringem Brennstoffverbrauch und niedriger Schadstoffemission.This object is achieved by the characterizing features of claim 1. Surprisingly, it has been shown that a pressure or relief valve can be dispensed with if there is a permanent flow connection between the high-pressure chamber and the low-pressure chamber in the time interval between the end of delivery and the start of delivery. This relieves the high pressure area into the low pressure chamber without the need for a pressure or relief valve. On the other hand, since the high-pressure area is under the pressure of the low-pressure space in the time interval between the end of delivery and the start of delivery, cavity formation in the high-pressure area is reliably avoided by the downward movement of the pump plunger. Due to the lack of the pressure or relief valve, the harmful space is considerably reduced, since a constant or approximately constant flow cross-section can now be realized between the delivery chamber and the injection valve. In this way, the rigidity of the high-pressure system is increased, so that higher injection pressures can be achieved with the same delivery rates of the injection pump. However, higher injection pressures lead to improved combustion with low fuel consumption and low pollutant emissions.

Weiterhin bedeutet der Fortfall des Druckventils eine Vereinfachung und Verbilligung des Einspritzelementes. Außerdem vermindern sich Bauhöhe und Wartungsaufwand der Einspritzvorrichtung durch Wegfall eines Verschleißteils.Furthermore, the elimination of the pressure valve means that the injection element is simplified and less expensive. In addition, the overall height and maintenance requirements of the injection device are reduced by eliminating a wearing part.

Durch die erfindungsgemäße Verwendung eines Sitzventils mit elektromagnetischer Stellvorrichtung als Steuerelement wird aufgrund von dessen kurzer Schaltzeit eine schnellere Entlastung des Hochdruckbereichs erreicht als bei dem üblichen mechanischen Steuerkantensystem, zumal das Entlastungsvolumen durch den Wegfall des Entlastungsventils erheblich vermindert ist. Dieser Vorteil wirkt sich aufgrund der zeitkonstanten und drehzahlunabhängigen Schaltzeit der elektromagnetischen Stellvorrichtung insbesondere bei niedrigen Motordrehzahlen aus.Due to the use of a seat valve with an electromagnetic actuating device as a control element according to the invention, a quick relief of the high pressure range is achieved due to its short switching time than with the conventional mechanical control edge system, especially since the relief volume is considerably reduced by the elimination of the relief valve. This advantage has an effect because of the time-constant and speed-independent switching time of the electromagnetic actuating device, in particular at low engine speeds.

Durch die erfindungsgemäße Lage und Anordnung des Sitzventils wird der schädliche Raum ebenfalls gering gehalten, da die Strömungsverbindung zwischen dem Hochdruckraum und dem Einspritzventil trotz des in dieser Strömungsverbindung eingebauten elektromagnetisch betätigten Sitzventils einen praktisch konstanten Strömungsquerschnitt aufweist. Das ist ermöglicht, da auch im Bereich des elektromagnetisch betätigten Sitzventils ein Hochdruckringraum als Umgehungsleitung mit konstantem Strömungsquerschnitt vorgesehen ist. Außerdem ist der schädliche Raum erfindungsgemäß durch das rechtwinklige Schneiden der Stufenbohrung und der Hochdruckbohrung minimiert.Due to the position and arrangement of the seat valve according to the invention, the harmful space is also kept small, since the flow connection between the high-pressure chamber and the injection valve has a practically constant flow cross section despite the electromagnetically operated seat valve installed in this flow connection. This is possible because a high-pressure annulus is also provided as a bypass line with a constant flow cross-section in the area of the electromagnetically actuated seat valve. In addition, according to the invention, the harmful space is minimized by cutting the stepped bore and the high-pressure bore at right angles.

Bei der erfindungsgemäßen Lösung wird der Hochdruckbereich während des Ansaugens mit dem im Niederdruckraum herrschenden Vordruck beaufschlagt. Dieser sogenannte Standdruck, dessen Höhe erfindungsgemäß durch ein Druckhalteventil im Saugraum gewährleistet ist, sichert in vorteilhafter Weise die Stabilität von Förderbeginn und Fördermenge der Einspritzpumpe und verringert die Kavitationsgefährdung des Systems.In the solution according to the invention, the high pressure area is acted upon by the admission pressure prevailing in the low pressure chamber during the suction. This so-called stand pressure, the level of which is ensured according to the invention by a pressure-maintaining valve in the suction chamber, advantageously ensures the stability of the start of delivery and the delivery rate of the injection pump and reduces the risk of cavitation in the system.

Die erfindungsgemäße Lösung bietet in einer weiteren Ausbildung den Vorteil, daß sich die Anordnung der Einspritzelemente den jeweiligen konstruktiven Gegebenheiten des Motorgehäuses optimal anpassen läßt.In a further embodiment, the solution according to the invention offers the advantage that the arrangement of the injection elements can be optimally adapted to the respective structural conditions of the engine housing.

Durch eine vorteilhafte Weiterbildung der Erfindung wird ein Leerlaufen der Brennstoffeinspritzpumpe bei stillstehendem Motor verhindert, da erfindungsgemäß ein dicht schließendes Zulaufventil den Niederdruckraum gegenüber dem Brennstoffzulauf abschließt.An advantageous development of the invention prevents the fuel injection pump from running dry when the engine is not running, since according to the invention a tightly closing inlet valve closes off the low-pressure chamber from the fuel inlet.

Die erfindungsgemäße Lösung bietet in einer weiteren Ausbildung den Vorteil, daß sich die Anordnung der Einspritzpumpenelemente den jeweiligen konstruktiven Gegebenheiten des Motorgehäuses optimal anpassen läßt.In a further embodiment, the solution according to the invention offers the advantage that the arrangement of the injection pump elements can be optimally adapted to the respective structural conditions of the engine housing.

Durch eine vorteilhafte Ausbildung der Erfindung wird die Einspritzleitung besonders kurz und damit der schädliche Raum besonders klein, so daß der Einspritzdruck besonders hoch werden kann.Due to an advantageous embodiment of the invention, the injection line is particularly short and thus the harmful space is particularly small, so that the injection pressure can be particularly high.

Durch eine vorteilhafte Ausbildung der Erfindung wird erreicht, daß getrennte Fertigung und Prüfung und Einzelaustausch von Einspritzpumpenelement und Steuerventil bzw. elektromagnetischer Stellvorichtung möglich ist.An advantageous embodiment of the invention ensures that separate manufacture and testing and individual replacement of the injection pump element and control valve or electromagnetic actuating device is possible.

Durch eine vorteilhafte Weiterbildung der Erfindung wird eine Verringerung des Totraumes der Brennstoffeinspritzvorrichtung erreicht.An advantageous development of the invention reduces the dead space of the fuel injection device.

Für eine uneingeschränkte Austauschbarkeit des Steuerventils ist es wichtig, ein gewisses Spiel zwischen der Stufenbohrung im Einspritzpumpenelement und dem Steuerventil vorzusehen.For an unrestricted interchangeability of the control valve, it is important to provide a certain play between the stepped bore in the injection pump element and the control valve.

In vorteilhafter Weise wird dieses Einbauspiel durch zwei Dichtelemente überbrückt, die neben ihrer Funktion als Hochdruckdichtung gleichsam eine Lagerung des Steuerventils in der Stufenbohrung der Plungerbüchse übernehmen.This installation clearance is advantageously bridged by two sealing elements which, in addition to their function as a high-pressure seal, also take over the bearing of the control valve in the stepped bore of the plunger bush.

Durch eine vorteilhafte Weiterbildung der Erfindung wird der Hochdruckbrennstoff, wenn er vom Steuerventilkörper abgesteuert wird, durch eine Bohrung in der Plungerbüchse zum Niederdruckraum zurückgeführt. Damit werden aufwendige äußere Verbindungsleitungen mit ihrer Leckagegefahr vermieden.In an advantageous development of the invention, the high-pressure fuel, when it is driven off by the control valve body, is returned to the low-pressure chamber through a hole in the plunger sleeve. This avoids expensive external connection lines with their risk of leakage.

Eine weitere vorteilhafte Weiterbildung der Erfindung ist die zur Achse des Steuerventilkörpers parallele Anordnung der Elemente, mit denen das Steuerventil an der Plungerbüchse befestigt ist. Diese Anordnung verhindert die Verspannung und damit ein Klemmen des Steuerventilkörpers in der Steuerventilbüchse.A further advantageous development of the invention is the arrangement of the elements parallel to the axis of the control valve body, with which the control valve is fastened to the plunger sleeve. This arrangement prevents the bracing and thus jamming of the control valve body in the control valve sleeve.

Durch eine vorteilhafte Ausbildung des Pumpenplungers mit einer Absteuernut wird erreicht, daß unabhängig von der Betriebstüchtigkeit des Steuerventils die Förderung der Einspritzpumpe unterbrochen wird, bevor die Förderung in den Kuppenradius des Einspritzpumpennockens läuft.An advantageous design of the pump plunger with a diverter groove ensures that the delivery of the injection pump is interrupted regardless of the serviceability of the control valve before the delivery runs into the tip radius of the injection pump cam.

Durch die erfindungsgemäße Anordnung der Ankerplatte in einem entlüfteten und mit Brennstoff gefüllten Raum ist bei entsprechender Abstimmung des Spaltes zwischen dem angezogenen Anker und der elektromagnetischen Stellvorrichtung auf die verschiedenen Auslegungsparameter des Steuerventils ist ein rückprallfreies Schließen und damit ein exaktes Steuern von Förderbeginn und Fördermenge des Brennstoffes ermöglicht.The arrangement of the anchor plate according to the invention in a vented and fuel-filled space, with appropriate adjustment of the gap between the attracted anchor and the electromagnetic actuating device to the various design parameters of the control valve, enables a rebound-free closing and thus an exact control of the start of delivery and the delivery rate of the fuel .

Eine vorteilhafte Weiterbildung der Erfindung mit einer Lecköllängs- und Querbohrung des Steuerventilkörpers erübrigt eine gesonderte Leckölrückführleitung und den damit verbundenen Aufwand und die Leckagegefahr.An advantageous development of the invention with a leak oil longitudinal and transverse bore of the control valve body eliminates the need for a separate leak oil return line and the associated effort and the risk of leakage.

Durch die erfindungsgemäße Ausbildung der äußeren Kontur des Einspritzpumpenelementes, ist ein Austausch eines Normalelementes gegen das Einspritzpumpenelement mit Steuerventil ohne jede Nacharbeit möglich.The inventive design of the outer contour of the injection pump element makes it possible to replace a normal element with the injection pump element with a control valve without any reworking.

Die erfindungsgemäße Lage von Hochdruckraum und Saug- bzw. Absteuerbohrung ermöglicht einen minimalen schädlichen Raum im Hochdruckbereich, der mit dem schädlichen Raum eines Normalelementes vergleichbar ist.The position of the high-pressure chamber and the suction or discharge borehole according to the invention enables a minimal harmful space in the high-pressure region, which is comparable to the harmful space of a normal element.

Weitere Merkmale der Erfindung ergeben sich aus der folgenden Beschreibung und der Zeichnung, in der Ausführungsbeispiele der Erfindung schematisch dargestellt sind.Further features of the invention result from the following description and the drawing, in which exemplary embodiments of the invention are shown schematically.

Es zeigen:

Fig.1:
einen Querschnitt durch eine schematisch dargestellte Einspritzpumpe mit elektromagnetisch betätigtem Steuerventil.
Fig.2:
einen Querschnitt durch die Brennstoffeinspritzvorrichtung,
Fig.3:
Detailschnitt durch die Brennstoffeinspritzvorrichtung.
Show it:
Fig.1:
a cross section through a schematically illustrated injection pump with an electromagnetically actuated control valve.
Fig. 2:
a cross section through the fuel injection device,
Fig. 3:
Detail section through the fuel injector.

Die Brennstoffeinspritzvorrichtung besteht aus einem Einspritzpumpenelement 1 und einem Steuerventil 2, wobei das Einspritzpumpenelement 1 zugleich Träger des Steuerventils 2 ist. Das Einspritzpumpenelement setzt sich zusammen aus einem Pumpenplunger 4, einer Plungerbüchse 5, das Steuerventil 2 aus einem Sitzventil 3 und einer elektromagnetischen Stellvorrichtung 7.The fuel injection device consists of an injection pump element 1 and a control valve 2, the injection pump element 1 also being the carrier of the control valve 2. The injection pump element is composed of a pump plunger 4, a plunger sleeve 5, the control valve 2 consists of a seat valve 3 and an electromagnetic actuator 7.

Der Plunger 4, der in einer Plungerbüchse 5 dichtend geführt ist, bildet mit dieser zusammen einen Hochdruckraum 11. Der Pumpenplunger 4 besitzt eine Absteuernut 8, die über eine Absteuerlängsbohrung 9 und eine Absteuerquerbohrung 10 mit einem Hochdruckraum 11 in Verbindung steht. Der Hochdruckaum 11 steht bei Stellung des Plungers 4 im unteren Totpunkt über eine Saug- bzw. Absteuerbohrung 14 mit dem Niederdruckraum 13 in Verbindung. Der Niederdruckraum 13 wird über ein Zulaufventil 51 von einer nicht dargestellten Brennstofförderpumpe beaufschlagt. Der Druck im Niederdruckraum 13 wird durch ein Druckhalteventil 52 konstant gehalten.The plunger 4, which is sealingly guided in a plunger sleeve 5, forms a high-pressure chamber 11 together with the plunger sleeve. When the plunger 4 is at bottom dead center, the high-pressure chamber 11 is connected to the low-pressure chamber 13 via a suction or discharge bore 14. The low-pressure chamber 13 is acted upon by a fuel feed pump, not shown, via an inlet valve 51. The pressure in the low pressure chamber 13 is kept constant by a pressure maintaining valve 52.

Der Plunger 1 wird über einen Rollenstößel 54 von einem Nocken 55 entgegen der Kraft einer Druckfeder 53 axial bewegt. Dadurch wird der Brennstoff nach Abschluß der Saug- bzw. Absteuerbohrung 14 in eine Hochdruckbohrung 12 gefördert. Solange das Sitzventil 3 offen steht, fließt der geförderte Brennstoff über den Hochdruckringraum 26, den Steuerventilsitz 25, den Niederdruckringraum 27 und die Rücklaufbohrung 15 zurück in den Niederdruckraum 13.The plunger 1 is moved axially via a roller tappet 54 by a cam 55 against the force of a compression spring 53. As a result, the fuel is conveyed into a high-pressure bore 12 after completion of the suction or discharge bore 14. As long as the seat valve 3 is open, the delivered fuel flows back into the low-pressure chamber 13 via the high-pressure annulus 26, the control valve seat 25, the low-pressure annulus 27 and the return bore 15.

Sobald das Sitzventil 3 durch Erregen der elektromagnetischen Stellvorrichtung 7 geschlossen wird, setzt die Hochdruckförderung ein, wobei Brennstoff durch die Hochdruckbohrung 12, den Hochdruckringraum 26 und die Einspritzleitung 48 zum Einspritzventil 49 gefördert wird.As soon as the seat valve 3 is closed by energizing the electromagnetic actuating device 7, high-pressure delivery begins, with fuel being delivered through the high-pressure bore 12, the high-pressure annular space 26 and the injection line 48 to the injection valve 49.

Der Hochdruckraum 11, die Hochdruckbohrung 12 mit dem Hochdruckringraum 26, die Einspritzleitung 48 und das Einspritzventil 49 bilden zusammen einen Hochdruckbereich 50.The high-pressure chamber 11, the high-pressure bore 12 with the high-pressure annular chamber 26, the injection line 48 and the injection valve 49 together form a high-pressure region 50.

Die Hochdruckförderung wird durch Öffnen des Sitzventils 3 beendet. Die dadurch geschaffene Verbindung zum Niederdruckraum 13 bewirkt eine Entlastung des Hochdruckbereichs 50, der bis zum erneuten Schließen des Sitzventils 3 unter dem Druck des Niederdruckraumes 13 steht. Dadurch werden Hohlraumbildung währen der Abwärtsbewegung des Pumpenplungers verhindert und konstante Druckverhältnisse zu Beginn der nächsten Einspritzung sichergestellt, die zu einer stabilen Förderbeginn- und Mengencharakteristik führen.The high-pressure delivery is ended by opening the seat valve 3. The connection thus created to the low-pressure chamber 13 relieves the high-pressure region 50, which is under the pressure of the low-pressure chamber 13 until the seat valve 3 is closed again. This prevents the formation of cavities during the downward movement of the pump plunger and ensures constant pressure conditions at the beginning of the next injection, which lead to a stable start of delivery and quantity characteristics.

Das Zulaufventil 51 und das Druckhalteventil 52, die als besonders dicht schließende Ventile ausgebildet sind, verhindern bei Motorstillstand ein Leerlaufen des Niederdruckraumes 13 und des Hochdruckbereichs 50, wodurch Schwierigkeiten beim Start des Motors vermieden werden.The inlet valve 51 and the pressure holding valve 52, which are designed as particularly tightly closing valves, prevent the low-pressure chamber 13 and the high-pressure region 50 from running dry when the engine is at a standstill, thereby avoiding difficulties when starting the engine.

Der Hochdruckraum 11 ist bis kurz unterhalb einer Stufenbohrung 19, die zur Aufnahme des Steuerventils 2 dient, hochgezogen. Dadurch wird das schädliche Volumen im Hochdruckraum 11 minimiert, was sich bei hohen Einspritzdrükken besonders vorteilhaft erweist.The high-pressure chamber 11 is pulled up to just below a stepped bore 19, which is used to hold the control valve 2. As a result, the harmful volume in the high-pressure chamber 11 is minimized, which proves to be particularly advantageous with high injection pressures.

Der Hochdruckraum 11 besitzt keinen Abschlußdeckel, da das Einspritzpumpenelement 1 als sogenanntes "Monoelement" ausgebildet ist. Die Ausbildung als Monoelement steigert in vorteilhafter Weise die Hochdruckfähigkeit der Brennstoffeinspritzvorrichtung durch Minimierung der Druckraumausweitung.The high-pressure chamber 11 has no end cover, since the injection pump element 1 is designed as a so-called "mono element". The design as a mono element advantageously increases the high-pressure capability of the fuel injection device by minimizing the expansion of the pressure space.

In der Plungerbüchse 5 befindet sich eine Saug- bzw. Absteuerbohrung 14, die den Hochdruckraum 11 mit einem Niederdruckraum 13 verbindet, der wiederum mit dem nicht dargestellten Saugraum des Einspritzpumpengehäuses verbunden ist.In the plunger bushing 5 there is a suction or discharge bore 14 which connects the high-pressure chamber 11 to a low-pressure chamber 13, which in turn is connected to the suction chamber of the injection pump housing, not shown.

Die Saug- bzw. Absteuerbohrung 14 ist vom Niederdruckraum 13 aus schräg in Richtung Hochdruckraum 11 gebohrt, um der Lage des Hochdruckraumes 11 Rechnung zu tragen.The suction or discharge bore 14 is drilled obliquely from the low pressure chamber 13 in the direction of the high pressure chamber 11 in order to take into account the position of the high pressure chamber 11.

Der Niederdruckraum 13 ist außerdem über eine Rücklaufbohrung 15 mit einem Ringraum 16 einer Steuerventilbüchse 17 des Sitzventils 3 verbunden. Dadurch wird eine externe Rücklaufleitung, die Bauaufwand und Leckagerisiko bedeutet, vermieden.The low-pressure chamber 13 is also connected via a return bore 15 to an annular space 16 of a control valve sleeve 17 of the seat valve 3. This avoids an external return line, which means construction costs and leakage risk.

Das Sitzventil 3 sitzt mit Spielpassung in der Stufenbohrung 19 der Plungerbüchse 5 und ist in zwei Hochdruckdichtelemente 20 gelagert. Es wird durch nicht dargestellte Schrauben, die durch Bohrungen in einem Abschlußdeckel 21 und der Plungerbüchse 5 hindurchgesteckt und in die Steuerventilbüchse 17 eingeschraubt werden, zu einem festen Verband mit der Plungerbüchse 5 verbunden, ohne daß das Sitzventil 3 verspannt würde. Durch das Einbauspiel zwischen Steuerventilbüchse 17 und Stufenbohrung 19 wird außerdem ein Verspannen und folglich ein Klemmen des Sitzventilels 3, verursacht durch das Anziehen der Einspritzleitung 48, vermieden.The seat valve 3 sits with a clearance fit in the stepped bore 19 of the plunger sleeve 5 and is mounted in two high-pressure sealing elements 20. It is connected by screws, not shown, which are inserted through bores in an end cover 21 and the plunger sleeve 5 and screwed into the control valve sleeve 17, to form a firm bond with the plunger sleeve 5 without the seat valve 3 being tensioned. Due to the installation clearance between the control valve sleeve 17 and the stepped bore 19, tensioning and consequently jamming of the seat valve 3, caused by the tightening of the injection line 48, is also avoided.

Ein besonderer Vorteil dieser Anordnung besteht darin, daß ein unabhängiger Austausch von Steuerventil 2 und Einspritzpumpenelement 1 so wie der elektromagnetischen Stellvorrichtung 7 sichergestellt ist. Durch diesen modularen Aufbau ist eine kostengünstige Fertigung und Reparatur der Brennstoffeinspritzvorrichtung möglich.A particular advantage of this arrangement is that an independent exchange of control valve 2 and injection pump element 1 as well as the electromagnetic actuating device 7 is ensured. This modular structure enables cost-effective production and repair of the fuel injection device.

Das Sitzventil 3 besitzt eine Steuerventilbüchse 17 und einen Steuerventilkörper 22, der in der Steuerventilbüchse 17 axial beweglich geführt ist, und zwar in einer Hochdruckführung 23 und einer Niederdruckführung 24.The seat valve 3 has a control valve sleeve 17 and a control valve body 22, which is guided so that it can move axially in the control valve sleeve 17, specifically in a high-pressure guide 23 and a low-pressure guide 24.

Der Steuerventilkörper 22 trennt mit einem Steuerventilsitz 25 einen Hochdruckringraum 26 von einem Niederdruckringraum 27. Der Hochdruckringraum 26 ist über eine Hochdrucksteuerbohrung 28 und die Hochdruckbohrung 12 mit dem Hochdruckraum 11 verbunden. Der Niederdruckringraum 27 ist über die Absteuerbohrung 29, den Ringraum 16 und die Rücklaufbohrung 15 mit dem Niederdruckraum 13 verbunden.The control valve body 22 separates a high-pressure annulus 26 from a low-pressure annulus 27 with a control valve seat 25. The high-pressure annulus 26 is via a high-pressure control bore 28 and the high pressure bore 12 connected to the high pressure chamber 11. The low-pressure annular space 27 is connected to the low-pressure space 13 via the control bore 29, the annular space 16 and the return bore 15.

Der Steuerventilkörper 22 besitzt eine Lecköllängsbohrung 42 und eine Leckölquerbohrung 43, die eine Verbindung zwischen einem Leckölraum 44 und einem Federraum 34 schaffen.The control valve body 22 has a leak oil longitudinal bore 42 and a leak oil transverse bore 43, which create a connection between a leak oil chamber 44 and a spring chamber 34.

An dem Ende des Steuerventilkörpers 22, an dem sich die Niederdruckführung 24 befindet, ist eine Ankerplatte 30 befestigt, die von der elektromagnetischen Stellvorrichtung 7 bewegt wird. Die Befestigung der Ankerplatte 30 geschieht mittels einer in den Steuerventilkörper 22 geschraubten Senkschraube 31, die die Ankerplatte 30 und einen Anschlagring 32 axial gegen den Steuerventilkörper 22 spannt.At the end of the control valve body 22, on which the low-pressure guide 24 is located, an anchor plate 30 is fastened, which is moved by the electromagnetic actuating device 7. The anchor plate 30 is fastened by means of a countersunk screw 31 screwed into the control valve body 22, which axially clamps the anchor plate 30 and a stop ring 32 against the control valve body 22.

Die Ankerplatte 30 befindet sich in einem kraftstoffgefüllten Dämpfungsraum 33, der von einem Zwischenstück 41 und der elektromagnetischen Stellvorrichtung 7 begrenzt wird. Das Volumen des Dämpfungsraumes 33 ist so dimensioniert, daß bei der axialen Bewegung der Ankerplatte 30 keine nennenswerten Strömungswiderstände zwischen der Ankerplatte 30 und den Wänden des Zwischenstückes 41 auftreten.The anchor plate 30 is located in a fuel-filled damping space 33 which is delimited by an intermediate piece 41 and the electromagnetic actuating device 7. The volume of the damping space 33 is dimensioned such that no significant flow resistances occur between the anchor plate 30 and the walls of the intermediate piece 41 during the axial movement of the anchor plate 30.

Der Dämpfungsraum 33 steht in Verbindung mit einem ebenfalls brennstoffgefüllten Federraum 34. Im Federraum 34 befindet sich eine Feder 36, deren Kraft den Anschlagring 32 in Richtung Anschlag 35 beaufschlagt. Der Anschlag 35 dient als Hubbegrenzung des Steuerventilkörpers 22.The damping chamber 33 is connected to a spring chamber 34, which is also fuel-filled. In the spring chamber 34 there is a spring 36, the force of which acts on the stop ring 32 in the direction of the stop 35. The stop 35 serves to limit the stroke of the control valve body 22.

Der Dämpfungsraum 33 und der Federraum 34 stehen über eine Drosselbohrung 37 mit der Absteuerbohrung 29 in Verbindung.The damping chamber 33 and the spring chamber 34 are connected to the control bore 29 via a throttle bore 37.

Im Bereich der in Einbaulage höchsten Stelle des Dämpfungsraumes 33 ist eine Gewindebohrung 38 angebracht, an die eine Entlüftungs- bzw. Brennstoffrücklaufleitung 39 angeschlossen ist, die zum nicht abgebildeten Brennstofftank führt.In the area of the highest point of the damping space 33 in the installed position, a threaded bore 38 is provided, to which a ventilation or fuel return line 39 is connected, which leads to the fuel tank (not shown).

In dieser Entlüftungs- bzw. Brennstoffrücklaufleitung 39 ist eine Druckhalteventil 40 angeordnet, dessen Absteuerdruck kleiner als der Förderdruck der nicht abgebildeten Kraftstofförderpumpe ist.In this venting or fuel return line 39, a pressure holding valve 40 is arranged, the cut-off pressure of which is lower than the delivery pressure of the fuel delivery pump, not shown.

Die elektromagnetische Stellvorrichtung 7 wird durch nicht dargestellte, parallel zur Achse des Steuerventilkörpers 22 wirkenden Schrauben mit dem Zwischenstück 41 gegen die Steuerventilbüchse 17 gespannt, ohne diese zu verspannen.The electromagnetic adjusting device 7 is clamped against the control valve sleeve 17 by screws (not shown), acting parallel to the axis of the control valve body 22, with the intermediate piece 41, without bracing the latter.

Der gesamte Niederdruckbereich des Steuerventils 2 wird durch Runddichtringe 45 abgedichtet.The entire low-pressure area of the control valve 2 is sealed by O-rings 45.

Die Brennstoffeinspritzvorrichtung funktioniert folgendermaßen:The fuel injector works as follows:

Beim Förderhub wird der Pumpenplunger 4 aus seiner unteren Totpunktlage in Richtung Steuerventil 2 bewegt. Dabei schließt er nach Durchlaufen eines Vorhubes zunächst die Saug- und Absteuerbohrung 14. Danach fördert der Plunger 4 Brennstoff in die Hochdruckbohrung 12 und in die Hochdrucksteuerbohrung 28.During the delivery stroke, the pump plunger 4 is moved from its bottom dead center position in the direction of the control valve 2. After passing through a preliminary stroke, it first closes the suction and discharge bore 14. The plunger 4 then delivers fuel into the high-pressure bore 12 and into the high-pressure control bore 28.

Solange der Steuerventilkörper 22 mit dem Anschlagring 32 und der Ankerplatte 30 von der Feder 36 am Anschlag 35 gehalten wird, sind der Hochdruckringraum 26 und der Niederdruckringraum 27 über den Steuerventilsitz 25 verbunden. Dadurch strömt der geförderte Kraftstoff über die Absteuerbohrungen 29, den Ringraum 16 und die Rücklaufbohrung 15 in den Niederdruckraum 13 zurück.As long as the control valve body 22 with the stop ring 32 and the anchor plate 30 is held by the spring 36 at the stop 35, the high-pressure annular space 26 and the low-pressure annular space 27 are connected via the control valve seat 25. As a result, the delivered fuel flows back into the low-pressure chamber 13 via the control bores 29, the annular space 16 and the return bore 15.

Sobald die elektromagnetische Stellvorrichtung 7 durch einen Stromimpuls erregt wird, wird die Ankerplatte 39 angezogen. Dadurch wird der Steuerventilkörper 22 gegen den Steuerventilsitz 25 gezogen, wodurch die Förderung des Brennstoffs über die Einspritzleitung 48 zur Einspritzdüse 49 beginnt.As soon as the electromagnetic actuating device 7 is excited by a current pulse, the armature plate 39 is attracted. As a result, the control valve body 22 is pulled against the control valve seat 25, as a result of which the delivery of the fuel via the injection line 48 to the injection nozzle 49 begins.

Mit dem Anziehen der Ankerplatte 30 wird zugleich die Feder 36 vorgespannt. Sobald die elektromagnetische Stellvorrichtung 7 stromlos gemacht wird, hebt die Feder 36 den Steuerventilkörper 22 von seinem Sitz 25 ab. Dadurch strömt der Brennstoff wieder in die Niederdruckräume und die Brennstoffeinspritzung ist beendet.When the anchor plate 30 is tightened, the spring 36 is also preloaded. As soon as the electromagnetic adjusting device 7 is de-energized, the spring 36 lifts the control valve body 22 from its seat 25. As a result, the fuel flows back into the low-pressure chambers and the fuel injection is ended.

Eine Voraussetzung für die präzise Funktion des Sitzventils 3 und damit für reproduzierbaren Förderbeginn und schwankungsfreie Fördermenge ist ein rückprallfreies Aufsetzen des Steuerventilkörpers 22 auf den Steuerventilsitz 25. Dies wird erfindungsgemäß erreicht durch eine fein abgestimmte Dämpfung der Bewegung des Steuerventilkörpers 22. Zur Dämpfung wird die Verdrängerströmung zwischen Ankerplatte 30 und der elektromagnetischen Stellvorrichtung 7 benutzt. Die Ankerplatte 30 ist ohne offene, axiale Bohrungen ausgeführt, um eine möglichst wirksame Quetschströmung am Hubende zwischen Ankerplatte 30 und elektromagnetische Stellvorrichtung 7 zu bewirken.A prerequisite for the precise function of the seat valve 3 and thus for reproducible delivery start and fluctuation-free delivery quantity is a rebound-free placement of the control valve body 22 on the control valve seat 25. This is achieved according to the invention by a finely tuned damping of the movement of the control valve body 22. For the damping, the displacement flow is between Anchor plate 30 and the electromagnetic actuator 7 used. The armature plate 30 is designed without open, axial bores in order to effect the most effective squeezing flow at the stroke end between the armature plate 30 and the electromagnetic actuating device 7.

Das erforderliche Maß der Dämpfung hängt unter anderem von der bewegten Masse ab, d. h. von der Masse des Steuerventilkörpers 22 + Ankerplatte 30 + Senkschraube 31 + Anschlagring 32 + Anteil der Masse der Feder 36. Ein weitere dämpfungsrelevanter Faktor ist die Federsteifigkeit des Steuerventilsitzes 25.The amount of damping required depends, among other things, on the moving mass, i. H. from the mass of the control valve body 22 + anchor plate 30 + countersunk screw 31 + stop ring 32 + proportion of the mass of the spring 36. Another factor relevant to damping is the spring stiffness of the control valve seat 25.

Die Dämpfung selbst hängt unter anderem von der Brennstoffviskosität, der Geometrie der Ankerplatte 30 und dem Mindestabstand 46 zwischen Ankerplatte 30 und elektromagnetischer Stellvorrichtung 7 sowie von dem Druck im Dämpfungsraum 33 ab. Diese Einflußfaktoren müssen aufeinander abgestimmt werden. Die optimale Abstimmung ist erreicht, wenn das Aufsetzen des Steuerventilkörpers 22 auf den Steuerventilsitz 25 gerade rückschlagfrei erfolgt und die dämpfungsbedingte Verlangsamung der Bewegung des Steuerventilkörpers 22 minimiert ist.The damping itself depends, among other things, on the fuel viscosity, the geometry of the anchor plate 30 and the minimum distance 46 between the anchor plate 30 and the electromagnetic actuating device 7 and the pressure in the damping space 33. These influencing factors have to be coordinated. The optimal adjustment is achieved when the control valve body 22 is placed on the control valve seat 25 without kickback and the damping-related slowdown in the movement of the control valve body 22 is minimized.

Die Versorgung des Dämpfungsraumes 33 mit Dämpfungsflüssigkeit, z. B. Dämpfungsöl, kann über einen gesonderten Dämpfungsölkreislauf erfolgen. Im vorliegenden Fall wird erfindungsgemäß Brennstoff aus dem Niederdruckbereich, speziell aus der Absteuerbohrung 29 des Sitzventils 3 entnommen und zwar über die Drosselbohrung 37. Letztere verhindert, daß die Druckstöße in der Absteuerbohrung 29 in den Dämpfungsraum 33 gelangen.The supply of the damping chamber 33 with damping liquid, for. B. damping oil, can be done via a separate damping oil circuit. In the present case, according to the invention, fuel is taken from the low-pressure area, specifically from the control bore 29 of the seat valve 3, specifically via the throttle bore 37. The latter prevents the pressure surges in the control bore 29 from reaching the damping chamber 33.

Für ein einwandfreies Funktionieren der Dämpfung ist es wichtig, daß sich keine Luft im Dämpfungsraum 33 befindet, da hierdurch die Viskosität und Kompressibilität des Dämpfungsmediums beeinflußt werden. Außerdem ist es wichtig, daß die Dämpfungsflüssigkeit kontinuierlich erneuert wird, da diese sich erwärmt und altert.For proper functioning of the damping, it is important that there is no air in the damping space 33, since this affects the viscosity and compressibility of the damping medium. It is also important that the damping fluid is renewed continuously as it warms up and ages.

Erfindungsgemäß wird die Entlüftung des Dämpfungsraumes 33 über die Gewindebohrung 38 bewerkstelligt, die so angebracht ist, daß sie sich in Einbaulage des Steuerventils 2 im Bereich der höchsten Stelle des Dämpfungsraumes 33 befindet.According to the invention, the venting of the damping space 33 is accomplished via the threaded bore 38, which is provided in such a way that it is in the installed position of the control valve 2 in the region of the highest point of the damping space 33.

An die Gewindebohrung 38 ist die Entlüftungs- bzw. Brennstoffrücklaufleitung 39 angeschlossen, durch die der Brennstoff über das Druckhalteventil 40 zurück zum nicht abgebildeten Brennstofftank fließt. Das Druckhalteventil 40 stellt einen bestimmten Flüssigkeitsdruck in Dämpfungsraum 33 sicher, der niedriger als der maximale Förderdruck der nicht dargestellten Niederdruckpumpe und niedriger als der Druck in den Niederdruckräumen der Brennstoffeinspritzvorrichtung ist. Dadurch wird eine Durchströmung des Dämpfungsraumes 33 und damit eine Erneuerung des Dämpfungsmediums Brennstoff und eine Kühlung des Steuerventils 2 sichergestellt. Außerdem bewirkt das Druckhalteventil 40, daß beim Stillstand des Motors der Dämpfungsraum 33 nicht leerlaufen kann, was zu ungedämpfter Hubbewegung und damit zu Sitzprellen des Steuerventils 3 führt. Dies hätte unter anderem einen falschen Förderbeginn beim Wiederanlassen des Motors zur Folge.The vent or fuel return line 39 is connected to the threaded bore 38, through which the fuel does not return to the pressure holding valve 40 shown fuel tank flows. The pressure holding valve 40 ensures a certain liquid pressure in the damping chamber 33, which is lower than the maximum delivery pressure of the low-pressure pump, not shown, and lower than the pressure in the low-pressure chambers of the fuel injector. This ensures a flow through the damping chamber 33 and thus renewal of the damping medium fuel and cooling of the control valve 2. In addition, the pressure control valve 40 has the effect that the damping chamber 33 cannot run empty when the engine is at a standstill, which leads to undamped lifting movement and thus to bouncing of the control valve 3. Among other things, this would result in an incorrect start of delivery when the engine is restarted.

Das Lecköl aus dem Leckölraum 44 wird über die Lecköllängsbohrung 42 und die Leckölquerbohrung 43 im Steuerventilkörper 22 zum Federraum 34 und damit in den Dämpfungsölkreislauf geführt. Diese erfindungsgemäße Lösung erspart eine separate Leckölrückführleitung.The leak oil from the leak oil chamber 44 is guided via the leak oil longitudinal bore 42 and the leak oil cross bore 43 in the control valve body 22 to the spring chamber 34 and thus into the damping oil circuit. This solution according to the invention saves a separate leakage oil return line.

Für den Fall eines Versagens des Steuerventils 2 sorgt die Absteuernut 8 des Pumpenplungers 4 am Ende des Förderhubes für ein Absteuern des Brennstoffes in die Saug- bzw. Absteuerbohrung 14. Damit wird die Brennstoffeinspritzung in jedem Fall beendet, bevor die Förderung in den Kuppenbereich des Einspritzpumpennockens gelangt und diesen überbelastet.In the event of a failure of the control valve 2, the control groove 8 of the pump plunger 4 ensures that the fuel is directed into the suction or control bore 14 at the end of the delivery stroke. In this case, the fuel injection is ended in any case before the delivery into the tip area of the injection pump cam arrives and overloaded it.

Der Pumpenplunger 4 des Einspritzpumpenelements 1 ist erheblich einfacher zu fertigen, als der des Normalelementes 1a, da die Verdreheinrichtung und die präzisen Steuerkanten entfallen.The pump plunger 4 of the injection pump element 1 is considerably easier to manufacture than that of the normal element 1a, since the rotating device and the precise control edges are eliminated.

Die erfindungsgemäße Brennstoffeinspritzvorrichtung gestattet eine genaue Bestimmung von Förderbeginn und Dosierung der Brennstoffeinspritzmenge durch das rückprallfreie Aufsetzen des Steuerventilkörpers 22 auf den Steuerventilsitz 25. Außerdem ist sie fertigungsund servicefreundlich, da die Hauptkomponenten Einspritzpumpenelement 1, Steuerventil 2 und elektromagnetische Stellvorrichtung 7 einzeln und unabhängig voneinander zu fertigen, zu prüfen und auszutauschen sind.The fuel injection device according to the invention allows an exact determination of the start of delivery and metering of the fuel injection quantity by the rebound-free placement of the control valve body 22 on the control valve seat 25. In addition, it is easy to manufacture and service, since the main components of injection pump element 1, control valve 2 and electromagnetic actuating device 7 are to be manufactured, checked and exchanged individually and independently of one another are.

Claims (11)

  1. Fuel injection apparatus for diesel internal combustion engines, comprising at least one pump plunger (4) which is guided in a sealing manner in a plunger casing (5) and, together with the plunger casing (5), forms a high pressure chamber (11) which is connectable via a control element with a low pressure chamber (13) to control the injection time and injection quantity, wherein the high pressure chamber (11) is in flow connection with an injection valve (49) via a high pressure bore (12) provided in the plunger casing (5) or an adapter respectively and via an injection line (48) adjoining thereto, wherein a permanently-open flow connection is provided between the high pressure chamber (11) and the injection valve (49), which flow connection has a constant or approximately constant flow cross-section, and wherein the control element is constructed as an electromagnetically operable seat valve (3) which controls a return bore (15) from the high pressure chamber (11) to the low pressure chamber (13) and which has a control valve body (22) axially movable in a control valve casing (17) through an electromagnetic servo or adjustment device (7) in association with a spring (36), and at one end of which valve body (22) an anchor plate (30) is secured,
    characterised in that a low pressure annular chamber (27) arranged in the control valve casing (17) communicates with the low pressure chamber (13) via the return bore (15); that, in the plunger casing (5) or in an adapter, at a small distance above the high pressure chamber (11), a stepped bore (19) is arranged to receive the seat valve (3); that the anchor plate (30) is arranged in a damping chamber (33) filled with fuel; that, between the damping chamber (33) and the low-pressure chambers, a throttle bore (37) is provided; and that, in the region of the highest point of the damping chamber (33) in the fitted position of the fuel injection apparatus,a vent or fuel return line (38) is connected.
  2. Fuel injection apparatus according to Claim 1,
    characterised in that the stepped bore (19) and the high pressure bore (12) intersect.
  3. Fuel injection apparatus according to Claim 1 or 2,
    characterised in that the angle of intersection between the stepped bore (19) and the high pressure bore (12) is 90°.
  4. Fuel injection apparatus according to any one of the preceding claims,
    characterised in that, in the vent or fuel return line (39), a pressure holding valve (40) is arranged, the opening pressure of which is lower than the pressure in the low pressure chambers of the injection pump element (1).
  5. Injection apparatus according to any one of the preceding claims,
    characterised in that the seat valve (3) is arranged between the high pressure chamber (11) and the injection line (48).
  6. Injection apparatus according to any one of the preceding claims,
    characterised in that the seat valve (3) penetrates the high pressure bore (12) and the high pressure bore (12) in the region of penetration is constructed as a high pressure annular chamber (26) surrounding the seat valve (3).
  7. Injection apparatus according to any one of the preceding claims,
    characterised in that the low pressure chamber (13) has a feed valve (51) tightly closing towards the exterior and a tightly-closing pressure holding valve (52) opening towards the exterior.
  8. Fuel injection apparatus according to any one of the preceding claims,
    characterised in that the seat valve (3) is arranged in the stepped bore (19) as a sliding fit.
  9. Fuel injection apparatus according to any one of the preceding Claims,
    characterised in that, between the control valve casing (17) and the stepped bore (19), sealing elements (20) are arranged on both sides of a high pressure control bore (28).
  10. Fuel injection apparatus according to any one of the preceding Claims,
    characterised in that, for the attachment of the seat valve (3) on the plunger casing (5), attachment elements are arranged with an attachment force acting parallel to the direction of the axis of the control valve body (22).
  11. Fuel injection apparatus according to any one of the preceding claims,
    characterised in that the anchor plate (30) is of solid construction and that, with a given mass of the moving parts of the seat valve (3), a given force of the spring (36), a given geometry of the anchor plate (30), and a given fuel viscosity in the operating temperature range, the force of the electromagnetic servo or adjustment device and the gap between the anchor plate (30) and the electromagnetic adjustment device (7) in a tightened state are coordinated such that the placing of the control valve body (22) onto a control valve seat (25) takes place free of rebound.
EP90106394A 1989-04-04 1990-04-04 Fuel injection apparatus Expired - Lifetime EP0391366B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90106394T ATE99386T1 (en) 1989-04-04 1990-04-04 FUEL INJECTOR.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3910793 1989-04-04
DE3910793A DE3910793C2 (en) 1989-04-04 1989-04-04 Fuel injector

Publications (3)

Publication Number Publication Date
EP0391366A2 EP0391366A2 (en) 1990-10-10
EP0391366A3 EP0391366A3 (en) 1991-01-09
EP0391366B1 true EP0391366B1 (en) 1993-12-29

Family

ID=6377773

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90106394A Expired - Lifetime EP0391366B1 (en) 1989-04-04 1990-04-04 Fuel injection apparatus

Country Status (4)

Country Link
US (1) US5125807A (en)
EP (1) EP0391366B1 (en)
AT (1) ATE99386T1 (en)
DE (2) DE3910793C2 (en)

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Also Published As

Publication number Publication date
EP0391366A2 (en) 1990-10-10
ATE99386T1 (en) 1994-01-15
DE3910793C2 (en) 1996-05-23
EP0391366A3 (en) 1991-01-09
DE59003995D1 (en) 1994-02-10
DE3910793A1 (en) 1990-10-11
US5125807A (en) 1992-06-30

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