EP1436499B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP1436499B1
EP1436499B1 EP02767139A EP02767139A EP1436499B1 EP 1436499 B1 EP1436499 B1 EP 1436499B1 EP 02767139 A EP02767139 A EP 02767139A EP 02767139 A EP02767139 A EP 02767139A EP 1436499 B1 EP1436499 B1 EP 1436499B1
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EP
European Patent Office
Prior art keywords
valve
sleeve
valve body
fuel injection
actuator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02767139A
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German (de)
French (fr)
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EP1436499A1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1436499A1 publication Critical patent/EP1436499A1/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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/26—Fuel-injection apparatus with elastically deformable elements other than coil springs

Definitions

  • the invention relates to a fuel injection valve according to the preamble of independent claim 1.
  • a fuel injection valve for fuel injection systems of internal combustion engines which has a valve body guided in a piezoelectric device whose cooperating with a needle-like valve closing body piezoelectric actuator is firmly clamped in an end piece facing away from the closing body and lifts the valve closing body of a valve seat when activated.
  • the tail is firmly connected to the valve body closely surrounding the piezoelectric actuator.
  • the valve body consists of a temperature-related changes in length of the piezoelectric actuator at least approximately compensating material.
  • the valve body is formed as a two-part sleeve having coaxial with each other sleeve parts. These sleeve parts are arranged successively in an imaginary longitudinal direction of the fuel injection valve and consist of materials with different thermal expansion coefficients. These materials include steel and invar. The sum of the temperature-related strains of this Both sleeve parts corresponds to the temperature-induced expansion of the piezoelectric actuator and of connecting elements to the valve closing body.
  • a disadvantage of this known prior art is that the sleeve, which has a very low or no temperature expansion and consists of an expensive material, must fulfill all the functions of a valve body. The sleeve is thus loaded not only on pressure, but also on train and must be made accordingly and provide fastening means. This means that threads or the like are to be provided and an increased material consumption is necessary because these fasteners cost construction volume.
  • Another disadvantage is that a redesign of the sleeve is necessary if only small changes to the overall length or the material properties of the actuator are made, since only the effective length of the shell determines the extent of the total thermal expansion.
  • a fuel injector with a controllable actuator which is incorporated in an actuator housing which is fixedly connected to a valve body.
  • the actuator is in operative connection with a valve needle, wherein on the valve needle, a valve closing body is formed, which cooperates with a valve seat surface to a valve sealing seat.
  • the material of the actuator housing has a thermal expansion coefficient which is almost equal to the thermal expansion coefficient of the piezoelectric actuator.
  • the actuator housing is inserted into a recess of the valve body and bolted to the valve body via a flange which is arranged approximately in the middle of the longitudinal extent of the actuator housing.
  • the temperature-induced expansion of the actuator and the transmission elements to the valve closing body corresponds to the temperature-induced expansion of the valve body and the section actuator housing from the flange to a closure element on which the actuator is supported.
  • DE 19 948 359 A discloses a spring outer sleeve zuan bracing a Gehaüses, in which a piezoelectric actuator is surrounded by a ceramic compensation sleeve.
  • a disadvantage of the stated prior art is that no possibility is offered, as the formation of the attachment of the actuator housing to the valve body in the material with low temperature expansion can be avoided.
  • the production of, for example, a flange requires a blank in the manufacture, which has at least the diameter of the flange and thus causes considerable losses of material. This leads to great costs due to the special material.
  • the fuel injection valve according to the invention with the features of the independent claim 1 has the advantage that the thermal expansion can be adjusted by the bias of the spring sleeve in more detail. Due to the bias, the thermal expansion can be influenced to a small extent and be adapted to the thermal expansion of the actuator more accurate. Furthermore, it is advantageous that the compensation section is not loaded on train and therefore can be constructed simpler. The material requirement for materials that have no or a negative thermal expansion is thereby reduced. This saves considerable costs, since these materials are very expensive.
  • the compensation section is held solely by the clamping between the upper valve body section and the lower valve body section and does not require a construction volume and no machining for connections, such as tapped holes.
  • the spring sleeve is designed as a tube spring.
  • a spring sleeve is effected with a spring constant in the direction of the longitudinal axis of the spring sleeve.
  • the bourdon tube is characterized by slots arranged in radial planes in the sleeve, the webs meeting between the slots on a slot in the next radial plane.
  • the Bourdon tube is bolted to the lower valve body portion and engages around the upper valve body portion on a collar.
  • the bias can be adjusted very accurately and easily, especially if a fine thread is used.
  • the Bourdon tube can advantageously consist of Invar. A reduction of the bias voltage at a temperature increase is avoided when the Bourdon tube from Invar, d. H. a nickel / iron alloy.
  • the compensation section consists of Invar.
  • Invar has a very low, close to zero temperature expansion coefficient. The determination of the total temperature expansion is thus simple, since the compensation section has no temperature expansion. The determination of the thermal expansion is effected solely by the effective length of the upper valve body portion and the lower valve body portion.
  • the compensation section may have the shape of a cylinder with flat-ground end faces.
  • the compensation section can be inexpensively manufactured from a semi-finished product.
  • the seal can be made by surface ground surfaces that do not require further sealant formations such as an O-ring.
  • Fig. 1 shows a schematic section through an embodiment of a fuel injection valve according to the invention 1.
  • An actuator 2 is supported against an upper valve body portion 3 and is driven via a connecting hole 4 in the upper valve body portion 3 via connecting lines, not shown here.
  • the actuator 2 is arranged in an actuator chamber 5, which is bounded radially outwardly by a compensation sleeve 6.
  • the actuator 2 transmits a lifting movement via an actuator tappet 7 to a valve needle 9.
  • a corrugated tube 8 is attached to the actuator tappet 7 via a weld seam 10 and seals the actuator chamber 5 with respect to a fuel chamber 11.
  • the valve needle 9 is connected to a valve closing body, not shown here, which cooperates with a valve seat surface to a valve seat.
  • a guide bore 12 in a lower valve body portion 13 guides the valve needle 9.
  • valve needle 9 has at its end facing the actuator ram 7 a collar 14 on which a valve spring 15 abuts and is supported against the lower valve body portion 13.
  • the valve spring 15 pushes the valve needle 9 in the fuel injection valve 1 shown here with outwardly opening valve needle 9 in the direction of the actuator 2 via an inlet bore 16a in the upper valve body portion 3, an inlet bore 16b in the compensation sleeve, an inlet bore 16c and a further inlet bore 16d, both in the lower valve body portion 13, the fuel is supplied to the valve seat not shown here.
  • the compensation sleeve 6 is surrounded radially on the outside by a spring sleeve 17.
  • the spring sleeve 17 is connected via a thread 18 with the lower valve body portion 13.
  • the upper valve body portion 3 has a collar 19 around which a bend 20 of the spring sleeve 17 engages.
  • the compensation sleeve 6 has a flat ground surface 21 at its interface with the upper valve body portion.
  • the compensation sleeve 6 has a further surface ground surface 22 which rests against the lower valve body portion 13 via a radial clamping surface 25 of the corrugated tube 8.
  • the spring sleeve 17 is screwed onto the thread 18 so far that it stretches and exerts a biasing force on the compensation sleeve 6.
  • Fig. 2 shows a schematic partial section through the spring sleeve 17 of the fuel injection valve 1 in the Fig. 1 ,
  • the spring sleeve 17 is formed as a tube spring 26, wherein slots 24 are arranged in radial planes. Remaining material webs 25 between the slots 24 meet in the next radial plane on a slot 24.
  • the bend 20 At the upper end of the tube spring 17 is the bend 20, which serves to grip the collar 19 of the upper valve body portion.
  • the actuator 2 When the actuator 2 is driven by an electrical voltage, it transmits a stroke to the actuator plunger 7, which in turn transmits the movement to the valve needle 9.
  • the corrugated tube 8 follows this lifting movement elastically deforming and seals the actuator chamber 5 from.
  • the valve seat, not shown, is opened and fuel is injected into a combustion chamber. After the voltage has dropped, the valve spring 15 pushes the valve needle 9 into its position Starting position back and presses at the same time on the Aktorst Jardinel 7 the actuator 2 to its original length together.
  • the valve needle 9, the actuator tappet 7 and the actuator 2 expand or change their length. It follows that the crucial for a stroke of the valve needle 9 length of the components actuator 2, actuator tappet 7 and valve needle 9 to the valve seat changes. At the same time, the length of the lower valve body section 13 also changes from the valve seat via the compensation sleeve 6. Now, if the length of the compensation sleeve 6 is designed so that the thermal expansion of the two described component sequences is substantially equal, the thermal expansion is compensated. In this case, the temperature expansion of the compensation sleeve 6 can be additionally influenced at least to a small extent by the bias of the spring sleeve 17.
  • the described fuel injection valve 1 according to the invention requires only small amounts of special materials, such as, for example, for the production of the compensation sleeve 6.
  • the alloy Invar since this compensation sleeve 6 is loaded only on pressure and is designed as a simple cylinder sleeve with two flat surfaces. Through the flat surfaces 21, 22 can be done in a simple manner a seal.
  • the preparation of the compensation sleeve 6 can in particular be made of a continuous semi-finished product, in particular a suitable tube and there is hardly any loss of material in the production.

Abstract

The invention relates to a fuel injection valve (1), especially an injection valve for fuel injection systems in internal combustion engines, wherein a piezoelecric or magneto-restrictive actuator (2) is surrounded by a compensation sleeve (6). The compensation sleeve (6) is made of a material having an extremely small or negative temperature expansion so that the temperature expansion of the compensation sleeve (6) and that of an upper valve body section (3) and/or lower valve body section (13) substantially corresponds to the temperature expansion of the actuator (2) and the active transmission elements (7,9) to the valve seat. The compensation sleeve (6) is radially outwardly encompassed by a spring sleeve (17) enabling the lower valve body section (13) to be connected to the upper valve body section (3) and the compensation sleeve (6) to be pre-stressed under pressure.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Brennstoffeinspritzventil nach dem Oberbegriff des unabhängigen Anspruchs 1.The invention relates to a fuel injection valve according to the preamble of independent claim 1.

Aus der DE 195 38 791 A1 ist ein Brennstoffeinspritzventil für Brennstoffeinspritzanlagen von Brennkraftmaschinen bekannt, das eine in einem Ventilkörper geführte piezoelektrische Einrichtung aufweist, deren mit einem nadelähnlichen Ventilschließkörper zusammenwirkender Piezoaktor in einem dem Schließkörper abgewandten Endstück fest eingespannt ist und bei Aktivierung den Ventilschließkörper von einem Ventilsitz abhebt. Das Endstück ist mit dem den Piezoaktor eng umgebenden Ventilkörper fest verbunden. Der Ventilkörper besteht aus einem die temperaturbedingten Längenänderungen des Piezoaktors zumindest annähernd ausgleichenden Werkstoff.From the DE 195 38 791 A1 a fuel injection valve for fuel injection systems of internal combustion engines is known, which has a valve body guided in a piezoelectric device whose cooperating with a needle-like valve closing body piezoelectric actuator is firmly clamped in an end piece facing away from the closing body and lifts the valve closing body of a valve seat when activated. The tail is firmly connected to the valve body closely surrounding the piezoelectric actuator. The valve body consists of a temperature-related changes in length of the piezoelectric actuator at least approximately compensating material.

In einer Ausführungsform ist aus der DE 195 38 791 A1 ein Brennstoffeinspritzventil bekannt, dessen Ventilkörper als zweiteilige Hülse ausgebildet ist, die koaxial zueinander liegende Hülsenteile aufweisen. Diese Hülsenteile sind in einer gedachten Längsrichtung des Brennstoffeinspritzventils aufeinander abfolgend angeordnet und bestehen aus Werkstoffen mit unterschiedlichen warmedehnunungskoeffizienten. Diese Werkstoffe sind beispielsweise Stahl und Invar. Die Summe der temperaturbedingten Dehnungen dieser beiden Hülsenteile entspricht der temperaturbedingten Dehnung des Piezoaktors und von Verbindungselementen zu dem Ventilschließkörper.In one embodiment, from the DE 195 38 791 A1 a fuel injection valve is known, the valve body is formed as a two-part sleeve having coaxial with each other sleeve parts. These sleeve parts are arranged successively in an imaginary longitudinal direction of the fuel injection valve and consist of materials with different thermal expansion coefficients. These materials include steel and invar. The sum of the temperature-related strains of this Both sleeve parts corresponds to the temperature-induced expansion of the piezoelectric actuator and of connecting elements to the valve closing body.

Nachteilig an diesem bekannten Stand der Technik ist, daß auch die Hülse, die eine sehr geringe oder keine Temperaturausdehnung aufweist und aus einem teuren Werkstoff besteht, alle Funktionen eines Ventilkörpers erfüllen muß. Die Hülse wird somit nicht nur auf Druck, sondern auch auf Zug belastet und muß dementsprechend gefertigt sein und Befestigungsmittel vorsehen. Dies bedeutet, daß Gewinde oder ähnliches vorzusehen sind und ein erhöhter Materialverbrauch nötig ist, da diese Befestigungsmittel Bauvolumen kosten. Weiterhin ist nachteilig, daß eine Umkonstruktion der Hülse nötig ist, wenn nur geringe Änderungen an der Baulänge oder den Materialeigenschaften des Aktors vorgenommen werden, da allein die wirksame Länge der Hülle das Maß der Temperatur-Gesamtdehnung festlegt.A disadvantage of this known prior art is that the sleeve, which has a very low or no temperature expansion and consists of an expensive material, must fulfill all the functions of a valve body. The sleeve is thus loaded not only on pressure, but also on train and must be made accordingly and provide fastening means. This means that threads or the like are to be provided and an increased material consumption is necessary because these fasteners cost construction volume. Another disadvantage is that a redesign of the sleeve is necessary if only small changes to the overall length or the material properties of the actuator are made, since only the effective length of the shell determines the extent of the total thermal expansion.

Aus der EP 0 869 278 A1 ist ein Brennstoffeinspritzventil mit einem steuerbaren Aktor bekannt, der in ein Aktorgehäuse eingebracht ist, das fest mit einem Ventilkörper verbunden ist. Der Aktor steht in Wirkverbindung mit einer Ventilnadel, wobei an der Ventilnadel ein Ventilschließkörper ausgeformt ist, der mit einer Ventilsitzfläche zu einem Ventildichtsitz zusammenwirkt. Das Material des Aktorgehäuses weist einen thermischen Ausdehnungskoeffizienten auf, der nahezu gleich dem thermischen Ausdehnungskoeffizienten des piezoelektrischen Aktors ist. Das Aktorgehäuse ist in eine Ausnehmung des Ventilkörpers eingesetzt und über einen Flansch, der ungefähr in der Mitte der Längserstreckung des Aktorgehäuses angeordnet ist, mit dem Ventilkörper verschraubt. Die temperaturbedingte Dehnung des Aktors und der Übertragungselemente bis zu dem Ventilschließkörper entspricht der temperaturbedingten Dehnung des Ventilkörpers und des Abschnitts-Aktorgehäuses von dem Flansch bis zu einem Abschlußelement, auf das sich der Aktor abstützt.From the EP 0 869 278 A1 For example, a fuel injector with a controllable actuator is known, which is incorporated in an actuator housing which is fixedly connected to a valve body. The actuator is in operative connection with a valve needle, wherein on the valve needle, a valve closing body is formed, which cooperates with a valve seat surface to a valve sealing seat. The material of the actuator housing has a thermal expansion coefficient which is almost equal to the thermal expansion coefficient of the piezoelectric actuator. The actuator housing is inserted into a recess of the valve body and bolted to the valve body via a flange which is arranged approximately in the middle of the longitudinal extent of the actuator housing. The temperature-induced expansion of the actuator and the transmission elements to the valve closing body corresponds to the temperature-induced expansion of the valve body and the section actuator housing from the flange to a closure element on which the actuator is supported.

DE 19 948 359 A offenbart eine Federnde aüßere Hülse zuan Verspannen eines Gehaüses, in welchen sich ein Piezoaktor umgeben von einer keramischen Kompensationshülse befindet. DE 19 948 359 A discloses a spring outer sleeve zuan bracing a Gehaüses, in which a piezoelectric actuator is surrounded by a ceramic compensation sleeve.

Nachteilig an dem dargelegten Stand der Technik ist, daß keine Möglichkeit geboten wird, wie die Ausformung der Befestigung des Aktorgehäuses an dem Ventilkörper in dem Material mit geringer Temperaturdehnung vermieden werden kann. Die Herstellung beispielsweise eines Flansches erfordert bei der Fertigung einen Rohling, der mindestens den Durchmesser des Flansches aufweist und bedingt somit erhebliche Verluste an Material. Dies führt aufgrund des Spezialwerkstoffes zu großen Kosten.A disadvantage of the stated prior art is that no possibility is offered, as the formation of the attachment of the actuator housing to the valve body in the material with low temperature expansion can be avoided. The production of, for example, a flange requires a blank in the manufacture, which has at least the diameter of the flange and thus causes considerable losses of material. This leads to great costs due to the special material.

Weiterhin ist nachteilig, daß auch hier keine Möglichkeit vorgesehen ist, eine Feinregulierung vorzunehmen und eine Änderung der Dimensionen oder Eigenschaften des Aktors eine Neukonstruktion und Änderung des Bauteils des Aktorgehäuses erfordert.Another disadvantage is that again no possibility is provided to perform a fine adjustment and a change in the dimensions or properties of the actuator requires a redesign and modification of the component of the actuator housing.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des unabhängigen Anspruchs 1 hat demgegenüber den Vorteil, daß die Temperaturdehnung durch die Vorspannung der Federhülse genauer eingestellt werden kann. Durch die Vorspannung kann die Temperaturdehnung in geringem Umfang beeinflußt werden und an die Temperaturdehnung des Aktors genauer angepaßt werden. Weiterhin ist vorteilhaft, daß der Kompensationsabschnitt nicht auf Zug belastet wird und daher einfacher aufgebaut werden kann. Der Materialbedarf an Werkstoffen, die keine oder eine negative Wärmedehnung aufweisen, wird dadurch verringert. Dies spart erhebliche Kosten ein, da diese Werkstoffe sehr teuer sind. Der Kompensationsabschnitt wird allein durch die Einspannung zwischen oberem Ventilkörperabschnitt und unterem Ventilkörperabschnitt gehalten und benötigt kein Bauvolumen und keine Bearbeitung für Verbindungen, wie beispielsweise Gewindebohrungen.The fuel injection valve according to the invention with the features of the independent claim 1 has the advantage that the thermal expansion can be adjusted by the bias of the spring sleeve in more detail. Due to the bias, the thermal expansion can be influenced to a small extent and be adapted to the thermal expansion of the actuator more accurate. Furthermore, it is advantageous that the compensation section is not loaded on train and therefore can be constructed simpler. The material requirement for materials that have no or a negative thermal expansion is thereby reduced. This saves considerable costs, since these materials are very expensive. The compensation section is held solely by the clamping between the upper valve body section and the lower valve body section and does not require a construction volume and no machining for connections, such as tapped holes.

Die Federhülse ist als eine Rohrfeder ausgebildet. So wird eine Federhülse mit einer Federkonstanten in Richtung der Längsachse der Federhülse bewirkt. Die Rohrfeder ist dabei durch in radialen Ebenen angeordnete Schlitze in der Hülse gekennzeichnet, wobei die Stege zwischen den Schlitzen auf einen Schlitz in der nächsten radialen Ebene treffen.The spring sleeve is designed as a tube spring. Thus, a spring sleeve is effected with a spring constant in the direction of the longitudinal axis of the spring sleeve. The bourdon tube is characterized by slots arranged in radial planes in the sleeve, the webs meeting between the slots on a slot in the next radial plane.

Die Rohrfeder ist mit dem unteren Ventilkörperabschnitt verschraubt und umgreift den oberen Ventilkörperabschnitt an einem Bund. Durch das Gewinde kann die Vorspannung sehr genau und einfach eingestellt werden, insbesondere, wenn ein Feingewinde verwendet wird.The Bourdon tube is bolted to the lower valve body portion and engages around the upper valve body portion on a collar. By the thread, the bias can be adjusted very accurately and easily, especially if a fine thread is used.

Durch die in den abhängigen. Ansprüchen angegebenen Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im unabhängigen Anspruchs 1 angegebenen Brennstoffeinspritzventils möglich.By in the dependent. Claims specified measures are advantageous refinements and improvements of the independent claim 1 fuel injector possible.

Die Rohrfeder kann vorteilhaft aus Invar bestehen. Eine Erniedrigung der Vorspannung bei einer Temperaturerhöhung wird vermieden, wenn die Rohrfeder aus Invar, d. h. einer Nickel/Eisen Legierung, besteht.The Bourdon tube can advantageously consist of Invar. A reduction of the bias voltage at a temperature increase is avoided when the Bourdon tube from Invar, d. H. a nickel / iron alloy.

In günstiger Ausführung besteht der Kompensationsabschnitt aus Invar. Invar besitzt einen sehr geringen, nahe Null gehenden Temperaturdehnungskoeffizienten. Die Bestimmung der Gesamttemperaturdehnung ist somit einfach, da der Kompensationsabschnitt keine Temperaturdehnung aufweist. Die Bestimmung der Temperaturdehnung erfolgt allein durch die wirksame Baulänge des oberen Ventilkörperabschnitts und des unteren Ventilkörperabschnitts.In a favorable embodiment, the compensation section consists of Invar. Invar has a very low, close to zero temperature expansion coefficient. The determination of the total temperature expansion is thus simple, since the compensation section has no temperature expansion. The determination of the thermal expansion is effected solely by the effective length of the upper valve body portion and the lower valve body portion.

Der Kompensationsabschnitt kann die Form eines Zylinders mit plangeschliffenen Abschlußflächen aufweist. Dadurch kann der Kompensationsabschnitt kostengünstig aus einem Halbzeug gefertigt werden. Die Abdichtung kann durch plangeschliffene Flächen erfolgen, die keine weiteren Ausformungen für Dichtungsmittel, wie beispielsweise für einen O-Ring erfordern.The compensation section may have the shape of a cylinder with flat-ground end faces. As a result, the compensation section can be inexpensively manufactured from a semi-finished product. The seal can be made by surface ground surfaces that do not require further sealant formations such as an O-ring.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
einen schematischen Teilschnitt durch ein Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils und
Fig. 2
einen schematischen Teilschnitt durch die Rohrfeder des Brennstoffeinspritzventil in der Fig. 1.
An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. Show it:
Fig. 1
a schematic partial section through an embodiment of a fuel injection valve according to the invention and
Fig. 2
a schematic partial section through the tube spring of the fuel injection valve in the Fig. 1 ,

Beschreibung des AusführungsbeispielsDescription of the embodiment

Fig. 1 zeigt einen schematischen Schnitt durch ein Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1. Ein Aktor 2 stützt sich gegen einen oberen Ventilkörperabschnitt 3 ab und wird über eine Anschlußbohrung 4 in dem oberen Ventilkörperabschnitt 3 über hier nicht dargestellte Anschlußleitungen angesteuert. Der Aktor 2 ist in einem Aktorraum 5 angeordnet, der radial nach außen von einer Kompensationshülse 6 begrenzt wird. Der Aktor 2 überträgt eine Hubbewegung über einen Aktorstößel 7 auf eine Ventilnadel 9. An dem Aktorstößel 7 ist über eine Schweißnaht 10 ein Wellrohr 8 befestigt und dichtet den Aktorraum 5 gegenüber einem Brennstoffraum 11 ab. Die Ventilnadel 9 ist mit einem hier nicht dargestellten Ventilschließkörper verbunden, der mit einer Ventilsitzfläche zu einem Ventildichtsitz zusammenwirkt. Eine Führungsbohrung 12 in einem unteren Ventilkörperabschnitt 13 führt die Ventilnadel 9. Fig. 1 shows a schematic section through an embodiment of a fuel injection valve according to the invention 1. An actuator 2 is supported against an upper valve body portion 3 and is driven via a connecting hole 4 in the upper valve body portion 3 via connecting lines, not shown here. The actuator 2 is arranged in an actuator chamber 5, which is bounded radially outwardly by a compensation sleeve 6. The actuator 2 transmits a lifting movement via an actuator tappet 7 to a valve needle 9. A corrugated tube 8 is attached to the actuator tappet 7 via a weld seam 10 and seals the actuator chamber 5 with respect to a fuel chamber 11. The valve needle 9 is connected to a valve closing body, not shown here, which cooperates with a valve seat surface to a valve seat. A guide bore 12 in a lower valve body portion 13 guides the valve needle 9.

Die Ventilnadel 9 weist an ihrem dem Aktorstößel 7 zugewandten Ende einen Bund 14 auf, an dem eine Ventilfeder 15 anliegt und sich gegen den unteren Ventilkörperabschnitt 13 abstützt. Die Ventilfeder 15 drückt die Ventilnadel 9 bei dem hier dargestellten Brennstoffeinspritzventil 1 mit nach außen öffnender Ventilnadel 9 in Richtung des Aktors 2. Über eine Zulaufbohrung 16a im oberen Ventilkörperabschnitt 3, eine Zulaufbohrung 16b in der Kompensationshülse, eine Zulaufbohrung 16c und eine weitere Zulaufbohrung 16d, beide im unteren Ventilkörperabschnitt 13 wird der Brennstoff dem hier nicht dargestellten Ventildichtsitz zugeführt.The valve needle 9 has at its end facing the actuator ram 7 a collar 14 on which a valve spring 15 abuts and is supported against the lower valve body portion 13. The valve spring 15 pushes the valve needle 9 in the fuel injection valve 1 shown here with outwardly opening valve needle 9 in the direction of the actuator 2 via an inlet bore 16a in the upper valve body portion 3, an inlet bore 16b in the compensation sleeve, an inlet bore 16c and a further inlet bore 16d, both in the lower valve body portion 13, the fuel is supplied to the valve seat not shown here.

Die Kompensationshülse 6 ist radial außen von einer Federhülse 17 umgeben. Die Federhülse 17 ist über ein Gewinde 18 mit dem unteren Ventilkörperabschnitt 13 verbunden. Der obere Ventilkörperabschnitt 3 weist einen Bund 19 auf, um den eine Umbiegung 20 der Federhülse 17 greift. Die Kompensationshülse 6 weist an ihrer Grenzfläche zu dem oberen Ventilkörperabschnitt eine plangeschliffene Fläche 21 auf. Ebenso weist die Kompensationshülse 6 eine weitere plangeschliffene Fläche 22 auf, die über eine radiale Einspannfläche 25 des Wellrohrs 8 an dem unteren Ventilkörperabschnitt 13 anliegt. Die Federhülse 17 ist soweit auf das Gewinde 18 aufgeschraubt, daß sie sich dehnt und eine Vorspannkraft auf die Kompensationshülse 6 ausübt.The compensation sleeve 6 is surrounded radially on the outside by a spring sleeve 17. The spring sleeve 17 is connected via a thread 18 with the lower valve body portion 13. The upper valve body portion 3 has a collar 19 around which a bend 20 of the spring sleeve 17 engages. The compensation sleeve 6 has a flat ground surface 21 at its interface with the upper valve body portion. Likewise, the compensation sleeve 6 has a further surface ground surface 22 which rests against the lower valve body portion 13 via a radial clamping surface 25 of the corrugated tube 8. The spring sleeve 17 is screwed onto the thread 18 so far that it stretches and exerts a biasing force on the compensation sleeve 6.

Fig. 2 zeigt einen schematischen Teilschnitt durch die Federhülse 17 des Brennstoffeinspritzventils 1 in der Fig. 1. Die Federhülse 17 ist als Rohrfeder 26 ausgebildet, wobei Schlitze 24 in radialen Ebenen angeordnet sind. Verbleibende Materialstege 25 zwischen den Schlitzen 24 treffen in der nächsten radialen Ebene auf einen Schlitz 24. An dem oberen Ende der Rohrfeder 17 befindet sich die Umbiegung 20, die dazu dient, den Bund 19 des oberen Ventilkörperabschnitts zu umgreifen. Fig. 2 shows a schematic partial section through the spring sleeve 17 of the fuel injection valve 1 in the Fig. 1 , The spring sleeve 17 is formed as a tube spring 26, wherein slots 24 are arranged in radial planes. Remaining material webs 25 between the slots 24 meet in the next radial plane on a slot 24. At the upper end of the tube spring 17 is the bend 20, which serves to grip the collar 19 of the upper valve body portion.

Wenn der Aktor 2 durch eine elektrische Spannung angesteuert wird, überträgt er einen Hub auf den Aktorstößel 7, der wiederum die Bewegung auf die Ventilnadel 9 überträgt. Dabei folgt das Wellrohr 8 dieser Hubbewegung elastisch sich verformend und dichtet den Aktorraum 5 ab. Der nicht dargestellte Ventildichtsitz wird geöffnet und Brennstoff wird in einen Brennraum eingespritzt. Nach dem Abfallen der Spannung drückt die Ventilfeder 15 die Ventilnadel 9 in ihre Ausgangslage zurück und drückt zugleich über den Aktorstößel 7 den Aktor 2 auf seine ursprüngliche Länge zusammen.When the actuator 2 is driven by an electrical voltage, it transmits a stroke to the actuator plunger 7, which in turn transmits the movement to the valve needle 9. In this case, the corrugated tube 8 follows this lifting movement elastically deforming and seals the actuator chamber 5 from. The valve seat, not shown, is opened and fuel is injected into a combustion chamber. After the voltage has dropped, the valve spring 15 pushes the valve needle 9 into its position Starting position back and presses at the same time on the Aktorstößel 7 the actuator 2 to its original length together.

Bei der mit fortschreitender Betriebsdauer des Brennstoffeinspritzventils 1 erfolgenden Temperaturerhöhung dehnen sich die Ventilnadel 9, der Aktorsößel 7 und der Aktor 2 aus, bzw. verändern ihre Länge. Daraus folgt, daß die für einen Hub der Ventilnadel 9 entscheidende Länge der Bauteile Aktor 2, Aktorstößel 7 und Ventilnadel 9 bis zum Ventildichtsitz sich verändert. Gleichzeitig verändert sich auch die Länge des unteren Ventilkörperabschnitts 13 von dem Ventildichtsitz über die Kompensationshülse 6. Wenn nun die Länge der Kompensationshülse 6 so ausgelegt wird, daß die Temperaturdehnung der beiden beschriebenen Bauteilabfolgen im wesentlichen gleich ist, wird die Temperaturdehnung kompensiert. Dabei kann die Temperaturdehnung der Kompensationshülse 6 zumindest in geringem Maße zusätzlich durch die Vorspannung der Federhülse 17 beeinflußt werden.When the temperature increase takes place as the operating life of the fuel injection valve 1 progresses, the valve needle 9, the actuator tappet 7 and the actuator 2 expand or change their length. It follows that the crucial for a stroke of the valve needle 9 length of the components actuator 2, actuator tappet 7 and valve needle 9 to the valve seat changes. At the same time, the length of the lower valve body section 13 also changes from the valve seat via the compensation sleeve 6. Now, if the length of the compensation sleeve 6 is designed so that the thermal expansion of the two described component sequences is substantially equal, the thermal expansion is compensated. In this case, the temperature expansion of the compensation sleeve 6 can be additionally influenced at least to a small extent by the bias of the spring sleeve 17.

Das beschriebene erfindungsgemäße Brennstoffeinspritzventil 1 benötigt für die Herstellung der Kompensationshülse 6 nur geringe Mengen an speziellen Werkstoffen, wie z.B. der Legierung Invar, da diese Kompensationshülse 6 nur auf Druck belastet ist und als einfache Zylinderhülse mit zwei planen Flächen ausgeführt wird. Durch die planen Flächen 21, 22 kann in einfacher Art und Weise eine Abdichtung erfolgen. Die Herstellung der Kompensationshülse 6 kann insbesondere aus einem Endloshalbzeug, insbesondere einem geeigneten Rohr erfolgen und es kommt kaum zu Materialverlusten im Rahmen der Fertigung.The described fuel injection valve 1 according to the invention requires only small amounts of special materials, such as, for example, for the production of the compensation sleeve 6. the alloy Invar, since this compensation sleeve 6 is loaded only on pressure and is designed as a simple cylinder sleeve with two flat surfaces. Through the flat surfaces 21, 22 can be done in a simple manner a seal. The preparation of the compensation sleeve 6 can in particular be made of a continuous semi-finished product, in particular a suitable tube and there is hardly any loss of material in the production.

Claims (4)

  1. Fuel injection valve (1), in particular injection valve for fuel injection systems of internal combustion engines, with a piezoelectric or magnetostrictive actuator (2) which actuates a valve needle (9) and a valve-closing body connected to the valve needle (9), wherein the valve-closing body interacts with a valve-seat surface to form a valve-sealing seat,
    wherein the actuator (2) is surrounded by a compensation sleeve (6) and the compensation sleeve (6) is composed of a material which exhibits virtually zero or negative temperature expansion, such that the temperature-dependent expansion of the compensation sleeve (6) and of an upper valve body section (3) and/or lower valve body section (13) substantially corresponds to the temperature-dependent expansion of the actuator (2) and of the acting transmission elements (7, 9) up to the valve-sealing seat,
    wherein the compensation sleeve (6) is encompassed radially on the outside by a spring sleeve (17) which connects the lower valve body section (13) to the upper valve body section (3) and prestresses the compensation sleeve (6) in compression,
    and wherein the spring sleeve (17) is a tube spring (26),
    characterized
    in that the tube spring (26) is connected to the lower valve body section (13) via a thread (18) and encompasses the upper valve body section (3) on a collar (19).
  2. Fuel injection valve according to Claim 1,
    characterized
    in that the tube spring (26) is composed of invar steel.
  3. Fuel injection valve according to Claim 1 or 2,
    characterized
    in that the compensation sleeve (6) is composed of invar steel.
  4. Fuel injection valve according to one of Claims 1 to 3,
    characterized
    in that the compensation sleeve (6) is in the form of a cylinder with surface-ground termination surfaces (21, 22).
EP02767139A 2001-10-10 2002-09-07 Fuel injection valve Expired - Lifetime EP1436499B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10149915A DE10149915A1 (en) 2001-10-10 2001-10-10 Fuel injection valve for IC engine fuel injection system has piezoelectric or magnetistrictive actuator enclosed by thermal expansion compensation sleeve
DE10149915 2001-10-10
PCT/DE2002/003336 WO2003033905A1 (en) 2001-10-10 2002-09-07 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP1436499A1 EP1436499A1 (en) 2004-07-14
EP1436499B1 true EP1436499B1 (en) 2008-10-08

Family

ID=7702003

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02767139A Expired - Lifetime EP1436499B1 (en) 2001-10-10 2002-09-07 Fuel injection valve

Country Status (5)

Country Link
US (1) US7032833B2 (en)
EP (1) EP1436499B1 (en)
JP (1) JP4191603B2 (en)
DE (2) DE10149915A1 (en)
WO (1) WO2003033905A1 (en)

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DE102004021920A1 (en) * 2004-05-04 2005-12-01 Robert Bosch Gmbh Fuel injector
EP1760306A1 (en) * 2005-09-06 2007-03-07 Siemens Aktiengesellschaft Housing
DE102007033033B4 (en) * 2007-07-16 2019-08-08 Continental Automotive Gmbh Actuator for an injection system of an internal combustion engine
US8074625B2 (en) 2008-01-07 2011-12-13 Mcalister Technologies, Llc Fuel injector actuator assemblies and associated methods of use and manufacture
US7762236B2 (en) * 2008-07-16 2010-07-27 Transonic Combustion, Inc. Piezoelectric fuel injector having a temperature compensating unit
DE102010031643A1 (en) * 2010-07-22 2012-01-26 Robert Bosch Gmbh Fuel injector with dry solenoid actuator
US9309846B2 (en) 2012-11-12 2016-04-12 Mcalister Technologies, Llc Motion modifiers for fuel injection systems
US20140131466A1 (en) * 2012-11-12 2014-05-15 Advanced Green Innovations, LLC Hydraulic displacement amplifiers for fuel injectors
JP2017066955A (en) * 2015-09-30 2017-04-06 日立オートモティブシステムズ株式会社 Flow control valve

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Also Published As

Publication number Publication date
US7032833B2 (en) 2006-04-25
EP1436499A1 (en) 2004-07-14
DE10149915A1 (en) 2003-04-24
DE50212877D1 (en) 2008-11-20
US20040061003A1 (en) 2004-04-01
JP2005505719A (en) 2005-02-24
JP4191603B2 (en) 2008-12-03
WO2003033905A1 (en) 2003-04-24

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