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EP1567765B1 - Injection valve - Google Patents

Injection valve Download PDF

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Publication number
EP1567765B1
EP1567765B1 EP03799426A EP03799426A EP1567765B1 EP 1567765 B1 EP1567765 B1 EP 1567765B1 EP 03799426 A EP03799426 A EP 03799426A EP 03799426 A EP03799426 A EP 03799426A EP 1567765 B1 EP1567765 B1 EP 1567765B1
Authority
EP
European Patent Office
Prior art keywords
throttle
nozzle
valve
module
injection valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03799426A
Other languages
German (de)
French (fr)
Other versions
EP1567765A1 (en
Inventor
Edgar Schneider
Thomas Koeppel
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1567765A1 publication Critical patent/EP1567765A1/en
Application granted granted Critical
Publication of EP1567765B1 publication Critical patent/EP1567765B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to an injection valve with a valve control module and a nozzle module according to the closer defined in the preamble of claim 1, such. shown in DE 101 39 622.
  • Such injectors are well known in practice and are used in particular in conjunction with common rail injection systems for diesel internal combustion engines.
  • a known from the art injection valve of the aforementioned type has a nozzle body of a nozzle module in which a nozzle needle is guided axially displaceable for opening and closing of the injection valve.
  • the nozzle body is provided with a plurality of injection openings, which can be controlled by means of the axially displaceable nozzle needle.
  • the injection valve is designed with a valve control module which has a module housing and a piezoelectric actuator module arranged thereon, which are operatively connected to the nozzle module via a valve control chamber in a manner known per se.
  • the piezoelectric actuator module is adjoined by a valve member arrangement, via which a travel of the piezoelectric actuator module is transferred to a valve closing member.
  • the valve member arrangement has a first piston, a so-called actuating piston, and a second piston, a so-called actuating piston, between which a hydraulic transmission device or a hydraulic coupler is arranged.
  • the hydraulic coupler also serves to compensate for axial length differences caused by temperature differences.
  • the nozzle needle is actuated by means of the valve control module via pressure changes in the so-called valve control chamber, wherein the pressure changes in the valve control chamber lead to an axial displacement of the nozzle needle, which in turn are released or closed to the combustion chamber of the engine leading injection openings of the nozzle body.
  • the pressure in the valve control chamber is set via two throttles opening into the valve control chamber, wherein an outlet throttle in a throttle plate and an inlet throttle is formed in a valve control space limiting and the nozzle needle enclosing sleeve.
  • Object of the present invention is therefore to provide an injection valve that is simple and inexpensive to produce.
  • a tuning required for the desired operation of the injector between the opening pressure of the injector module and the relationship between the throttling effects of the two throttles of the valve control chamber is determined by measuring the opening pressure in a measuring device and the defined pair of a component, i. throttle plate, performed in a simple manner.
  • Such throttle plates or throttle disks which are designed simultaneously with the inlet throttle and the outlet throttle for the valve control chamber, are advantageously produced in a contiguous production section.
  • an injection valve according to the invention over known from practice injectors has the advantage on that a vote is made with respect to the diameter ratio between the diameter of the inlet throttle and the diameter of the outlet throttle with only a single component.
  • the arrangement of the inlet throttle in the elevation of the throttle plate compared to a known from practice injection valve has no significant change in the position of the inlet throttle result, so that a known structural design of an injection valve executed only with an inventive Throttle plate and must be provided with an adapted to the throttle plate according to the invention intermediate element to obtain an injection valve according to the invention.
  • FIG. 1 shows an injection valve 1 with a valve control module 2 and a nozzle module 3.
  • the valve control module 2 is formed with an actuator module 4 only partially shown, wherein the actuator module 4 is a piezoelectric actuator unit.
  • a valve member assembly 5 which has an actuating piston 6 and an actuating piston 7, wherein between these two pistons 6, 7 acting as a hydraulic coupler or hydraulic ratio and as a compensation element of temperature-induced variations in length of the injection valve 1 hydraulic chamber 8 is provided.
  • the injection valve 1 is designed with a high-pressure region or a high-pressure connection 9, via which a channel 11 extending in components 10A, 10B of the valve control module 2 is supplied with fuel under common-rail high pressure, which is supplied to the nozzle module 3, wherein the Common rail pressure can take up to 1.6 kbar.
  • the injection valve 1 is presently provided in a conventional manner with a pressure limiting valve, not shown, via which a system pressure of a low pressure region 30 of the injection valve 1 is set.
  • the system pressure of the injection valve 1 is preferably less than 30 bar, wherein the height of the system pressure in each case depending on the present application is set to a required and on the operation of the injector positively acting value via the pressure relief valve.
  • the nozzle module 3 is designed with a nozzle needle 12 which is arranged axially displaceably in a nozzle body 13.
  • the nozzle body 13 rests against a throttle plate 14 of the valve control module 2 as shown in FIG. 1 and is firmly connected to the valve control module 2 via a nozzle clamping nut 15.
  • the nozzle needle 12 acts at its end facing away from the valve control module 2 with a valve seat 16 of the nozzle body 13 such that when a lifting of the nozzle needle 12 of the valve seat 16 injection openings 17 of the nozzle body 13 are released and an injection of fuel into a combustion chamber of an internal combustion engine ,
  • the nozzle needle 12 is moved in the nozzle body 13 against a force acting on the nozzle needle 12 in the closing direction of the nozzle needle 12 spring force of a spring 18 of the valve seat 16 in the direction of the valve control module 2 and the throttle plate 14.
  • the spring 18 is supported with its end facing away from the valve control module 2 via a disc 19 on a shoulder 20 of the nozzle needle 12 from. At its end facing the valve control module 2, the spring 18 bears against an intermediate element or a so-called spring plate 21, which in turn is supported on the throttle plate 14.
  • the behavior of the spring 18 can be influenced depending on the thickness of the disk 19, so that during the assembly of the injection valve 1, a defined selection of a plurality of classified classified discs 19 can be made to compensate for manufacturing tolerances.
  • the nozzle needle 12, the spring plate 21 and the throttle plate 14 define a valve control chamber 22, in which present in each case an inlet throttle 23 and an outlet throttle 24 open, both of which are arranged in the throttle plate 14.
  • FIG. 2 shows the region X of the injection valve 1 marked in FIG. 1 in an enlarged view.
  • the throttle plate 14 on its nozzle module 3 side facing a closed circumferential and an interior 25 bounding survey 26 which defines the valve control chamber 22 together with the spring plate 21 and an end portion 12A of the nozzle needle 12.
  • the survey is in the present case designed as an annular collar 26 which rises above a nozzle module 3 facing the end face 27 of the throttle plate 14 in the direction of the spring 18.
  • the inlet throttle 23 is disposed in the annular collar 26, whereby the high pressure region 9 of the injection valve 1, which surrounds the spring plate 21, is connected to the valve control chamber 22 via the inlet throttle 23. Furthermore, the outlet throttle 24 branches off from the valve control chamber 22 or from the interior 25 of the annular collar 26 in the direction of the low-pressure region 30 of the injection valve 1.
  • a minimum distance of a center line 44 of the inlet throttle 23 in the annular collar 26 from the end face 27 of the throttle plate 14 should not be less than 2 mm in order to provide sufficient space for an electrode guide during erosion for introducing the inlet throttle 23 in the annular collar 26 ,
  • the size of the diameter of the inlet throttle 23 is preferably in a range of 0.15 to 0.25 mm, wherein the diameter of the inlet throttle in the present case is 0.2 mm.
  • a the spring plate 21 facing end face 28 of the annular collar 26 is designed conically with respect to a throttle plate 14 facing surface 29 of the spring plate 21 in cross-section such that upon contact of the spring plate 21 on the annular collar 26 between these two components is a line contact, which for a seal of the valve control chamber 21 with respect to the high-pressure region 8 is particularly advantageous.
  • the system of the spring plate 21 on the annular collar 26 is effected by the spring 18, which presses the spring plate 21 due to their biased mounting position against the annular collar 26.
  • the end portion 12A of the nozzle needle 12, which is axially displaceably guided in a guide 41 of the spring plate 21, is designed with a smaller diameter than a region of the nozzle needle 12 which lies outside of the spring plate and is surrounded by the spring 18.
  • This gradation of the nozzle needle 12 on the side facing away from the throttle plate 14 of the spring plate 21 designed a paragraph 32, the Hubwegbegrenzung for the nozzle needle 12 during a movement the nozzle needle 12 in the opening direction of the nozzle module 3 and the injection valve 1 represents.
  • a recess 33 is formed in the end face 27 of the throttle plate 14, which is provided, inter alia, that the end face 27 of the throttle plate 14 with a grinding tool in the area near the annular collar 26 can be edited.
  • the valve member assembly 5 is controlled via the actuator module 4, which is arranged on the valve control chamber and combustion chamber side facing away from the valve member assembly 5.
  • the piezoelectric actuator of the Aktormodules 4, not shown, is constructed in a conventional manner of several ceramic layers and has on its valve member assembly 5 side facing an actuator head 42 and on its valve member assembly 5 side facing away from a non-illustrated Actuator foot on, which is connected to a Wall of a valve housing of the injection valve 1 is supported.
  • a control chamber 34 of the injection valve 1 is separated from the low-pressure region 30.
  • a valve element 35 of a control valve 36 is arranged, which sealingly abuts when not energized actuator module 4 to a first control valve seat 37 which is formed in the component 10A of the valve control module 2.
  • the connection between the control chamber 34 and the valve control chamber 22 via the outlet throttle 24 is opened, since the valve element 35 is pressed by a spring device and prevailing in the control chamber 34 pressure against the first control valve seat 37.
  • the valve element 35, the piezoelectric actuator is not energized and the injection valve 1 is closed by contact of the nozzle needle 12 to the valve seat 16 of the nozzle body 13.
  • the actuator module 4 or its piezoelectric ceramic is energized, the length of the piezoelectric ceramic is increased due to the piezoelectric effect. This elongation is transmitted from the valve member assembly in a conventional manner to the valve member 35, so that the valve element 35 is lifted from the first control valve seat 37 and in the direction of a second control valve seat 38, on the control chamber 34 side facing the Throttle plate 14 is formed, axially displaced.
  • the high-pressure region 9 is connected to the low-pressure region 30 via the valve control chamber 22 and the control chamber 34, and the pressure of the valve control chamber 22 is reduced via the outlet throttle 24 in the direction of the low-pressure region 30. Due to the pressure and the area ratios in the nozzle module 3, the nozzle needle 12 lifts off from the valve seat 16 of the nozzle body 13.
  • valve member 35 is sealingly applied either to the first control valve seat 37 or the second control valve seat 38, so that the connection between the valve control chamber 22 and the low-pressure region 30 is closed.
  • the energization of the actuator module 4 is interrupted; whereby the elongation of the piezoelectric ceramic of the Aktormodules regresses.
  • This is an axial adjustment of the valve member assembly 5 in the direction of the Aktormodules 4 accompanied and the valve member 35 is due to a force acting in the direction of the first control valve seat 37 on the valve element 35 spring force of a spring element 43 and the pressure of the control chamber 34 in turn sealingly against the first control valve seat 37 pressed.
  • the connection between the valve control chamber 22 and the low pressure region 30 is closed, so that the pressure in the valve control chamber 22 via the inlet throttle 23 builds up, which leads in the manner described above to a closing of the injection valve 1.
  • the closing of the injection valve 1 by contact of the valve member 35 to the first control valve seat 37 is preferably used when an injection phase is completed in a combustion chamber of an internal combustion engine and preferably no further injections follow in this injection phase.
  • the closing of the injection valve 1 by the contact of the valve member 35 to the second control valve seat 37 is preferred during an injection phase, which is composed of a plurality of short-term successive injections.
  • the nozzle needle 12 is longitudinally movably guided in a guide 40 of the nozzle body 13 and in the guide 41 of the spring plate 21, wherein the two guides 40 and 41 are matched to the axial mobility of the nozzle needle 12 by a possible malposition of the nozzle needle 12, which would lead to increased frictional forces between the nozzle needle 12 and the nozzle body 13 and the spring plate 21, to avoid.
  • the guide 41 of the spring plate 21 is designed to be relatively short in the axial direction of the injection valve 1, resulting in a cost advantage in the production compared to known from practice sleeve-like design and formed with longer guide areas components.
  • the throttle plate 14 with the inlet throttle 23 and the outlet throttle 24 represents a prefabricated classified disc, which is designed with a defined diameter ratio between a diameter of the inlet throttle 23 and a diameter of the outlet throttle 24, the proper functioning of the Injector 1 ensures.
  • the so-called opening pressure represents that pressure value in the valve control chamber 22 when it is open Control valve 36, in which the nozzle needle 12 lifts from the valve seat 16 of the nozzle body 13.
  • the injection valve according to the invention it is thus possible to use a determined in a special measuring apparatus opening pressure of the nozzle module 3 and the injection valve 1 to a throttle plate with a required for proper operation of the injection valve 1 diameter ratio between a diameter of the inlet throttle and a Diameter of the outlet throttle or a ratio between the throttle effects of the inlet throttle 23 and the outlet throttle 24 to select. Due to manufacturing tolerances, this diameter ratio or ratio between the throttling effects of the two throttles is different from nozzle module to nozzle module. Therefore, classified in an assembly process classified throttle disks with different diameter ratios and paired depending on the opening pressure of a nozzle module.
  • throttle plates are simple and inexpensive to produce, since the inlet throttle and the outlet throttle are integrated into a workpiece or a single component. In addition, the tuning of an injection valve during assembly is considerably simplified.
  • an injection valve can be adjusted, for example, via the pairing of throttle plates whose inlet throttles each have a function of the determined opening pressure selected and suitable for proper operation of the injection valve Have flow.
  • the diameter of the outlet throttle is in each case adapted to the diameter of the inlet throttle, that the diameter ratio of the throttles is constant for all throttle plates zuzupodenden.
  • the operation of the injectors is adjusted via throttle plates with varying diameter ratios.
  • the diameter ratio of the classified orifice plates is varied either by changing the diameter of the inlet throttle, by changing the diameter of the outlet throttle or by changing the diameter of the inlet throttle and the outlet throttle.
  • a minimum distance of the center line of the inlet throttle 23 in the annular collar 26 from the end face 27 of the throttle plate 14 should not be less than 2 mm in order to provide sufficient space for an electrode guide during erosion.
  • the diameter of the inlet throttle is in a range of 0.15 to 0.25 mm and in the present case preferably has a diameter of 0.2 mm.
  • the elevation of the throttle plate for the radial adjustment of the valve control module with respect to the nozzle module engages in a form-fitting manner at least in sections into a device of the nozzle module.

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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

The invention concerns an injection valve (1) comprising a valve-control module (2) and an injector module (3) which is connected to said valve-control module and includes an injector needle valve (12) axially mobile in an injector body (13) The valve-control module (2) is adjacent the injector module (3) with a throttle plate (14). An intermediate element is located in the zone of one end of the injector needle valve (12) facing the throttle plate (14). Said intermediate element is compressed on the throttle plate (14) by a spring (18) arranged between the intermediate element (21) and the injector needle valve (12) and said throttle plate biases the injector needle valve (12) in the closure direction with axial force. The inventive injection valve further comprises at least one outlet throttle (24) in the throttle plate (14) and at least one intake throttle (23) connected to a high pressure zone (9), said throttles emerging into a valve-control chamber (22). The throttle plate has on its side facing the injector module (3) a closed projecting portion (26) which defines an inner chamber (25), constituting a delimitation of the valve-control chamber (22) wherein is located the intake throttle (23).

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Einspritzventil mit einem Ventilsteuermodul und einem Düsenmodul gemäß der im Oberbegriff des Patentanspruches 1 näher definierten Art, wie z.B. in der DE 101 39 622 gezeigt.The invention relates to an injection valve with a valve control module and a nozzle module according to the closer defined in the preamble of claim 1, such. shown in DE 101 39 622.

Derartige Einspritzventile sind aus der Praxis hinlänglich bekannt und werden insbesondere in Verbindung mit Common-Rail-Einspritzsystemen für Dieselbrennkraftmaschinen eingesetzt.Such injectors are well known in practice and are used in particular in conjunction with common rail injection systems for diesel internal combustion engines.

Ein aus der Praxis bekanntes Einspritzventil der einleitend genannten Art weist einen Düsenkörper eines Düsenmodules auf, in dem zum Öffnen und Schließen des Einspritzventils eine Düsennadel axial verschiebbar geführt ist. An seinem einem Brennraum der Brennkraftmaschine zugewandten Ende ist der Düsenkörper mit mehreren Einspritzöffnungen versehen, die mittels der axial verschiebbaren Düsennadel ansteuerbar sind. Zusätzlich ist das Einspritzventil mit einem Ventilsteuermodul ausgeführt, welches ein Modulgehäuse und ein daran angeordnetes piezoelektrisches Aktormodul aufweist, die mit dem Düsenmodul über einen Ventilsteuerraum in an sich bekannter Art und Weise wirkverbunden sind.A known from the art injection valve of the aforementioned type has a nozzle body of a nozzle module in which a nozzle needle is guided axially displaceable for opening and closing of the injection valve. At its end facing a combustion chamber of the internal combustion engine, the nozzle body is provided with a plurality of injection openings, which can be controlled by means of the axially displaceable nozzle needle. In addition, the injection valve is designed with a valve control module which has a module housing and a piezoelectric actuator module arranged thereon, which are operatively connected to the nozzle module via a valve control chamber in a manner known per se.

An das piezoelektrische Aktormodul schließt sich eine Ventilglied-Anordnung an, über welche ein Stellweg des piezoelektrischen Aktormodules auf ein Ventilschließglied übertragen wird. Die Ventilglied-Anordnung weist einen ersten Kolben, einen sogenannten Stellkolben, und einen zweiten Kolben, einen sogenannten Betätigungskolben, auf, zwischen welchen eine hydraulische Übersetzungseinrichtung bzw. ein hydraulischer Koppler angeordnet ist. Der hydraulische Koppler dient zugleich dem Ausgleich von axialen Längenunterschieden, die durch Temperaturunterschiede verursacht werden.The piezoelectric actuator module is adjoined by a valve member arrangement, via which a travel of the piezoelectric actuator module is transferred to a valve closing member. The valve member arrangement has a first piston, a so-called actuating piston, and a second piston, a so-called actuating piston, between which a hydraulic transmission device or a hydraulic coupler is arranged. The hydraulic coupler also serves to compensate for axial length differences caused by temperature differences.

Die Düsennadel wird mittels des Ventilsteuermodules über Druckänderungen in dem sogenannten Ventilsteuerraum angesteuert, wobei die Druckänderungen in dem Ventilsteuerraum zu einer axialen Verschiebung der Düsennadel führen, wodurch wiederum die zu dem Brennraum der Brennkraftmaschine führenden Einspritzöffnungen des Düsenkörpers freigegeben bzw. verschlossen werden.The nozzle needle is actuated by means of the valve control module via pressure changes in the so-called valve control chamber, wherein the pressure changes in the valve control chamber lead to an axial displacement of the nozzle needle, which in turn are released or closed to the combustion chamber of the engine leading injection openings of the nozzle body.

Der Druck in dem Ventilsteuerraum wird über zwei in den Ventilsteuerraum mündende Drosseln eingestellt, wobei eine Ablaufdrossel in einer Drosselplatte und eine Zulaufdrossel in einer den Ventilsteuerraum begrenzenden und die Düsennadel umschließenden Hülse ausgebildet ist.The pressure in the valve control chamber is set via two throttles opening into the valve control chamber, wherein an outlet throttle in a throttle plate and an inlet throttle is formed in a valve control space limiting and the nozzle needle enclosing sleeve.

Dabei ist jedoch von Nachteil, daß die für eine einwandfreie Funktionsweise des Einspritzventiles geforderten Toleranzbereiche, insbesondere bei der Abstimmung eines Durchmesserverhältnisses zwischen der Zulaufdrossel und der Ablaufdrossel in Abhängigkeit eines Öffnungsdruckes des Einspritzdruckes im Ventilsteuerraum, nur durch eine sehr aufwendige Prüfung sowie einen hohen fertigungstechnischen Aufwand, die einen großen technischen bzw. apparativen Aufwand erfordern, erreicht werden können.However, it is disadvantageous that the required for proper functioning of the injector tolerance ranges, especially when tuning a diameter ratio between the inlet throttle and the outlet throttle in response to an opening pressure of the injection pressure in the valve control room, only by a very complex test and a high manufacturing effort, which require a large technical or equipment expense, can be achieved.

Aufgabe der vorliegenden Erfindung ist es daher, ein Einspritzventil zu schaffen, das einfach und kostengünstig herstellbar ist.Object of the present invention is therefore to provide an injection valve that is simple and inexpensive to produce.

Erfindungsgemäß wird diese Aufgabe mit einem Einspritzventil gemäß den Merkmalen des Patentanspruches 1 gelöst.According to the invention this object is achieved with an injection valve according to the features of claim 1.

Vorteile der ErfindungAdvantages of the invention

Das Einspritzventil nach der Erfindung mit den Merkmalen nach dem Oberbegriff des Patentanspruches 1, bei welchem die Drosselplatte auf ihrer dem Düsenmodul zugewandten Seite eine in sich geschlossene, einen Innenraum begrenzende Erhebung aufweist, die eine Begrenzung für den Ventilsteuerraum darstellt und in der die Zulaufdrossel angeordnet ist, weist den Vorteil auf, daß die Ablaufdrossel und die Zulaufdrossel in ein einziges Bauteil, d.h. in die Drosselplatte integriert sind, was eine erhebliche Vereinfachung der Abstimmung des Durchmesserverhältnisses eines Durchmessers der Ablaufdrossel und eines Durchmessers der Zulaufdrossel in Abhängigkeit eines Öffnungsdrucks des Einspritzventils in dem Ventilsteuerraum zur Folge hat.The injection valve according to the invention with the features according to the preamble of claim 1, wherein the throttle plate on its side facing the nozzle module has a self-contained, an interior bounding elevation, which constitutes a boundary for the valve control chamber and in which the inlet throttle is arranged , Has the advantage that the outlet throttle and the inlet throttle in a single component, ie in the throttle plate are integrated, which has a considerable simplification of the vote of the diameter ratio of a diameter of the outlet throttle and a diameter of the inlet throttle in response to an opening pressure of the injection valve in the valve control chamber result.

Insbesondere besteht die Möglichkeit, in Bezug auf das Durchmesserverhältnis bzw. in Bezug auf das Verhältnis zwischen der Drosselwirkung der Ablaufdrossel und der Drosselwirkung der Zulaufdrossel klassifizierte Drosselplatten vorzuhalten und in Abhängigkeit eines empirisch bestimmten Öffnungsdruckes eines Düsenmoduls die jeweils "passende" Drosselplatte aus den klassifizierten Drosselplatten auszuwählen und diesem Düsenmodul zuzupaaren.In particular, it is possible, with respect to the diameter ratio or in relation to the ratio between the throttle effect of the outlet throttle and the throttling effect of the inlet throttle classified gerfassungsplatten and select depending on an empirically determined opening pressure of a nozzle module, the "matching" throttle plate from the classified throttle plates and to match this nozzle module.

Damit wird bei der Montage eines Einspritzventiles eine für die gewünschte Funktionsweise des Einspritzventils erforderliche Abstimmung zwischen dem Öffnungsdruck des Düsenmoduls und dem Verhältnis zwischen den Drosselwirkungen der beiden Drosseln des Ventilsteuerraumes über das Messen des Öffnungsdruckes in einer Meßvorrichtung und dem definierten Zupaaren eines Bauteiles, d.h. der Drosselplatte, auf einfache Art und Weise durchgeführt.Thus, when assembling an injector valve, a tuning required for the desired operation of the injector between the opening pressure of the injector module and the relationship between the throttling effects of the two throttles of the valve control chamber is determined by measuring the opening pressure in a measuring device and the defined pair of a component, i. throttle plate, performed in a simple manner.

Derartige Drosselplatten bzw. Drosselscheiben, die gleichzeitig mit der Zulaufdrossel und der Ablaufdrossel für den Ventilsteuerraum ausgeführt sind, werden vorteilhafterweise in einem zusammenhängenden Fertigungsabschnitt hergestellt.Such throttle plates or throttle disks, which are designed simultaneously with the inlet throttle and the outlet throttle for the valve control chamber, are advantageously produced in a contiguous production section.

Zusätzlich weist ein Einspritzventil nach der Erfindung gegenüber aus der Praxis bekannten Einspritzventilen den Vorteil auf, daß eine Abstimmung bezüglich des Durchmesserverhältnisses zwischen dem Durchmesser der Zulaufdrossel und dem Durchmesser der Ablaufdrossel mit nur einem einzigen Bauteil erfolgt.In addition, an injection valve according to the invention over known from practice injectors has the advantage on that a vote is made with respect to the diameter ratio between the diameter of the inlet throttle and the diameter of the outlet throttle with only a single component.

Darüber hinaus ist von Vorteil, daß die Anordnung der Zulaufdrossel im Bereich der Erhebung der Drosselplatte im Vergleich zu einem aus der Praxis bekannten Einspritzventil keine wesentliche Veränderung der Position der Zulaufdrossel zur Folge hat, so daß eine bekannte konstruktive Ausführung eines Einspritzventiles nur mit einer erfindungsgemäß ausgeführten Drosselplatte und mit einem an die erfindungsgemäße Drosselplatte angepaßten Zwischenelement versehen werden muß, um ein Einspritzventil nach der Erfindung zu erhalten.Moreover, it is advantageous that the arrangement of the inlet throttle in the elevation of the throttle plate compared to a known from practice injection valve has no significant change in the position of the inlet throttle result, so that a known structural design of an injection valve executed only with an inventive Throttle plate and must be provided with an adapted to the throttle plate according to the invention intermediate element to obtain an injection valve according to the invention.

Weitere Vorteile und vorteilhafte Weiterbildungen des Gegenstandes nach der Erfindung ergeben sich aus der Beschreibung, der Zeichnung und den Patentansprüchen.Further advantages and advantageous developments of the subject matter of the invention will become apparent from the description, the drawings and the claims.

Zeichnungdrawing

In der Zeichnung ist ein Ausführungsbeispiel des Einspritzventiles nach der Erfindung schematisch vereinfacht dargestellt, welches in der nachfolgenden Beschreibung näher erläutert wird. Es zeigen

  • Figur 1 eine schematisierte Teildarstellung eines Einspritzventiles im Längsschnitt, und
  • Figur 2 einen vergrößert dargestellten Ausschnitt X des Einspritzventiles gemäß Figur 1.
In the drawing, an embodiment of the injection valve according to the invention is shown schematically simplified, which will be explained in more detail in the following description. Show it
  • Figure 1 is a schematic partial representation of an injection valve in longitudinal section, and
  • FIG. 2 shows an enlarged section X of the injection valve according to FIG. 1.

Beschreibung der AusführungsbeispielesDescription of the embodiment

In Figur 1 ist ein Einspritzventil 1 mit einem Ventilsteuermodul 2 und einem Düsenmodul 3 dargestellt. Das Ventilsteuermodul 2 ist mit einem nur teilweise dargestellten Aktormodul 4 ausgebildet, wobei das Aktormodul 4 eine piezoelektrische Aktuator-Einheit darstellt. An das Aktormodul 4 schließt sich eine Ventilglied-Anordnung 5 an, welche einen Stellkolben 6 und einen Betätigungskolben 7 aufweist, wobei zwischen diesen beiden Kolben 6, 7 eine als hydraulischer Koppler bzw. hydraulische Übersetzung und als Ausgleichselement von temperaturbedingten Längenschwankungen des Einspritzventiles 1 wirkende Hydraulikkammer 8 vorgesehen ist.FIG. 1 shows an injection valve 1 with a valve control module 2 and a nozzle module 3. The valve control module 2 is formed with an actuator module 4 only partially shown, wherein the actuator module 4 is a piezoelectric actuator unit. To the actuator module 4 is followed by a valve member assembly 5, which has an actuating piston 6 and an actuating piston 7, wherein between these two pistons 6, 7 acting as a hydraulic coupler or hydraulic ratio and as a compensation element of temperature-induced variations in length of the injection valve 1 hydraulic chamber 8 is provided.

Weiter ist das Einspritzventil 1 mit einem Hochdruckbereich bzw. einem Hochdruckanschluß 9 ausgeführt, über den ein in Bauteilen 10A, 10B des Ventilsteuermodules 2 verlaufender Kanal 11 mit unter Common-Rail-Hochdruck stehendem Kraftstoff gespeist wird, der dem Düsenmodul 3 zugeführt wird, wobei der Common-Rail-Druck bis zu 1,6 kbar annehmen kann.Furthermore, the injection valve 1 is designed with a high-pressure region or a high-pressure connection 9, via which a channel 11 extending in components 10A, 10B of the valve control module 2 is supplied with fuel under common-rail high pressure, which is supplied to the nozzle module 3, wherein the Common rail pressure can take up to 1.6 kbar.

Das Einspritzventil 1 ist vorliegend in an sich bekannter Weise mit einem nicht näher dargestellten Druckbegrenzungsventil versehen, über welches ein Systemdruck eines Niederdruckbereiches 30 des Einspritzventiles 1 eingestellt wird. Der Systemdruck des Einspritzventiles 1 ist vorzugsweise kleiner als 30 bar, wobei die Höhe des Systemdruckes jeweils in Abhängigkeit des vorliegenden Anwendungsfalles über das Druckbegrenzungsventil auf einen erforderlichen und sich auf die Funktionsweise des Einspritzventiles positiv auswirkenden Wert eingestellt wird.The injection valve 1 is presently provided in a conventional manner with a pressure limiting valve, not shown, via which a system pressure of a low pressure region 30 of the injection valve 1 is set. The system pressure of the injection valve 1 is preferably less than 30 bar, wherein the height of the system pressure in each case depending on the present application is set to a required and on the operation of the injector positively acting value via the pressure relief valve.

Das Düsenmodul 3 ist mit einer Düsennadel 12 ausgeführt, die in einem Düsenkörper 13 axial verschiebbar angeordnet ist. Der Düsenkörper 13 liegt gemäß der Darstellung in Figur 1 an einer Drosselplatte 14 des Ventilsteuermodules 2 an und ist über eine Düsenspannmutter 15 fest mit dem Ventilsteuermodul 2 verbunden.The nozzle module 3 is designed with a nozzle needle 12 which is arranged axially displaceably in a nozzle body 13. The nozzle body 13 rests against a throttle plate 14 of the valve control module 2 as shown in FIG. 1 and is firmly connected to the valve control module 2 via a nozzle clamping nut 15.

Die Düsennadel 12 wirkt an ihrem dem Ventilsteuermodul 2 abgewandten Ende mit einem Ventilsitz 16 des Düsenkörpers 13 derart zusammen, daß bei einem Abheben der Düsennadel 12 von dem Ventilsitz 16 Einspritzöffnungen 17 des Düsenkörpers 13 freigegeben werden und eine Einspritzung von Kraftstoff in einen Brennraum einer Brennkraftmaschine erfolgt.The nozzle needle 12 acts at its end facing away from the valve control module 2 with a valve seat 16 of the nozzle body 13 such that when a lifting of the nozzle needle 12 of the valve seat 16 injection openings 17 of the nozzle body 13 are released and an injection of fuel into a combustion chamber of an internal combustion engine ,

Beim Einspritzvorgang wird die Düsennadel 12 in dem Düsenkörper 13 entgegen einer auf die Düsennadel 12 in Schließrichtung der Düsennadel 12 wirkenden Federkraft einer Feder 18 von dem Ventilsitz 16 in Richtung des Ventilsteuermodules 2 bzw. der Drosselplatte 14 bewegt.During the injection process, the nozzle needle 12 is moved in the nozzle body 13 against a force acting on the nozzle needle 12 in the closing direction of the nozzle needle 12 spring force of a spring 18 of the valve seat 16 in the direction of the valve control module 2 and the throttle plate 14.

Die Feder 18 stützt sich mit ihrem dem Ventilsteuermodul 2 abgewandten Ende über eine Scheibe 19 an einem Absatz 20 der Düsennadel 12 ab. An ihrem dem Ventilsteuermodul 2 zugewandten Ende liegt die Feder 18 an einem Zwischenelement bzw. einem sogenannten Federteller 21 an, welcher sich wiederum an der Drosselplatte 14 abstützt. Das Verhalten der Feder 18 ist in Abhängigkeit der Dicke der Scheibe 19 beeinflußbar, so daß während der Montage des Einspritzventils 1 eine definierte Auswahl aus mehreren vorgehaltenen klassifizierten Scheiben 19 zum Ausgleich von Fertigungstoleranzen getroffen werden kann.The spring 18 is supported with its end facing away from the valve control module 2 via a disc 19 on a shoulder 20 of the nozzle needle 12 from. At its end facing the valve control module 2, the spring 18 bears against an intermediate element or a so-called spring plate 21, which in turn is supported on the throttle plate 14. The behavior of the spring 18 can be influenced depending on the thickness of the disk 19, so that during the assembly of the injection valve 1, a defined selection of a plurality of classified classified discs 19 can be made to compensate for manufacturing tolerances.

Die Düsennadel 12, der Federteller 21 und die Drosselplatte 14 begrenzen einen Ventilsteuerraum 22, in welchen vorliegend jeweils eine Zulaufdrossel 23 und eine Ablaufdrossel 24 münden, die beide in der Drosselplatte 14 angeordnet sind.The nozzle needle 12, the spring plate 21 and the throttle plate 14 define a valve control chamber 22, in which present in each case an inlet throttle 23 and an outlet throttle 24 open, both of which are arranged in the throttle plate 14.

In Figur 2 ist der in Figur 1 gekennzeichnete Bereich X des Einspritzventiles 1 in vergrößerter Ansicht gezeigt. In dem Bereich X weist die Drosselplatte 14 auf ihrer dem Düsenmodul 3 zugewandten Seite eine geschlossen umlaufende und einen Innenraum 25 begrenzende Erhebung 26 auf, die gemeinsam mit dem Federteller 21 und einem Endbereich 12A der Düsennadel 12 den Ventilsteuerraum 22 begrenzt. Die Erhebung ist vorliegend als ein Ringbund 26 ausgeführt, der sich über eine dem Düsenmodul 3 zugewandte Stirnfläche 27 der Drosselplatte 14 in Richtung der Feder 18 erhebt.FIG. 2 shows the region X of the injection valve 1 marked in FIG. 1 in an enlarged view. In the region X, the throttle plate 14 on its nozzle module 3 side facing a closed circumferential and an interior 25 bounding survey 26 which defines the valve control chamber 22 together with the spring plate 21 and an end portion 12A of the nozzle needle 12. The survey is in the present case designed as an annular collar 26 which rises above a nozzle module 3 facing the end face 27 of the throttle plate 14 in the direction of the spring 18.

In dem in Figur 2 dargestellten Schnitt ist die Zulaufdrossel 23 in dem Ringbund 26 angeordnet, wodurch der Hochdruckbereich 9 des Einspritzventils 1, der den Federteller 21 umgibt, mit dem Ventilsteuerraum 22 über die Zulaufdrossel 23 verbunden ist. Des weiteren zweigt von dem Ventilsteuerraum 22 bzw. von dem Innenraum 25 des Ringbundes 26 die Ablaufdrossel 24 in Richtung des Niederdruckbereiches 30 des Einspritzventils 1 ab.In the section shown in Figure 2, the inlet throttle 23 is disposed in the annular collar 26, whereby the high pressure region 9 of the injection valve 1, which surrounds the spring plate 21, is connected to the valve control chamber 22 via the inlet throttle 23. Furthermore, the outlet throttle 24 branches off from the valve control chamber 22 or from the interior 25 of the annular collar 26 in the direction of the low-pressure region 30 of the injection valve 1.

Ein minimaler Abstand einer Mittellinie 44 der Zulaufdrossel 23 in dem Ringbund 26 von der Stirnseite 27 der Drosselplatte 14 sollte nicht kleiner als 2 mm sein, um einen ausreichenden Platzbedarf für eine Elektrodenführung beim Erodieren zum Einbringen der Zulaufdrossel 23 in dem Ringbund 26 zur Verfügung zu stellen. Die Größe des Durchmessers der Zulaufdrossel 23 liegt vorzugsweise in einem Bereich von 0,15 bis 0,25 mm, wobei der Durchmesser der Zulaufdrossel vorliegend 0,2 mm beträgt.A minimum distance of a center line 44 of the inlet throttle 23 in the annular collar 26 from the end face 27 of the throttle plate 14 should not be less than 2 mm in order to provide sufficient space for an electrode guide during erosion for introducing the inlet throttle 23 in the annular collar 26 , The size of the diameter of the inlet throttle 23 is preferably in a range of 0.15 to 0.25 mm, wherein the diameter of the inlet throttle in the present case is 0.2 mm.

Eine dem Federteller 21 zugewandte Stirnfläche 28 des Ringbundes 26 ist in bezug auf eine der Drosselplatte 14 zugewandte Fläche 29 des Federtellers 21 im Querschnitt derart konisch ausgeführt, daß bei Anlage des Federtellers 21 an dem Ringbund 26 zwischen diesen beiden Bauteilen eine Linienberührung vorliegt, welche für eine Abdichtung des Ventilsteuerraumes 21 gegenüber dem Hochdruckbereich 8 besonders vorteilhaft ist. Die Anlage des Federtellers 21 an dem Ringbund 26 wird durch die Feder 18 bewirkt, die den Federteller 21 aufgrund ihrer vorgespannten Einbaulage gegen den Ringbund 26 drückt.A the spring plate 21 facing end face 28 of the annular collar 26 is designed conically with respect to a throttle plate 14 facing surface 29 of the spring plate 21 in cross-section such that upon contact of the spring plate 21 on the annular collar 26 between these two components is a line contact, which for a seal of the valve control chamber 21 with respect to the high-pressure region 8 is particularly advantageous. The system of the spring plate 21 on the annular collar 26 is effected by the spring 18, which presses the spring plate 21 due to their biased mounting position against the annular collar 26.

Der Endbereich 12A der Düsennadel 12, welcher axial verschieblich in einer Führung 41 des Federtellers 21 geführt ist, ist mit einem kleineren Durchmesser ausgeführt als ein Bereich der Düsennadel 12, welcher außerhalb des Federtellers liegt und von der Feder 18 umgeben ist. Diese Stufung der Düsennadel 12 auf der der Drosselplatte 14 abgewandten Seite des Federtellers 21 gestaltet einen Absatz 32, der eine Hubwegbegrenzung für die Düsennadel 12 bei einer Bewegung der Düsennadel 12 in Öffnungsrichtung des Düsenmodules 3 bzw. des Einspritzventiles 1 darstellt.The end portion 12A of the nozzle needle 12, which is axially displaceably guided in a guide 41 of the spring plate 21, is designed with a smaller diameter than a region of the nozzle needle 12 which lies outside of the spring plate and is surrounded by the spring 18. This gradation of the nozzle needle 12 on the side facing away from the throttle plate 14 of the spring plate 21 designed a paragraph 32, the Hubwegbegrenzung for the nozzle needle 12 during a movement the nozzle needle 12 in the opening direction of the nozzle module 3 and the injection valve 1 represents.

An einem Übergang zwischen der Stirnfläche 27 der Drosselplatte 14 und dem Ringbund 26 ist in der Stirnfläche 27 der Drosselplatte 14 eine Ausnehmung 33 ausgebildet, welche unter anderem dazu vorgesehen ist, daß die Stirnfläche 27 der Drosselplatte 14 mit einem Schleifwerkzeug auch im Bereich nahe des Ringbundes 26 bearbeitet werden kann.At a transition between the end face 27 of the throttle plate 14 and the annular collar 26, a recess 33 is formed in the end face 27 of the throttle plate 14, which is provided, inter alia, that the end face 27 of the throttle plate 14 with a grinding tool in the area near the annular collar 26 can be edited.

Nachfolgend wird die Funktionsweise des in Figur 1 dargestellten Ausführungsbeispiels eines Einspritzventils bei einer Verwendung bei einem Kraftstoffeinspritzventil für Brennkraftmaschinen von Kraftfahrzeugen beschrieben, wobei das Kraftstoffeinspritzventil bzw. das Einspritzventil 1 in der vorliegenden Ausführungsform als ein Common-Rail-Injektor ausgeführt ist.The operation of the embodiment of an injection valve shown in Figure 1 when used in a fuel injection valve for motor vehicles of motor vehicles is described below, wherein the fuel injection valve or the injection valve 1 is designed in the present embodiment as a common rail injector.

Zur Einstellung eines Einspritzbeginns, einer Einspritzdauer und einer Einspritzmenge über Kraftverhältnisse in dem Kraftstoffeinspritzventil 1 wird die Ventilglied-Anordnung 5 über das Aktormodul 4 angesteuert, welches auf der ventilsteuerraum- und brennraumabgewandten Seite der Ventilglied-Anordnung 5 angeordnet ist. Der nicht näher dargestellte piezoelektrische Aktuator des Aktormodules 4 ist in an sich bekannter Art und Weise aus mehreren keramischen Schichten aufgebaut und weist auf seiner der Ventilglied-Anordnung 5 zugewandten Seite einen Aktuatorkopf 42 und auf seiner der Ventilglied-Anordnung 5 abgewandten Seite einen nicht näher dargestellten Aktuatorfuß auf, der sich an einer Wand eines Ventilgehäuses des Einspritzventiles 1 abstützt.To set an injection start, an injection duration and an injection quantity via force ratios in the fuel injection valve 1, the valve member assembly 5 is controlled via the actuator module 4, which is arranged on the valve control chamber and combustion chamber side facing away from the valve member assembly 5. The piezoelectric actuator of the Aktormodules 4, not shown, is constructed in a conventional manner of several ceramic layers and has on its valve member assembly 5 side facing an actuator head 42 and on its valve member assembly 5 side facing away from a non-illustrated Actuator foot on, which is connected to a Wall of a valve housing of the injection valve 1 is supported.

In der in der Figur 1 dargestellten Position der Ventilglied-Anordnung 5 ist ein Steuerraum 34 des Einspritzventiles 1 von dem Niederdruckbereich 30 getrennt. In dem Steuerraum 34 ist ein Ventilelement 35 eines Steuerventiles 36 angeordnet, welches bei nicht bestromtem Aktormodul 4 an einem ersten Steuerventilsitz 37, der in dem Bauteil 10A des Ventilsteuermodules 2 ausgebildet ist, dichtend anliegt. Die Verbindung zwischen dem Steuerraum 34 und dem Ventilsteuerraum 22 über die Ablaufdrossel 24 ist geöffnet, da das Ventilelement 35 durch eine Federeinrichtung und den in dem Steuerraum 34 vorherrschenden Druck gegen den ersten Steuerventilsitz 37 gedrückt ist. In dieser Stellung des Ventilelementes 35 ist der piezoelektrische Aktuator nicht bestromt und das Einspritzventil 1 ist durch Anlage der Düsennadel 12 an dem Ventilsitz 16 des Düsenkörpers 13 geschlossen.In the position of the valve member arrangement 5 shown in FIG. 1, a control chamber 34 of the injection valve 1 is separated from the low-pressure region 30. In the control chamber 34, a valve element 35 of a control valve 36 is arranged, which sealingly abuts when not energized actuator module 4 to a first control valve seat 37 which is formed in the component 10A of the valve control module 2. The connection between the control chamber 34 and the valve control chamber 22 via the outlet throttle 24 is opened, since the valve element 35 is pressed by a spring device and prevailing in the control chamber 34 pressure against the first control valve seat 37. In this position, the valve element 35, the piezoelectric actuator is not energized and the injection valve 1 is closed by contact of the nozzle needle 12 to the valve seat 16 of the nozzle body 13.

Wird das Aktormodul 4 bzw. dessen piezoelektrische Keramik bestromt, wird die Länge der piezoelektrischen Keramik aufgrund des piezoelektrischen Effektes vergrößert. Diese Längung wird von der Ventilglied-Anordnung in an sich bekannter Art und Weise auf das Ventilelement 35 übertragen, so daß das Ventilelement 35 von dem ersten Steuerventilsitz 37 abgehoben wird und in Richtung eines zweiten Steuerventilsitzes 38, der an der dem Steuerraum 34 zugewandten Seite der Drosselplatte 14 ausgebildet ist, axial verschoben.If the actuator module 4 or its piezoelectric ceramic is energized, the length of the piezoelectric ceramic is increased due to the piezoelectric effect. This elongation is transmitted from the valve member assembly in a conventional manner to the valve member 35, so that the valve element 35 is lifted from the first control valve seat 37 and in the direction of a second control valve seat 38, on the control chamber 34 side facing the Throttle plate 14 is formed, axially displaced.

In dieser Position des Ventilelementes 35 ist der Hochdruckbereich 9 über den Ventilsteuerraum 22 und den Steuerraum 34 mit dem Niederdruckbereich 30 verbunden, und der Druck des Ventilsteuerraumes 22 wird über die Ablaufdrossel 24 in Richtung des Niederdruckbereiches 30 abgebaut. Aufgrund der Druck- sowie der Flächenverhältnisse in dem Düsenmodul 3 hebt die Düsennadel 12 von dem Ventilsitz 16 des Düsenkörpers 13 ab.In this position of the valve element 35, the high-pressure region 9 is connected to the low-pressure region 30 via the valve control chamber 22 and the control chamber 34, and the pressure of the valve control chamber 22 is reduced via the outlet throttle 24 in the direction of the low-pressure region 30. Due to the pressure and the area ratios in the nozzle module 3, the nozzle needle 12 lifts off from the valve seat 16 of the nozzle body 13.

Zum Schließen des Einspritzventiles 1 wird das Ventilelement 35 entweder an den ersten Steuerventilsitz 37 oder den zweiten Steuerventilsitz 38 dichtend angelegt, so daß die Verbindung zwischen dem Ventilsteuerraum 22 und dem Niederdruckbereich 30 geschlossen ist. Um das Ventilelement 35 dichtend an dem ersten Steuerventilsitz 37 anzulegen, wird die Bestromung des Aktormodules 4 unterbrochen; wodurch sich die Längung der piezoelektrischen Keramik des Aktormodules zurückbildet. Damit geht eine axiale Verstellung der Ventilglied-Anordnung 5 in Richtung des Aktormodules 4 einher und das Ventilelement 35 wird aufgrund einer in Richtung des ersten Steuerventilsitzes 37 auf das Ventilelement 35 wirkende Federkraft eines Federelementes 43 und dem Druck des Steuerraumes 34 wiederum dichtend an den ersten Steuerventilsitz 37 gedrückt.To close the injection valve 1, the valve member 35 is sealingly applied either to the first control valve seat 37 or the second control valve seat 38, so that the connection between the valve control chamber 22 and the low-pressure region 30 is closed. In order to apply the valve element 35 sealingly to the first control valve seat 37, the energization of the actuator module 4 is interrupted; whereby the elongation of the piezoelectric ceramic of the Aktormodules regresses. This is an axial adjustment of the valve member assembly 5 in the direction of the Aktormodules 4 accompanied and the valve member 35 is due to a force acting in the direction of the first control valve seat 37 on the valve element 35 spring force of a spring element 43 and the pressure of the control chamber 34 in turn sealingly against the first control valve seat 37 pressed.

In dieser Lage des Ventilelementes 35 ist die Verbindung zwischen dem Niederdruckbereich 30 und dem Ventilsteuerraum 22 unterbrochen bzw. geschlossen. Dadurch baut sich der Druck in dem Ventilsteuerraum 22 über die Zulaufdrossel 23 in Richtung des Drucks des Hochdruckbereiches 9 auf, wobei die Düsennadel 12 ab einem definierten Druckwert in dem Ventilsteuerraum 22 dichtend gegen den Ventilsitz 16 des Düsenkörpers 13 gedrückt wird und das Einspritzventil 1 bzw. dessen Einspritzöffnungen 17 verschlossen sind.In this position of the valve element 35, the connection between the low-pressure region 30 and the valve control chamber 22 is interrupted or closed. As a result, the pressure builds up in the valve control chamber 22 via the inlet throttle 23 in the direction of the pressure of the high pressure region 9, wherein the nozzle needle 12 from a defined pressure value in the Valve control chamber 22 is sealingly pressed against the valve seat 16 of the nozzle body 13 and the injection valve 1 and its injection openings 17 are closed.

Die zweite vorbeschriebene Position des Ventilelementes 35, welche zum Schließen des Einspritzventiles 1 führt, wird dadurch erreicht, daß eine Bestromung des Aktormodules 4 derart eingestellt wird, daß die Längung des Aktormodules 4 zu einer dichtenden Anlage des Ventilelementes 35 an dem zweiten Steuerventilsitz 38 führt und die Ablaufdrossel 24 von dem Ventilelement 35 verschlossen wird. Dadurch ist gleichzeitig die Verbindung zwischen dem Ventilsteuerraum 22 und dem Niederdruckbereich 30 geschlossen, so daß sich der Druck im Ventilsteuerraum 22 über die Zulaufdrossel 23 aufbaut, was in der vorbeschriebenen Art und Weise zu einem Schließen des Einspritzventiles 1 führt.The second prescribed position of the valve element 35, which leads to the closing of the injection valve 1, is achieved by energizing the Aktormodules 4 is set such that the elongation of the Aktormodules 4 leads to a sealing contact of the valve element 35 to the second control valve seat 38 and the outlet throttle 24 is closed by the valve element 35. As a result, at the same time the connection between the valve control chamber 22 and the low pressure region 30 is closed, so that the pressure in the valve control chamber 22 via the inlet throttle 23 builds up, which leads in the manner described above to a closing of the injection valve 1.

Das Schließen des Einspritzventiles 1 durch Anlage des Ventilgliedes 35 an dem ersten Steuerventilsitz 37 wird bevorzugt dann eingesetzt, wenn eine Einspritzphase in einen Brennraum einer Brennkraftmaschine abgeschlossen ist und vorzugsweise keine weiteren Einspritzungen in dieser Einspritzphase folgen.The closing of the injection valve 1 by contact of the valve member 35 to the first control valve seat 37 is preferably used when an injection phase is completed in a combustion chamber of an internal combustion engine and preferably no further injections follow in this injection phase.

Das Schließen des Einspritzventiles 1 durch die Anlage des Ventilgliedes 35 an dem zweiten Steuerventilsitz 37 wird während einer Einspritzphase, die sich aus mehreren kurzfristig aufeinanderfolgenden Einspritzungen zusammensetzt, bevorzugt. Dies resultiert aus der Tatsache, daß das Ventilglied 35 zum Öffnen des Einspritzventiles 1 nicht wie beim Abheben von dem ersten Steuerventilsitz 37 gegen den Hochdruck des Ventilsteuerraumes 22 bewegt werden muß, sondern daß ein Öffnen der Verbindung zwischen dem Ventilsteuerraum 22 und dem Steuerraum 34 bei einer Reduzierung der Bestromung des Aktormodules 4 durch den Hochdruck des Ventilsteuerraumes 22 und die Federkraft des Federelementes 43 erfolgt.The closing of the injection valve 1 by the contact of the valve member 35 to the second control valve seat 37 is preferred during an injection phase, which is composed of a plurality of short-term successive injections. This results from the fact that the valve member 35 for opening the injection valve 1 is not the same as when lifting from the first control valve seat 37 against the High pressure of the valve control chamber 22 must be moved, but that an opening of the connection between the valve control chamber 22 and the control chamber 34 is carried out at a reduction in the energization of the Aktormodules 4 by the high pressure of the valve control chamber 22 and the spring force of the spring element 43.

Die Düsennadel 12 ist in einer Führung 40 des Düsenkörpers 13 und in der Führung 41 des Federtellers 21 längs beweglich dichtend geführt, wobei die beiden Führungen 40 und 41 aufeinander abgestimmt sind, um die axiale Beweglichkeit der Düsennadel 12 durch eine eventuelle Fehlstellung der Düsennadel 12, die zu erhöhten Reibkräften zwischen der Düsennadel 12 und dem Düsenkörper 13 bzw. dem Federteller 21 führen würde, zu vermeiden. Insbesondere die Führung 41 des Federtellers 21 ist in axialer Richtung des Einspritzventiles 1 relativ kurz ausgeführt, wodurch sich ein Kostenvorteil in der Herstellung gegenüber aus der Praxis bekannten hülsenartig ausgeführten und mit längeren Führungsbereichen ausgebildeten Bauteilen ergibt.The nozzle needle 12 is longitudinally movably guided in a guide 40 of the nozzle body 13 and in the guide 41 of the spring plate 21, wherein the two guides 40 and 41 are matched to the axial mobility of the nozzle needle 12 by a possible malposition of the nozzle needle 12, which would lead to increased frictional forces between the nozzle needle 12 and the nozzle body 13 and the spring plate 21, to avoid. In particular, the guide 41 of the spring plate 21 is designed to be relatively short in the axial direction of the injection valve 1, resulting in a cost advantage in the production compared to known from practice sleeve-like design and formed with longer guide areas components.

Die Drosselplatte 14 mit der Zulaufdrossel 23 und der Ablaufdrossel 24 stellt eine vorgefertigte klassifizierte Scheibe dar, welche mit einem definierten Durchmesserverhältnis zwischen einem Durchmesser der Zulaufdrossel 23 und einem Durchmesser der Ablaufdrossel 24 ausgeführt ist, das für einen bestimmten Öffnungsdruck des Einspritzventiles 1 eine einwandfreie Funktionsweise des Einspritzventiles 1 gewährleistet. Der sogenannte Öffnungsdruck stellt dabei jenen Druckwert in dem Ventilsteuerraum 22 bei geöffnetem Steuerventil 36 dar, bei welchem die Düsennadel 12 von dem Ventilsitz 16 des Düsenkörpers 13 abhebt.The throttle plate 14 with the inlet throttle 23 and the outlet throttle 24 represents a prefabricated classified disc, which is designed with a defined diameter ratio between a diameter of the inlet throttle 23 and a diameter of the outlet throttle 24, the proper functioning of the Injector 1 ensures. The so-called opening pressure represents that pressure value in the valve control chamber 22 when it is open Control valve 36, in which the nozzle needle 12 lifts from the valve seat 16 of the nozzle body 13.

Bei dem Einspritzventil nach der Erfindung besteht somit die Möglichkeit, einen in einer speziellen Meßapparatur ermittelten Öffnungsdruck des Düsenmoduls 3 bzw. des Einspritzventils 1 zu verwenden, um eine Drosselplatte mit einem für eine einwandfreie Funktionsweise des Einspritzventiles 1 erforderlichen Durchmesserverhältnis zwischen einem Durchmesser der Zulaufdrossel und einem Durchmesser der Ablaufdrossel bzw. einem Verhältnis zwischen den Drosselwirkungen der Zulaufdrossel 23 und der Ablaufdrossel 24 auszuwählen. Aufgrund von Fertigungstoleranzen ist dieses Durchmesserverhältnis bzw. Verhältnis zwischen den Drosselwirkungen der beiden Drosseln von Düsenmodul zu Düsenmodul unterschiedlich. Deshalb werden in einem Montageprozeß klassifizierte Drosselscheiben mit unterschiedlichen Durchmesserverhältnissen vorgehalten und in Abhängigkeit des Öffnungsdruckes einem Düsenmodul zugepaart.In the injection valve according to the invention, it is thus possible to use a determined in a special measuring apparatus opening pressure of the nozzle module 3 and the injection valve 1 to a throttle plate with a required for proper operation of the injection valve 1 diameter ratio between a diameter of the inlet throttle and a Diameter of the outlet throttle or a ratio between the throttle effects of the inlet throttle 23 and the outlet throttle 24 to select. Due to manufacturing tolerances, this diameter ratio or ratio between the throttling effects of the two throttles is different from nozzle module to nozzle module. Therefore, classified in an assembly process classified throttle disks with different diameter ratios and paired depending on the opening pressure of a nozzle module.

Derartige Drosselplatten sind einfach und kostengünstig herstellbar, da die Zulaufdrossel und die Ablaufdrossel in ein Werkstück bzw. ein einziges Bauteil integriert sind. Zusätzlich ist dadurch die Abstimmung eines Einspritzventiles während der Montage erheblich vereinfacht.Such throttle plates are simple and inexpensive to produce, since the inlet throttle and the outlet throttle are integrated into a workpiece or a single component. In addition, the tuning of an injection valve during assembly is considerably simplified.

Die Funktionsweise eines Einspritzventiles kann beispielsweise über das Zupaaren von Drosselplatten eingestellt werden, deren Zulaufdrosseln jeweils einen in Abhängigkeit des ermittelten Öffnungsdruckes ausgewählten und für eine einwandfreie Funktionsweise des Einspritzventils geeigneten Durchfluß aufweisen. Der Durchmesser der Ablaufdrossel ist jeweils derart an den Durchmesser der Zulaufdrossel angepaßt, daß das Durchmesserverhältnis der Drosseln bei allen zuzupaarenden Drosselplatten konstant ist.The operation of an injection valve can be adjusted, for example, via the pairing of throttle plates whose inlet throttles each have a function of the determined opening pressure selected and suitable for proper operation of the injection valve Have flow. The diameter of the outlet throttle is in each case adapted to the diameter of the inlet throttle, that the diameter ratio of the throttles is constant for all throttle plates zuzupaarenden.

Ferner kann es selbstverständlich auch vorgesehen sein, daß die Funktionsweise der Einspritzventile über Drosselplatten mit variierenden Durchmesserverhältnissen eingestellt wird. Das Durchmesserverhältnis der klassifizierten Drosselscheiben wird entweder durch Veränderung des Durchmessers der Zulaufdrossel, durch Veränderung des Durchmessers der Ablaufdrossel oder durch Veränderung der Durchmesser der Zulaufdrossel und der Ablaufdrossel variiert.Furthermore, it may of course also be provided that the operation of the injectors is adjusted via throttle plates with varying diameter ratios. The diameter ratio of the classified orifice plates is varied either by changing the diameter of the inlet throttle, by changing the diameter of the outlet throttle or by changing the diameter of the inlet throttle and the outlet throttle.

Ein minimaler Abstand der Mittellinie der Zulaufdrossel 23 in dem Ringbund 26 von der Stirnseite 27 der Drosselplatte 14 sollte nicht kleiner als 2 mm sein, um einen ausreichenden Platzbedarf für eine Elektrodenführung beim Erodieren zur Verfügung zu stellen. Der Durchmesser der Zulaufdrossel liegt in einem Bereich von 0,15 bis 0,25 mm und weist vorliegend vorzugsweise einen Durchmesser von 0,2 mm auf.A minimum distance of the center line of the inlet throttle 23 in the annular collar 26 from the end face 27 of the throttle plate 14 should not be less than 2 mm in order to provide sufficient space for an electrode guide during erosion. The diameter of the inlet throttle is in a range of 0.15 to 0.25 mm and in the present case preferably has a diameter of 0.2 mm.

In einer weiteren von der vorliegend beschriebenen Ausführungsform abweichenden Ausgestaltung des Einspritzventiles ist es vorgesehen, daß die Erhebung der Drosselplatte zur radialen Justierung des Ventilsteuermodules gegenüber dem Düsenmodul wenigstens abschnittsweise in eine Einrichtung des Düsenmoduls formschlüssig eingreift. Dadurch besteht in vorteilhafterweise die Möglichkeit bei aus der Praxis bekannten Einspritzventilen zur Zentrierung des Ventilsteuermodules gegenüber dem Düsenmodul vorzugsweise eingesetzte Zentrierstifte im Bereich zwischen der Drosselplatte und dem Düsenkörper des Düsenmodules durch die Erhebung zu ersetzten, wodurch vorteilhafterweise die Teileanzahl eines Einspritzventiles reduziert wird, was wiederum zur Vereinfachung der Montage führt.In a further embodiment of the injection valve deviating from the embodiment described here, it is provided that the elevation of the throttle plate for the radial adjustment of the valve control module with respect to the nozzle module engages in a form-fitting manner at least in sections into a device of the nozzle module. As a result, it is advantageously possible to use injection valves known from practice for centering the valve control module with respect to the nozzle module Centering pins in the area between the throttle plate and the nozzle body of the nozzle module to be replaced by the survey, which advantageously the number of parts of an injection valve is reduced, which in turn leads to the simplification of assembly.

Claims (10)

  1. Injection valve (1), with a valve control module (2) and with a nozzle module (3) which adjoins the latter and has a nozzle needle (12) arranged axially displaceably in a nozzle body (13), the valve control module (2) being contiguous with a throttle plate (14) to the nozzle module (3), and, in the region of an end of the nozzle needle (12) which faces the throttle plate (14), an intermediate element (21) being provided, which is pressed, via a spring (18) arranged between the intermediate element (21) and the nozzle needle (12), against the throttle plate (14) which acts with an axial force upon the nozzle needle (12) in the closing direction, there being provided in the throttle plate (14) at least one outflow throttle (24) and at least one inflow throttle (23) which is connected to a high-pressure region (9), the said outflow throttle and inflow throttle issuing into a valve control space (22), characterized in that the throttle plate (14) has, on its side facing the nozzle module (3), an elevation (26) which is closed on itself and delimits an inner space (25) and which forms a boundary for the valve control space (22) and in which the inflow throttle (23) is arranged.
  2. Injection valve according to Claim 1, characterized in that the intermediate element (21) is designed as a spring plate which bears against the throttle plate (14) on that end face (28) of the elevation (26) which faces the nozzle module (3).
  3. Injection valve according to Claim 1 or 2, characterized in that the nozzle needle (12) of the nozzle module (3) is guided in a guide (41) of the intermediate element (21) and, in the event of an opening of the nozzle module (3), is displaced axially in the guide (41) of the intermediate element (21) in such a way that the nozzle needle (12) engages with its end (12A) facing the throttle plate (14) into an inner space (25) of the elevation (26).
  4. Injection valve according to one of Claims 1 to 3, characterized in that the nozzle needle (12) has, in the region of the intermediate element (21), a step (32) which, in the presence of a defined stroke travel of the nozzle needle (12) during an axial movement of the nozzle needle (12) in order to open the nozzle module (3), comes to bear against that side of the intermediate element (21) which faces away from the throttle plate (14).
  5. Injection valve according to one of Claims 1 to 4, characterized in that that end face (28) of the elevation (26) which faces the intermediate element (21) is designed conically in cross section in such a way that there is linear contact between the elevation (26) and the intermediate element (21).
  6. Injection valve according to one of Claims 1 to 5, characterized in that a washer (19) for setting a spring force of the spring (18) is provided between one end of the spring (18) which faces away from the throttle plate (14) and a step (20) of the nozzle needle (12).
  7. Injection valve according to one of Claims 1 to 6, characterized in that a recess (33) is provided in the throttle plate (14) at a transition between an end face (27) of the throttle plate (14) which faces the intermediate element (21) and the elevation (26).
  8. Injection valve according to one of Claims 3 to 7, characterized in that the guide (41) of the intermediate element (21) for the nozzle needle (12) is coordinated with a guide (40) of the nozzle body (13) of the nozzle module (3) for the nozzle needle (12).
  9. Injection valve according to one of Claims 1 to 8, characterized in that a ratio between a diameter of the outflow throttle (24) and a diameter of the inflow throttle (23) is set as a function of a pressure in the valve control space (22) at which the nozzle module (3) is open.
  10. Injection valve according to one of Claims 1 to 9, characterized in that the elevation (26) of the throttle plate (14) positively engages at least partially into a device of the nozzle module (3) for the radial adjustment of the control module (2) with respect to the nozzle module (3).
EP03799426A 2002-10-31 2003-08-11 Injection valve Expired - Lifetime EP1567765B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10250720A DE10250720A1 (en) 2002-10-31 2002-10-31 Injector
DE10250720 2002-10-31
PCT/DE2003/002704 WO2004040119A1 (en) 2002-10-31 2003-08-11 Injection valve

Publications (2)

Publication Number Publication Date
EP1567765A1 EP1567765A1 (en) 2005-08-31
EP1567765B1 true EP1567765B1 (en) 2006-10-04

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP03799426A Expired - Lifetime EP1567765B1 (en) 2002-10-31 2003-08-11 Injection valve

Country Status (6)

Country Link
US (1) US20060151637A1 (en)
EP (1) EP1567765B1 (en)
JP (1) JP2006504893A (en)
CN (1) CN1639456A (en)
DE (2) DE10250720A1 (en)
WO (1) WO2004040119A1 (en)

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Publication number Publication date
US20060151637A1 (en) 2006-07-13
DE10250720A1 (en) 2004-05-13
JP2006504893A (en) 2006-02-09
CN1639456A (en) 2005-07-13
DE50305301D1 (en) 2006-11-16
EP1567765A1 (en) 2005-08-31
WO2004040119A1 (en) 2004-05-13

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