EP1187985A2 - Control element for controlling injection systems - Google Patents

Control element for controlling injection systems

Info

Publication number
EP1187985A2
EP1187985A2 EP00988559A EP00988559A EP1187985A2 EP 1187985 A2 EP1187985 A2 EP 1187985A2 EP 00988559 A EP00988559 A EP 00988559A EP 00988559 A EP00988559 A EP 00988559A EP 1187985 A2 EP1187985 A2 EP 1187985A2
Authority
EP
European Patent Office
Prior art keywords
control element
control
element according
housing
actuators
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP00988559A
Other languages
German (de)
French (fr)
Other versions
EP1187985B1 (en
Inventor
Jaroslaw Hlousek
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1187985A2 publication Critical patent/EP1187985A2/en
Application granted granted Critical
Publication of EP1187985B1 publication Critical patent/EP1187985B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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 hydraulically operated injectors carry out a control process which effects the end of delivery and the beginning of delivery by means of a movable control element.
  • the control element is activated within very short switching times, which can be less than 2 ms.
  • the strokes that the control element executes are above 0.3 mm.
  • very short switching or activation times may be required in order to carry out stroke movements of a control element.
  • the required switching times can be less than 2 ms; direct magnet control can be used for very small hydraulically actuated units, ie units with very small cross-sectional areas.
  • the direct solenoid control can be used in units with a small flow cross-section, where, for example, a 3/2-way control element can be implemented if the control element is to perform stroke movements that are less than 0.3 mm stroke. If longer actuating element strokes are required, the direct magnetic actuation of a control element designed as a control slide reaches its limits.
  • Another variant is a servo control of the control slide, which can, however, only be implemented if the stroke distances to be covered by the control element to close the control edges do not exceed the limits mentioned.
  • the servo control is preferably only used in small units with a small flow cross-section, in which consequently the actuating forces are still of a magnitude that can be controlled with servomotors.
  • the force accumulator assigned to the inlet end - for example designed as a helical spring - is dimensioned such that in the event of a power failure at one of the actuators, the high-pressure inlet line is always closed.
  • stops are provided in the bore in the housing surrounding the control element, which limit the preload of the energy accumulators.
  • the control element according to the invention can be connected, for example, in the form of a control slide, to an injection nozzle in order to inject fuel under extremely high pressure into a combustion chamber, or to supply a hydraulically operated piston pump.
  • the shortest switching times can be achieved with an extended stroke length.
  • the short switching times on the control element can be realized in that in each case one of the energy stores assigned to the control element end supports the control element movement carried out by actuating one of the actuating members and thereby shortens the switching time.
  • the energy accumulator supporting the closing of the high-pressure supply line is dimensioned to be larger on the inlet-side end of the control element designed as a control slide Generate clamping forces.
  • FIG. 1 shows the structure of a 3/2-way valve unit with the control element associated with electrically controllable actuators
  • Fig. La a connectable to the housing of the 3/2-way valve
  • Fig. Lb a hydraulically driven high pressure pump.
  • a 3/2-way valve is shown, with a control element which can be moved via two individually controllable actuators.
  • a control element 1 designed as a control slide is accommodated in a housing 6 of a 3/2-way valve. Surfaces are provided at the respective ends of the control element 1, the actuating members 2, 3 being arranged opposite one another.
  • the actuating members 2, 3 are preferably designed as electrically controllable electromagnets, which can be actuated via a control unit 15 which actuates the two actuating members 2, 3 separately.
  • the actuators 2, 3, which are preferably embodied as electromagnets, are located in comparison to the diameter of the control element 1 with surfaces of larger diameter.
  • the control element 1 designed as a control slide is received in a bore 31 of the housing 6.
  • the bore 31 around the control element 1 is designed with the narrowest tolerances in order to keep the leakage losses that occur when the components move relative to one another as low as possible.
  • the control element 1 as a movable component is preferably made of high-quality material, while the housing 6 of the 3/2-way valve can also consist of less expensive material.
  • Provided on the control element 1 are two cylindrical closing bodies 32 with their mutually facing end faces.
  • the cylindrical closing bodies 32 on the one hand delimit a cavity 28 within the bore 31 of the housing 6, on the other hand the cylindrical closing bodies 32 serve as annular stop surfaces for the energy accumulators 4 and 5 respectively assigned in the inlet-side and outlet-side end of the control element 1.
  • the energy accumulators 4, 5 can preferably be designed as coil springs.
  • the coil springs can be designed as spring assemblies, for example connected in parallel, inserted one inside the other, or can also be arranged in series in a row.
  • other spring elements such as for example spring washers or disc springs, could also be provided in the bore 31 of the housing 6 as the energy stores 4, 5 acting on the control element.
  • annular stop surfaces 13 and 14 are formed, which limit the stroke of the control element 1.
  • the stops 13, 14 can be shrunk in the bore 31, for example as an 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 through the control edge 17 on the housing side and the control edge 18 provided on the slide side on the cylindrical closing body 32 are just released by the cylindrical closing element 32 on the inlet side, while the closing cylinder 32 on the outlet side is in contact at the stop 13 - as shown in Fig. 1 - the unpressurized outlet 8 for Reservoir 21 is just released so that excess fuel or engine oil still present in the cavity 28 can flow off.
  • a high-pressure feed line 7 is implemented in the housing 6 according to FIG. 1, via which the housing 6 is connected to a high-pressure plenum 12.
  • the high-pressure collecting space 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 number 22.
  • the pressure-free drain line 8, which extends from the housing 6, opens directly into the reservoir 21 and returns excess fuel to the reservoir 21.
  • the high-pressure plenum 12 is subjected to fuel under extremely high pressure.
  • the high-pressure plenum 12 is replaced, for example, with mineral oil, e.g. Engine oil filled.
  • the two actuators 2, 3 can be connected to each other via tie rods 26 and 27, which in turn can be provided with lock nuts 29 in order to brace the two actuators 2, 3 against each other.
  • the operation of the 3/2-way valve proposed according to the invention takes place on the basis of the actuation of the actuators 2, 3, preferably electromagnets, via the control unit 15 via actuation lines 30.
  • the position of the control element 1 shown in FIG. 1 is, for example, the inlet side Actuating element 2 is controlled and repels the surface of control element 1 opposite this, while the operating element 3 positioned on the outlet side attracts the opposite surface of control element 1.
  • the high-pressure supply line 7 is covered by overlapping 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 reached the supply line 9, while after opening the cavity 28 excess fuel or possibly excess engine oil can flow back into the reservoir 21 by opening the pressureless drain 8, depending on the application ,
  • the actuating element 3 provided on the outlet side is actuated such that the surface of the control element 1 opposite it is repelled.
  • the actuator 2 arranged on the inlet side can be controlled by the control unit 15 such that it attracts the outlet-side surface of the control element 1 opposite this.
  • the control element 1 moves towards the high-pressure line 7 and closes the drainage edge 8 by the overlapping control edge 20 on the housing and the control edge provided on the cylindrical closing body 32 ,
  • the closing movement of the outlet 8 is supported by the outlet-side energy store 5, which supports the closing movement by relaxing it.
  • the supply line 9 is acted upon on the short side only by the fluid volume enclosed in the cavity 28 and passes this via a supply line 9 to the housing 6 of the 3- / 2- Directional valve-related injection systems.
  • the locking cylinders 32 are accommodated coaxially to the axis 25 of the control element 1.
  • fuel or motor oil quantities can be dimensioned easily and inexpensively Manufacture limiting control edges, depending on the injection system to be acted on.
  • the degree of overlap of the control edge pairs 17, 18 and 19, 20 ensures leakage losses to a sealing which limits it to a minimum.
  • the quantity of fuel or motor oil enclosed in the cavity 28 can be precisely specified by specifying the diameter of the section of the control element 1 which connects the locking cylinders 32 to one another.
  • FIG. 1 a shows an injection nozzle 10 in a schematic arrangement as an injection system connected to the connecting bore. Its opening 35
  • Fig. Lb schematically shown high pressure pump 11 are 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 a certain presettable overpressure is exceeded.
  • High-pressure pump 11 the high-pressure plenum 12 is acted upon by high-pressure engine oil instead of fuel, which should only be mentioned here for example.

Landscapes

  • 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

Steuerelement für die Steuerung von Einspritzsystemen Control element for the control of injection systems
Technisches Gebiet:Technical field:
Hydraulisch angetriebene Einspritzpumpen über hydraulisch zu betreibende Injektoren fuhren 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 ausfuhrt, liegen oberhalb von 0,3 mm.Hydraulically driven injection pumps via hydraulically operated injectors carry out a control process which effects the end of delivery and the beginning of delivery by means of a movable control element. The control element is activated within very short switching times, which can be less than 2 ms. The strokes that the control element executes 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 Diirchflußquer-schnitts, kann eine direkte Magnetsteuerung verwendet werden. 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.In the case of injectors which are connected to a high-pressure collecting space (common rail) which is common to a plurality of injectors, or in the case of hydraulically driven injection pumps, very short switching or activation times may be required in order to carry out stroke movements of a control element. The required switching times can be less than 2 ms; direct magnet control can be used for very small hydraulically actuated units, ie units with very small cross-sectional areas. The direct solenoid control can be used in units with a small flow cross-section, where, for example, a 3/2-way control element can be implemented if the control element is to perform stroke movements that are less than 0.3 mm stroke. If longer actuating element strokes are required, the direct magnetic actuation of a control element designed as a control slide 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. Bein 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 a servo control of the control slide, which can, however, only be implemented if the stroke distances to be covered by the control element to close the control edges do not exceed the limits mentioned. The restriction mentioned above also applies here that the servo control is preferably only used in small units with a small flow cross-section, in which consequently the actuating forces are still of a magnitude that can be controlled with servomotors. When used in large diesel engines that require actuators with a larger flow cross-section, however, there are larger flow rates and, as a result, larger actuating forces that can no longer be controlled with servomotors alone or with an exclusive solenoid control of the control spool alone.
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, direct electronic control of a valve unit for larger flow cross-sections can now be realized, which is also suitable for large diesel applications, among other things. The high pressures that occur there result in high actuating forces that can be managed with the proposed energy storage solution. The larger travel distances for larger units can be covered much faster with the solution according to the invention and the closing forces that occur can be made available more quickly; the degree of coverage 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 unpressurized drain line can be 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 end of the control element with an energy store that supports the closing movement of the control element, system security is ensured in the event of a supply voltage failure. The force accumulator assigned to the inlet end - for example designed as a helical spring - is dimensioned such that in the event of a power failure at one of the actuators, the high-pressure inlet line is always closed. To limit the opening and closing of the high pressure supply line and the unpressurized outlet, stops are provided in the bore in the housing surrounding the control element, which limit the preload 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. Zeichnung:The control element according to the invention can be connected, for example, in the form of a control slide, to an injection nozzle in order to inject fuel under extremely high pressure into a combustion chamber, or to supply a hydraulically operated piston pump. With the inventive design of the control element as an energy storage-assisted actuating system, the shortest switching times can be achieved with an extended stroke length. The short switching times on the control element can be realized in that in each case one of the energy stores assigned to the control element end supports the control element movement carried out by actuating one of the actuating members and thereby shortens the switching time. Depending on the dimensioning of the preferably as coil springs - be it connected in parallel or in series connection - the system security in the event of a power failure can be realized in that in the event of a power failure, the energy accumulator supporting the closing of the high-pressure supply line is dimensioned to be larger on the inlet-side end of the control element designed as a control slide Generate clamping forces. Drawing:
Anhand der Zeichnung wird die Erfindung nachstehend näher erläutert:The invention is explained in more detail below with the aid of the drawing:
Es zeigt:It shows:
Fig. 1 den Aufbau einer 3-/2- Wege- Ventileinheit mit dem Steuerelement zugeordneten, elektrisch ansteuerbaren Betätigungsorganen,1 shows the structure of a 3/2-way valve unit with the control element associated with electrically controllable actuators,
Fig. la eine mit dem Gehäuse des 3-/2-Wege-Ventils verbindbareFig. La a connectable to the housing of the 3/2-way valve
Einspritzdüse undInjector and
Fig. lb eine hydraulisch angetriebene Hochdruckpumpe.Fig. Lb a hydraulically driven high pressure pump.
Ausfuhrungsvarianten:design variants:
In der Ausfuhrungsvariante gemäß Fig. 1 ist ein 3-/2- Wege- Ventil dargestellt, mit einem Steuererlement, welches über zwei individuell ansteuerbare Betätigungsorgane bewegbar ist.In the embodiment variant according to FIG. 1, a 3/2-way valve is shown, with a control element which can be moved 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. 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.A control element 1 designed as a control slide is accommodated in a housing 6 of a 3/2-way valve. Surfaces are provided at the respective ends of the control element 1, the actuating members 2, 3 being arranged opposite one another. The actuating members 2, 3 are preferably designed as electrically controllable electromagnets, which can be actuated via a control unit 15 which actuates the two actuating members 2, 3 separately. The actuators 2, 3, which are preferably embodied as electromagnets, are located in comparison to the diameter of the control element 1 with surfaces of larger diameter. The control element 1 designed as a control slide is received in a bore 31 of the housing 6. The bore 31 around the control element 1 is designed with the narrowest tolerances in order to keep the leakage losses that occur when the components move relative to one another as low as possible. The control element 1 as a movable component is preferably made of high-quality material, while the housing 6 of the 3/2-way valve can also consist of less expensive material. Provided on the control element 1 are two cylindrical closing bodies 32 with their mutually facing end faces. The cylindrical closing bodies 32 on the one hand delimit a cavity 28 within the bore 31 of the housing 6, on the other hand the cylindrical closing bodies 32 serve as annular stop surfaces for the energy accumulators 4 and 5 respectively assigned in the inlet-side and outlet-side end of the control element 1. The energy accumulators 4, 5 can preferably be designed as coil springs. To increase the preload force that can be generated on the control element 1, the coil springs can be designed as spring assemblies, for example connected in parallel, inserted one inside the other, or can also be arranged in series in a row. Instead of helical springs, other spring elements, such as for example spring washers or disc springs, could also be provided in the bore 31 of the housing 6 as the energy stores 4, 5 acting on the control element.
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 can be shrunk in the bore 31, for example as an 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 through the control edge 17 on the housing side and the control edge 18 provided on the slide side on the cylindrical closing body 32 are just released by the cylindrical closing element 32 on the inlet side, while the closing cylinder 32 on the outlet side is in contact at the stop 13 - as shown in Fig. 1 - the unpressurized outlet 8 for Reservoir 21 is just released so that excess fuel or engine oil still present in the cavity 28 can flow off.
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.A high-pressure feed line 7 is implemented in the housing 6 according to FIG. 1, via which the housing 6 is connected to a high-pressure plenum 12. The high-pressure collecting space 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 number 22. The pressure-free drain line 8, which extends from the housing 6, opens directly into the reservoir 21 and returns excess fuel to 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 plenum 12 is subjected to fuel under extremely high pressure. In the case of a high-pressure pump, which can also be acted on via the 3/2-way valve, the high-pressure plenum 12 is replaced, for example, with mineral oil, e.g. Engine oil filled. The two actuators 2, 3 can be connected to each other via tie rods 26 and 27, which in turn can be provided with lock nuts 29 in order to brace 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 3/2-way valve proposed according to the invention takes place on the basis of the actuation of the actuators 2, 3, preferably electromagnets, via the control unit 15 via actuation lines 30. The position of the control element 1 shown in FIG. 1 is, for example, the inlet side Actuating element 2 is controlled and repels the surface of control element 1 opposite this, while the operating element 3 positioned on the outlet side attracts the opposite surface of control element 1. Supported by the relaxation of the energy accumulator 4 arranged on the inlet side, the high-pressure supply line 7 is covered by overlapping the control edges 17, the housing-side control edge 17 and the slide-side control edge 18, closed. In the actuating state of the control element 1 shown in FIG. 1, a quantity of fuel or engine oil has reached the supply line 9, while after opening the cavity 28 excess fuel or possibly excess engine oil can flow back into the reservoir 21 by opening the pressureless drain 8, depending on the application ,
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 ablaufseitig vorgesehene Kraftspeicher 4 zusammengedrückt, bis der ablaufseitige 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.When the control element 1 moves in the opposite direction, the actuating element 3 provided on the outlet side is actuated such that the surface of the control element 1 opposite it is repelled. The actuator 2 arranged on the inlet side can be controlled by the control unit 15 such that it attracts the outlet-side surface of the control element 1 opposite this. As a result, the control element 1 moves towards the high-pressure line 7 and closes the drainage edge 8 by the overlapping control edge 20 on the housing and the control edge provided on the cylindrical closing body 32 , The closing movement of the outlet 8 is supported by the outlet-side energy store 5, which supports the closing movement by relaxing it.
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 stehende Einspritzsysteme weiter.During the period from the closing movement of the high-pressure line 7 to the opening of the outlet-side outlet 8, the supply line 9 is acted upon on the short side only by the fluid volume enclosed in the cavity 28 and passes this via a supply line 9 to the housing 6 of the 3- / 2- Directional valve-related injection systems.
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 beaufschlagendem Einspritzsystem. 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.The locking cylinders 32 are accommodated coaxially to the axis 25 of the control element 1. On the end faces of the locking cylinder 32, fuel or motor oil quantities can be dimensioned easily and inexpensively Manufacture limiting control edges, depending on the injection system to be acted on. In addition to a precise metering of the volume to be injected, the degree of overlap of the control edge pairs 17, 18 and 19, 20 ensures leakage losses to a sealing which limits it to a minimum. The quantity of fuel or motor oil enclosed in the cavity 28 can be precisely specified by specifying the diameter of the section of the control element 1 which connects the locking cylinders 32 to one another.
Fig. la zeigt in schematischer Anordnung als an die Verbindungsbohrung angeschlossenes Einspritzsystem eine Einspritzdüse 10. Deren Öffnung 35FIG. 1 a shows an injection nozzle 10 in a schematic arrangement as an injection system connected to the connecting bore. Its opening 35
- durch eine Düsennadelverschluß - freigebbar - ragt in die Brennkammer einer- through a nozzle needle closure - releasable - protrudes into the combustion chamber
Brennkraftmaschine hinein. Alternativ dazu kann als Einspritzsystem auch eine inInternal combustion engine. Alternatively, an in
Fig. lb 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 erfϊndungs gemäßen 3-/2 -Wege- Ventiles zur Beaufschlagung einerFig. Lb schematically shown high pressure pump 11 are 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 a certain presettable overpressure is exceeded. In this application of the 3- / 2-way valve according to the invention for acting on a
Hochdruckpumpe 11 wird der Hochdrucksammelraum 12 statt mit Kraftstoff mit unter hohem Druck stehenden Motoröl - was hier lediglich beispielsweise genannt werden soll - beaufschlagt. High-pressure pump 11, the high-pressure plenum 12 is acted upon by high-pressure engine oil instead of fuel, which should only be mentioned here for example.

Claims

Patentansprüche claims
1. Steuerelement für ein Einspritzsystem, welches einen Hochdrucksammelbehälter (12) umfaßt, von dem aus sich eine Hochdruckzuleitung (7) zu einem das Steuerelement (1) umschließenden Gehäuse (6) erstreckt und das Gehäuse (6) einen drucklosen Ablauf (8) zu einem Reservoir (21) und eine Verbindungsbohrung (9) zu Einspritzsystemen (34, 35) umfaßt, dadurch gekennzeichnet, daß die ein Verschließen der1. Control element for an injection system, which comprises a high-pressure collecting container (12), from which a high-pressure feed line (7) extends to a housing (6) enclosing the control element (1) and the housing (6) to a non-pressurized outlet (8) a reservoir (21) and a connecting bore (9) to injection systems (34, 35), characterized in that the closing of the
Hochdruckleitung (7) bewirkende Überdeckung zulaufseitiger Steuerkanten (17, 18) durch Ansteuerung von Betätigungsorganen (2, 3) und durch die Entspannung eines Kraftspeichers (14) am Steuerelement (1) erfolgt.High-pressure line (7) causing overlap of control edges (17, 18) on the inlet side by activating actuators (2, 3) and by relieving the pressure of an energy accumulator (14) on the control element (1).
2. Steuerelement gemäß Anspruch 1, dadurch gekennzeichnet, daß das Steuerelement (1) Schließkörper (32) aufnimmt, an denen steuerelementseitige Steuerkanten (18, 19) ausgebildet sind.2. Control element according to claim 1, characterized in that the control element (1) receives closing body (32) on which control element-side control edges (18, 19) are formed.
3. Steuerelement gemäß Anspruch 2, dadurch gekennzeichnet, daß die Schließkörper (32) mit am Gehäuse (6) ausgebildeten Steuerkanten (17, 20) zusammenarbeiten.3. Control element according to claim 2, characterized in that the closing body (32) with the housing (6) formed control edges (17, 20) cooperate.
4. Steuerelement gemäß Anspruch 1, dadurch gekennzeichnet, daß das Steuerelement (1) durch mindestens einen sich am Gehäuse (6) abstützenden Kraftspeicher (4, 5) beaufschlagt ist.4. Control element according to claim 1, characterized in that the control element (1) is acted upon by at least one energy store (4, 5) which is supported on the housing (6).
5. Steuerelement gemäß Anspruch 2, dadurch gekennzeichnet, daß von einem zwischen Steuerkanten (18, 19) des Steuerschiebers (1) liegenden Hohlraum (28) die Verbindungsbohrung (9) zu den Einspritzsystemen (34, 35) abzweigt. 5. Control element according to claim 2, characterized in that from a between control edges (18, 19) of the control slide (1) lying cavity (28) branches off the connecting bore (9) to the injection systems (34, 35).
6. Steuerelement gemäß Anspruch 1, dadurch gekennzeichnet, daß die maximale Öffnung von Hochdruckzulauf (7) und drucklosem Ablauf (8) durch in der Bohrung (31) für das Steuerelement (1) vorgesehene Anschläge (13, 14) begrenzt ist.6. Control element according to claim 1, characterized in that the maximum opening of the high pressure inlet (7) and depressurized outlet (8) through the bore (31) for the control element (1) provided stops (13, 14) is limited.
7. Steuerelement gemäß Anspruch 1, dadurch gekennzeichnet, daß die den Enden des Steuerelementes (1) jeweils gegenüberliegenden Betätigungsorgane (2, 3) jeweils unabhängig voneinander durch eine Steuereinheit (15) ansteuerbar sind.7. Control element according to claim 1, characterized in that the ends of the control element (1) respectively opposite actuators (2, 3) are each independently controllable by a control unit (15).
8. Steuerelement gemäß Anspruch 7, dadurch gekennzeichnet, daß die Betätigungsorgane (2, 3) als Elektromagnete ausgefüllt sind.8. Control element according to claim 7, characterized in that the actuators (2, 3) are filled as electromagnets.
9. Steuerelement gemäß Anspruch 1, dadurch gekennzeichnet, daß das Verschließen des Hochdruckzulaufes (7) und die Freigabe des drucklosen9. Control element according to claim 1, characterized in that the closing of the high pressure inlet (7) and the release of the unpressurized
Ablaufes (8) durch den Steuerschieber (1) nach Ansteuerung der Betätigungsorgane (2, 3) entgegen der Wirkung des ablaufseitigen Kraftspeichers (5) erfolgt.Sequence (8) through the control slide (1) after actuation of the actuators (2, 3) against the effect of the outflow-side energy store (5).
10. Steuerelement gemäß Anspruch 1, dadurch gekennzeichnet, daß das Verschließen des Ablaufes (8) und die Freigabe des Hochdruckzulaufes (7) durch das Steuerelement (1) nach Ansteuerung der Betätigungsorgane (2, 3) entgegen der Wirkung des zulaufseitigen Kraftspeichers (4) erfolgt. 10. Control element according to claim 1, characterized in that the closing of the drain (8) and the release of the high pressure inlet (7) by the control element (1) after actuation of the actuators (2, 3) against the action of the inlet-side energy store (4) he follows.
EP00988559A 1999-11-10 2000-11-08 Control element for controlling injection systems Expired - Lifetime EP1187985B1 (en)

Applications Claiming Priority (3)

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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

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

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EP (1) EP1187985B1 (en)
JP (1) JP2003514188A (en)
KR (1) KR100665934B1 (en)
DE (2) DE19954057A1 (en)
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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

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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.
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JPH11218253A (en) * 1998-02-02 1999-08-10 Kenji Masuda Proportional solenoid type direction throttle valve

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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
EP1187985B1 (en) 2006-08-09

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