EP1046809B1 - Fluid metering device - Google Patents

Fluid metering device Download PDF

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Publication number
EP1046809B1
EP1046809B1 EP00107401A EP00107401A EP1046809B1 EP 1046809 B1 EP1046809 B1 EP 1046809B1 EP 00107401 A EP00107401 A EP 00107401A EP 00107401 A EP00107401 A EP 00107401A EP 1046809 B1 EP1046809 B1 EP 1046809B1
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EP
European Patent Office
Prior art keywords
valve needle
metering device
metal bellows
fluid metering
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00107401A
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German (de)
French (fr)
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EP1046809A2 (en
EP1046809A3 (en
Inventor
Andreas Dr. Kappel
Bernhard Fischer
Bernhard Dr. Gottlieb
Randolf Dr. Mock
Eric Chemisky
Hans Prof. Meixner
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Siemens AG
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Siemens AG
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Publication of EP1046809A3 publication Critical patent/EP1046809A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M61/08—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 the valves opening in direction of fuel flow
    • 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
    • F02M63/0012—Valves
    • F02M63/0057—Means for avoiding fuel contact with valve actuator, e.g. isolating actuators by using bellows or diaphragms
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for

Definitions

  • the invention relates to a Fluiddosiervoriques with the an in-housing, pressurized Fluid, either a liquid or a gas, in predetermined Quantities can be dispensed or injected. It is passed through the housing a valve needle, the outside of the housing is mechanically operated on the one hand and on the other hand represents an element of a valve.
  • O-rings and membrane seals such as metal beads o. ⁇ . Can be used.
  • these have the disadvantage of a very high pressure-loaded surface, which has a corresponding force introduction into the valve needle result. If a pressure area of 1 mm 2 is considered at a one-sided overpressure of, for example, 300 bar, then a force of 30 N results.
  • the use of diaphragms as lead-through element of a valve needle by a pressurized chamber can therefore meet the requirements for high axial compliance at the same time do not satisfy sufficient compressive strength. A high compressive strength inevitably leads to a correspondingly dimensioned membrane thickness, which in turn requires a high axial rigidity.
  • valve needle feedthrough can be similar to diesel injectors also by a clearance of the needle in a cylindrical Housing bore done.
  • the disadvantage here is the unavoidable leakage, along the needle feedthrough, the one Return line into the tank or to the low pressure connection of the Fuel pump required. Due to the higher hydraulic Losses will also increase the overall efficiency of the engine reduced.
  • a fluid metering device with a metal bag as leadthrough element is known for example from the publications JP 07 158534 A, DE 591 559 A and DE 41 41 274 A.
  • the object of the invention is a fluid metering device to make such that a hermetically sealed Carrying out a valve needle by one with a lower Pressure-filled fluid-filled chamber is ensured, wherein a feedthrough element to be used is not essential exerts pressure-dependent forces on the valve needle.
  • the invention is based on the exact understanding the behavior of a pressurized metal bellows.
  • the metal bellows on the two-sided attachment to the outside be transmitted. It is on by high pressure differences Both sides of the metal bladder go out, with the higher Pressure inside or outside the metal bellows can be.
  • the basic insight is, in particular, that the wall of the metal bellows even at low axial spring constant at a pressurization only small force changes at the ends of a bellows fastened on both sides leads.
  • a particularly advantageous embodiment provides the radial Fixation of the valve needle by the firm connection of the metal bellows with the valve needle on the one hand and with the housing on the other hand.
  • In another embodiment of the invention provides the use a compression spring between the housing and valve needle for a reliable closing force acting on the valve.
  • the metal bellows may under certain circumstances partially rest on his leadership. A residual risk of a Buckling is thus reduced again.
  • metal bellows are achieved both with internal pressure as well as external pressure.
  • the dimensioning of the edge strength of the metal bellows in the area from 25 to 500 microns shows that small wall thickness at large pressures, such as 300 bar, are sufficient.
  • the metal bellows is advantageously fixed to the valve needle and connected to the housing.
  • joints For mounting the valve needle and the metal bellows in the housing, for example at a Injection valve with several nested ones Elements, joints must be freely accessible. This can advantageously by welded joints, For example, laser welding done.
  • the fluid metering device can be formed with valves be that open inward or outward.
  • the Construction of the metal bellows in relation to the rest Elements in particular for the impact-generating actuator is corresponding adapt.
  • the high-pressure injectors considered here are fuel-injected PFUEL operated up to, for example, 500 bar.
  • a stroke of the valve needle is extremely short and lies in the range from 10 to 100 ⁇ m.
  • the housing is divided into the chamber 13, which is connected by means of a conduit bore 7, over the the fluid is supplied under pressure.
  • Such a fluid metering device or a hydraulic valve for dosing the Fluids thus separates a high pressure room from a room for example, may have ambient pressure.
  • the implementation the valve needle 3 through the housing 1, in particular through the chamber 13 and the actuator chamber 14 represents the core of Invention.
  • a lead-through element is a metal bellows 17 used.
  • the high-pressure injector shown in FIG. 1 has the injector housing 1 a valve seat 2 on.
  • the valve seat 2 is in Basic state by the second end 23 of the valve needle 3 connected valve disc 4 kept closed.
  • injection nozzle is formed by the tensioned Compression spring 5 ensures that with the valve needle 3 via a snap ring 6 is connected.
  • the fuel supply takes place through the attached in the housing 1 bore 7th
  • the drive unit formed from a piezoelectric multilayer actuator (PMA) 8 in low voltage technology, combined with a Bourdon tube 9, a top plate 10 and a base plate 11.
  • PMA piezoelectric multilayer actuator
  • Die Bourdon tube 9 is so with the top plate 10 and the base plate 11th welded, that the PMA 8 under a mechanical compression bias stands.
  • the housing 1 and the base plate 1 are also as stiff as possible connected by a weld.
  • the gap 12 serves on the one hand for setting defined force relationships in the valve seat and on the other hand to catch small differences in the thermal length changes.
  • the injector components are made of materials with low thermal expansion coefficients or made of different materials, in terms of their thermal Linear expansion coefficients so matched are that the constancy of the gap height approximately is guaranteed.
  • the perforated plate 15 To carry out the valve needle 3 from the fuel chamber 13 in the pressureless actuator chamber 14 is the perforated plate 15, which is welded to an inner bore 16 of the housing 1. Likewise, the perforated plate 15 also worked out of the housing 1 be. Between the first end 22 of the valve needle 3 and the perforated plate 15 is the cylindrical metal bellows 17th welded, which hermetically seals the fuel chamber 13 with respect to the actuator chamber 14 at the same time large axial compliance is used. In the one shown in FIG Configuration, the metal bellows 17 by the fuel pressure applied inside. However, it is also possible that Metal bellows 17 directed downwards between valve needle 3 (no longer at the needle end) and the perforated plate 15, this is applied externally by the fuel pressure would be as shown in Figure 2.
  • the actuator 8 in In this case, a piezoelectric actuator, via the electrical leads 18 charged, whereupon the PMA 8 expands and the valve plate 4 of the valve needle 3 lifts off from the valve seat 2 and Fluid or fuel exiting the injection valve.
  • the PMA 8 becomes electrical discharged.
  • the PMA 8 contracts again its original length and the valve needle 3 is through the biased strong return spring 5 moves back so far that the valve disk 4 rests sealingly in the valve seat 2 and the annular injection port is closed.
  • metal bellows fulfills suitably chosen Geometry in full all to a feedthrough element or sealing element requirements. These include, that the metal bellows a perfect, durable and reliable Sealing represents.
  • the metal bellows 17 holds what calculations and tests have shown, despite low wall thicknesses for example, 50 to 500 microns due to its high radial Stiffness very high pressures without irreversible to be deformed.
  • the specification of a wall thickness range is be interpreted that a metal bellows 17 not varying, but for the individual case a constant wall thickness having.
  • the metal bellows can with a sufficient number of waves at the same time the required high axial compliance, i.e. a possibly required low axial spring constant exhibit.
  • the diameter of the metal bellows 17 be coordinated accordingly. This will be different from the pressurized fluid on the valve needle 3 with Valve plate 4 acting compressive forces and those of the end face the metal bellows introduced into the valve needle 3 pressure-related Forces compensate each other so that no resulting Compressive force component acts on the valve needle 3. As a result, such an injector shows a fuel pressure almost completely independent switching behavior, since for the opening and closing forces only the piezoelectric actuator 8 and the force of the prestressed return spring 5 prevail are.
  • the metal bellows 17 has a wide due to the metallic material Working temperature range with consistent functions. Thermal length changes of the bellows themselves lead due to the low axial spring constant of the metal bellows only too negligible small force changes to the valve needle. 3 seen in the axial direction.
  • the metal bellows may be due its mechanical spring action in the axial direction the Return spring, the compression spring 5, partially or completely replace.
  • the metal bellows 17 is double-sided fastened with elements on which in the metal bellows by external Press transferred forces in the axial direction become.
  • a valve needle can be designed in such a way that a specifiable balance of forces is present. This realization could by simulation calculations and by experiments be proved ..
  • the bellows has a from semicircle segments joined together in longitudinal section existing geometry proved. Opposite a sinusoidal Waveform shows the semicircle segments existing wall lower mechanical stresses in the axial Direction at higher axial compliance on.
  • FIG. 2 shows a externally pressurized metal bellows within the system and FIG. 3 shows an internal pressure-loaded metal bellows 17.
  • the high-pressure injector according to FIGS. 2 and 3 has, for example, the following dimensions:
  • the diameter DN of the valve needle 3 is 3 mm and the diameter DS of the valve seat 2 is 4 mm.
  • On the valve needle 3 thus acts at a fuel pressure of 250 bar due to the resulting annular differential area AD of 5.5 mm 2 directed downwardly in the opening direction opening force FU with 137.5 N. Since the wall of the externa pressurized metal bellows 17 almost no forces on the Valve needle 3 transmits, can be selectively adjusted by the diameter of the metal bellows 17, ie by the diameter DP of the end plate 19, which is the connection between Metallbalgwandung and valve needle 3, the size of the upward acting compensation pressure forces and thus the upward compensation pressure force FO.
  • the valve seat force is completely drukkuntouch under these conditions and is determined exclusively by the height of the set biasing force FR of the return spring.
  • the diameter of the valve needle in the region of the metal bellows can be reduced.
  • An adaptation of the pressure-effective surfaces is not limited to cylindrical metal bellows, but can be done with appropriate design even in non-cylindrical formations.
  • Figure 3 shows the complementary to Figure 2 arrangement with top-oriented internal pressure-loaded metal bellows 17. Die cheaper embodiment results from the particular situation the welds, for reasons of reliability preferably be subjected to mechanical compressive stresses should.
  • a certain advantage is in the embodiment of FIG 2 the shorter length of the upward through the (compensation force FO) and downward (opening force FU) acting Compressive forces loaded area of the valve needle opposite Figure 3 is thereby slightly less stretched.
  • the return spring. 5 partly or completely replace. This results a considerable design simplification and cost savings. Is applied to an additional return spring (compression spring 5) not waived, this can reduce the height also housed inside or outside of the metal bellows 17 be.
  • cylindrical metal bellows 17 come also other types, e.g. conical bellows or bellows with of the circular shape deviating cross-sectional geometry in question.

Description

Die Erfindung betrifft eine Fluiddosiervorrichtung mit der ein in einem Gehäuse befindliches, unter Druck stehendes Fluid, entweder eine Flüssigkeit oder ein Gas, in vorbestimmten Mengen abgegeben bzw. eingespritzt werden kann. Dabei ist durch das Gehäuse eine Ventilnadel hindurchgeführt, die außerhalb des Gehäuses einerseits mechanisch betätigt wird und andererseits ein Element eines Ventils darstellt.The invention relates to a Fluiddosiervorrichtung with the an in-housing, pressurized Fluid, either a liquid or a gas, in predetermined Quantities can be dispensed or injected. It is passed through the housing a valve needle, the outside of the housing is mechanically operated on the one hand and on the other hand represents an element of a valve.

Im Stand der Technik sind verschiedenartige Abdichtungs- oder Durchführungselemente bekannt. Für den Anwendungsfall der Dosierung von unter Druck stehenden Kraftstoffen mit einem Druck bis zu beispielsweise 300 bar und einem Arbeitstemperaturbereich von -40°C bis +150 °C werden jedoch besondere Anforderungen an ein serientaugliches Produkt gestellt. Allgemein müssen Anforderungen hinsichtlich der Versprödung, des Verschleißes und der Zuverlässigkeit erfüllt werden.In the prior art are various sealing or Implementation elements known. For the application of the dosage of pressurized fuels with a Pressure up to, for example, 300 bar and a working temperature range from -40 ° C to +150 ° C, however, special requirements placed on a product suitable for serial production. Generally requirements for embrittlement, the Wear and reliability are met.

Die Dauerstandfestigkeit von bisher verwendeten O-Ring-Dichtungen entspricht den obigen Anforderungen nicht. Anstelle von O-Ringen können auch Membrandichtungen wie beispielsweise Metallsicken o. ä. verwendet werden. Diese weisen jedoch den Nachteil einer sehr hohen druckbelasteten Fläche auf, was eine entsprechende Krafteinleitung in die Ventilnadel zur Folge hat. Wird bei einem einseitigen Überdruck von beispielsweise 300 bar eine 1 mm2 große druckbelastete Fläche betrachtet, so ergibt sich bereits eine Kraft von 30 N. Der Einsatz von Membranen als Durchführungselement einer Ventilnadel durch eine druckbeaufschlagte Kammer kann somit die Anforderungen bezüglich einer hohen axialen Nachgiebigkeit bei gleichzeitig ausreichender Druckfestigkeit nicht erfüllen. Eine hohe Druckfestigkeit führt zwangsläufig zu einer entsprechend dimensionierten Membrandicke, die wiederum eine hohe axiale Steifigkeit bedingt. Aufgrund der großen Membranfläche und der dadurch auch auf die Ventilnadel wirkenden sehr hohen Druckkräfte ist keine druckunabhängige Funktion einer Fluiddosiervorrichtung möglich. Dies ist jedoch beispielsweise für einen Motorstart oder für bestimmte Kennfeldbereiche notwendig. Eine Kompensation der Druckkräfte beim Einsatz einer Membran, beispielsweise durch eine mechanische Feder, ist bei der ausgeprägten Druckabhängigkeit der auf die Ventilnadel wirkenden Kräfte daher bestenfalls in einem einzigen Betriebspunkt möglich.The fatigue life of previously used O-ring seals does not meet the above requirements. Instead of O-rings and membrane seals such as metal beads o. Ä. Can be used. However, these have the disadvantage of a very high pressure-loaded surface, which has a corresponding force introduction into the valve needle result. If a pressure area of 1 mm 2 is considered at a one-sided overpressure of, for example, 300 bar, then a force of 30 N results. The use of diaphragms as lead-through element of a valve needle by a pressurized chamber can therefore meet the requirements for high axial compliance at the same time do not satisfy sufficient compressive strength. A high compressive strength inevitably leads to a correspondingly dimensioned membrane thickness, which in turn requires a high axial rigidity. Due to the large membrane area and thereby also acting on the valve needle very high pressure forces no pressure-independent function of a fluid metering is possible. However, this is necessary for example for an engine start or for specific map areas. A compensation of the pressure forces when using a membrane, for example by a mechanical spring, is therefore possible at the pronounced pressure dependence of the forces acting on the valve needle forces at best in a single operating point.

Die Ventilnadeldurchführung kann ähnlich wie bei Dieselinjektoren auch durch eine Spielpassung der Nadel in einer zylindrischen Gehäusebohrung erfolgen. Nachteilig hierbei ist die unvermeidbare Leckage, längs der Nadeldurchführung, die eine Rücklaufleitung in den Tank oder zum Niederdruckanschluß der Kraftstofförderpumpe erfordert. Durch die höheren hydraulischen Verluste wird außerdem der Gesamtwirkungsgrad des Motors herabgesetzt.The valve needle feedthrough can be similar to diesel injectors also by a clearance of the needle in a cylindrical Housing bore done. The disadvantage here is the unavoidable leakage, along the needle feedthrough, the one Return line into the tank or to the low pressure connection of the Fuel pump required. Due to the higher hydraulic Losses will also increase the overall efficiency of the engine reduced.

Eine Fluiddosiervorrichtung mit einem Metallbag als Durchführungselement ist beispielsweise aus den Druckschriften JP 07 158534 A, DE 591 559 A und DE 41 41 274 A bekannt.A fluid metering device with a metal bag as leadthrough element is known for example from the publications JP 07 158534 A, DE 591 559 A and DE 41 41 274 A.

Die Aufgabe der Erfindung besteht darin, eine Fluiddosiervorrichtung derart zu gestalten, daß eine hermetisch dichte Durchführung einer Ventilnadel durch eine mit einem unter Druck stehenden Fluid gefüllte Kammer gewährleistet wird, wobei ein zu verwendendes Durchführungselement keine wesentlichen druckabhängigen Kräfte auf die Ventilnadel ausübt.The object of the invention is a fluid metering device to make such that a hermetically sealed Carrying out a valve needle by one with a lower Pressure-filled fluid-filled chamber is ensured, wherein a feedthrough element to be used is not essential exerts pressure-dependent forces on the valve needle.

Die Lösung dieser Aufgabe geschieht durch die Merkmalskombination des Anspruchs 1.The solution of this task is done by the feature combination of claim 1.

Durch den Einsatz eines Metallbalges als Durchführungselement für eine Ventilnadel durch eine Kammer, die das zu dosierende Fluid beinhaltet, lassen sich viele bestehende Probleme lösen. Die Erfindung begründet sich dabei auf dem genauen Verständnis des Verhaltens eines druckbeaufschlagten Metallbalges. Hierbei werden insbesondere durch den Druck auf den Metallbalg und damit verbundene Verformungen Kräfte ausgelöst, die vom Metallbalg bei beidseitiger Befestigung nach außen übertragen werden. Dabei ist von hohen Druckunterschieden auf beiden Seiten des Metallbalges auszugehen, wobei der höhere Druck innerhalb oder außerhalb des Metallbalges sein kann. Die grundlegende Erkenntnis besteht insbesondere darin, daß die Wandung des Metallbalges auch bei geringer axialer Federkonstante bei einer Druckbeaufschlagung nur zu kleinen Kraftänderungen an den Enden eines beidseitig befestigten Balges führt. Die axialen Deformationen der Balgwellen sind durchaus nicht gering, heben sich aber genau wie die auf die einzelnen Balgwellen wirkenden Kräfte in ihrer Summe über die Gesamtlänge des Metallbalges nahezu auf. Somit kann mit geringen druckbedingten Kräften, die vom Metallbalg axial auf die Ventilnadel übertragen werden, gerechnet werden.By using a metal bellows as a lead-through element for a valve needle through a chamber containing the dosing Containing fluid, many existing problems can be solved. The invention is based on the exact understanding the behavior of a pressurized metal bellows. In this case, in particular by the pressure on the metal bellows and related deformations triggered forces, the metal bellows on the two-sided attachment to the outside be transmitted. It is on by high pressure differences Both sides of the metal bladder go out, with the higher Pressure inside or outside the metal bellows can be. The basic insight is, in particular, that the wall of the metal bellows even at low axial spring constant at a pressurization only small force changes at the ends of a bellows fastened on both sides leads. The axial deformations of the bellows shafts are quite not small, but stand out just like those on the individual Balbwellen acting forces in their total over the entire length of the metal bellows almost on. Thus, with little pressure-related forces, the metal bellows axially on the valve needle be transferred.

Eine besonders vorteilhafte Ausgestaltung sieht die radiale Fixierung der Ventilnadel durch die feste Verbindung des Metallbalges mit der Ventilnadel einerseits und mit dem Gehäuse andererseits vor.A particularly advantageous embodiment provides the radial Fixation of the valve needle by the firm connection of the metal bellows with the valve needle on the one hand and with the housing on the other hand.

In einer anderen Ausgestaltung der Erfindung sorgt der Einsatz einer Druckfeder zwischen Gehäuse und Ventilnadel für eine zuverlässige Schließkraft, die auf das Ventil wirkt.In another embodiment of the invention provides the use a compression spring between the housing and valve needle for a reliable closing force acting on the valve.

Trotz der großen Stabilität des Metallbalges kann insbesondere bei zylindrischer Ausführung die Ventilnadel oder eine über dem Metallbalg gestülpte Außenhülse eine Führung für diesen darstellen. Der Metallbalg kann dabei unter Umständen bereichsweise an seiner Führung anliegen. Ein Restrisiko eines Ausknickens wird damit nochmals reduziert.Despite the great stability of the metal bellows in particular in the case of a cylindrical design, the valve needle or a over the metal bellows inverted outer sleeve a guide for represent this. The metal bellows may under certain circumstances partially rest on his leadership. A residual risk of a Buckling is thus reduced again.

Die besonderen Vorteile des Metallbalges werden erzielt sowohl bei Innendruck- als auch bei Außendruckbeaufschlagung. Die Dimensionierung der Randstärke des Metallbalges im Bereich von 25 bis 500 µm zeigt, daß kleine Wandstärken bei großen Drücken, wie beispielsweise 300 bar, ausreichend sind. The particular advantages of metal bellows are achieved both with internal pressure as well as external pressure. The dimensioning of the edge strength of the metal bellows in the area from 25 to 500 microns shows that small wall thickness at large pressures, such as 300 bar, are sufficient.

Versuche haben ergeben, daß eine Ausbildung des Metallbalges in Form von im Längsschnitt sichtbaren aneinandergereihten Halbkreissegmenten besondere Vorteile erbringt. Diese Halbkreissegmente können jeweils durch zwischenliegende gerade Teilstücke ergänzt werden.Experiments have shown that an education of the metal bellows in the form of longitudinally visible strung together Semicircular segments provides special advantages. These semicircle segments can each be through intervening straight Pieces are supplemented.

Der Metallbalg ist vorteilhafterweise fest mit der Ventilnadel und dem Gehäuse verbunden. Zur Montierbarkeit der Ventilnadel und des Metallbalges im Gehäuse, beispielsweise bei einem Einspritzventil mit mehreren ineinander verschachtelten Elementen, müssen Verbindungsstellen frei zugänglich sein. Dies kann in vorteilhafterweise durch Schweißverbindungen, beispielsweise Laserschweißungen, geschehen.The metal bellows is advantageously fixed to the valve needle and connected to the housing. For mounting the valve needle and the metal bellows in the housing, for example at a Injection valve with several nested ones Elements, joints must be freely accessible. This can advantageously by welded joints, For example, laser welding done.

Um die bei hohen anliegenden Fluiddrücken auf die druckbeaufschlagten Flächen wirkenden Druckkräfte gezielt zu beeinflussen, sollte ein bestimmtes Gleichgewicht, bezogen auf die Ventilnade, der in entgegengesetzten Richtungen wirkenden fluiddruckbedingten Kräfte vorhanden sein. Es wird angestrebt, insgesamt eine Kompensierung dieser Kräfte zu erzielen, so daß die Ventilnadel bezüglich der genannten Kräfte annähernd kräftefrei ist oder am Ventil eine mit dem Druck proportional steigende Schließkraft anliegt. D.h. daß in Schließrichtung die druckwirksamen Kräfte geringfügig größer sind als die, die gegen die Schließkraft gerichtet sind. Zusätzlich kann die Kraft einer Schließfeder vorteilhaft sein.To the at high applied fluid pressures on the pressurized To selectively influence surfaces acting compressive forces, should have a certain balance, based on the Ventilnade acting in opposite directions fluid pressure forces are present. It is intended to achieve a total compensation of these forces so that the valve needle with respect to said forces is almost free of force or at the valve one with the pressure proportional rising closing force is applied. That that in Closing direction of the pressure-effective forces slightly larger are as those directed against the closing force. additionally the force of a closing spring can be advantageous.

Prinzipiell kann die Fluiddosiervorrichtung mit Ventilen ausgebildet sein, die nach innen oder nach außen öffnen. Die Konstruktion des Metallbalges im Verhältnis zu den restlichen Elementen insbesondere zum huberzeugenden Aktor ist entsprechend anzupassen. Als Aktor kommen Elektromagnete in Frage. Vorteilhaft ist es, Piezoaktoren einzusetzen, die beispielsweise in einer Rohrfeder vorgespannt sind. In principle, the fluid metering device can be formed with valves be that open inward or outward. The Construction of the metal bellows in relation to the rest Elements in particular for the impact-generating actuator is corresponding adapt. As an actuator electromagnets come into question. It is advantageous to use piezoelectric actuators, for example are biased in a Bourdon tube.

Im folgenden werden anhand von schematischen den Schutzbereich nicht einschränkenden Figuren Ausführungsbeispiele beschrieben.

Figur 1
zeigt einen Hochdruckinjektor mit einem Aktor, einem innendruckbeaufschlagten Metallbalg und einem nach außen öffnenden Ventil,
Figur 2
zeigt einen Hochdruckinjektor mit einem außendruckbeaufschlagten Metallbalg und einem nach außen öffnenden Ventil,
Figur 3
zeigt einen Hochdruckinjektor mit einem innendruckbeaufschlagten Metallbalg und einem nach außen öffnenden Ventil und
Figur 4
zeigt einen Hochdruckinjektor mit einem Aktor, einem inndruckbeaufbeschlagten Metallbalg und einem nach innen öffnenden Ventil.
Exemplary embodiments will be described below with reference to schematic figures which do not limit the scope of protection.
FIG. 1
shows a high-pressure injector with an actuator, a pressure-loaded metal bellows and an outward-opening valve,
FIG. 2
shows a high pressure injector with an externally pressurized metal bellows and an outwardly opening valve,
FIG. 3
shows a Hochdruckinjektor with an inner pressure-loaded metal bellows and an outwardly opening valve and
FIG. 4
shows a Hochdruckinjektor with an actuator, a druckbeauflaglagten metal bellows and an inwardly opening valve.

Die hier betrachteten Hochdruckinjektoren werden mit Kraftstoffdrücken PFUEL bis zu beispielsweise 500 bar betrieben. Ein Hub der Ventilnadel ist extrem kurz und liegt im Bereich von 10 bis 100 µm. Bei der Betrachtung des Gehäuses 1 ist zwischen dem fluidisch druckbeaufschlagtem Bereich und dem Bereich des Aktors mit wesentlich geringerem Druck zu unterscheiden. Hierzu ist das Gehäuse unterteilt in die Kammer 13, die mittels einer Leitungsbohrung 7 verbunden ist, über die das Fluid unter Druck zugeführt wird. Eine derartige Fluiddosiervorrichtung bzw. ein Hydraulikventil zur Dosierung des Fluides trennt demnach einen Hochdruckraum von einem Raum, der beispielsweise Umgebungsdruck aufweisen kann. Die Durchführung der Ventilnadel 3 durch das Gehäuse 1, insbesondere durch die Kammer 13 und zum Aktorraum 14 stellt den Kern der Erfindung dar. Als Durchführungselement wird ein Metallbalg 17 eingesetzt.The high-pressure injectors considered here are fuel-injected PFUEL operated up to, for example, 500 bar. A stroke of the valve needle is extremely short and lies in the range from 10 to 100 μm. When looking at the housing 1 is between the fluidically pressurized area and the Area of the actuator with much lower pressure to distinguish. For this purpose, the housing is divided into the chamber 13, which is connected by means of a conduit bore 7, over the the fluid is supplied under pressure. Such a fluid metering device or a hydraulic valve for dosing the Fluids thus separates a high pressure room from a room for example, may have ambient pressure. The implementation the valve needle 3 through the housing 1, in particular through the chamber 13 and the actuator chamber 14 represents the core of Invention. As a lead-through element is a metal bellows 17 used.

Bei der Konstruktion eines Hochdruckeinspritzventils für direkteinspritzende Magermotoren, insbesondere wenn das Einspritzventil einen piezoelektrischen Aktor 8 als Antrieb aufweist, gilt es folgende Probleme zu lösen:

  • Die Durchführung der Ventilnadel 3 aus der druckbeaufschlagten Kraftstoffkammer 13 in den Antriebsteil des Injektors ist hermetisch dicht auszuführen;
  • das Durchführungselement, hier der Metallbalg 17, soll eine hohe mechanische Nachgiebigkeit (geringe Federrate) in Bewegungsrichtung der Ventilnadel 3 aufweisen, um die Auslenkung der Ventilnadel 3 nicht zu beeinträchtigen und um die durch temperaturbedingte Längenänderungen des Durchführungselementes in die Ventilnadel 3 eingeleiteten Kräfte gering zu halten;
  • es soll eine hinreichende Druckfestigkeit des Durchführungselementes bei typischen Kraftstoffdrücken bis zu 500 bar gewährleistet sein;
  • druckbedingte Kräfte, die direkt auf die Ventilnadel wirken oder die durch mit der Ventilnadel mechanisch verbundene Elemente, wie das Durchführungselement, in die Ventilnadel eingeleitet werden, sollen geeignet kompensiert werden;
  • weiterhin muß eine sehr hohe Zuverlässigkeit des Durchführungselementes hinsichtlich einer Leckage garantiert sein, d.h. die im Durchführungselement auftretenden mechanischen Druck-/Zugspannungen müssen in einem materialverträglichen Bereich liegen, in dem das Durchführungselement lediglich elastisch reversibel verformt wird;
  • die Funktion des Durchführungselementes muß typischerweise in einem Temperaturbereich von -40 bis +150°C gewährleistet sein;
  • das Durchführungselement soll weiterhin die Möglichkeit bieten, die auf die Ventilnadel 3 wirkenden druckbedingten Kräfte geeignet zu kompensieren, um die Ventilnadel insgesamt druckkräftefrei zu machen. Beispielsweise wird aufgrund der druckbelasteten Fläche des Ventiltellers 4 eines nach außen öffnenden Injektors entsprechend Figur 1 bei hohem Kraftstoffdruck eine hohe in Öffnungsrichtung wirkende Druckkraft (Öffnungskraft FU), die vorteilhafterweise durch eine zweite druckbelastete Fläche die eine in Gegenrichtung wirkende Druckkraft FO erzeugt, kompensiert wird. Mit einer solchen Möglichkeit bestehen bezüglich des Ventilsitzdurchmessers DS und des Ventilnadeldurchmessers DN keinerlei Einschränkungen;
  • das Durchführungselement muß so gestaltet sein, daß die Montierbarkeit des Injektors gewährleistet ist.
In the construction of a high-pressure injection valve for direct-injection lean-burn engines, particularly when the injection valve has a piezoelectric actuator 8 as a drive, the following problems are to be solved:
  • The implementation of the valve needle 3 from the pressurized fuel chamber 13 in the drive part of the injector is to perform hermetically sealed;
  • the lead-through element, here the metal bellows 17, should have a high mechanical resilience (low spring rate) in the direction of movement of the valve needle 3 so as not to impair the deflection of the valve needle 3 and keep the forces introduced by the temperature-induced changes in length of the lead-through element into the valve needle 3 low ;
  • it should be ensured a sufficient compressive strength of the lead-through element at typical fuel pressures up to 500 bar;
  • pressure-related forces that act directly on the valve needle or that are introduced by connected with the valve needle mechanically connected elements, such as the lead-through element in the valve needle to be compensated appropriately;
  • Furthermore, a very high reliability of the lead-through element must be guaranteed in terms of leakage, ie the mechanical compressive / tensile stresses occurring in the lead-through element must be in a material-compatible range, in which the lead-through element is deformed only elastically reversible;
  • the function of the lead-through element must typically be ensured in a temperature range of -40 to + 150 ° C;
  • the lead-through element should continue to offer the opportunity to compensate for the forces acting on the valve needle 3 pressure-related forces suitable to make the valve needle total pressure-free. For example, due to the pressure-loaded surface of the valve disk 4 of an outwardly opening injector according to Figure 1 at high fuel pressure, a high pressure acting in the opening direction (opening force FU), which advantageously by a second pressure-loaded surface which generates a force acting in the opposite direction FO, is compensated. With such a possibility exist with respect to the valve seat diameter DS and the valve needle diameter DN no restrictions;
  • the lead-through element must be designed so that the mountability of the injector is ensured.

Durch Verwendung eines jeweils entsprechend konstruierten Metallbalges 17 als Durchführungselement lassen sich sämtliche oben aufgeführten Probleme lösen. Anhand der in Figur 1 dargestellten Ausführung eines nach außen öffnenden Kraftstoffhochdruckeinspritzventiles werden zunächst die Funktion des Injektors und anschließend die verschiedenen Funktionen des Metallbalges 17 erläutert.By using a correspondingly designed metal bellows 17 as an implementing element can be all solve the problems listed above. With reference to the illustrated in Figure 1 Execution of an outwardly opening high-pressure fuel injection valve First, the function of the Injectors and then the various functions of the Metal bellows 17 explained.

Der in Figur 1 gezeigte Hochdruckinjektor weist im Injektorgehäuse 1 einen Ventilsitz 2 auf. Der Ventilsitz 2 wird im Grundzustand durch den mit dem zweiten Ende 23 der Ventilnadel 3 verbundenen Ventilteller 4 geschlossen gehalten. Der geschlossene Zustand der durch den Ventilsitz 2 und den Ventilteller 4 gebildeten Einspritzdüse wird durch die gespannte Druckfeder 5 gewährleistet, die mit der Ventilnadel 3 über einen Sprengring 6 verbunden ist. Die Kraftstoffzuführung erfolgt durch die im Gehäuse 1 angebrachte Leitungsbohrung 7. Im oberen Teil des Injektorgehäuses 1 befindet sich die Antriebseinheit, gebildet aus einem piezoelektrischen Multilayeraktor (PMA) 8 in Niedervolttechnik, kombiniert mit einer Rohrfeder 9, einer Kopfplatte 10 und einer Fußplatte 11. Die Rohrfeder 9 ist so mit der Kopfplatte 10 und der Fußplatte 11 verschweißt, daß der PMA 8 unter einer mechanischen Druckvorspannung steht. Das Gehäuse 1 und die Fußplatte 1 sind ebenfalls möglichst steif über eine Schweißung miteinander verbunden. Zwischen Kopfplatte 10 und erstem Ende 22 der Ventilnadel 3 befindet sich ein Spalt 12, dessen Höhe erheblich kleiner ist als der Hub des PMA 8. Der Spalt 12 dient einerseits zur Einstellung definierter Kräfteverhältnisse im Ventilsitz und andererseits zum Abfangen geringer Unterschiede in den thermischen Längenänderungen. Zur Kompensation der verschiedenen thermischen Längenänderungen, d.h. zur Sicherstellung einer weitgehenden Temperaturunabhängigkeit der Höhe des Spaltes 12, bestehen die Injektorkomponenten aus Materialien mit geringen thermischen Ausdehnungskoeffizienten bzw. aus verschiedenen Materialien, die hinsichtlich ihrer thermischen Längenausdehnungskoeffizienten so aufeinander abgestimmt sind, daß die Konstanz der Spalthöhe näherungsweise gewährleistet ist.The high-pressure injector shown in FIG. 1 has the injector housing 1 a valve seat 2 on. The valve seat 2 is in Basic state by the second end 23 of the valve needle 3 connected valve disc 4 kept closed. Of the closed state of the valve seat 2 and the valve disc 4 injection nozzle is formed by the tensioned Compression spring 5 ensures that with the valve needle 3 via a snap ring 6 is connected. The fuel supply takes place through the attached in the housing 1 bore 7th In the upper part of the injector housing 1 is the drive unit, formed from a piezoelectric multilayer actuator (PMA) 8 in low voltage technology, combined with a Bourdon tube 9, a top plate 10 and a base plate 11. Die Bourdon tube 9 is so with the top plate 10 and the base plate 11th welded, that the PMA 8 under a mechanical compression bias stands. The housing 1 and the base plate 1 are also as stiff as possible connected by a weld. Between top plate 10 and first end 22 of the valve needle 3 there is a gap 12 whose height is considerable smaller than the stroke of the PMA 8. The gap 12 serves on the one hand for setting defined force relationships in the valve seat and on the other hand to catch small differences in the thermal length changes. To compensate for different thermal length changes, i. to make sure a substantial temperature independence of the height of the gap 12, the injector components are made of materials with low thermal expansion coefficients or made of different materials, in terms of their thermal Linear expansion coefficients so matched are that the constancy of the gap height approximately is guaranteed.

Zur Durchführung der Ventilnadel 3 aus der Kraftstoffkammer 13 in den drucklosen Aktorraum 14 dient die Lochplatte 15, die mit einer Innenbohrung 16 des Gehäuses 1 verschweißt ist. Ebenso kann die Lochplatte 15 auch aus dem Gehäuse 1 herausgearbeitet sein. Zwischen dem ersten Ende 22 der Ventilnadel 3 und der Lochplatte 15 ist der zylindrische Metallbalg 17 angeschweißt, der zur hermetischen Abdichtung der Kraftstoffkammer 13 gegenüber dem Aktorraum 14 bei gleichzeitig großer axialer Nachgiebigkeit dient. In der in Figur 1 gezeigten Konfiguration wird der Metallbalg 17 durch den Kraftstoffdruck innen beaufschlagt. Es ist jedoch ebenso möglich, den Metallbalg 17 nach unten gerichtet zwischen Ventilnadel 3 (jetzt nicht mehr am Nadelende) und der Lochplatte 15 anzuordnen, wobei dieser vom Kraftstoffdruck außen beaufschlagt werden würde, wie es in Figur 2 dargestellt ist.To carry out the valve needle 3 from the fuel chamber 13 in the pressureless actuator chamber 14 is the perforated plate 15, which is welded to an inner bore 16 of the housing 1. Likewise, the perforated plate 15 also worked out of the housing 1 be. Between the first end 22 of the valve needle 3 and the perforated plate 15 is the cylindrical metal bellows 17th welded, which hermetically seals the fuel chamber 13 with respect to the actuator chamber 14 at the same time large axial compliance is used. In the one shown in FIG Configuration, the metal bellows 17 by the fuel pressure applied inside. However, it is also possible that Metal bellows 17 directed downwards between valve needle 3 (no longer at the needle end) and the perforated plate 15, this is applied externally by the fuel pressure would be as shown in Figure 2.

Zur Einleitung des Einspritzvorganges wird der Aktor 8, in diesem Fall ein Piezoaktor, über die elektrischen Zuleitungen 18 aufgeladen, worauf der PMA 8 expandiert und den Ventilteller 4 der Ventilnadel 3 vom Ventildichtsitz 2 abhebt und Fluid bzw. Kraftstoff aus dem Einspritzventil austritt.To initiate the injection process, the actuator 8, in In this case, a piezoelectric actuator, via the electrical leads 18 charged, whereupon the PMA 8 expands and the valve plate 4 of the valve needle 3 lifts off from the valve seat 2 and Fluid or fuel exiting the injection valve.

Zur Beendigung des Einspritzvorganges wird der PMA 8 elektrisch entladen. Dabei kontrahiert sich der PMA 8 wieder auf seine ursprüngliche Länge und die Ventilnadel 3 wird durch die vorgespannte starke Rückstellfeder 5 so weit zurückbewegt, daß der Ventilteller 4 im Ventilsitz 2 dichtend anliegt und die ringförmige Einspritzöffnung verschlossen ist. To complete the injection process, the PMA 8 becomes electrical discharged. The PMA 8 contracts again its original length and the valve needle 3 is through the biased strong return spring 5 moves back so far that the valve disk 4 rests sealingly in the valve seat 2 and the annular injection port is closed.

Der Einsatz eines Metallbalges erfüllt bei geeignet gewählter Geometrie in vollem Umfang sämtliche an ein Durchführungselement bzw. Dichtelement gestellten Anforderungen. Dazu zählen, daß der Metallbalg eine perfekte, dauerhafte und zuverlässige Abdichtung darstellt. Der Metallbalg 17 hält, was Berechnungen und Versuche ergeben haben, trotz geringer Wandstärken von beispielsweise 50 bis 500 µm aufgrund seiner hohen radialen Steifigkeit sehr hohen Drücken stand, ohne irreversibel verformt zu werden. Die Angabe eines Wandstärkenbereiches ist so auszulegen, daß ein Metallbalg 17 keine variierende, sondern für den einzelnen Fall eine gleichbleibende Wandstärke aufweist. Der Metallbalg kann bei einer hinreichenden Anzahl von Wellen gleichzeitig die geforderte hohe axiale Nachgiebigkeit, d.h. eine eventuell geforderte niedrige axiale Federkonstante aufweisen.The use of a metal bellows fulfills suitably chosen Geometry in full all to a feedthrough element or sealing element requirements. These include, that the metal bellows a perfect, durable and reliable Sealing represents. The metal bellows 17 holds what calculations and tests have shown, despite low wall thicknesses for example, 50 to 500 microns due to its high radial Stiffness very high pressures without irreversible to be deformed. The specification of a wall thickness range is be interpreted that a metal bellows 17 not varying, but for the individual case a constant wall thickness having. The metal bellows can with a sufficient number of waves at the same time the required high axial compliance, i.e. a possibly required low axial spring constant exhibit.

Um die druckwirksamen Flächen an der Ventilnadel 3 insgesamt gezielt zu beeinflussen, so daß im Idealfall ein Zustand vollständiger Kräftekompensation bzw. ein Zustand mit geringer Fließkraft vorliegt, kann der Durchmessers des Metallbalges 17 entsprechend abgestimmt werden. Damit werden sich von dem unter Druck stehenden Fluid auf die Ventilnadel 3 mit Ventilteller 4 wirkende Druckkräfte und die von der Endfläche des Metallbalges in die Ventilnadel 3 eingeleiteten druckbedingten Kräfte so gegenseitig kompensieren, daß keine resultierende Druckkraftkomponente auf die Ventilnadel 3 wirkt. Hierdurch zeigt ein solcher Injektor ein vom Kraftstoffdruck nahezu völlig unabhängiges Schaltverhalten, da für die Öffnungs- und Schließkräfte alleinig der piezoelektrische Aktor 8 und die Kraft der vorgespannten Rückstellfeder 5 maßgebend sind. Dieses gilt zwar nicht im gleichen Umfang für dynamische Druckkräfte (Druckwellen), die beim Öffnen und Schließen eines Hochdruckinjektors unvermeidbar sind, doch ist eine druckausgeglichene Ventilnadel 3 gegenüber solchen Effekten naturgemäß wesentlich weniger empfindlich. Der Metallbalg 17 verfügt aufgrund des metallischen Werkstoffes über einen weiten Arbeitstemperaturbereich mit gleichbleibenden Funktionen. Thermische Längenänderungen des Balges selbst führen aufgrund der niedrigen axialen Federkonstante des Metallbalges nur zu vernachläßigbar geringen Kraftänderungen an der Ventilnadel 3 in axialer Richtung gesehen. Der Metallbalg kann aufgrund seiner mechanischen Federwirkung in axialer Richtung die Rückstellfeder, die Druckfeder 5, teilweise oder vollständig ersetzen.To the pressure-effective surfaces of the valve needle 3 in total to influence specifically, so that ideally a state complete power compensation or a state with low Flow force is present, the diameter of the metal bellows 17 be coordinated accordingly. This will be different from the pressurized fluid on the valve needle 3 with Valve plate 4 acting compressive forces and those of the end face the metal bellows introduced into the valve needle 3 pressure-related Forces compensate each other so that no resulting Compressive force component acts on the valve needle 3. As a result, such an injector shows a fuel pressure almost completely independent switching behavior, since for the opening and closing forces only the piezoelectric actuator 8 and the force of the prestressed return spring 5 prevail are. Although this is not true to the same extent for dynamic Compressive forces (pressure waves) when opening and closing a high-pressure injector are unavoidable, but is one pressure balanced valve needle 3 against such effects naturally much less sensitive. The metal bellows 17 has a wide due to the metallic material Working temperature range with consistent functions. Thermal length changes of the bellows themselves lead due to the low axial spring constant of the metal bellows only too negligible small force changes to the valve needle. 3 seen in the axial direction. The metal bellows may be due its mechanical spring action in the axial direction the Return spring, the compression spring 5, partially or completely replace.

Zum Verständnis der Erfindung ist die Klarstellung des Verhaltens eines druckbeaufschlagten Metallbalges, insbesondere der durch den Druck bewirkten Verformungen und der dadurch ausgelösten Kräfte notwendig. Der Metallbalg 17 ist beidseitig mit Elementen befestigt, auf die im Metallbalg durch äußere Drücke entstehende Kräfte in axialer Richtung übertragen werden. In Verbindung mit der gezielten Einstellung dieser Kräfte durch den Durchmesser des Balges bei möglichst kleiner axialer Federkonstanten durch die Gestaltung der Metallbalgwandung kann eine Ventilnadel derart ausgelegt werden, daß ein vorgebbares Kräftegleichgewicht vorliegt. Diese Erkenntnis konnte durch Simulationsrechnungen und durch Versuche bewiesen werden..To understand the invention is the clarification of the behavior a pressurized metal bellows, in particular the deformations caused by the pressure and thereby triggered forces necessary. The metal bellows 17 is double-sided fastened with elements on which in the metal bellows by external Press transferred forces in the axial direction become. In conjunction with the targeted setting of this Forces through the diameter of the bellows at the smallest possible axial spring constant by the design of Metallbalgwandung a valve needle can be designed in such a way that a specifiable balance of forces is present. This realization could by simulation calculations and by experiments be proved ..

Insbesondere hat sich gezeigt, daß bei fluidischer Druckbeaufschlagung die Änderung der Gesamtlänge der Wandung eines Metallbalges mit mehreren Wellen, wobei lediglich die Wand des Metallbalges als druckbeaufschlagt betrachtet wird, äußerst gering ist. Bei Innendruckbeaufschlagung verkürzt sich die Wand des Metallbalges 17 geringfügig, bei Außendruckbeaufschlagung verlängert sie sich geringfügig. Beispielsweise wird bei einem Druck von 200 bar und einer Metallbalggeometrie mit zwölf Wellen, einem Innendurchmesser von 3,5 mm, einem Außendurchmesser von 5,3 mm, einer Wanddicke von 100 µm und einer Wandlänge von 12,1 mm eine typische Längenänderung von 10 bis 20 µm auftreten. Aufgrund der geringen axialen Federkonstante von beispielsweise 0,2 /µm der Metallbalgwandung führt dies nur zu kleinen Kraftänderungen an den Enden eines beidseitig befestigten Metallbalges 17. Die axialen Deformationen der Balgwellen sind durchaus nicht gering, heben sich aber genau wie die auf die einzelnen Balgwellen wirkenden Kräfte in ihrer Summe über die Gesamtlänge des Balges nahezu auf. Durch diese Erkenntnis über die Zusammenhänge der hervorgerufenen Kräfte an einem Metallbalg durch Druckbeaufschlagung kann ein solcher Metallbalg 17 in beiden Orientierungen eingebaut werden, d.h. Innen- oder Außendruckbeaufschlagung. Trotz der Deformationen der Balgwellen lassen sich die mechanischen Spannungen in der Wandung des Metallbalges 17 durch Steuerung der Wanddicke, beispielsweise 25 bis 500 µm, leicht in einem materialverträglichen Bereich halten, ohne daß die axiale Nachgiebigkeit wesentlich verringert wird.In particular, it has been found that with fluidic pressurization the change in the total length of the wall of a Metal bellows with multiple waves, with only the wall the metal bellows is considered pressurized extremely is low. At internal pressure is shortened the wall of the metal bellows 17 slightly, with external pressure it extends slightly. For example is at a pressure of 200 bar and a metal bellows geometry with twelve shafts, an inner diameter of 3.5 mm, one Outer diameter of 5.3 mm, a wall thickness of 100 microns and a wall length of 12.1 mm a typical change in length from 10 to 20 microns occur. Due to the low axial spring constant for example 0.2 / μm of the metal bellows wall This only leads to small force changes at the ends of a Both sides attached metal bellows 17. The axial deformations the bellows shafts are not small, stand out but just like the ones acting on the individual bellows shafts Forces in their total over the total length of the bellows almost on. Through this knowledge about the connections of the evoked Forces on a metal bellows by pressurization For example, such a metal bellows 17 may be in both orientations be incorporated, i. Internal or external pressurization. Despite the deformations of the bellows waves can be the mechanical stresses in the wall of the metal bellows 17 by controlling the wall thickness, for example 25 to 500 μm, easily hold in a material-compatible area, without that the axial compliance is substantially reduced.

Als besonders günstige Form für die Balgwellen hat sich eine aus im Längsschnitt betrachtet aneinandergefügten Halbkreissegmenten bestehende Geometrie erwiesen. Gegenüber einem sinusförmigen Wellenverlauf weist die aus Halbkreissegmenten bestehende Wandung geringere mechanische Spannungen in axialer Richtung bei höherer axialer Nachgiebigkeit auf.As a particularly favorable form for the bellows has a from semicircle segments joined together in longitudinal section existing geometry proved. Opposite a sinusoidal Waveform shows the semicircle segments existing wall lower mechanical stresses in the axial Direction at higher axial compliance on.

Da von der Balgwandung auch bei hohen Drücken oder Druckänderungen nahezu keine resultierenden Kräfte auf die Balgenden übertragen werden, können solche für die Druckausgeglichenheit der Ventilnadel 3 erforderlichen Kompensationskräfte gezielt durch den Balgdurchmesser eingestellt werden. Dies wird im einzelnen durch die Darstellungen der Figuren 2 und 3 verdeutlicht. In den Figuren 2 und 3 wird jeweils ein nach außen öffnendes Einspritzventil dargestellt. Figur 2 zeigt einen außendruckbeaufschlagten Metallbalg innerhalb des Systems und Figur 3 einen innendruckbeaufschlagten Metallbalg 17.Because of the bellows wall even at high pressures or pressure changes almost no resulting forces on the bellows can be transferred, such for the pressure balance the valve needle 3 required compensation forces targeted be adjusted by the bellows diameter. this will illustrated in detail by the representations of Figures 2 and 3. In Figures 2 and 3, one outwards opening injection valve shown. FIG. 2 shows a externally pressurized metal bellows within the system and FIG. 3 shows an internal pressure-loaded metal bellows 17.

Der Hochdruckinjektor entsprechend den Figuren 2 und 3 hat beispielsweise folgende Abmessungen:
Der Durchmesser DN der Ventilnadel 3 beträgt 3 mm und der Durchmesser DS des Ventilsitzes 2 beträgt 4 mm. Auf die Ventilnadel 3 wirkt damit bei einem Kraftstoffdruck von 250 bar aufgrund der resultierenden ringförmigen Differenzfläche AD von 5,5 mm2 eine nach unten in Öffnungsrichtung gerichtete Öffnungskraft FU mit 137,5 N. Da die Wandung des außendruckbeaufschlagten Metallbalges 17 nahezu keine Kräfte auf die Ventilnadel 3 überträgt, kann durch den Durchmesser des Metallbalges 17, d.h. durch den Durchmesser DP der Stirnplatte 19, welche die Verbindung zwischen Metallbalgwandung und Ventilnadel 3 darstellt, die Größe der nach oben wirkenden Kompensationsdruckkräfte und damit die nach oben gerichtete Kompensationsdruckkraft FO gezielt eingestellt werden. Um in dem gewählten Beispiel die Bedingung FO = FU (Öffnungskraft = Kompensationskraft) zu erfüllen, ergibt sich für den Durchmesser der Stirnplatte 19 ein Wert von DP = 4 mm. Die Ventilsitzkraft ist unter diesen Voraussetzungen vollkommen drukkunabhängig und wird ausschließlich durch die Höhe der eingestellten Vorspannkraft FR der Rückstellfeder bestimmt. Um eine Berührung der Balgwellen mit der Ventilnadel zu vermeiden, kann ggf. der Durchmesser der Ventilnadel im Bereich des Metallbalges verringert werden. Eine Anpassung der druckwirksamen Flächen ist nicht nur auf zylindrische Metallbälge beschränkt, sondern kann bei entsprechender Konstruktion auch bei nichtzylindrischen Ausbildungen geschehen.The high-pressure injector according to FIGS. 2 and 3 has, for example, the following dimensions:
The diameter DN of the valve needle 3 is 3 mm and the diameter DS of the valve seat 2 is 4 mm. On the valve needle 3 thus acts at a fuel pressure of 250 bar due to the resulting annular differential area AD of 5.5 mm 2 directed downwardly in the opening direction opening force FU with 137.5 N. Since the wall of the externa pressurized metal bellows 17 almost no forces on the Valve needle 3 transmits, can be selectively adjusted by the diameter of the metal bellows 17, ie by the diameter DP of the end plate 19, which is the connection between Metallbalgwandung and valve needle 3, the size of the upward acting compensation pressure forces and thus the upward compensation pressure force FO. In order to fulfill the condition FO = FU (opening force = compensation force) in the example chosen, the diameter of the end plate 19 is given a value of DP = 4 mm. The valve seat force is completely drukkunabhängig under these conditions and is determined exclusively by the height of the set biasing force FR of the return spring. In order to avoid contact of the bellows shafts with the valve needle, if necessary, the diameter of the valve needle in the region of the metal bellows can be reduced. An adaptation of the pressure-effective surfaces is not limited to cylindrical metal bellows, but can be done with appropriate design even in non-cylindrical formations.

Montagetechnisch kann der Metallbalg 17 nach Einführung der Ventilnadel 3 in das Gehäuse des Injektors nachträglich mittels Laserschweißung 20 an der Lochplatte 15 des Ventilgehäuses 1 und an der Ventilnadel 3 befestigt werden.Montagetechnisch the metal bellows 17 after the introduction of Valve needle 3 in the housing of the injector subsequently by means Laser welding 20 on the perforated plate 15 of the valve housing 1 and attached to the valve needle 3.

Figur 3 zeigt die zu Figur 2 komplementäre Anordnung mit nach oben orientiertem innendruckbeaufschlagtem Metallbalg 17. Die günstigere Ausführungsform ergibt sich aus der jeweiligen Lage der Schweißnähte, die aus Zuverlässigkeitsgründen vorzugsweise mit mechanischen Druckspannungen beaufschlagt werden sollten. Ein gewisser Vorteil ist bei der Ausführung nach Figur 2 die geringere Länge des durch die nach oben (Kompensationskraft FO) und nach unten (Öffnungskraft FU) wirkenden Druckkräfte belasteten Bereiches der Ventilnadel, die gegenüber Figur 3 dadurch etwas weniger gedehnt wird.Figure 3 shows the complementary to Figure 2 arrangement with top-oriented internal pressure-loaded metal bellows 17. Die cheaper embodiment results from the particular situation the welds, for reasons of reliability preferably be subjected to mechanical compressive stresses should. A certain advantage is in the embodiment of FIG 2 the shorter length of the upward through the (compensation force FO) and downward (opening force FU) acting Compressive forces loaded area of the valve needle opposite Figure 3 is thereby slightly less stretched.

Durch die mechanische Federwirkung des Metallbalges 17 in axialer Richtung kann der Metallbalg 17 bei den in Figur 1, 2 und 3 gezeigten Ausführungsbeispielen die Rückstellfeder 5 teilweise oder auch vollständig ersetzen. Damit ergibt sich eine erhebliche Konstruktionsvereinfachung und Kostenersparnis. Wird auf eine zusätzliche Rückstellfeder (Druckfeder 5) nicht verzichtet, so kann diese zur Verringerung der Bauhöhe auch innerhalb oder außerhalb des Metallbalges 17 untergebracht sein.By the mechanical spring action of the metal bellows 17 in axial direction, the metal bellows 17 in the in Figure 1, 2 and 3 shown embodiments, the return spring. 5 partly or completely replace. This results a considerable design simplification and cost savings. Is applied to an additional return spring (compression spring 5) not waived, this can reduce the height also housed inside or outside of the metal bellows 17 be.

Neben den vorgeschlagenen zylindrischen Metallbälgen 17 kommen auch andere Bauformen, z.B. konische Bälge oder Bälge mit von der Kreisform abweichender Querschnittsgeometrie in Frage.In addition to the proposed cylindrical metal bellows 17 come also other types, e.g. conical bellows or bellows with of the circular shape deviating cross-sectional geometry in question.

Claims (19)

  1. Fluid metering device for a pressurized fluid, comprising:
    a chamber (13) in a housing (1), said chamber (13) containing the fluid subject to pressure,
    a valve needle (3) passed through the chamber (13), the first end (22) of which can be lifted outside the chamber (13) and the second end (23) of which together with a valve seat (2) positioned on the housing (1) forms a valve connected to the chamber (13), and
    metal bellows (17) as the passage element for the first end (22) of the valve needle (3) from outside into the chamber (13), the chamber (13) being connected in a hermetically sealed manner at the point of passage by means of the connection between the first end (22) of the valve needle (3) via the metal bellows (17) to the housing, characterised in that the resulting force acting as a pressure at the valve needle (3) and exerted on elements connected thereto is adjusted by means of selected areas acting as pressure at the metal bellows (17) and the valve needle (3), such that the forces acting as a pressure at the valve needle (3) are compensated for overall or a closing force that increases in proportion to the pressure is present at the valve.
  2. Fluid metering device according to Claim 1,
    the radial angle position of the valve needle (3) being fixed by connecting the metal bellows (17) to the valve needle (3) on the one hand and to the housing (1) on the other hand.
  3. Fluid metering device according to Claim 1,
    a compression spring (5) also being provided between the housing (1) and the valve needle (3) to apply a predefinable closing force.
  4. Fluid metering device according to one of the preceding claims, the metal bellows (17) being configured as cylindrical.
  5. Fluid metering device according to one of the preceding claims, the valve needle (3) or an outer sleeve representing a guide for the metal bellows (17).
  6. Fluid metering device according to one of the preceding claims, the metal bellows (17) being subject to internal or external pressure.
  7. Fluid metering device according to one of the preceding claims, the metal bellows having a wall thickness of 25 to 500 µm.
  8. Fluid metering device according to one of the preceding claims, the metal bellows (17) being made up of semicircular segments joined together side by side in the longitudinal cross-section.
  9. Fluid metering device according to Claim 8, straight parts being present between each of the semicircular segments.
  10. Fluid metering device according to one of the preceding claims, the metal bellows (17) being connected by weld seams (20) directly or indirectly to the housing (1) on the one hand and to the first end (22) of the valve needle (3) on the other hand.
  11. Fluid metering device according to Claim 10, the weld seams being laser weld seams.
  12. Fluid metering device according to one of the preceding claims, a face plate (19) being provided between the first end (22) of the valve needle (3) and the metal bellows (17).
  13. Fluid metering device according to one of Claims 11 or 12, the diameter of the metal bellows (17) being designed in conjunction with the diameter of the face plate (19) such that forces acting as a pressure at the valve needle (3) are compensated for overall or a closing force that increases in proportion to the pressure is present at the valve.
  14. Fluid metering device according to one of the preceding claims, the fuel pressure (PFUEL) being 1 to 500 bar.
  15. Fluid metering device according to one of the preceding claims for use with injectors that open outwards.
  16. Fluid metering device according to one of the preceding claims, the first end (22) of the valve needle (3) being such that it can be lifted by an actuator (8) connected permanently to the housing (1).
  17. Fluid metering device according to Claim 16, the actuator (8) being a piezo-actuator, which is pretensioned in a Bourdon spring and held at a distance from the first end (22) of the valve needle (3) by a gap (12) of predefined width in the idle state.
  18. Fluid metering device according to Claim 16, the actuator (8) being an electromagnet.
  19. Fluid metering device according to one of the preceding claims, the lift of the valve needle (3) being limited in a defined manner by stops.
EP00107401A 1999-04-20 2000-04-05 Fluid metering device Expired - Lifetime EP1046809B1 (en)

Applications Claiming Priority (2)

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DE19917839 1999-04-20
DE19917839 1999-04-20

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DE591559C (en) * 1932-01-06 1934-01-23 Schweizerische Lokomotiv Fluid controlled fuel valve
DE1036575B (en) * 1950-04-11 1958-08-14 Fritz Ostwald Dipl Phys Injection nozzle with bellows
US5205492A (en) * 1991-12-16 1993-04-27 Gregory Khinchuk Fuel injection valve

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2308602A2 (en) 2009-10-06 2011-04-13 Nordson Corporation Liquid dispensing module

Also Published As

Publication number Publication date
EP1046809A2 (en) 2000-10-25
US6311950B1 (en) 2001-11-06
EP1046809A3 (en) 2003-06-18
DE50010902D1 (en) 2005-09-15

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