EP1530680B1 - Method for the production of a module with a moving insert for an injection valve and injection valve - Google Patents

Method for the production of a module with a moving insert for an injection valve and injection valve Download PDF

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Publication number
EP1530680B1
EP1530680B1 EP03762417A EP03762417A EP1530680B1 EP 1530680 B1 EP1530680 B1 EP 1530680B1 EP 03762417 A EP03762417 A EP 03762417A EP 03762417 A EP03762417 A EP 03762417A EP 1530680 B1 EP1530680 B1 EP 1530680B1
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EP
European Patent Office
Prior art keywords
module
valve
injection valve
insert
actuator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP03762417A
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German (de)
French (fr)
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EP1530680A1 (en
Inventor
Heinz Lixl
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.)
Continental Automotive GmbH
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Continental Automotive GmbH
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Publication date
Application filed by Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of EP1530680A1 publication Critical patent/EP1530680A1/en
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Publication of EP1530680B1 publication Critical patent/EP1530680B1/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the invention relates to a method for producing a module with a movable insert for an injection valve according to the preamble of patent claim 1 and an injection valve according to the preamble of patent claim 3.
  • an injection valve has a module with a movable insert.
  • the movable insert is used, for example, to transmit a deflection of an actuator to an injection needle. If piezoelectric actuators are used, then a precise adjustment of the movable insert with respect to an actuator is required, since piezoelectric actuators can realize only a small movement stroke on the one hand and on the other due to different thermal expansion coefficients between an injection valve housing and the piezoelectric actuator, a defined idle stroke between must be complied with the piezoelectric actuator and an actuator to be controlled.
  • both the module and the movable insert have a flat ground surface.
  • the module rests on another module and the movable insert is in turn driven by an actuator. In both cases, a precise determination of the height of the module or the length of the movable insert is advantageous.
  • a control valve for a fuel injection valve which comprises a module with a valve body.
  • the valve body has a surface which is a Associated plunger, which is in operative connection with a piezoelectric actuator.
  • a Leerhub is preset, which is formed in the closed position of the valve body and in the non-energized state of the piezoelectric actuator.
  • a method for positioning the actuator in a fuel injector and an apparatus for carrying out the method is known.
  • a compensation ring with a suitable thickness is also provided between the housing of the fuel injector and the housing of the piezoelectric actuator.
  • a control valve for a fuel valve is known.
  • the injection valve has a control chamber, which communicates via an inlet throttle with a high-pressure accumulator, and which can be brought via the control valve and an outlet throttle with a non-pressurized return to a fuel tank in combination.
  • the pressure prevailing in the control chamber acts on a movable nozzle body, which is provided with a nozzle needle, which releases the injection during the movement of the nozzle body and closes.
  • the control valve is formed adjacent to the control chamber, so that the pressure prevailing in the control chamber pressure on a first active surface also acts on the valve body of the control valve.
  • the control valve has a valve chamber which is arranged opposite to the control chamber, communicates with the control chamber via the outlet throttle and has a second effective area which is smaller than the first effective area.
  • the object of the invention is to provide a method for producing a module with a movable insert for an injection valve, wherein the insert and the module have abutment sides, which are worked flat in a fixed relationship to each other.
  • a significant advantage of the method according to the invention is that the valve plate and the closing member are positively held together, that the valve plate and / or the closing member are acted upon by a biasing force and that during the application of the biasing force, the valve plate and the closing member worked plan on a contact side become.
  • a biasing force acting on the valve plate and / or the closing member during actual grinding operation of the injection valve is simulated during plan grinding. This will be a determination of Bearing sides of the valve plate with respect to the contact side of the closing member adapted to the prevailing in use in the injector clamping forces.
  • the closing member is pressed against a sealing seat of the valve plate, wherein a pin part of the closing member protrudes through a drain opening of the valve plate.
  • the closing member is pressed against the sealing seat with a predetermined biasing force and when the biasing force is applied, the pin part and the area surrounding the pin part of the valve plate are worked to a height, in particular ground flat.
  • the closing member is assigned in the installed state in the injection valve of a control chamber in which a fixed maximum control pressure prevails. The maximum control pressure exerts a biasing force on the closing member.
  • An injection valve having a valve plate with a closing member which were prepared according to the method of claim 1, have a precise, fixed for use in the injection valve adjustment of support surfaces of the valve plate and the closing member to each other. This gives an improved adjustment.
  • Fig. 1 shows a cross section through an injection valve with an actuator housing 1, in which an actuator 2 is introduced.
  • the Actuator housing 1 is bolted to a clamping nut 3.
  • the clamping nut 3 biases a nozzle body 4, a guide plate 11 and a valve plate 5 against the actuator housing 1.
  • the nozzle body 4 abuts with an upper end surface on a lower end surface of the guide plate 11.
  • the guide plate 11 in turn abuts with an upper end surface on a lower end surface of the valve plate 5.
  • the valve plate 5 in turn abuts with an upper end surface on a lower end surface of the actuator housing 1.
  • the actuator 2 is clamped between a bottom plate 7 and a top plate 9 via a spring sleeve 8.
  • the top plate 9 is fixedly connected to the actuator housing 1.
  • the bottom plate 7 is arranged movable relative to the actuator housing 1.
  • the bottom plate 7 has a control pin 16 which is associated with a pin part 23 of a closing member 6.
  • the closing member 6 is arranged in a drain opening 17 of the valve plate 5.
  • the drain opening 17 is formed substantially cylindrical and tapers in the upper region in a conical shape.
  • the conical region of the drain opening 17 is a sealing seat for the closing member 6.
  • a plate spring 25 is arranged, which biases the closing member 6 on the associated sealing seat.
  • the closing member 6 is substantially cylindrical and also tapers in the upper region via a conical shape in the pin part 23.
  • the drain opening 17 is connected via an inlet bore 18 which is inserted into the guide plate 11, with an inlet channel 10 in the connection Actuator 1 is guided and represents a fuel connection. Between the inlet bore 18 and the drain opening 17, an inlet throttle 19 is arranged.
  • the drain opening 17 is connected to a control chamber 20 in hydraulic communication, which is introduced into the guide plate 11 and is bounded by a movably mounted control piston 21.
  • the control piston 21 is in operative connection with a valve needle 12, the tip of which is associated with an injection opening 14.
  • To the injection port 14 is a Sealing seat for the tip of the valve needle 12 is formed.
  • a fuel chamber 13 is formed, which is also connected to the inlet channel 10 in communication. For this purpose, corresponding fuel bores are introduced in the nozzle body 4, in the guide plate 11 and in the valve plate 5.
  • the injector operates in the following manner: In the non-actuated state of the piezoelectric actuator 2, the control pin 16 is a fixed Leerhubrange of the pin member of the closing member 6 away.
  • the inlet channel 10 is in communication with a fuel reservoir that holds fuel at a high pressure. Consequently, there is high pressure fuel in the fuel chamber 13, the control chamber 20 and the drain opening 17. Due to the high fuel pressure, the closure member 6 is pressed into the associated sealing seat and closes the drain opening 17.
  • the valve needle 12 by the high fuel pressure in the control chamber 20 prevails, pressed down over the control piston 21 onto the sealing seat of the injection opening 14. Consequently, the injection port 14 is closed and there is no injection.
  • the piezoelectric actuator 2 If the piezoelectric actuator 2 is energized, then the piezoelectric actuator 2 expands and presses the bottom plate 7 downwards and thus the control pin 16 against the pin part 23 of the closing member 6. As a result, the closing member 6 is lifted from the associated sealing seat. As a result, the drain port 17 is opened and fuel flows out of the control chamber 20. Thus, the fuel pressure in the control chamber 20 decreases because less fuel flows through the inlet throttle 19 than flows through the outlet opening 17. Since the valve needle 12 has a pressure shoulder 15 in the region of the fuel chamber 13, the high fuel pressure prevailing in the fuel chamber 13 lifts the valve needle 12 away from the sealing seat of the injection port 14. Thus, the injection port 14 is opened and fuel is discharged from the fuel chamber 13 via the injection port 14.
  • Fig. 2 shows a cross section through a valve plate 5 and a closing member 6, wherein the valve plate 5 is pressed with an upper abutment surface against a grinding plate 22.
  • the closing member 6 is pressed with an additional biasing force F against the sealing seat.
  • the pin member 23 is further pushed out over the abutment surface of the valve plate 5.
  • the grinding plate 22 grinds the upper abutment surface of the valve plate 5 and the upper abutment surface of the pin member 23 on a plane plan.
  • other machining methods can be selected with which a uniform height between the pin member 23 and the valve plate 5 is set.
  • the pin member 23 is sanded shorter than would be the case without the additional biasing force.
  • the additional biasing force is preferably selected in such a way that the biasing force is simulated, which acts on the closing member 6 in a closed drain opening 17. In this way, the end surface of the pin member 23 is precisely aligned in a plane to the end face of the valve plate 5.
  • Fig. 3 shows a cross section through the actuator housing 1 and the actuator 2 with the bottom plate 7.
  • the bottom plate 7 has the control pin 16.
  • the actuator housing 1 is clamped in the region of the abutment surface against a stop 24.
  • the actuator housing 1 is biased against the stop 24 with a defined biasing force. In this way, a bias of the actuator housing 1 relative to the actuator 2 and the bottom plate 7 is achieved.
  • the biasing force is preferably selected such that the biasing force corresponds to the biasing force exerted on the actuator housing 1 upon clamping the injector valve into a cylinder head.
  • an additional biasing force is exerted on the actuator housing 1, which corresponds to a displacement of the bottom plate 7 relative to the actuator housing 1 by a desired idle stroke between the abutment surface of the control pin 16 and the abutment surface of the pin member 23.
  • slightly varied preload forces can be used.
  • a biasing force is selected, which corresponds to the idle stroke. If the idle stroke is adjusted via shims, then the biasing force is selected according to the clamping force with which the injection valve is clamped in the cylinder head via clamping claws.
  • the forces are in the range of 3 to 12 kN for the clamping in the cylinder head and in the range of 0.5 to 5 kN for setting the idle stroke.
  • the abutment surfaces of the actuator housing 1 and the abutment surface of the control mandrel 16 are brought to a plane, preferably ground flat with a grinding plate 22 and gefinished.
  • Fig. 4 shows in an enlarged view the fit of the actuator housing 1, which rests with a lower abutment surface on an upper abutment surface of the valve plate 5.
  • the control pin 16 is assigned to the pin part 23 of the closing member 6. Between the abutment surface of the pin member 23 and the abutment surface of the control pin 16, an idle stroke is formed. If the injection valve is not clamped in the cylinder head, then the idle stroke is significantly greater than the desired idle stroke. A desired idle stroke is in the range of preferably 0.5 to 5 ⁇ m. However, if the injection valve is clamped in the cylinder head, then the actuator housing 1 according to Fig. 3 biased and thus reduces the idle stroke between the pin member 23 and the control pin 16.
  • the optimal idle stroke is not yet reached, since the closing member 6 is not yet pressed by the fuel pressure prevailing in the control chamber, against the sealing seat. If the closing member is pressed by the fuel pressure against the sealing seat, then finally the optimum and desired idle stroke is set.
  • the injection valve according to the invention is not according to the injection valve according to Fig. 1 limited, but can be used with any type of injector type.

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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)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

A method for the production of a module with a moving insert for an injection valve is disclosed, whereby the insert is arranged such as to move within the module and the module and the insert comprise contact surfaces on a common side. According to the invention, the insert and/or the module are pre-tensioned and whilst in the pre-tensioned state the contact surfaces of the module and the insert are ground to a plane. By applying the pre-tensioning, a tensioning is simulated during the plane grinding which occurs during application of the module in an injection valve. A precise matching of the end surfaces to each other can thus be achieved.

Description

Die Erfindung betrifft ein Verfahren zum Herstellen eines Moduls mit einem beweglichen Einsatz für ein Einspritzventil gemäß dem Oberbegriff des Patentanspruchs 1 und ein Einspritzventil gemäß dem Oberbegriff des Patentanspruchs 3.The invention relates to a method for producing a module with a movable insert for an injection valve according to the preamble of patent claim 1 and an injection valve according to the preamble of patent claim 3.

Je nach Ausführungsform des Einspritzventils weist ein Einspritzventil ein Modul mit einem beweglichen Einsatz auf. Der bewegliche Einsatz wird beispielsweise dazu verwendet, um eine Auslenkung eines Aktors auf eine Einspritznadel zu übertragen. Werden piezoelektrische Aktoren verwendet, so ist eine präzise Justierung des beweglichen Einsatzes in Bezug auf ein Stellglied erforderlich, da piezoelektrische Aktoren zum einen nur einen geringen Bewegungshub realisieren können und zum anderen aufgrund von unterschiedlichen thermischen Ausdehnungskoeffizienten zwischen einem Einspritzventilgehäuse und dem piezoelektrischen Aktor ein definierter Leerhub zwischen dem piezoelektrischen Aktor und einem anzusteuernden Stellglied eingehalten werden muss.Depending on the embodiment of the injection valve, an injection valve has a module with a movable insert. The movable insert is used, for example, to transmit a deflection of an actuator to an injection needle. If piezoelectric actuators are used, then a precise adjustment of the movable insert with respect to an actuator is required, since piezoelectric actuators can realize only a small movement stroke on the one hand and on the other due to different thermal expansion coefficients between an injection valve housing and the piezoelectric actuator, a defined idle stroke between must be complied with the piezoelectric actuator and an actuator to be controlled.

Zum Aufbau eines Einspritzventils werden Module mit beweglichen Einsätzen verwendet, die in einem Gehäuse des Einspritzventils eingespannt sind. Für eine präzise Einstellung weisen sowohl das Modul als auch der bewegliche Einsatz eine plan geschliffene Fläche auf. Beispielsweise liegt das Modul auf einem anderen Modul auf und der bewegliche Einsatz wird wiederum von einem Stellglied angesteuert. In beiden Fällen ist eine präzise Festlegung der Höhe des Moduls bzw. der Länge des beweglichen Einsatzes vorteilhaft.To build an injector modules are used with movable inserts, which are clamped in a housing of the injector. For precise adjustment, both the module and the movable insert have a flat ground surface. For example, the module rests on another module and the movable insert is in turn driven by an actuator. In both cases, a precise determination of the height of the module or the length of the movable insert is advantageous.

Aus DE 19 822 503 C1 ist ein Steuerventil für ein Kraftstoffeinspritzventil bekannt, das ein Modul mit einem Ventilkörper aufweist. Der Ventilkörper weist eine Fläche auf, die einem Stößel zugeordnet ist, der mit einem piezoelektrischen Aktor in Wirkverbindung steht. Zwischen dem Ende des Stößels und dem Schließglied ist ein Leerhub voreingestellt, der in der Schließposition des Ventilkörpers und bei nicht bestromtem Zustand des piezoelektrischen Aktors ausgebildet ist. Für eine präzise Einstellung des Leerhubes ist es erforderlich, die Fläche des Ventilkörpers präzise festzulegen.Out DE 19 822 503 C1 a control valve for a fuel injection valve is known which comprises a module with a valve body. The valve body has a surface which is a Associated plunger, which is in operative connection with a piezoelectric actuator. Between the end of the plunger and the closing member a Leerhub is preset, which is formed in the closed position of the valve body and in the non-energized state of the piezoelectric actuator. For a precise adjustment of the idle stroke, it is necessary to precisely set the area of the valve body.

Aus DE 19921242 C1 ist ein Verfahren zum Positionieren des Stellantriebs in einem Kraftstoffinjektor und eine Vorrichtung zur Durchführung des Verfahrens bekannt. Das Positionieren des Stellantriebs in dem Kraftstoffinjektor mit einem Piezoaktor, der in das Gehäuse des Kraftstoffinjektors eingeschraubt ist, erfolgt durch das Anlegen einer Spannung an den Piezoaktor, die einem vorgegebenen Leerhub entspricht, und das Planschleifen von Gehäuse und Bodenplatte des Piezoaktors bei Anlegen der Spannung. Zwischen dem Gehäuse des Kraftstoffinjektors und dem Gehäuse des Piezoaktors ist darüber hinaus ein Ausgleichsring mit passender Dicke vorgesehen.Out DE 19921242 C1 For example, a method for positioning the actuator in a fuel injector and an apparatus for carrying out the method is known. The positioning of the actuator in the fuel injector with a piezoelectric actuator, which is screwed into the housing of the fuel injector, by applying a voltage to the piezoelectric actuator, which corresponds to a predetermined idle stroke, and the surface grinding of the housing and bottom plate of the piezoelectric actuator upon application of the voltage. Between the housing of the fuel injector and the housing of the piezoelectric actuator, a compensation ring with a suitable thickness is also provided.

Aus DE 19822503 C1 ist ein Steuerventil für ein Kraftstoffventil bekannt. Das Einspritzventil weist eine Steuerkammer auf, die über eine Zulaufdrossel mit einem Hochdruckspeicher in Verbindung steht, und die über das Steuerventil und eine Ablaufdrossel mit einem drucklosen Rücklauf zu einem Kraftstofftank in Verbindung gebracht werden kann. Der in der Steuerkammer herrschende Druck wirkt auf einen beweglichen Düsenkörper, der mit einer Düsennadel versehen ist, die bei der Bewegung des Düsenkörpers die Einspritzung freigibt und verschließt. Das Steuerventil ist angrenzend an die Steuerkammer ausgebildet, so dass der in der Steuerkammer herrschende Druck an einer ersten Wirkfläche auch auf den Ventilkörper des Steuerventils einwirkt. Das Steuerventil weist eine Ventilkammer auf, die entgegengesetzt zur Steuerkammer angeordnet ist, mit der Steuerkammer über die Ablaufdrossel in Verbindung steht und eine zweite Wirkfläche besitzt, die kleiner ist als die erste Wirkfläche.Out DE 19822503 C1 a control valve for a fuel valve is known. The injection valve has a control chamber, which communicates via an inlet throttle with a high-pressure accumulator, and which can be brought via the control valve and an outlet throttle with a non-pressurized return to a fuel tank in combination. The pressure prevailing in the control chamber acts on a movable nozzle body, which is provided with a nozzle needle, which releases the injection during the movement of the nozzle body and closes. The control valve is formed adjacent to the control chamber, so that the pressure prevailing in the control chamber pressure on a first active surface also acts on the valve body of the control valve. The control valve has a valve chamber which is arranged opposite to the control chamber, communicates with the control chamber via the outlet throttle and has a second effective area which is smaller than the first effective area.

Aus DE 10055644 A1 ist ein Verfahren zum Einstellen eines Leerhubes eines Injektors bekannt, wobei der Leerhub durch eine Aktoreinheit mit einem elektrisch ansteuerbaren Aktor und einem vom Aktor betätigbaren Kolben gebildet wird. Es wird der Abstand zwischen einer ersten Stelle, die einen bekannten Abstand von der der Aktoreinheit abgewandten Fläche des Ventilkolbens im unangesteuerten Zustand des Aktors hat, und einer Stelle, die einen bekannten Abstand von der dem Ventilkolben zugewandten Fläche der hinzuzufügenden Aktoreinheit im unangesteuerten Zustand hat, bestimmt. Abhängig vom Abstand zwischen der ersten Stelle und der zweiten Stelle wird die für einen vorgegebenen Leerhub erforderliche Länge des Ventilkolbens bestimmt. Der Ventilkolben wird so gewählt, dass er die erforderliche Länge aufweist, und wird anschließend in das Injektorkopfgehäuse eingesetzt. Anschließend wird das Injektorgehäuse auf die Aufsatzfläche des Injektorkopfgehäuses aufgesetzt.Out DE 10055644 A1 a method for adjusting a Leerhubes an injector is known, wherein the idle stroke is formed by an actuator with an electrically controllable actuator and a piston actuated by the actuator. It is the distance between a first position, which has a known distance from the actuator unit facing away from the surface of the valve piston in the uncontrolled state of the actuator, and a location which has a known distance from the valve piston surface facing the actuator unit to be added in the uncontrolled state, certainly. Depending on the distance between the first location and the second location, the length of the valve piston required for a given idle stroke is determined. The valve piston is selected to have the required length and is then inserted into the injector head housing. Subsequently, the injector is placed on the top surface of the Injektorkopfgehäuses.

Die Aufgabe der Erfindung besteht darin, ein Verfahren zum Herstellen eines Moduls mit einem beweglichen Einsatz für ein Einspritzventil bereitzustellen, wobei der Einsatz und das Modul Anliegeseiten aufweisen, die in einem festgelegten Verhältnis zueinander plan gearbeitet sind.The object of the invention is to provide a method for producing a module with a movable insert for an injection valve, wherein the insert and the module have abutment sides, which are worked flat in a fixed relationship to each other.

Die Aufgabe der Erfindung wird durch das Verfahren gemäß dem Merkmal des Anspruchs 1 gelöst. Ein wesentlicher Vorteil des erfindungsgemäßen Verfahrens besteht darin, dass die Ventilplatte und das Schließglied formschlüssig miteinander gehaltert werden, dass die Ventilplatte und/oder das Schließglied mit einer Vorspannkraft beaufschlagt werden und dass während des Anlegens der Vorspannkraft die Ventilplatte und das Schließglied auf einer Anliegeseite plan gearbeitet werden.The object of the invention is achieved by the method according to the feature of claim 1. A significant advantage of the method according to the invention is that the valve plate and the closing member are positively held together, that the valve plate and / or the closing member are acted upon by a biasing force and that during the application of the biasing force, the valve plate and the closing member worked plan on a contact side become.

Durch die Einbringung der Vorspannkraft wird eine im tatsächlichen Betrieb des Einspritzventils auf die Ventilplatte und/oder das Schließglied einwirkende Vorspannkraft während des Planschleifens simuliert. Damit wird eine Festlegung der Anliegeseiten der Ventilplatte in Bezug auf die Anliegeseite des Schließgliedes auf die im Einsatz im Einspritzventil herrschenden Spannkräfte angepasst.By introducing the biasing force, a biasing force acting on the valve plate and / or the closing member during actual grinding operation of the injection valve is simulated during plan grinding. This will be a determination of Bearing sides of the valve plate with respect to the contact side of the closing member adapted to the prevailing in use in the injector clamping forces.

In der erfindungsgemäßen Ausführungsform wird das Schließglied gegen einen Dichtsitz der Ventilplatte gedrückt, wobei ein Stiftteil des Schließgliedes durch eine Ablauföffnung der Ventilplatte ragt. Das Schließglied wird mit einer festgelegten Vorspannkraft gegen den Dichtsitz gedrückt und bei anliegender Vorspannkraft werden das Stiftteil und die das Stiftteil umgebende Fläche der Ventilplatte auf eine Höhe gearbeitet, insbesondere plan geschliffen. Durch die Einbringung der Vorspannkraft auf das Schließglied wird wieder eine im Einspritzventil herrschende Situation simuliert. Das Schließglied ist im verbauten Zustand im Einspritzventil einer Steuerkammer zugeordnet, in der ein festgelegter maximaler Steuerdruck herrscht. Der maximale Steuerdruck übt eine Vorspannkraft auf das Schließglied aus. Da die im realen Betrieb auf das Schließglied einwirkende Vorspannkraft bereits bei dem Planschleifen der Ventilplatte und des Stiftteils des Schließgliedes berücksichtigt wurde, ist die Oberseite der Ventilplatte und die Oberfläche des Stiftteils im Einsatz im Einspritzventil auf einer Ebene. Somit ist eine optimale Justierung der Oberfläche des Stiftteils in Bezug auf die Oberfläche der Ventilplatte für den Betrieb im Einspritzventil gegeben.In the embodiment of the invention, the closing member is pressed against a sealing seat of the valve plate, wherein a pin part of the closing member protrudes through a drain opening of the valve plate. The closing member is pressed against the sealing seat with a predetermined biasing force and when the biasing force is applied, the pin part and the area surrounding the pin part of the valve plate are worked to a height, in particular ground flat. By introducing the biasing force on the closing member, a situation prevailing in the injection valve is again simulated. The closing member is assigned in the installed state in the injection valve of a control chamber in which a fixed maximum control pressure prevails. The maximum control pressure exerts a biasing force on the closing member. Since the biasing force acting on the closing member in real operation has already been taken into account during the surface grinding of the valve plate and the pin part of the closing member, the upper side of the valve plate and the surface of the pin part in use in the injection valve on one level. Thus, an optimal adjustment of the surface of the pin member is given with respect to the surface of the valve plate for operation in the injection valve.

Ein Einspritzventil, das eine Ventilplatte mit einem Schließglied aufweist, die gemäß dem Verfahren nach Anspruch 1 hergestellt wurden, weisen eine präzise, für den Einsatz im Einspritzventil festgelegte Justierung von Aufliegeflächen der Ventilplatte und des Schließgliedes zueinander auf. Damit ist eine verbesserte Justierung gegeben.An injection valve having a valve plate with a closing member, which were prepared according to the method of claim 1, have a precise, fixed for use in the injection valve adjustment of support surfaces of the valve plate and the closing member to each other. This gives an improved adjustment.

Die Erfindung wird im Folgenden anhand eines Ausführungsbeispiels näher erläutert. Es zeigen

  • Fig. 1 schematisch einen Aufbau eines Einspritzventils,
  • Fig. 2 einen Querschnitt durch eine Ventilplatte mit einem Schließglied,
  • Fig. 3 einen Querschnitt durch ein Aktorgehäuse mit einem piezoelektrischen Aktor und
  • Fig. 4 eine vergrößerte Darstellung eines Querschnitts durch die Ventilplatte und die Bodenplatte.
The invention is explained in more detail below with reference to an embodiment. Show it
  • Fig. 1 schematically a structure of an injection valve,
  • Fig. 2 a cross section through a valve plate with a closing member,
  • Fig. 3 a cross section through an actuator housing with a piezoelectric actuator and
  • Fig. 4 an enlarged view of a cross section through the valve plate and the bottom plate.

Fig. 1 zeigt einen Querschnitt durch ein Einspritzventil mit einem Aktorgehäuse 1, in das ein Aktor 2 eingebracht ist. Das Aktorgehäuse 1 ist mit einer Spannmutter 3 verschraubt. Die Spannmutter 3 spannt einen Düsenkörper 4, eine Führungsplatte 11 und eine Ventilplatte 5 gegen das Aktorgehäuse 1. Dabei liegt der Düsenkörper 4 mit einer oberen Endfläche an einer unteren Endfläche der Führungsplatte 11 an. Die Führungsplatte 11 wiederum liegt mit einer oberen Endfläche an einer unteren Endfläche der Ventilplatte 5 an. Die Ventilplatte 5 wiederum liegt mit einer oberen Endfläche an einer unteren Endfläche des Aktorgehäuses 1 an. Fig. 1 shows a cross section through an injection valve with an actuator housing 1, in which an actuator 2 is introduced. The Actuator housing 1 is bolted to a clamping nut 3. The clamping nut 3 biases a nozzle body 4, a guide plate 11 and a valve plate 5 against the actuator housing 1. In this case, the nozzle body 4 abuts with an upper end surface on a lower end surface of the guide plate 11. The guide plate 11 in turn abuts with an upper end surface on a lower end surface of the valve plate 5. The valve plate 5 in turn abuts with an upper end surface on a lower end surface of the actuator housing 1.

Der Aktor 2 ist zwischen eine Bodenplatte 7 und eine Kopfplatte 9 über eine Federhülse 8 eingespannt. Die Kopfplatte 9 ist mit dem Aktorgehäuse 1 fest verbunden. Die Bodenplatte 7 ist gegenüber dem Aktorgehäuse 1 beweglich angeordnet. Die Bodenplatte 7 weist einen Steuerdorn 16 auf, der einem Stiftteil 23 eines Schließgliedes 6 zugeordnet ist. Das Schließglied 6 ist in einer Ablauföffnung 17 der Ventilplatte 5 angeordnet. Die Ablauföffnung 17 ist im Wesentlichen zylindrisch ausgebildet und verjüngt sich im oberen Bereich in einer konischen Form. Der konische Bereich der Ablauföffnung 17 stellt einen Dichtsitz für das Schließglied 6 dar. Zwischen dem Schließglied 6 und der Ventilplatte 5 ist eine Tellerfeder 25 angeordnet, die das Schließglied 6 auf den zugeordneten Dichtsitz vorspannt. Das Schließglied 6 ist im Wesentlichen zylinderförmig ausgebildet und verjüngt sich ebenfalls im oberen Bereich über eine konische Form in das Stiftteil 23. Die Ablauföffnung 17 steht über eine Zulaufbohrung 18, die in die Führungsplatte 11 eingebracht ist, mit einem Zulaufkanal 10 in Verbindung, der im Aktorgehäuse 1 geführt ist und einen Kraftstoffanschluss darstellt. Zwischen der Zulaufbohrung 18 und der Ablauföffnung 17 ist eine Zulaufdrossel 19 angeordnet. Die Ablauföffnung 17 steht mit einer Steuerkammer 20 in hydraulischer Verbindung, die in der Führungsplatte 11 eingebracht ist und von einem beweglich gelagerten Steuerkolben 21 begrenzt ist. Der Steuerkolben 21 steht in Wirkverbindung mit einer Ventilnadel 12, deren Spitze einer Einspritzöffnung 14 zugeordnet ist. Um die Einspritzöffnung 14 ist ein Dichtsitz für die Spitze der Ventilnadel 12 ausgebildet. Zwischen der Ventilnadel 12 und dem Düsenkörper 4 ist ein Kraftstoffraum 13 ausgebildet, der ebenfalls mit dem Zulauf kanal 10 in Verbindung steht. Dazu sind entsprechende Kraftstoffbohrungen im Düsenkörper 4, in der Führungsplatte 11 und in der Ventilplatte 5 eingebracht.The actuator 2 is clamped between a bottom plate 7 and a top plate 9 via a spring sleeve 8. The top plate 9 is fixedly connected to the actuator housing 1. The bottom plate 7 is arranged movable relative to the actuator housing 1. The bottom plate 7 has a control pin 16 which is associated with a pin part 23 of a closing member 6. The closing member 6 is arranged in a drain opening 17 of the valve plate 5. The drain opening 17 is formed substantially cylindrical and tapers in the upper region in a conical shape. The conical region of the drain opening 17 is a sealing seat for the closing member 6. Between the closing member 6 and the valve plate 5, a plate spring 25 is arranged, which biases the closing member 6 on the associated sealing seat. The closing member 6 is substantially cylindrical and also tapers in the upper region via a conical shape in the pin part 23. The drain opening 17 is connected via an inlet bore 18 which is inserted into the guide plate 11, with an inlet channel 10 in the connection Actuator 1 is guided and represents a fuel connection. Between the inlet bore 18 and the drain opening 17, an inlet throttle 19 is arranged. The drain opening 17 is connected to a control chamber 20 in hydraulic communication, which is introduced into the guide plate 11 and is bounded by a movably mounted control piston 21. The control piston 21 is in operative connection with a valve needle 12, the tip of which is associated with an injection opening 14. To the injection port 14 is a Sealing seat for the tip of the valve needle 12 is formed. Between the valve needle 12 and the nozzle body 4, a fuel chamber 13 is formed, which is also connected to the inlet channel 10 in communication. For this purpose, corresponding fuel bores are introduced in the nozzle body 4, in the guide plate 11 and in the valve plate 5.

Das Einspritzventil funktioniert in folgender Weise: Im nicht angesteuerten Zustand des piezoelektrischen Aktors 2 ist der Steuerdorn 16 eine festgelegte Leerhubstrecke von dem Stiftteil des Schließgliedes 6 entfernt. Der Zulaufkanal 10 steht mit einem Kraftstoffreservoir in Verbindung, das Kraftstoff mit einem hohen Druck bereithält. Folglich befindet sich Kraftstoff mit hohem Druck im Kraftstoffraum 13, der Steuerkammer 20 und der Ablauföffnung 17. Durch den hohen Kraftstoffdruck ist das Schließglied 6 in den zugeordneten Dichtsitz gedrückt und verschließt die Ablauföffnung 17. Gleichzeitig wird die Ventilnadel 12 durch den hohen Kraftstoffdruck, der in der Steuerkammer 20 herrscht, über den Steuerkolben 21 nach unten auf den Dichtsitz der Einspritzöffnung 14 gedrückt. Folglich ist die Einspritzöffnung 14 verschlossen und es erfolgt keine Einspritzung.The injector operates in the following manner: In the non-actuated state of the piezoelectric actuator 2, the control pin 16 is a fixed Leerhubstrecke of the pin member of the closing member 6 away. The inlet channel 10 is in communication with a fuel reservoir that holds fuel at a high pressure. Consequently, there is high pressure fuel in the fuel chamber 13, the control chamber 20 and the drain opening 17. Due to the high fuel pressure, the closure member 6 is pressed into the associated sealing seat and closes the drain opening 17. At the same time, the valve needle 12 by the high fuel pressure in the control chamber 20 prevails, pressed down over the control piston 21 onto the sealing seat of the injection opening 14. Consequently, the injection port 14 is closed and there is no injection.

Wird nun der piezoelektrische Aktor 2 bestromt, so dehnt sich der piezoelektrische Aktor 2 aus und drückt dabei die Bodenplatte 7 nach unten und damit den Steuerdorn 16 gegen das Stiftteil 23 des Schließglieds 6. Als Folge davon wird das Schließglied 6 vom zugeordneten Dichtsitz abgehoben. Folglich wird die Ablauföffnung 17 geöffnet und es fließt Kraftstoff aus der Steuerkammer 20 ab. Somit sinkt der Kraftstoffdruck in der Steuerkammer 20, da über die Zulaufdrossel 19 weniger Kraftstoff zufließt als über die Ablauföffnung 17 abfließt. Da die Ventilnadel 12 eine Druckschulter 15 im Bereich des Kraftstoffraumes 13 aufweist, hebt der im Kraftstoffraum 13 vorherrschende hohe Kraftstoffdruck die Ventilnadel 12 vom Dichtsitz der Einspritzöffnung 14 ab. Somit wird die Einspritzöffnung 14 geöffnet und Kraftstoff wird von dem Kraftstoffraum 13 über die Einspritzöffnung 14 abgegeben.If the piezoelectric actuator 2 is energized, then the piezoelectric actuator 2 expands and presses the bottom plate 7 downwards and thus the control pin 16 against the pin part 23 of the closing member 6. As a result, the closing member 6 is lifted from the associated sealing seat. As a result, the drain port 17 is opened and fuel flows out of the control chamber 20. Thus, the fuel pressure in the control chamber 20 decreases because less fuel flows through the inlet throttle 19 than flows through the outlet opening 17. Since the valve needle 12 has a pressure shoulder 15 in the region of the fuel chamber 13, the high fuel pressure prevailing in the fuel chamber 13 lifts the valve needle 12 away from the sealing seat of the injection port 14. Thus, the injection port 14 is opened and fuel is discharged from the fuel chamber 13 via the injection port 14.

Für eine präzise Funktionsweise des Einspritzventiles ist es erforderlich, die Leerhubstrecke zwischen dem Steuerdorn 16 und dem Schließglied 6 genau einzustellen. Eine genaue Einstellung der Leerhubstrecke wird im Wesentlichen durch die relative Anordnung der unteren Anliegefläche des Aktorgehäuses 1 zur unteren Anliegefläche des Steuerdornes 16 und durch die relative Lage der oberen Anliegefläche der Ventilplatte 5 zur oberen Anliegefläche des Stiftteils 23 des Schließgliedes 6 bei geschlossener Ablauföffnung 17 bestimmt.For a precise operation of the injection valve, it is necessary to set the Leerhubstrecke between the control pin 16 and the closing member 6 exactly. An accurate adjustment of the Leerhubstrecke is essentially determined by the relative arrangement of the lower abutment surface of the actuator housing 1 to the lower abutment surface of the control mandrel 16 and by the relative position of the upper abutment surface of the valve plate 5 to the upper abutment surface of the pin member 23 of the closure member 6 at the closed drain opening 17.

Fig. 2 zeigt einen Querschnitt durch eine Ventilplatte 5 und ein Schließglied 6, wobei die Ventilplatte 5 mit einer oberen Anliegefläche gegen eine Schleifplatte 22 gedrückt wird. Zusätzlich wird das Schließglied 6 mit einer zusätzlichen Vorspannkraft F gegen den Dichtsitz gedrückt. Als Folge davon wird das Stiftteil 23 weiter über die Anliegefläche der Ventilplatte 5 herausgedrückt. Die Schleifplatte 22 schleift die obere Anliegefläche der Ventilplatte 5 und die obere Anliegefläche des Stiftteils 23 auf einer Ebene plan. Anstelle eines Schleifvorgangs können auch andere Bearbeitungsverfahren gewählt werden, mit denen eine einheitliche Höhe zwischen dem Stiftteil 23 und der Ventilplatte 5 eingestellt wird. Durch die zusätzlich auf das Schließglied 6 aufgebrachte Vorspannkraft wird das Stiftteil 23 kürzer abgeschliffen als es ohne die zusätzliche Vorspannkraft der Fall wäre. Die zusätzliche Vorspannkraft ist vorzugsweise in der Weise gewählt, dass die Vorspannkraft simuliert wird, die bei einer geschlossenen Ablauföffnung 17 auf das Schließglied 6 einwirkt. Auf diese Weise wird präzise die Endfläche des Stiftteils 23 in einer Ebene zur Endfläche der Ventilplatte 5 ausgerichtet. Fig. 2 shows a cross section through a valve plate 5 and a closing member 6, wherein the valve plate 5 is pressed with an upper abutment surface against a grinding plate 22. In addition, the closing member 6 is pressed with an additional biasing force F against the sealing seat. As a result, the pin member 23 is further pushed out over the abutment surface of the valve plate 5. The grinding plate 22 grinds the upper abutment surface of the valve plate 5 and the upper abutment surface of the pin member 23 on a plane plan. Instead of a grinding operation, other machining methods can be selected with which a uniform height between the pin member 23 and the valve plate 5 is set. By additionally applied to the closing member 6 biasing force, the pin member 23 is sanded shorter than would be the case without the additional biasing force. The additional biasing force is preferably selected in such a way that the biasing force is simulated, which acts on the closing member 6 in a closed drain opening 17. In this way, the end surface of the pin member 23 is precisely aligned in a plane to the end face of the valve plate 5.

Fig. 3 zeigt einen Querschnitt durch das Aktorgehäuse 1 und den Aktor 2 mit der Bodenplatte 7. Die Bodenplatte 7 weist den Steuerdorn 16 auf. Für eine präzise Einstellung der Anliegefläche des Steuerdornes 16, mit der der Steuerdorn 16 in Kontakt mit dem Stiftteil 23 tritt, und der Anliegefläche des Aktorgehäuses 1, mit der das Aktorgehäuse 1 auf der Ventilplatte 5 aufliegt, wird das Aktorgehäuse 1 im Bereich der Anliegefläche gegen einen Anschlag 24 eingespannt. Zudem wird das Aktorgehäuse 1 mit einer definierten Vorspannkraft gegen den Anschlag 24 vorgespannt. Auf diese Weise wird eine Vorspannung des Aktorgehäuses 1 gegenüber den Aktor 2 und die Bodenplatte 7 erreicht. Die Vorspannkraft wird vorzugsweise in der Weise gewählt, dass die Vorspannkraft der Vorspannkraft entspricht, die auf das Aktorgehäuse 1 bei einem Einspannen des Einspritzventiles in einen Zylinderkopf ausgeübt wird. Vorzugsweise wird eine zusätzliche Vorspannkraft auf das Aktorgehäuse 1 ausgeübt, die eine Verschiebung der Bodenplatte 7 gegenüber dem Aktorgehäuse 1 um einen gewünschten Leerhub zwischen der Anliegefläche des Steuerdorns 16 und der Anliegefläche des Stiftteils 23 entspricht. In Abhängigkeit von den Gegebenheiten können auch etwas variierte Vorspannkräfte verwendet werden. Fig. 3 shows a cross section through the actuator housing 1 and the actuator 2 with the bottom plate 7. The bottom plate 7 has the control pin 16. For a precise adjustment of the contact surface of the control pin 16, with which the control pin 16 comes into contact with the pin member 23, and the abutment surface of the actuator housing 1, with the actuator housing 1 rests on the valve plate 5, the actuator housing 1 is clamped in the region of the abutment surface against a stop 24. In addition, the actuator housing 1 is biased against the stop 24 with a defined biasing force. In this way, a bias of the actuator housing 1 relative to the actuator 2 and the bottom plate 7 is achieved. The biasing force is preferably selected such that the biasing force corresponds to the biasing force exerted on the actuator housing 1 upon clamping the injector valve into a cylinder head. Preferably, an additional biasing force is exerted on the actuator housing 1, which corresponds to a displacement of the bottom plate 7 relative to the actuator housing 1 by a desired idle stroke between the abutment surface of the control pin 16 and the abutment surface of the pin member 23. Depending on the circumstances also slightly varied preload forces can be used.

Wird beispielsweise das Einspritzventil nicht eingespannt, dann wird nur eine Vorspannkraft gewählt, die dem Leerhub entspricht. Wird der Leerhub über Einstellscheiben eingestellt, dann wird die Vorspannkraft entsprechend der Einspannkraft gewählt, mit der das Einspritzventil in den Zylinderkopf über Spannpratzen eingespannt wird. Die Kräfte liegen im Bereich von 3 bis 12 kN für die Einspannung im Zylinderkopf und im Bereich von 0,5 bis 5 kN für die Einstellung des Leerhubs.For example, if the injector is not clamped, then only a biasing force is selected, which corresponds to the idle stroke. If the idle stroke is adjusted via shims, then the biasing force is selected according to the clamping force with which the injection valve is clamped in the cylinder head via clamping claws. The forces are in the range of 3 to 12 kN for the clamping in the cylinder head and in the range of 0.5 to 5 kN for setting the idle stroke.

Während der Einbringung der Vorspannkraft werden die Anliegeflächen des Aktorgehäuses 1 und die Anliegefläche des Steuerdornes 16 auf eine Ebene gebracht, vorzugsweise mit einer Schleifplatte 22 plan geschliffen und gefinished. Versuche haben gezeigt, dass sich bei einer Einbringung einer Vorspannkraft von 100 N eine Leerhubänderung bei der Gehäusefertigung um +0,25 µm ergeben. Durch das beschriebene Verfahren wird eine präzise Einstellung der gewünschten Lage des Steuerdornes 16 in Bezug auf das Aktorgehäuse 1 erreicht.During the introduction of the biasing force, the abutment surfaces of the actuator housing 1 and the abutment surface of the control mandrel 16 are brought to a plane, preferably ground flat with a grinding plate 22 and gefinished. Experiments have shown that when introducing a preload force of 100 N, a Leerhubänderung in the housing production to +0.25 microns. By the method described a precise adjustment of the desired position of the control mandrel 16 with respect to the actuator housing 1 is achieved.

Fig. 4 zeigt in einer vergrößerten Darstellung die Passung des Aktorgehäuses 1, das mit einer unteren Anliegefläche auf einer oberen Anliegefläche der Ventilplatte 5 aufliegt. Zudem ist der Steuerdorn 16 dem Stiftteil 23 des Schließgliedes 6 zugeordnet. Zwischen der Anliegefläche des Stiftteiles 23 und der Anliegefläche des Steuerdorns 16 ist ein Leerhub ausgebildet. Ist das Einspritzventil nicht in den Zylinderkopf eingespannt, so ist der Leerhub deutlich größer als der gewünschte Leerhub. Ein gewünschter Leerhub liegt im Bereich von vorzugsweise 0,5 bis 5 µm. Wird jedoch das Einspritzventil in den Zylinderkopf eingespannt, so wird das Aktorgehäuse 1 gemäß Fig. 3 vorgespannt und somit der Leerhub zwischen dem Stiftteil 23 und dem Steuerdorn 16 reduziert. Der optimale Leerhub wird jedoch noch nicht erreicht, da das Schließglied 6 noch nicht von dem Kraftstoffdruck, der in der Steuerkammer herrscht, gegen den Dichtsitz gedrückt wird. Wird das Schließglied von dem Kraftstoffdruck gegen den Dichtsitz gedrückt, so wird schließlich der optimale und gewünschte Leerhub eingestellt. Fig. 4 shows in an enlarged view the fit of the actuator housing 1, which rests with a lower abutment surface on an upper abutment surface of the valve plate 5. In addition, the control pin 16 is assigned to the pin part 23 of the closing member 6. Between the abutment surface of the pin member 23 and the abutment surface of the control pin 16, an idle stroke is formed. If the injection valve is not clamped in the cylinder head, then the idle stroke is significantly greater than the desired idle stroke. A desired idle stroke is in the range of preferably 0.5 to 5 μm. However, if the injection valve is clamped in the cylinder head, then the actuator housing 1 according to Fig. 3 biased and thus reduces the idle stroke between the pin member 23 and the control pin 16. However, the optimal idle stroke is not yet reached, since the closing member 6 is not yet pressed by the fuel pressure prevailing in the control chamber, against the sealing seat. If the closing member is pressed by the fuel pressure against the sealing seat, then finally the optimum and desired idle stroke is set.

Das erfindungsgemäße Einspritzventil ist nicht auf den Einspritzventiltyp gemäß Fig. 1 beschränkt, sondern kann bei jeder Art von Einspritzventiltyp eingesetzt werden.The injection valve according to the invention is not according to the injection valve according to Fig. 1 limited, but can be used with any type of injector type.

Claims (3)

  1. Method for machining bearing faces of a module (1, 5) and an associated insert (2, 6) of an injection valve, the module (1, 5) and the insert (2, 6) having bearing faces which are arranged on one side, the module (1, 5) and the insert (2, 6) being secured positively to one another, a prestressing force being applied to the module (1, 5) and/or the insert (2, 6), the bearing faces being machined on the same side to an identical level under the prestressing force, characterized in that a valve plate (5) is configured as module and a closing element (6) is configured as insert, in that the closing element (6) has a pin part (23) which protrudes into an outflow opening (17) which is formed in the valve plate (5), in that a sealing seat surrounds the outflow opening (17), in that the closing element is pressed with a prestress against the sealing seat, and in that, when the prestressing force is applied, the pin part (23) and that face of the valve plate (5) which surrounds the outflow opening are machined to one level.
  2. Method according to Claim 1, characterized in that the prestressing force is selected in accordance with the order of magnitude of the stressing force which, during operation in the injection valve, acts on the closing element (6) in the closed position, in which the closing element (6) bears against the sealing seat.
  3. Injection valve having a valve plate (5) and a closing element (6) which have been machined according to Claim 1 or 2.
EP03762417A 2002-07-02 2003-06-24 Method for the production of a module with a moving insert for an injection valve and injection valve Expired - Fee Related EP1530680B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10229638 2002-07-02
DE10229638 2002-07-02
PCT/DE2003/002105 WO2004005704A1 (en) 2002-07-02 2003-06-24 Method for the production of a module with a moving insert for an injection valve and injection valve

Publications (2)

Publication Number Publication Date
EP1530680A1 EP1530680A1 (en) 2005-05-18
EP1530680B1 true EP1530680B1 (en) 2011-09-28

Family

ID=30009774

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Application Number Title Priority Date Filing Date
EP03737904A Expired - Fee Related EP1518050B1 (en) 2002-07-02 2003-05-26 Injector for an injection system
EP03762417A Expired - Fee Related EP1530680B1 (en) 2002-07-02 2003-06-24 Method for the production of a module with a moving insert for an injection valve and injection valve

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP03737904A Expired - Fee Related EP1518050B1 (en) 2002-07-02 2003-05-26 Injector for an injection system

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WO (2) WO2004005699A1 (en)

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Publication number Priority date Publication date Assignee Title
DE102004026171B4 (en) * 2004-05-28 2010-05-20 Continental Automotive Gmbh Injector
US7334570B2 (en) * 2005-04-01 2008-02-26 Achates Power, Inc. Common rail fuel injection system with accumulator injectors
DE102005055359A1 (en) 2005-11-21 2007-05-24 Robert Bosch Gmbh Intermediate plate for a fuel injector and fuel injector
DE102006046898A1 (en) * 2006-10-04 2008-04-10 Robert Bosch Gmbh Throttle plate for solenoid valve
FI123513B (en) * 2010-12-02 2013-06-14 Waertsilae Finland Oy Fuel supply unit, method for operating it and combustion engine
AT512439B1 (en) * 2012-01-26 2013-12-15 Bosch Gmbh Robert DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE

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DE2033051A1 (en) * 1970-07-03 1972-01-05 Bosch Gmbh Robert Electrically controlled fuel injection device
DE2120030A1 (en) * 1971-04-23 1972-11-02 Robert Bosch Gmbh, 7000 Stuttgart Fuel injector
DE2461309A1 (en) * 1973-12-26 1975-07-10 Isuzu Motors Ltd FUEL INJECTION DEVICE
US4526151A (en) * 1982-03-12 1985-07-02 Mitsubishi Jukogyo Kabushiki Kaisha Fuel injection device
JPH0688557A (en) * 1992-07-24 1994-03-29 Nippondenso Co Ltd Electromagnetic control fuel injection system
DE19822503C1 (en) * 1998-05-19 1999-11-25 Siemens Ag Control valve for fuel injector
DE19921242C1 (en) * 1999-05-07 2000-10-26 Siemens Ag Method of positioning control drive in common rail fuel injector for motor vehicle internal combustion engine
DE10055644A1 (en) * 2000-11-10 2002-05-23 Siemens Ag Procedure, for adjusting discharge control of fuel injector, consists of measuring spacing between two defined locations and selecting valve piston to suit.
JP3928362B2 (en) * 2001-02-14 2007-06-13 株式会社デンソー Structure to improve seal surface pressure of fluid transfer device
US6629650B2 (en) * 2001-07-10 2003-10-07 Delphi Technologies, Inc. Fuel injector with integral damper

Also Published As

Publication number Publication date
EP1518050B1 (en) 2011-10-05
WO2004005704A1 (en) 2004-01-15
WO2004005699A1 (en) 2004-01-15
EP1518050A1 (en) 2005-03-30
EP1530680A1 (en) 2005-05-18

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