EP1187985B1 - Control element for controlling injection systems - Google Patents

Control element for controlling injection systems Download PDF

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Publication number
EP1187985B1
EP1187985B1 EP00988559A EP00988559A EP1187985B1 EP 1187985 B1 EP1187985 B1 EP 1187985B1 EP 00988559 A EP00988559 A EP 00988559A EP 00988559 A EP00988559 A EP 00988559A EP 1187985 B1 EP1187985 B1 EP 1187985B1
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EP
European Patent Office
Prior art keywords
control
control element
injection system
outflow
housing
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Expired - Lifetime
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EP00988559A
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German (de)
French (fr)
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EP1187985A2 (en
Inventor
Jaroslaw Hlousek
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1187985A2 publication Critical patent/EP1187985A2/en
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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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/08—Feeding by means of driven pumps electrically driven
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • 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
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines

Definitions

  • Hydraulically driven injection pumps via injectors to be hydraulically operated perform a control process which effects the delivery end and the respective start of delivery by means of a movable control element.
  • the control is controlled within very short switching times, which may be less than 2 ms.
  • the strokes that the control performs are above 0.3 mm.
  • In injectors which are in communication with a common high-pressure accumulator (common rail) in multiple injectors, or in hydraulically driven injection pumps very short switching or An Kunststoffindustrie concerns may be required to perform strokes of a control.
  • the required switching times can be less than 2 ms; for very small hydraulically actuated units, ie units of very small flow cross-section, a direct magnetic control can be used.
  • the direct solenoid control can be used with small flow area units, where, for example, a 3/2-way control can be implemented when strokes are to be performed by the control, which are less than 0.3 mm stroke. If longer Sachlementhübe be required, the direct magnetic control of a designed as a control slide control reaches its limits.
  • Another variant is in a servo control of the spool, but which can only be realized if the closing of the control edges in each case from the control travel not exceed the limits mentioned.
  • the above-mentioned restriction applies that the servo control is preferably used only in small units with a small flow area, in which consequently the restoring forces are still in controllable with servo motors order of magnitude.
  • larger flow rates and resulting larger actuating forces occur, which are no longer controllable with servomotors alone or with an exclusive magnetic control of the spool alone.
  • DE 197 38 397 A1 discloses a fuel injection system for an internal combustion engine, which has a two-fuel injector, in the pressure chamber alternately fuel and an additional liquid can be conveyed.
  • a valve arrangement is provided, through which the high-pressure side fuel supply to the two-component injection nozzle and the connection of the pressure chamber with a low-pressure side and with a feed line of the additional liquid can be controlled.
  • the valve arrangement has a switching valve, which is designed both for controlling the admission of the pressure chamber with high or low pressure and for controlling the filling of the pressure chamber with the additional liquid.
  • EP 0 879 979 A2 relates to a hydraulic valve with two connections, which can be switched such that in each case only one outlet can be supplied with liquid at the same time.
  • a spindle with two seals is movable in a housing by two solenoids and is held by means of two springs in a central position in which the seals close both outlets. When the spindle is moved in one direction, it releases the flow to an outlet and further allows flow through a bypass channel to an opposite side of the spindle, thereby counteracting the force exerted by the solenoid. This allows the force exerted on an outlet to be controlled in stages.
  • stops are provided in the housing enclosing the control element and limit the prestressing of the energy accumulators.
  • the control according to the invention can be connected, for example-designed as a control slide-with an injection nozzle to inject fuel under extremely high pressure in a combustion chamber, or serve to supply a hydraulically operated piston pump.
  • inventive design of the control as a force storage assisted control system can be the shortest switching times at longer stroke lengths realized.
  • the short switching times on the control can be realized in that each one of the control end associated with energy storage, which supports the control element movement performed by the control of one of the actuators and thereby shortens the switching time.
  • a 3- / 2-way valve is shown, with a Steuererlement which is movable via two individually controllable actuators.
  • a housing 6 of a 3- / 2-way valve designed as a control slide control 1 is added.
  • the actuators 2, 3 are arranged opposite one another.
  • the actuators 2, 3 are preferably designed as electrically controllable electromagnets, which can be controlled via a control unit 15 which controls both actuators 2, 3 separately.
  • the preferably designed as electromagnets actuators 2, 3 are compared to the diameter of the control element 1 in the larger diameter dimensioned surfaces.
  • control element 1 Trained as a control slide control 1 is received in a bore 31 of the housing 6.
  • the bore 31 around the control element 1 is executed in the narrowest tolerances in order to minimize the leakage losses which occur relative to one another during the relative movement of the components.
  • the control element 1 is preferably made of a high-quality material as a movable component, while the housing 6 of the 3- / 2-way valve may also consist of less expensive material.
  • two cylindrical closing bodies 32 spaced apart from one another with their facing end faces are provided on the control element 1.
  • the cylindrical closing body 32 limit on the one hand a cavity 28 within the bore 31 of the housing 6, on the other hand serve the cylindrical closing body 32 as annular abutment surfaces for the inlet side and the outlet end of the control element 1 respectively associated with energy storage 4 and 5.
  • the energy storage 4, 5th can preferably be formed as coil springs.
  • the coil springs can be designed as spring assemblies, for example connected in parallel, inserted into one another or also arranged one behind the other in series.
  • coil springs and other spring elements such as spring rings or disc springs could be provided in the bore 31 of the housing 6 as the control acting force storage 4, 5.
  • annular stop surfaces 13 and 14 are formed, which limit the stroke of the control element 1.
  • the stops 13, 14 may be shrunk in the bore 31, for example, as annularly extending sleeve elements.
  • the stops 13, 14 are placed in the bore 31 in such a way that the high-pressure feed line 7 is just released by the housing-side control edge 17 and the slider side on the cylindrical closing body 32 provided control edge 18 by the inlet side provided cylindrical closing element 32, while abutting the drain-side lock cylinder 32 on the stop 13 - as shown in Fig. 1 - the non-pressure flow 8 for Reservoir 21 is just released, so that excess in the cavity 28 still existing fuel or engine oil can flow.
  • a high-pressure feed line 7 is carried out, via which the housing 6 communicates with a high-pressure accumulation chamber 12.
  • the high-pressure accumulation chamber 12 (common rail) is acted upon by a high-pressure pump 23, for example with fuel from a reservoir 21; the current fuel level prevailing in the reservoir 21 is designated by reference numeral 22.
  • the pressureless drain line 8 extending from the housing 6 opens directly into the reservoir 21 and returns excess fuel into the reservoir 21.
  • the high-pressure accumulation chamber 12 is subjected to fuel under extremely high pressure.
  • the high-pressure accumulation chamber 12 instead of fuel, for example with mineral oil, e.g. Engine oil filled.
  • the two actuators 2, 3 can be interconnected via tie rods 26 and 27, which in turn can be provided with lock nuts 29 to clamp the two actuators 2, 3 against each other.
  • the operation of the inventively proposed 3- / 2-way valve is based on the control of the actuators 2, 3, preferably electromagnets, via the control unit 15 via control lines 30.
  • the inlet side Actuator 2 driven and repels the this opposite surface of the control element 1, while the drain side positioned actuator 3 which this opposite surface on the control element 1 attracts.
  • the high-pressure feed line 7 by covering the control edges 17, the housing-side control edge 17 and the slide-side control edge 18, closed.
  • a quantity of fuel or engine oil has entered the supply line 9, while after opening the cavity 28 excess fuel or possibly excess engine oil can flow back into the reservoir 21, depending on the application, by controlling the pressure-free outlet 8 ,
  • control element 1 In an oppositely extending movement of the control element 1 is a control of the drain side provided actuator 3 such that the opposite surface of the control element 1 is repelled.
  • the inlet side arranged actuator 2 can be controlled by the control unit 15 so that it attracts the opposite drain-side surface of the control element 1.
  • the control element 1 moves toward the high-pressure line 7 and closes the flow edge 8 by the overlapping housing-side control edge 20 and the control edge provided on the cylindrical closing body 32.
  • the energy store 4 provided on the upstream side is compressed until the inlet-side lock cylinder 32 bears against the stop 14 ,
  • the closing movement of the drain 8 is supported by the drain-side power accumulator 5, which supports the closing movement by its relaxation.
  • the supply line 9 is acted upon on the short side solely by the volume of fluid trapped in the cavity 28 and conducts it via a supply line 9 to the housing 3 of FIGS. Way valve related injectors on.
  • the lock cylinder 32 Coaxial with the axis 25 of the control 1, the lock cylinder 32 are added. At the end faces of the lock cylinder 32 can be easily and inexpensively to be dimensioned fuel or engine oil quantities produce limiting control edges, depending on the injector to be acted upon. In addition to a precise metering of the volume to be injected, the degree of overlap of the pairs of control edges 17, 18 or 19, 20 ensures leakage leakage to a minimum.
  • each amount of fuel or engine oil can be specified by specifying the diameter of the lock cylinder 32 interconnecting portion of the control 1 exactly.
  • Fig. 1a shows in a schematic arrangement as an injection device connected to the connecting hole an injection nozzle 10.
  • the opening 35 - by a nozzle needle closure - releasable - protrudes into the combustion chamber of an internal combustion engine.
  • a high-pressure pump 11 shown schematically in FIG. 1b, may be charged with engine oil, for example, which acts on a line 34 with increased pressure.
  • the pressure chamber can be sealed with a check valve 33 and open when exceeding a certain presettable overpressure.
  • the inventive 3- / 2-way valve for pressurizing a high-pressure pump 11, the high-pressure accumulation chamber 12 instead of fuel with high-pressure engine oil - which is only to be mentioned here for example - acted upon.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Multiple-Way Valves (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

The invention relates to a control element (1) for an injection system comprising a high pressure collector tank (12) from which a high pressure supply line (7) extends to a housing (6) that surrounds the control element (1). Said housing (6) comprises a pressureless runoff (8) to a reservoir (21) and a connecting bore (9) connecting to injection systems (34, 35). The overlapping of the metering ramps (17, 18) on the supply side that causes the high pressure supply line (7) to be closed is effected by controlling the actuating mechanisms (2, 3). This is supported by at least one energy accumulator (4) allocated to the control element (1).

Description

Technisches Gebiet:Technical area:

Hydraulisch angetriebene Einspritzpumpen über hydraulisch zu betreibende Injektoren führen ein das Förderende und den jeweiligen Förderbeginn bewirkenden Steuervorgang mittels eines bewegbaren Steuerelementes aus. Das Steuerelement wird innerhalb sehr kurzer Schaltzeiten, die unterhalb von 2 ms liegen können, angesteuert. Die Hübe, die das Steuerelement ausführt, liegen oberhalb von 0,3 mm.Hydraulically driven injection pumps via injectors to be hydraulically operated perform a control process which effects the delivery end and the respective start of delivery by means of a movable control element. The control is controlled within very short switching times, which may be less than 2 ms. The strokes that the control performs are above 0.3 mm.

Stand der Technik:State of the art:

Bei Injektoren, die mit einem mehreren Injektoren gemeinsamen Hochdrucksammelraum (Common Rail) in Verbindung stehen, oder bei hydraulisch angetriebenen Einspritzpumpen können sehr kurze Schalt- bzw. Ansteuerzeiten erforderlich sein, um Hubbewegungen eines Steuerelementes auszuführen. Die geforderten Schaltzeiten können unterhalb von 2 ms liegen; bei sehr kleinen hydraulisch beaufschlagten Einheiten, d.h. Einheiten sehr kleinen Durchflußquer-schnitts, kann eine direkte Magnetsteuerung verwendet werden.In injectors, which are in communication with a common high-pressure accumulator (common rail) in multiple injectors, or in hydraulically driven injection pumps very short switching or Ansteuerzeiten may be required to perform strokes of a control. The required switching times can be less than 2 ms; for very small hydraulically actuated units, ie units of very small flow cross-section, a direct magnetic control can be used.

Die direkte Magnetsteuerung lässt sich bei Einheiten mit kleinem Durchflußquerschnitt verwenden, wo beispielsweise ein 3-/2-Wege Steuerelement ausgeführt sein kann, wenn Hubbewegungen durch das Steuerelement auszuführen sind, die kleiner als 0,3 mm Hubweg betragen. Wenn längere Stellelementhübe erforderlich werden, stößt die direkte Magnetansteuerung des eines als Steuerschiebers ausgebildeten Steuerelementes an ihre Grenzen.The direct solenoid control can be used with small flow area units, where, for example, a 3/2-way control can be implemented when strokes are to be performed by the control, which are less than 0.3 mm stroke. If longer Stellelementhübe be required, the direct magnetic control of a designed as a control slide control reaches its limits.

Eine andere Variante liegt in einer Servoansteuerung des Steuerschiebers, die aber nur dann realisiert werden kann, wenn die zum Verschluß der Steuerkanten jeweils vom Steuerelement zurückzulegenden Hubwege die genannten Grenzen nicht überschreiten. Auch hier gilt die bereits erwähnte Einschränkung, daß die Servoansteuerung vorzugsweise nur bei kleinen Einheiten mit geringem Durchflußquerschnitt zum Einsatz kommt, bei denen demzufolge die Stellkräfte noch in mit Servomotoren beherrschbarer Größenordnung liegen. Beim Einsatz bei Großdieselmotoren, die Stelleinheiten mit größerem Durchflußquerschnitt benötigen, treten hingegen größere Durchflußmengen sowie daraus resultierend größere Stellkräfte auf, die mit Servomotoren allein oder mit einer ausschließlichen Magnetansteuerung des Steuerschiebers alleine nicht mehr beherrschbar sind.Another variant is in a servo control of the spool, but which can only be realized if the closing of the control edges in each case from the control travel not exceed the limits mentioned. Again, the above-mentioned restriction applies that the servo control is preferably used only in small units with a small flow area, in which consequently the restoring forces are still in controllable with servo motors order of magnitude. When used in large diesel engines that require actuators with a larger flow area, however, larger flow rates and resulting larger actuating forces occur, which are no longer controllable with servomotors alone or with an exclusive magnetic control of the spool alone.

DE 197 38 397 A1 offenbart eine Kraftstoffeinspritzanlage für eine Brennkraftmaschine, welche eine Zweistoffeinspritzdüse aufweist, in deren Druckraum abwechselnd Kraftstoff und eine Zusatzflüssigkeit förderbar sind. Dabei ist eine Ventilanordnung vorgesehen, durch die die hochdruckseitige Kraftstoffzufuhr zur Zweistoffeinspritzdüse und die Verbindung des Druckraums mit einer Niederdruckseite und mit einer Zuführleitung der Zusatzflüssigkeit steuerbar ist. Die Ventilanordnung weist ein Umschaltventil auf, welches sowohl zur Ansteuerung der Beaufschlagung des Druckraums mit Hoch- oder Niederdruck als auch zur Ansteuerung der Befüllung des Druckraums mit der Zusatzflüssigkeit ausgebildet ist.DE 197 38 397 A1 discloses a fuel injection system for an internal combustion engine, which has a two-fuel injector, in the pressure chamber alternately fuel and an additional liquid can be conveyed. In this case, a valve arrangement is provided, through which the high-pressure side fuel supply to the two-component injection nozzle and the connection of the pressure chamber with a low-pressure side and with a feed line of the additional liquid can be controlled. The valve arrangement has a switching valve, which is designed both for controlling the admission of the pressure chamber with high or low pressure and for controlling the filling of the pressure chamber with the additional liquid.

EP 0 879 979 A2 bezieht sich auf ein hydraulisches Ventil mit zwei Anschlüssen, welches derart schaltbar ist, dass jeweils nur ein Auslass gleichzeitig mit Flüssigkeit versorgt werden kann. Eine Spindel mit zwei Dichtungen ist in einem Gehäuse durch zwei Solenoide bewegbar und wird mittels zweier Federn in einer zentralen Position gehalten, in der die Dichtungen beide Auslässe verschließen. Wird die Spindel in eine Richtung bewegt, so gibt sie den Fluss zu einem Auslass frei und ermöglicht weiterhin einen Fluss über einen Bypasskanal auf eine gegenüberliegende Seite der Spindel, wodurch der Kraft, die durch den Solenoid ausgeübt wird, entgegengewirkt wird. Dadurch kann die Kraft, die auf einen Auslass ausgeübt wird, stufenweise kontrolliert werden.EP 0 879 979 A2 relates to a hydraulic valve with two connections, which can be switched such that in each case only one outlet can be supplied with liquid at the same time. A spindle with two seals is movable in a housing by two solenoids and is held by means of two springs in a central position in which the seals close both outlets. When the spindle is moved in one direction, it releases the flow to an outlet and further allows flow through a bypass channel to an opposite side of the spindle, thereby counteracting the force exerted by the solenoid. This allows the force exerted on an outlet to be controlled in stages.

Darstellung der Erfindung:Presentation of the invention:

Mit der erfindungsgemäßen Lösung ist nunmehr eine direkte elektronische Regelung einer Ventileinheit für größere Durchflußquerschnitte realisierbar, die unter anderem auch für Großdieselapplikationen geeignet ist. Durch die dort auftretenden hohen Drücke entstehen hohe Stellkräfte, die mit der vorgeschlagenen Kraftspeicher unterstützten Lösung beherrschbar werden. Die bei größeren Einheiten größeren Stellwege lassen sich mit der erfindungsgemäßen Lösung wesentlich schneller zurücklegen und die auftretenden Schließkräfte schneller bereitstellen; der Überdeckungsgrad der Steuerkanten zwischen Steuerelement und dieses umschließenden Gehäuse läßt sich so wählen, daß eine effektive Abdichtung von Hochdruckzuleitung gegenüber der drucklosen Ablaufleitung erzielbar ist.With the solution according to the invention is now a direct electronic control of a valve unit for larger flow areas feasible, which is also suitable for large diesel applications, among others. Due to the high pressures occurring there arise high actuating forces, which are manageable with the proposed energy storage solution. The larger travel units with larger units can be covered much faster with the solution according to the invention and provide the closing forces occurring faster; the degree of overlap of the control edges between the control element and this enclosing housing can be chosen so that a Effective sealing of high pressure supply line against the non-pressurized drain line is achieved.

Durch die Beaufschlagung des zulaufseitigen Stellelementendes mit einem die Schließbewegung des Steuerelementes unterstützenden Kraftspeicher ist die Systemsicherheit bei Ausfall der Versorgungsspannung sichergestellt. Der dem zulaufseitigen Ende zugeordnete Kraftspeicher - beispielsweise ausgeführt als eine Schraubenfeder - ist derart dimensioniert, daß im Falle des Spannungsausfalles an einem der Betätigungsorgane immer ein Schließen der Hochdruckzulaufleitung gewährleistet ist. Zur Begrenzung der zur Auf- bzw. Zusteuerung von Hochdruckzuleitung und drucklosem Ablauf sind in der das Steuerelement umschließenden Bohrung im Gehäuse Anschläge vorgesehen, die die Vorspannung der Kraftspeicher begrenzen.By acting on the inlet-side actuator end with a closing movement of the control supporting energy storage system security is ensured in case of failure of the supply voltage. The energy store associated with the inlet-side end-for example, designed as a helical spring-is dimensioned such that, in the event of a power failure, closing of the high-pressure feed line is always ensured on one of the actuators. In order to limit the opening or closing of the high-pressure supply line and the non-pressurized drain, stops are provided in the housing enclosing the control element and limit the prestressing of the energy accumulators.

Das erfindungsgemäße Steuerelement kann beispielsweise - ausgebildet als Steuerschieber - mit einer Einspritzdüse verbunden sein, um unter extrem hohen Druck stehenden Kraftstoff in eine Brennkammer einzuspritzen, oder der Versorgung einer hydraulisch betreibbaren Kolbenpumpe dienen. Mit der erfindungsgemäßen Ausbildung des Steuerelementes als Kraftspeicher unterstütztes Stellsystem lassen sich kürzeste Schaltzeiten bei dennoch verlängerten Hubwegen realisieren. Die kurzen Schaltzeiten am Steuerelement sind dadurch realisierbar, daß jeweils einer der dem Steuerelementende zugeordneten Kraftspeicher, die durch die Ansteuerung eines der Betätigungsorgane ausgeführten Steuerelementbewegung unterstützt und dadurch die Schaltzeit verkürzt. Je nach Dimensionierung der vorzugsweise als Schraubenfedern - sei es parallel geschaltet oder in Serienschaltung - läßt sich die Systemsicherheit bei Stromausfall dadurch realisieren, daß bei Stromausfall der das Verschließen der Hochdruckzulaufleitung unterstützende Kraftspeicher größer dimensioniert ist, um auf dem zulaufseitigen Ende des als Steuerschieber ausgebildeten Steuerelementes höhere Schließkräfte zu erzeugen.The control according to the invention can be connected, for example-designed as a control slide-with an injection nozzle to inject fuel under extremely high pressure in a combustion chamber, or serve to supply a hydraulically operated piston pump. With the inventive design of the control as a force storage assisted control system can be the shortest switching times at longer stroke lengths realized. The short switching times on the control can be realized in that each one of the control end associated with energy storage, which supports the control element movement performed by the control of one of the actuators and thereby shortens the switching time. Depending on the dimensions of preferably coil springs - be it connected in parallel or in series - the system security can be realized in case of power failure, that in case of power failure of the closure of the high pressure feed line supporting force storage is larger sized to higher on the inlet end of the control valve designed as a control To produce closing forces.

Zeichnung:Drawing:

Anhand der Zeichnung wird die Erfindung nachstehend näher erläutert:Reference to the drawing, the invention is explained in more detail below:

Es zeigt:

Fig. 1
den Aufbau einer 3-/2-Wege-Ventileinheit mit dem Steuerelement zugeordneten, elektrisch ansteuerbaren Betätigungsorganen,
Fig. 1a
eine mit dem Gehäuse des 3-/2-Wege-Ventils verbindbare Einspritzdüse und
Fig. 1b
eine hydraulisch angetriebene Hochdruckpumpe.
It shows:
Fig. 1
the construction of a 3- / 2-way valve unit associated with the control, electrically controllable actuators,
Fig. 1a
a connectable to the housing of the 3- / 2-way valve injector and
Fig. 1b
a hydraulically driven high pressure pump.

Ausführungsvarianten:Models:

In der Ausführungsvariante gemäß Fig. 1 ist ein 3-/2-Wege-Ventil dargestellt, mit einem Steuererlement, welches über zwei individuell ansteuerbare Betätigungsorgane bewegbar ist.In the embodiment of FIG. 1, a 3- / 2-way valve is shown, with a Steuererlement which is movable via two individually controllable actuators.

In einem Gehäuse 6 eines 3-/2-Wege-Ventils ist ein als Steuerschieber ausgebildetes Steuerelement 1 aufgenommen. An den jeweiligen Enden des Steuerelementes 1 sind Flächen vorgesehen, die Betätigungsorganen 2, 3 gegenüberliegend angeordnet sind. Die Betätigungsorgane 2, 3 sind vorzugsweise als elektrisch ansteuerbare Elektromagnete ausgebildet, die über eine beide Betätigungsorgane 2, 3 getrennt voneinander ansteuernde Steuereinheit 15 angesteuert werden können. Den vorzugsweise als Elektromagneten ausgebildeten Betätigungsorganen 2, 3 liegen im Vergleich zum Durchmesser des Steuerelementes 1 im größeren Durchmesser dimensionierte Flächen gegenüber.In a housing 6 of a 3- / 2-way valve designed as a control slide control 1 is added. At the respective ends of the control element 1 surfaces are provided, the actuators 2, 3 are arranged opposite one another. The actuators 2, 3 are preferably designed as electrically controllable electromagnets, which can be controlled via a control unit 15 which controls both actuators 2, 3 separately. The preferably designed as electromagnets actuators 2, 3 are compared to the diameter of the control element 1 in the larger diameter dimensioned surfaces.

Das als Steuerschieber ausgebildete Steuerelement 1 ist in einer Bohrung 31 des Gehäuses 6 aufgenommen. Die Bohrung 31 um das Steuerelement 1 ist in engsten Toleranzen ausgeführt, um die bei der Relativbewegung der Bauteile zueinander auftretenden Leckageverluste möglichst gering zu halten. Das Steuerelement 1 ist als bewegbares Bauteil vorzugsweise aus hochwertigem Material hergestellt, während das Gehäuse 6 des 3-/2-Wege-Ventils auch aus preisgünstigerem Werkstoff bestehen kann. Am Steuerelement 1 sind zwei mit ihren einander zugewandten Stirnflächen voneinander beanstandete zylindrische Schließkörper 32 vorgesehen. Die zylindrischen Schließkörper 32 begrenzen einerseits einen Hohlraum 28 innerhalb der Bohrung 31 des Gehäuses 6, andererseits dienen die zylindrischen Schließkörper 32 als ringförmige Anschlagflächen für die im zulaufseitigen und dem ablaufseitigen Ende des Steuerelementes 1 jeweils zugeordneten Kraftspeicher 4 bzw. 5. Die Kraftspeicher 4, 5 können vorzugsweise als Schraubenfedern ausgebildet werden. Zur Erhöhung der erzeugbaren Vorspannkraft am Steuerelement 1 können die Schraubenfedern als Federpakete, beispielsweise parallel geschaltet ineinander gesteckt ausgeführt sein oder auch in Reihenschaltung hintereinander liegend angeordnet werden. Anstelle von Schraubenfedern könnten auch andere Federelemente wie beispielsweise Federringe oder Tellerfedern in der Bohrung 31 des Gehäuses 6 als das Steuerelement beaufschlagende Kraftspeicher 4, 5 vorgesehen sein.Trained as a control slide control 1 is received in a bore 31 of the housing 6. The bore 31 around the control element 1 is executed in the narrowest tolerances in order to minimize the leakage losses which occur relative to one another during the relative movement of the components. The control element 1 is preferably made of a high-quality material as a movable component, while the housing 6 of the 3- / 2-way valve may also consist of less expensive material. On the control element 1, two cylindrical closing bodies 32 spaced apart from one another with their facing end faces are provided. The cylindrical closing body 32 limit on the one hand a cavity 28 within the bore 31 of the housing 6, on the other hand serve the cylindrical closing body 32 as annular abutment surfaces for the inlet side and the outlet end of the control element 1 respectively associated with energy storage 4 and 5. The energy storage 4, 5th can preferably be formed as coil springs. To increase the producible preload force on the control element 1, the coil springs can be designed as spring assemblies, for example connected in parallel, inserted into one another or also arranged one behind the other in series. Instead of coil springs and other spring elements such as spring rings or disc springs could be provided in the bore 31 of the housing 6 as the control acting force storage 4, 5.

In der Bohrung 31 sind ringförmige Anschlagflächen 13 bzw. 14 ausgebildet, die den Hubweg des Steuerelementes 1 begrenzen. Die Anschläge 13, 14 können in der Bohrung 31 beispielsweise als ringförmig sich erstreckende Hülsenelemente eingeschrumpft sein. Die Anschläge 13, 14 sind in der Bohrung 31 derart plaziert, daß durch das zulaufseitig vorgesehene zylindrische Schließelement 32 die Hochdruckzuleitung 7 durch die gehäuseseitige Steuerkante 17 und die schieberseitig am zylindrischen Schließkörper 32 vorgesehene Steuerkante 18 gerade freigegeben ist, während bei Anliegen des ablaufseitigen Schließzylinders 32 am Anschlag 13 - wie in Fig. 1 gezeigt - der drucklose Ablauf 8 zum Reservoir 21 gerade freigegeben ist, so daß überschüssiger im Hohlraum 28 noch vorhandener Kraftstoff bzw. Motoröl abfließen kann.In the bore 31 annular stop surfaces 13 and 14 are formed, which limit the stroke of the control element 1. The stops 13, 14 may be shrunk in the bore 31, for example, as annularly extending sleeve elements. The stops 13, 14 are placed in the bore 31 in such a way that the high-pressure feed line 7 is just released by the housing-side control edge 17 and the slider side on the cylindrical closing body 32 provided control edge 18 by the inlet side provided cylindrical closing element 32, while abutting the drain-side lock cylinder 32 on the stop 13 - as shown in Fig. 1 - the non-pressure flow 8 for Reservoir 21 is just released, so that excess in the cavity 28 still existing fuel or engine oil can flow.

Im Gehäuse 6 gemäß Fig. 1 ist eine Hochdruckzuleitung 7 ausgeführt, über welche das Gehäuse 6 mit einem Hochdrucksammelraum 12 in Verbindung steht. Der Hochdrucksammelraum 12 (Common Rail) wird über eine Hochdruckpumpe 23 beispielsweise mit Kraftstoff aus einem Reservoir 21 beaufschlagt; der aktuelle im Reservoir 21 herrschende Kraftstoffpegel ist mit Bezugszeichen 22 bezeichnet. Die vom Gehäuse 6 aus sich erstreckende drucklose Ablaufleitung 8 mündet unmittelbar in das Reservoir 21 und leitet überschüssigen Kraftstoff in das Reservoir 21 zurück.In the housing 6 according to FIG. 1, a high-pressure feed line 7 is carried out, via which the housing 6 communicates with a high-pressure accumulation chamber 12. The high-pressure accumulation chamber 12 (common rail) is acted upon by a high-pressure pump 23, for example with fuel from a reservoir 21; the current fuel level prevailing in the reservoir 21 is designated by reference numeral 22. The pressureless drain line 8 extending from the housing 6 opens directly into the reservoir 21 and returns excess fuel into the reservoir 21.

Bei Einspritzsystemen für Brennkraftmaschinen wird der Hochdrucksammelraum 12 mit unter extrem hohem Druck stehenden Kraftstoff beaufschlagt. Bei einer Hochdruckpumpe, die über das 3-/2-Wege-Ventil ebenfalls beaufschlagt werden kann, ist der Hochdrucksammelraum 12 anstelle von Kraftstoff beispielsweise mit Mineralöl, z.B. Motoröl angefüllt. Die beiden Betätigungsorgane 2, 3 können untereinander über Zuganker 26 bzw. 27 miteinander verbunden sein, die ihrerseits mit Sicherungsmuttern 29 versehen werden können, um die beiden Betätigungsorgane 2, 3 gegeneinander zu verspannen.In injection systems for internal combustion engines, the high-pressure accumulation chamber 12 is subjected to fuel under extremely high pressure. In a high-pressure pump, which can also be acted upon via the 3/2-way valve, the high-pressure accumulation chamber 12 instead of fuel, for example with mineral oil, e.g. Engine oil filled. The two actuators 2, 3 can be interconnected via tie rods 26 and 27, which in turn can be provided with lock nuts 29 to clamp the two actuators 2, 3 against each other.

Die Funktionsweise des erfindungsgemäß vorgeschlagenen 3-/2-Wege-Ventils erfolgt ausgehend von der Ansteuerung der Betätigungsorgane 2, 3, vorzugsweise Elektromagneten, über die Steuereinheit 15 via Ansteuerleitungen 30. In der in Fig. 1 dargestellten Position des Steuerelementes 1 ist beispielsweise das zulaufseitige Betätigungsorgan 2 angesteuert und stößt die diesem gegenüberliegende Fläche des Steuerelementes 1 ab, während das ablaufseitig positionierte Betätigungsorgan 3 die diesem gegenüberliegende Fläche am Steuerelement 1 anzieht. Unterstützt durch die Entspannung des zulaufseitig angeordneten Kraftspeichers 4 wird die Hochdruckzuleitung 7 durch Überdeckung der Steuerkanten 17, der gehäuseseitigen Steuerkante 17 und der schieberseitigen Steuerkante 18, verschlossen. Im in Fig. 1 gezeigten Stellzustand des Steuerelementes 1 ist eine Kraftstoff- oder Motorölmenge in die Versorgungsleitung 9 gelangt, während nach Öffnen des Hohlraumes 28 durch Aufsteuern des drucklosen Ablaufes 8 überschüssiger Kraftstoff oder gegebenenfalls überschüssiges Motoröl je nach Applikation zurück in das Reservoir 21 strömen kann.The operation of the inventively proposed 3- / 2-way valve is based on the control of the actuators 2, 3, preferably electromagnets, via the control unit 15 via control lines 30. In the position of the control 1 shown in Fig. 1, for example, the inlet side Actuator 2 driven and repels the this opposite surface of the control element 1, while the drain side positioned actuator 3 which this opposite surface on the control element 1 attracts. Supported by the relaxation of the inlet side arranged force accumulator 4, the high-pressure feed line 7 by covering the control edges 17, the housing-side control edge 17 and the slide-side control edge 18, closed. In the control state of the control element 1 shown in FIG. 1, a quantity of fuel or engine oil has entered the supply line 9, while after opening the cavity 28 excess fuel or possibly excess engine oil can flow back into the reservoir 21, depending on the application, by controlling the pressure-free outlet 8 ,

Bei einer entgegengesetzt verlaufenden Bewegung des Steuerelementes 1 erfolgt eine Ansteuerung des ablaufseitig vorgesehenen Betätigungsorganes 3 derart, daß die diesem gegenüberliegende Fläche des Steuerelementes 1 abgestoßen wird. Das zulaufseitig angeordnete Betätigungsorgan 2 kann durch die Steuereinheit 15 so angesteuert werden, daß es die diesem gegenüberliegende ablaufseitige Fläche des Steuerelementes 1 anzieht. Dadurch bewegt sich das Steuerelement 1 auf die Hochdruckleitung 7 zu und verschließt durch die sich überdeckenden gehäuseseitige Steuerkante 20 und die am zylindrischen Schließkörper 32 vorgesehene Steuerkante die Ablaufkante 8. Dabei wird der zulaufseitig vorgesehene Kraftspeicher 4 zusammengedrückt, bis der zulaufseitige Schließzylinder 32 am Anschlag 14 anlegt. Die Schließbewegung des Ablaufes 8 wird durch den ablaufseitigen Kraftspeicher 5 unterstützt, der die Schließbewegung durch seine Entspannung untersützt.In an oppositely extending movement of the control element 1 is a control of the drain side provided actuator 3 such that the opposite surface of the control element 1 is repelled. The inlet side arranged actuator 2 can be controlled by the control unit 15 so that it attracts the opposite drain-side surface of the control element 1. As a result, the control element 1 moves toward the high-pressure line 7 and closes the flow edge 8 by the overlapping housing-side control edge 20 and the control edge provided on the cylindrical closing body 32. The energy store 4 provided on the upstream side is compressed until the inlet-side lock cylinder 32 bears against the stop 14 , The closing movement of the drain 8 is supported by the drain-side power accumulator 5, which supports the closing movement by its relaxation.

Während der von der Schließbewegung der Hochdruckleitung 7 bis zur Öffnung des ablaufseitigen Ablaufes 8 vergehenden Zeitspanne ist die Versorgungsleitung 9 kurzseitig allein durch das im Hohlraum 28 eingeschlossene Fluidvolumen beaufschlagt und leitet dieses über eine Versorgungsleitung 9 an die mit dem Gehäuse 6 des 3-/2-Wege-Ventils in Verbindung stehenden Einspritzeinrichtungen weiter.During the time passing from the closing movement of the high-pressure line 7 to the opening of the drain-side outlet 8, the supply line 9 is acted upon on the short side solely by the volume of fluid trapped in the cavity 28 and conducts it via a supply line 9 to the housing 3 of FIGS. Way valve related injectors on.

Coaxial zur Achse 25 des Steuerelementes 1 sind die Schließzylinder 32 aufgenommen. An den Stirnflächen der Schließzylinder 32 lassen sich einfach und preisgünstig zu dimensionierende Kraftstoff- oder Motorölmengen begrenzende Steuerkanten fertigen, je nach zu beaufschlagender Einspritzeinrichtung. Neben einer genauen Dosierung des einzuspritzenden Volumens ist durch den Grad der Überdeckung der Steuerkantenpaare 17, 18 bzw. 19, 20 für eine Leckageverluste auf ein Minimum begrenzende Abdichtung gesorgt. Die im Hohlraum 28 jeweils eingeschlossene Menge von Kraftstoff bzw. Motoröl läßt sich durch die Vorgabe des Durchmessers des die Schließzylinder 32 miteinander verbindenden Abschnittes des Steuerelementes 1 genau vorgeben.Coaxial with the axis 25 of the control 1, the lock cylinder 32 are added. At the end faces of the lock cylinder 32 can be easily and inexpensively to be dimensioned fuel or engine oil quantities produce limiting control edges, depending on the injector to be acted upon. In addition to a precise metering of the volume to be injected, the degree of overlap of the pairs of control edges 17, 18 or 19, 20 ensures leakage leakage to a minimum. The enclosed in the cavity 28 each amount of fuel or engine oil can be specified by specifying the diameter of the lock cylinder 32 interconnecting portion of the control 1 exactly.

Fig. 1a zeigt in schematischer Anordnung als an die Verbindungsbohrung angeschlossene Einspritzeinrichtung eine Einspritzdüse 10. Deren Öffnung 35 - durch eine Düsennadelverschluß - freigebbar - ragt in die Brennkammer einer Brennkraftmaschine hinein. Alternativ dazu kann als Einspritzeinrichtung auch eine in Fig. 1b schematisch dargestellte Hochdruckpumpe 11 mit Motoröl beispielsweise beaufschlagt werden, die eine Leitung 34 mit erhöhtem Druck beaufschlagt. Der Druckraum kann mit einem Sperrventil 33 abgedichtet sein und ab Überschreiten eines bestimmten voreinstellbaren Überdruckes öffnen. Bei dieser Anwendung des erfindungsgemäßen 3-/2-Wege-Ventiles zur Beaufschlagung einer Hochdruckpumpe 11 wird der Hochdrucksammelraum 12 statt mit Kraftstoff mit unter hohem Druck stehenden Motoröl - was hier lediglich beispielsweise genannt werden soll - beaufschlagt.Fig. 1a shows in a schematic arrangement as an injection device connected to the connecting hole an injection nozzle 10. The opening 35 - by a nozzle needle closure - releasable - protrudes into the combustion chamber of an internal combustion engine. Alternatively, as an injection device, a high-pressure pump 11, shown schematically in FIG. 1b, may be charged with engine oil, for example, which acts on a line 34 with increased pressure. The pressure chamber can be sealed with a check valve 33 and open when exceeding a certain presettable overpressure. In this application, the inventive 3- / 2-way valve for pressurizing a high-pressure pump 11, the high-pressure accumulation chamber 12 instead of fuel with high-pressure engine oil - which is only to be mentioned here for example - acted upon.

Claims (8)

  1. Injection system, comprising a control element (1) and a high-pressure collecting tank (12) from which a high-pressure supply line (7) to a housing (6) surrounding the control element (1) extends, the housing (6) having a bore (31) receiving the control element (1), the housing (6) comprising a pressureless outflow (8) to a reservoir (21) and a connecting bore (9) to injection devices (34, 35), characterized in that the overlap of inflow-side control edges (17, 18) which causes a closing of the high-pressure supply line (7) and the overlap of outflow-side control edges (19, 20) which causes a closing of the pressureless outflow (8) take place in each case as a result of the activation of actuating members (2, 3) and as a result of the expansion of one of two force accumulators (4, 5) on the control element (1), the maximum opening of the high-pressure supply line (7) and at the pressureless outflow (8) being limited by stops (13, 14) provided in the bore (31) for the control element (1), a prestress of the force accumulator (4, 5) being limited by the stops (13, 14), and in each case an actuating member (2, 3) co-operating with a force accumulator (4, 5) in order to shorten the switching time of the control element (1).
  2. Injection system according to Claim 1, characterized in that the control element (1) receives closing bodies (32), on which are formed control edges (18, 19) located on the control-element side.
  3. Injection system according to Claim 2, characterized in that the closing bodies (32) co-operate with control edges (17, 20) formed on the housing (6).
  4. Injection system according to Claim 2, characterized in that the connecting bore (9) to the injection devices (34, 35) branches off from a cavity (28) lying between the control edges (18, 19) of the control slide (1).
  5. Injection system according to Claim 1, characterized in that the actuating members (2, 3) in each case lying opposite the ends of the control element (1) are activatable in each case independently of one another by means of a control unit (15).
  6. Injection system according to Claim 5, characterized in that the actuating members (2, 3) are designed as electromagnets.
  7. Injection system according to Claim 1, characterized in that the injection system has an outflow-side force accumulator (5), the closing of the high-pressure inflow (7) and the opening of the pressureless outflow (8) by means of the control slide (1) taking place, counter to the action of the outflow-side force accumulator (5), after the activation of the actuating members (2, 3).
  8. Injection system according to Claim 1, characterized in that the injection system has an inflow-side force accumulator (4), the closing of the outflow (8) and the opening of the high-pressure inflow (7) by means of the control element (1) taking place, counter to the action of the inflow-side force accumulator (4), after the activation of the actuating members (2, 3).
EP00988559A 1999-11-10 2000-11-08 Control element for controlling injection systems Expired - Lifetime EP1187985B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19954057A DE19954057A1 (en) 1999-11-10 1999-11-10 Control element for the control of injection systems
DE19954057 1999-11-10
PCT/DE2000/003900 WO2001034966A2 (en) 1999-11-10 2000-11-08 Control element for controlling injection systems

Publications (2)

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EP1187985A2 EP1187985A2 (en) 2002-03-20
EP1187985B1 true EP1187985B1 (en) 2006-08-09

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EP00988559A Expired - Lifetime EP1187985B1 (en) 1999-11-10 2000-11-08 Control element for controlling injection systems

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US (1) US6446607B1 (en)
EP (1) EP1187985B1 (en)
JP (1) JP2003514188A (en)
KR (1) KR100665934B1 (en)
DE (2) DE19954057A1 (en)
RU (1) RU2264557C2 (en)
WO (1) WO2001034966A2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10244551A1 (en) * 2002-09-25 2004-04-08 Robert Bosch Gmbh Fuel injection device for an internal combustion engine
RU2635743C1 (en) * 2017-01-16 2017-11-15 Общество с ограниченной ответственностью Управляющая компания "Алтайский завод прецизионных изделий" High-pressure fuel pump capacity control valve
KR102592735B1 (en) 2021-03-02 2023-10-20 한국수력원자력 주식회사 Fire extinguishing system using sprinkler

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4911484Y1 (en) * 1970-06-30 1974-03-19
DE3314633A1 (en) * 1982-12-28 1984-06-28 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION SYSTEM
JPS59156166U (en) * 1983-04-07 1984-10-19 株式会社小松製作所 Rotary valve of fuel supply system
DE3910793C2 (en) * 1989-04-04 1996-05-23 Kloeckner Humboldt Deutz Ag Fuel injector
DE4129828C1 (en) * 1991-09-07 1993-04-29 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE4236882C1 (en) * 1992-10-31 1994-04-21 Daimler Benz Ag IC engine fuel injection system with high pump pressure - uses electromagnetically operated three=way valve in fuel path to each fuel injection jet.
GB9710529D0 (en) * 1997-05-23 1997-07-16 Seddon Donald Hydraulic valves and systems
DE19738397A1 (en) * 1997-09-03 1999-03-18 Bosch Gmbh Robert Fuel injection system for an internal combustion engine
JPH11218253A (en) * 1998-02-02 1999-08-10 Kenji Masuda Proportional solenoid type direction throttle valve

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EP1187985A2 (en) 2002-03-20
WO2001034966A3 (en) 2002-01-10
WO2001034966A2 (en) 2001-05-17
KR20010113645A (en) 2001-12-28
US6446607B1 (en) 2002-09-10
KR100665934B1 (en) 2007-01-09
DE19954057A1 (en) 2001-06-07
RU2264557C2 (en) 2005-11-20
JP2003514188A (en) 2003-04-15
DE50013306D1 (en) 2006-09-21

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