EP2317117B1 - Actuator module and fuel injection valve - Google Patents

Actuator module and fuel injection valve Download PDF

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Publication number
EP2317117B1
EP2317117B1 EP20100181972 EP10181972A EP2317117B1 EP 2317117 B1 EP2317117 B1 EP 2317117B1 EP 20100181972 EP20100181972 EP 20100181972 EP 10181972 A EP10181972 A EP 10181972A EP 2317117 B1 EP2317117 B1 EP 2317117B1
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EP
European Patent Office
Prior art keywords
actuator
compensation chamber
actuator module
transition piece
guide sleeve
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.)
Not-in-force
Application number
EP20100181972
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German (de)
French (fr)
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EP2317117A1 (en
Inventor
Dieter Junger
Michael Kurrle
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2317117A1 publication Critical patent/EP2317117A1/en
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Publication of EP2317117B1 publication Critical patent/EP2317117B1/en
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    • 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
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion

Definitions

  • the invention relates to an actuator module for a fuel injection valve and a fuel injection valve with an actuator module. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.
  • the known injector has a piezoelectric actuator arranged in an injector body, which is held in abutment via spring means on the one hand with the injector and on the other hand with a sleeve-like booster piston. Furthermore, a nozzle body connected to the injector body is provided, which has at least one nozzle outlet opening. In the nozzle body, a nozzle needle is guided axially displaceable.
  • EP 1457 662 A1 or DE 102007053423 discloses a fuel injector valve with a piezoelectric, electrostrictive or magnetostrictive actuator.
  • the actuator module according to the invention with the features of claim 1 and the fuel injection valve according to the invention with the features of claim 9 have the advantage that temperature-induced changes in length are at least partially compensated. Specifically, the requirements for an additionally provided within the fuel injection valve temperature compensation is reduced, whereby the chain of effects of the actuator module is optimized for actuating a valve closing body.
  • a guide sleeve is provided, in which the pressure pin is guided, and that the compensation space of the transition piece, the guide sleeve and guided in the guide sleeve pressure pin is limited.
  • the sealing sleeve has a hollow cylindrical portion which forms the guide sleeve.
  • the sealing sleeve is configured in an advantageous manner as a metallic sealing sleeve, so that the actuator module can be arranged in a space filled with fuel.
  • this can be used to ensure a seal against high-pressure fuel.
  • this can be used to realize a directly controlled fuel injection valve.
  • the transition piece has at least one throttled connection channel, which connects the interior of the sealing sleeve with the compensation chamber, and that the throttled connection between the interior and the compensation chamber comprises at least the throttled connection channel.
  • the throttled connection channel can be designed as a throttle bore. This is a exact specification of the throttle effect and thus interpretation of the throttled connection possible.
  • a guide sleeve connected to the transition piece is provided, in which the pressure bolt is guided, that between the guide sleeve and an outer side of the transition piece at least a throttled connection point is formed and that the throttled connection between the interior and the compensation space at least the throttled junction comprises.
  • the throttled connection point is formed by a throttled connection gap in a partially circumferential weld, which connects the guide sleeve with the transition piece.
  • a plurality of such connection gaps can also be provided.
  • the pressure fluid is formed at least substantially on the basis of a transformer oil. It is also advantageous that the actuator body is surrounded by a gel-like insulating layer on the basis of at least one material with a backbone of perfluoropolyether and crosslinking groups of silicon. Specifically, the material may be selected from a group of materials known under the name Sifel.
  • Fig. 1 shows a fuel injection valve 1 with an actuator module 2 in a schematic, excerpted sectional view according to a first embodiment.
  • the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail, the diesel fuel under high pressure leads to a plurality of fuel injection valves 1.
  • the actuator module 2 according to the invention is particularly suitable for such fuel injection valves 1.
  • the fuel injection valve 1 according to the invention and the actuator module 2 according to the invention are also suitable for other applications.
  • the fuel injection valve 1 has a valve housing 3 and a nozzle body 4.
  • the nozzle body 4 is connected, for example via a nozzle lock nut with the valve housing 3.
  • a valve seat surface 5 is configured on the nozzle body 4.
  • a valve closing body 6 is provided, which is formed integrally with a nozzle needle 7 in this embodiment.
  • the valve closing body 6 cooperates with the valve seat surface 5 to form a sealing seat.
  • a fuel chamber 8 is configured, in which there is in operation under high pressure fuel.
  • an actuator chamber 15 is configured, in which the actuator module 2 is located.
  • high-pressure fuel may be provided in the actuator chamber 15 which is guided, for example, through the actuator chamber 15 of the valve housing 3 to the fuel chamber 8.
  • the actuator module 2 is supported on one side on a housing part 16. On another side, the actuator module 2 is acted upon by a compression spring 17.
  • the compression spring 17 is supported here on the valve housing 3.
  • the actuator module 2 has a piezoelectric actuator body 18, which comprises a plurality of ceramic layers and a plurality of electrode layers arranged between the ceramic layers. In this case, the electrode layers are alternately contacted with electrical leads (not shown) in order to allow loading and unloading of the actuator body 18.
  • the actuator body 18 is arranged between transition pieces 19, 20.
  • the transition pieces 19, 20 of the actuator module 2 at opposite end faces 21, 22 of the actuator body 18 to the Actuator 18 added.
  • the transition piece 19 is designed as an actuator head
  • the transition piece 20 is designed as Aktorfuß.
  • the actuator module 2 further comprises a sealing sleeve 23, which is designed as a metallic sealing sleeve 23 in the form of a corrugated bellows 23.
  • the sealing sleeve 23 seals an inner space 24 of the actuator module 2.
  • the actuator body 18 is arranged in the interior 24.
  • the sealing sleeve 23 is in this case connected via a peripheral weld 25 with the actuator head 19.
  • the sealing sleeve 23 is connected to a circumferential weld 26 with the actuator base 20.
  • the welds 25, 26 are designed sealingly, so that no fuel from the actuator chamber 15 can get into the interior 24 via this.
  • a seal of the inner space 24 is formed by the sealing sleeve 23 against the fuel. Therefore, the inner space 24 of the actuator module 2 is reliably sealed from the environment.
  • the sealing sleeve 23 is bent collar-shaped at one end portion 27 to allow a support of the compression spring 17. As a result, the number of required components can be reduced. Furthermore, the sealing sleeve 23 has a hollow cylindrical portion 28. The hollow cylindrical portion 28 forms a guide sleeve 28 of the actuator module 2. In this embodiment, the guide sleeve 28 is disposed within the compression spring 17. Within the guide sleeve 28, a pressure pin 29 is arranged. In this case, the pressure pin 29 is displaceably guided in the guide sleeve 28 along a longitudinal axis 30 of the actuator module 2. The displacement is possible within certain limits.
  • a metallic membrane 31 is provided, which is connected both by means of a circumferential weld 32 at one end of the guide sleeve 28 and by means of a circumferential weld with one end of the pressure pin 29.
  • laser welding can be used to form the welds 32, 33.
  • a gas-tight seal is ensured.
  • a distance 36 is formed between an end face 34 of the transition piece 19 and an end face 35 of the pressure pin 29.
  • the end faces 34, 35 face each other. Furthermore, the end faces 34, 35 each extend radially to the longitudinal axis 30. The distance 36 between the end faces 34, 35 therefore results along the longitudinal axis 30.
  • the pressure pin 29 is displaceable within certain limits, so that a variation of the distance 36 is made possible .
  • the end face 34 of the transition piece 19, the end face 35 of the pressure pin 29 and the guide sleeve 28 include a compensation chamber 37 a.
  • a volume of the compensation chamber 37 is determined by the distance 36. Corresponding to the distance 36 thus results in a certain Volume of the compensation chamber 37. In this case, the volume of the compensation chamber 37 varies according to the distance 36.
  • the interior 24 is connected via a connecting channel 38 with the compensation chamber 37.
  • the connecting channel 38 has a throttle 39.
  • the connecting channel 38 is therefore designed as a throttled connecting channel 38.
  • the interior 24, the connection channel 38 and the compensation chamber 37 are filled with a pressure fluid 40.
  • the pressurized fluid 40 may be formed, for example, by a transformer oil.
  • About the throttled connection channel 38 is gradually a balance between the interior 24 and the compensation chamber 37 allows in both directions. This compensation is due to the throttle 39 is relatively slow.
  • the actuator body 18 is charged to actuate the nozzle needle 7 and again discharged or discharged and then reloaded.
  • the actuator module 2 acts on the nozzle needle 7, as illustrated by the double arrow 41.
  • the force and the stroke of the actuator body 18 transmits to the actuator head 19.
  • the actuator head 19 is at non-disappearing distance 36, however, only by means provided in the expansion chamber 37 pressure fluid 40 in operative connection with the pressure pin 29.
  • the force acting on the actuator head 19 Aktorkraft and The related Aktorhub thus transferred via the pressure fluid 40 to the pressure pin 29. From the pressure pin 29 there is a direct or indirect transfer to the nozzle needle 7.
  • the throttle 39 prevents this transfer, that due to the Aktorhubs a significant amount of the pressurized fluid 40 is displaced from the expansion chamber 37 into the interior 24 of the sealing sleeve 23.
  • the actuator force and the stroke of the actuator body 18 can be transmitted at least substantially to the pressure pin 29.
  • a substantially undamped transmission of the force and the stroke of the actuator body 18 on the pressure pin 29 is made possible.
  • the actuator body 18 heats up.
  • the heat of the actuator body 18 is dissipated in the interior 24, inter alia via the pressure fluid 40.
  • the pressure fluid 40 in the interior 24 also heats up.
  • the ceramic material of the piezoelectric actuator body 18 has a negative coefficient of thermal expansion.
  • the actuator body 18 is shortened along the longitudinal axis 30.
  • the pressurized fluid 40 has a positive coefficient of thermal expansion, so that the volume of the pressurized fluid 40 in the interior space 24 increases. This means a certain pressure increase of the pressure fluid 40 in the interior space 24.
  • the pressure fluid 40 flows from the interior 24 via the connecting channel 38 in the expansion chamber 37.
  • This compensation takes place until at least approximately the same pressure of the pressure fluid 40 prevails in the interior 24 and in the compensation chamber 37.
  • the pressurized fluid is incompressible.
  • the amount of pressurized fluid 40 in the expansion chamber 37 has increased.
  • the distance 36 between the end faces 34, 35 has increased. Since the actuator body 18 is shortened during the temperature increase, but the distance 36 has increased, the result is at least partial compensation.
  • the total length of the actuator module 2 remains at least approximately constant even with temperature increases. The same applies to temperature reductions.
  • a defined distance 36 may be predetermined at a temperature of for example 20 ° C. This allows even at temperature drops below 20 ° C, for example, when the fuel injector 1 is operated at low ambient temperatures, a balance over the entire application area.
  • the actuator body 18 is surrounded on its outer side by an insulating layer 45.
  • the insulation layer 45 is configured here as a gel-like insulation layer 45.
  • the insulating layer 45 may be formed on the basis of an insulating gel.
  • Such an insulating gel may be formed by a material having a backbone of perfluoropolyether and silicon crosslinking groups.
  • the isolation gel can be selected from a group of materials known under the name Sifel.
  • Fig. 2 shows an actuator module 2 of a fuel injection valve 1 in a schematic sectional view according to a second embodiment.
  • a weld 25 is formed between an outer side 46 of the actuator head 19 and the sealing sleeve 23, which includes the guide sleeve 28, which is interrupted in sections.
  • 19 one or more connection points 47 are formed between the guide sleeve 28 and the outer side 46 of the actuator head, which are configured as a connecting gap 47.
  • a throttled connection between the interior 24 and the compensation chamber 37 is formed.
  • pressure fluid 40 from the interior 24 via the connection point 47 in the Compensation space 37, as illustrated by a flow line 48, and vice versa.
  • temperature-induced changes in length of the actuator body 18 can be compensated by a successively taking place exchange of pressurized fluid 40 between the interior 24 and the compensation chamber 37.
  • a kind of hydraulic coupler is formed over the compensation chamber 37.
  • the stroke which is given by the distance 36, determined by the expansion of the pressure fluid 40 in the interior 24.
  • the configured as a bellows metallic sealing sleeve 23 receives occurring during operation length changes. This ensures good durability. Due to the compensation of the temperature-induced changes in length of the actuator body 18, the actuator module 2 can be installed depending on the application without further thermal compensation components in a fuel injector 1 or the like.
  • a cross section of the compensation chamber 37 may be predetermined. This is achieved via the radial extent of the end faces 34, 35 or the diameters of the transition piece 19 and the pressure pin 29.
  • a pressurized fluid 40 having a certain coefficient of thermal expansion can be selected.
  • a pressurized fluid 40 with a certain coefficient of thermal expansion can be selected.
  • the effect of the throttle 39 or the throttle effect of one or more connection points 47 can be adapted to the respective application.
  • temperature changes occur during operation of the fuel injection valve 1 is relatively slow, the throttle effect can be relatively pronounced in the rule.
  • a related loss of efficiency of the actuator module 2 is at least largely prevented.
  • a compression spring 17 may be designed to be weaker in terms of their spring constant and / or bias or omitted entirely.
  • the sealing sleeve 23 a bias between the two transition pieces 19, 20 apply. This is in the Fig. 2 illustrated.
  • the compensation taking place via the compensation chamber 37 can also take place in the area of the actuator foot 20.
  • a configuration is also conceivable in which a compensation chamber 47 is provided both on the actuator head 19 and on the actuator base 20.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Aktormodul für ein Brennstoffeinspritzventil und ein Brennstoffeinspritzventil mit einem Aktormodul. Speziell betrifft die Erfindung das Gebiet der Injektoren für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to an actuator module for a fuel injection valve and a fuel injection valve with an actuator module. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.

Aus der DE 103 36 327 A1 ist ein Injektor für Einspritzsysteme von Brennkraftmaschinen, insbesondere von direkteinspritzenden Dieselmotoren, bekannt. Der bekannte Injektor besitzt einen in einem Injektorkörper angeordneten Piezoaktor, der über Federmittel einerseits mit dem Injektor und andererseits mit einem hülsenartigen Übersetzerkolben in Anlage gehalten wird. Ferner ist ein mit dem Injektorkörper verbundener Düsenkörper vorgesehen, der mindestens eine Düsenaustrittsöffnung aufweist. In dem Düsenkörper ist eine Düsennadel axial verschieblich geführt.From the DE 103 36 327 A1 is an injector for injection systems of internal combustion engines, in particular direct injection diesel engines, known. The known injector has a piezoelectric actuator arranged in an injector body, which is held in abutment via spring means on the one hand with the injector and on the other hand with a sleeve-like booster piston. Furthermore, a nozzle body connected to the injector body is provided, which has at least one nozzle outlet opening. In the nozzle body, a nozzle needle is guided axially displaceable.

Der aus der DE 103 36 327 A1 bekannte Injektor hat den Nachteil, dass im Betrieb temperaturbedingte Dehnungen des Piezoaktors und des Injektorkörpers zu einer relativen Verstellung des Übersetzerkolbens führen, die daher ausgeglichen werden müssen. Dies stellt eine zusätzliche Anforderung an die Auslegung des Übersetzerkolbens.The from the DE 103 36 327 A1 known injector has the disadvantage that in operation temperature-induced expansions of the piezoelectric actuator and the injector lead to a relative displacement of the booster piston, which must therefore be compensated. This places an additional requirement on the design of the booster piston.

Dokument EP 1457 662 A1 oder DE 102007053423 offenbart ein Brennstoffeinspritiventil, mit einem piezoelektrischen, elektrostriktiven oder magnetostriktiven Aktor.document EP 1457 662 A1 or DE 102007053423 discloses a fuel injector valve with a piezoelectric, electrostrictive or magnetostrictive actuator.

Vorteile der ErfindungAdvantages of the invention

Der erfindungsgemäße Aktormodul mit den Merkmalen des Anspruchs 1 und das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 9 haben demgegenüber den Vorteil, dass temperaturbedingte Längenänderungen zumindest teilweise kompensiert sind. Speziell sind die Anforderungen an einen innerhalb des Brennstoffeinspritzventils zusätzlich vorgesehenen Temperaturausgleich verringert, wodurch die Wirkungskette des Aktormoduls zum Betätigen eines Ventilschließkörpers optimiert ist.The actuator module according to the invention with the features of claim 1 and the fuel injection valve according to the invention with the features of claim 9 have the advantage that temperature-induced changes in length are at least partially compensated. Specifically, the requirements for an additionally provided within the fuel injection valve temperature compensation is reduced, whereby the chain of effects of the actuator module is optimized for actuating a valve closing body.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Aktormoduls und des im Anspruch 9 angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous refinements of the actuator module specified in claim 1 and the fuel injection valve specified in claim 9 are possible.

Vorteilhaft ist es, dass eine Führungshülse vorgesehen ist, in der der Druckbolzen geführt ist, und dass der Ausgleichsraum von dem Übergangsstück, der Führungshülse und dem in der Führungshülse geführten Druckbolzen begrenzt ist. Hierbei ist es ferner vorteilhaft, dass die Dichthülse einen hohlzylinderförmigen Abschnitt aufweist, der die Führungshülse bildet. Durch ein Verschieben des Druckbolzens entlang der Längsachse wird das Volumen des Ausgleichsraums vergrößert oder verringert. Hierbei dehnt sich bei einer Temperaturerhöhung des Druckfluids das Druckfluid aus, so dass dieses nach und nach über die gedrosselte Verbindung in den Ausgleichsraum gedrängt wird. Hierdurch wird das Volumen des Ausgleichsraums vergrößert. Dadurch nimmt auch der Abstand des Druckbolzens von dem Übergangsstück zu. Bei der Temperaturerhöhung kommt es auf Grund eines negativen Temperaturausdehnungskoeffizienten des piezokeramischen Werkstoffs des Aktorkörpers zu einer Verkürzung des Aktorkörpers. Diese beiden Effekte wirken somit gegeneinander, so dass temperaturbedingte Längenänderungen der Bauteile des Aktormoduls über die hierbei auftretende Volumenänderung des Ausgleichsraums zumindest teilweise, insbesondere im Wesentlichen, kompensiert sind. Durch die gedrosselte Verbindung erfolgt ein solcher Temperaturausgleich durch Volumenzu- oderabnahme des Ausgleichsraums über einen relativ langen Zeitraum verglichen mit dem beim Betätigen des Aktormoduls auftretenden Hüben des Aktorkörpers. Hierdurch kann eine Aktorkraft und ein Aktorhub zumindest im Wesentlichen dämpfungsfrei zum Betätigen einer Ventilnadel oder dergleichen genutzt werden.It is advantageous that a guide sleeve is provided, in which the pressure pin is guided, and that the compensation space of the transition piece, the guide sleeve and guided in the guide sleeve pressure pin is limited. Here, it is also advantageous that the sealing sleeve has a hollow cylindrical portion which forms the guide sleeve. By moving the pressure pin along the longitudinal axis, the volume of the expansion chamber is increased or decreased. In this case expands at a temperature increase of the pressurized fluid, the pressure fluid, so that this is gradually pushed over the throttled connection in the expansion chamber. As a result, the volume of the compensation chamber is increased. As a result, the distance of the pressure bolt from the transition piece increases. When the temperature increases, it comes to a shortening of the actuator body due to a negative coefficient of thermal expansion of the piezoceramic material of the actuator body. These two effects thus act against each other, so that temperature-induced changes in length of the components of the actuator module on the case occurring volume change of the expansion chamber are at least partially, in particular substantially compensated. Due to the throttled connection, such a temperature compensation takes place by increasing or decreasing the volume of the compensation chamber over a relatively long period compared to the strokes of the actuator body occurring when the actuator module is actuated. As a result, an actuator force and an actuator stroke can be used at least substantially without damping for actuating a valve needle or the like.

Die Dichthülse ist in vorteilhafter Weise als metallische Dichthülse ausgestaltet, so dass das Aktormodul in einem mit Brennstoff gefüllten Raum angeordnet sein kann. Speziell kann hierdurch eine Abdichtung gegenüber unter hohem Druck stehenden Brennstoff gewährleistet werden. Speziell kann hierdurch ein direkt gesteuertes Brennstoffeinspritzventil realisiert werden.The sealing sleeve is configured in an advantageous manner as a metallic sealing sleeve, so that the actuator module can be arranged in a space filled with fuel. In particular, this can be used to ensure a seal against high-pressure fuel. In particular, this can be used to realize a directly controlled fuel injection valve.

Vorteilhaft ist es auch, dass das Übergangsstück zumindest einen gedrosselten Verbindungskanal aufweist, der den Innenraum der Dichthülse mit dem Ausgleichsraum verbindet, und dass die gedrosselte Verbindung zwischen dem Innenraum und dem Ausgleichsraum zumindest den gedrosselten Verbindungskanal umfasst. Speziell kann der gedrosselte Verbindungskanal als Drosselbohrung ausgestaltet sein. Hierdurch ist eine genaue Vorgabe der Drosselwirkung und somit Auslegung der gedrosselten Verbindung möglich.It is also advantageous that the transition piece has at least one throttled connection channel, which connects the interior of the sealing sleeve with the compensation chamber, and that the throttled connection between the interior and the compensation chamber comprises at least the throttled connection channel. Specifically, the throttled connection channel can be designed as a throttle bore. This is a exact specification of the throttle effect and thus interpretation of the throttled connection possible.

Vorteilhaft ist es auch, dass eine mit dem Übergangsstück verbundene Führungshülse vorgesehen ist, in der der Druckbolzen geführt ist, dass zwischen der Führungshülse und einer Außenseite des Übergangsstücks zumindest eine gedrosselte Verbindungsstelle gebildet ist und dass die gedrosselte Verbindung zwischen dem Innenraum und dem Ausgleichsraum zumindest die gedrosselte Verbindungsstelle umfasst. Hierdurch ist eine kostengünstige Ausgestaltung der gedrosselten Verbindung möglich. Außerdem steht bei einem gegebenenfalls als Aktorfuß ausgestalteten Übergangsstück das Übergangsstück selbst für Kabeldurchführungen oder dergleichen zur Verfügung.It is also advantageous that a guide sleeve connected to the transition piece is provided, in which the pressure bolt is guided, that between the guide sleeve and an outer side of the transition piece at least a throttled connection point is formed and that the throttled connection between the interior and the compensation space at least the throttled junction comprises. As a result, a cost-effective design of the throttled connection is possible. In addition, in an optionally designed as Aktorfuß transition piece, the transition piece itself for cable glands or the like is available.

Ferner ist es vorteilhaft, dass die gedrosselte Verbindungsstelle durch einen gedrosselten Verbindungsspalt in einer abschnittsweise umlaufenden Schweißnaht gebildet ist, die die Führungshülse mit dem Übergangsstück verbindet. Hierbei können auch mehrere solche Verbindungsspalte vorgesehen sein.Further, it is advantageous that the throttled connection point is formed by a throttled connection gap in a partially circumferential weld, which connects the guide sleeve with the transition piece. In this case, a plurality of such connection gaps can also be provided.

Ferner ist es vorteilhaft, dass das Druckfluid zumindest im Wesentlichen auf der Basis eines Trafoöls gebildet ist. Vorteilhaft ist es auch, dass der Aktorkörper von einer gelartigen Isolationsschicht auf der Basis zumindest eines Werkstoffs mit einem Backbone aus Perfluorpolyether und Vernetzungsgruppen aus Silizium umgeben ist. Speziell kann der Werkstoff aus einer Werkstoffgruppe gewählt sein, die unter dem Namen Sifel bekannt ist.Furthermore, it is advantageous that the pressure fluid is formed at least substantially on the basis of a transformer oil. It is also advantageous that the actuator body is surrounded by a gel-like insulating layer on the basis of at least one material with a backbone of perfluoropolyether and crosslinking groups of silicon. Specifically, the material may be selected from a group of materials known under the name Sifel.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung anhand der beigefügten Zeichnungen, in denen sich entsprechende Element mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 ein Brennstoffeinspritzventil mit einem Aktormodul in einer schematischen, auszugsweisen Schnittdarstellung entsprechend einem ersten Ausführungsbeispiel der Erfindung und
  • Fig. 2 ein Aktormodul für ein Brennstoffeinspritzventil in einer schematischen Schnittdarstellung entsprechend einem zweiten Ausführungsbeispiel der Erfindung.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with corresponding reference numerals. It shows:
  • Fig. 1 a fuel injection valve with an actuator module in a schematic, partial sectional view according to a first embodiment of the invention and
  • Fig. 2 an actuator module for a fuel injection valve in a schematic sectional view according to a second embodiment of the invention.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt ein Brennstoffeinspritzventil 1 mit einem Aktormodul 2 in einer schematischen, auszugsweisen Schnittdarstellung entsprechend einem ersten Ausführungsbeispiel. Das Brennstoffeinspritzventil 1 kann insbesondere als Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Ein bevorzugter Einsatz des Brennstoffeinspritzventils 1 besteht für eine Brennstoffeinspritzanlage mit einem Common-Rail, das Dieselbrennstoff unter hohem Druck zu mehreren Brennstoffeinspritzventilen 1 führt. Das erfindungsgemäße Aktormodul 2 eignet sich besonders für solche Brennstoffeinspritzventile 1. Das erfindungsgemäße Brennstoffeinspritzventil 1 und das erfindungsgemäße Aktormodul 2 eignen sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows a fuel injection valve 1 with an actuator module 2 in a schematic, excerpted sectional view according to a first embodiment. The fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines. A preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail, the diesel fuel under high pressure leads to a plurality of fuel injection valves 1. The actuator module 2 according to the invention is particularly suitable for such fuel injection valves 1. However, the fuel injection valve 1 according to the invention and the actuator module 2 according to the invention are also suitable for other applications.

Das Brennstoffeinspritzventil 1 weist ein Ventilgehäuse 3 und einen Düsenkörper 4 auf. Der Düsenkörper 4 ist beispielsweise über eine Düsenspannmutter mit dem Ventilgehäuse 3 verbunden. An dem Düsenkörper 4 ist eine Ventilsitzfläche 5 ausgestaltet. Ferner ist ein Ventilschließkörper 6 vorgesehen, der in diesem Ausführungsbeispiel einstückig mit einer Düsennadel 7 ausgebildet ist. Der Ventilschließkörper 6 wirkt mit der Ventilsitzfläche 5 zu einem Dichtsitz zusammen. In dem Düsenkörper 4 ist ein Brennstoffraum 8 ausgestaltet, in dem sich im Betrieb unter hohem Druck stehender Brennstoff befindet. Mittels der Düsennadel 7 kann der Ventilschließkörper 6 betätigt werden, so dass der Dichtsitz geöffnet und Brennstoff aus dem Brennstoffraum 8 über eine Düsenöffnung 9 in den Brennraum einer Brennkraftmaschine einspritzbar ist.The fuel injection valve 1 has a valve housing 3 and a nozzle body 4. The nozzle body 4 is connected, for example via a nozzle lock nut with the valve housing 3. On the nozzle body 4, a valve seat surface 5 is configured. Further, a valve closing body 6 is provided, which is formed integrally with a nozzle needle 7 in this embodiment. The valve closing body 6 cooperates with the valve seat surface 5 to form a sealing seat. In the nozzle body 4, a fuel chamber 8 is configured, in which there is in operation under high pressure fuel. By means of the nozzle needle 7, the valve closing body 6 can be actuated, so that the sealing seat is opened and fuel from the fuel chamber 8 via a nozzle opening 9 in the combustion chamber of an internal combustion engine can be injected.

Innerhalb des Ventilgehäuses 3 ist ein Aktorraum 15 ausgestaltet, in dem sich das Aktormodul 2 befindet. Hierbei kann je nach Ausgestaltung des Brennstoffeinspritzventils 1 im Aktorraum 15 unter hohem Druck stehender Brennstoff vorgesehen sein, der beispielsweise durch den Aktorraum 15 des Ventilgehäuses 3 zu dem Brennstoffraum 8 geführt wird. Das Aktormodul 2 ist an einer Seite an einem Gehäuseteil 16 abgestützt. An einer anderen Seite ist das Aktormodul 2 von einer Druckfeder 17 beaufschlagt. Die Druckfeder 17 stützt sich hierbei an dem Ventilgehäuse 3 ab.Within the valve housing 3, an actuator chamber 15 is configured, in which the actuator module 2 is located. Depending on the design of the fuel injection valve 1, high-pressure fuel may be provided in the actuator chamber 15 which is guided, for example, through the actuator chamber 15 of the valve housing 3 to the fuel chamber 8. The actuator module 2 is supported on one side on a housing part 16. On another side, the actuator module 2 is acted upon by a compression spring 17. The compression spring 17 is supported here on the valve housing 3.

Das Aktormodul 2 weist einen piezoelektrischen Aktorkörper 18 auf, der eine Vielzahl von keramischen Schichten und eine Vielzahl von zwischen den keramischen Schichten angeordneten Elektrodenschichten umfasst. Hierbei sind die Elektrodenschichten abwechselnd mit elektrischen Zuleitungen (nicht dargestellt) kontaktiert, um ein Laden und Entladen des Aktorkörpers 18 zu ermöglichen. Der Aktorkörper 18 ist zwischen Übergangsstücken 19, 20 angeordnet. Hierbei sind die Übergangsstücke 19, 20 des Aktormoduls 2 an voneinander abgewandten Stirnseiten 21, 22 des Aktorkörpers 18 an den Aktorkörper 18 angefügt. In diesem Ausführungsbeispiel ist das Übergangsstück 19 als Aktorkopf ausgestaltet, und das Übergangsstück 20 ist als Aktorfuß ausgestaltet.The actuator module 2 has a piezoelectric actuator body 18, which comprises a plurality of ceramic layers and a plurality of electrode layers arranged between the ceramic layers. In this case, the electrode layers are alternately contacted with electrical leads (not shown) in order to allow loading and unloading of the actuator body 18. The actuator body 18 is arranged between transition pieces 19, 20. Here, the transition pieces 19, 20 of the actuator module 2 at opposite end faces 21, 22 of the actuator body 18 to the Actuator 18 added. In this embodiment, the transition piece 19 is designed as an actuator head, and the transition piece 20 is designed as Aktorfuß.

Das Aktormodul 2 weist ferner eine Dichthülse 23 auf, die als metallische Dichthülse 23 in Form eines Wellbalgs 23 ausgestaltet ist. Die Dichthülse 23 dichtet einen Innenraum 24 des Aktormoduls 2 ab. Der Aktorkörper 18 ist in dem Innenraum 24 angeordnet. Die Dichthülse 23 ist hierbei über eine umlaufende Schweißnaht 25 mit dem Aktorkopf 19 verbunden. Ferner ist die Dichthülse 23 mit einer umlaufenden Schweißnaht 26 mit dem Aktorfuß 20 verbunden. Die Schweißnähte 25, 26 sind hierbei abdichtend ausgestaltet, so dass über diese kein Brennstoff aus dem Aktorraum 15 in den Innenraum 24 gelangen kann. Außerdem ist durch die Dichthülse 23 eine Abdichtung des Innenraums 24 gegenüber dem Brennstoff gebildet. Daher ist der Innenraum 24 des Aktormoduls 2 zuverlässig gegenüber der Umgebung abgedichtet.The actuator module 2 further comprises a sealing sleeve 23, which is designed as a metallic sealing sleeve 23 in the form of a corrugated bellows 23. The sealing sleeve 23 seals an inner space 24 of the actuator module 2. The actuator body 18 is arranged in the interior 24. The sealing sleeve 23 is in this case connected via a peripheral weld 25 with the actuator head 19. Further, the sealing sleeve 23 is connected to a circumferential weld 26 with the actuator base 20. The welds 25, 26 are designed sealingly, so that no fuel from the actuator chamber 15 can get into the interior 24 via this. In addition, a seal of the inner space 24 is formed by the sealing sleeve 23 against the fuel. Therefore, the inner space 24 of the actuator module 2 is reliably sealed from the environment.

In diesem Ausführungsbeispiel ist die Dichthülse 23 an einem Endabschnitt 27 kragenförmig aufgebogen, um eine Abstützung der Druckfeder 17 zu ermöglichen. Hierdurch kann die Anzahl der benötigten Bauteile reduziert werden. Ferner weist die Dichthülse 23 einen hohlzylinderförmigen Abschnitt 28 auf. Der hohlzylinderförmige Abschnitt 28 bildet eine Führungshülse 28 des Aktormoduls 2. In diesem Ausführungsbeispiel ist die Führungshülse 28 innerhalb der Druckfeder 17 angeordnet. Innerhalb der Führungshülse 28 ist ein Druckbolzen 29 angeordnet. Der Druckbolzen 29 ist hierbei entlang einer Längsachse 30 des Aktormoduls 2 verschiebbar in der Führungshülse 28 geführt. Die Verschiebbarkeit ist hierbei innerhalb gewisser Grenzen ermöglicht. Ferner ist eine metallische Membran 31 vorgesehen, die sowohl mittels einer umlaufenden Schweißnaht 32 an einem Ende der Führungshülse 28 als auch mittels einer umlaufenden Schweißnaht mit einem Ende des Druckbolzens 29 verbunden ist. Hierbei kann zum Ausbilden der Schweißnähte 32, 33 ein Laserschweißen zum Einsatz kommen. Durch die Membran 31 ist eine gasdichte Abdichtung gewährleistet.In this embodiment, the sealing sleeve 23 is bent collar-shaped at one end portion 27 to allow a support of the compression spring 17. As a result, the number of required components can be reduced. Furthermore, the sealing sleeve 23 has a hollow cylindrical portion 28. The hollow cylindrical portion 28 forms a guide sleeve 28 of the actuator module 2. In this embodiment, the guide sleeve 28 is disposed within the compression spring 17. Within the guide sleeve 28, a pressure pin 29 is arranged. In this case, the pressure pin 29 is displaceably guided in the guide sleeve 28 along a longitudinal axis 30 of the actuator module 2. The displacement is possible within certain limits. Further, a metallic membrane 31 is provided, which is connected both by means of a circumferential weld 32 at one end of the guide sleeve 28 and by means of a circumferential weld with one end of the pressure pin 29. In this case, laser welding can be used to form the welds 32, 33. Through the membrane 31, a gas-tight seal is ensured.

In diesem Ausführungsbeispiel ist zwischen einer Stirnfläche 34 des Übergangsstücks 19 und einer Stirnfläche 35 des Druckbolzens 29 ein Abstand 36 gebildet. Die Stirnflächen 34, 35 sind einander zugewandt. Ferner erstrecken sich die Stirnflächen 34, 35 jeweils radial zu der Längsachse 30. Der Abstand 36 zwischen den Stirnflächen 34, 35 ergibt sich daher entlang der Längsachse 30. Der Druckbolzen 29 ist innerhalb gewisser Grenzen verschiebbar, so dass eine Variation des Abstands 36 ermöglicht ist. Die Stirnfläche 34 des Übergangsstücks 19, die Stirnfläche 35 des Druckbolzens 29 und die Führungshülse 28 schließen einen Ausgleichsraum 37 ein. Ein Volumen des Ausgleichsraums 37 ist durch den Abstand 36 bestimmt. Entsprechend dem Abstand 36 ergibt sich somit ein gewisses Volumen des Ausgleichsraums 37. Hierbei variiert das Volumen des Ausgleichsraums 37 entsprechend dem Abstand 36.In this embodiment, a distance 36 is formed between an end face 34 of the transition piece 19 and an end face 35 of the pressure pin 29. The end faces 34, 35 face each other. Furthermore, the end faces 34, 35 each extend radially to the longitudinal axis 30. The distance 36 between the end faces 34, 35 therefore results along the longitudinal axis 30. The pressure pin 29 is displaceable within certain limits, so that a variation of the distance 36 is made possible , The end face 34 of the transition piece 19, the end face 35 of the pressure pin 29 and the guide sleeve 28 include a compensation chamber 37 a. A volume of the compensation chamber 37 is determined by the distance 36. Corresponding to the distance 36 thus results in a certain Volume of the compensation chamber 37. In this case, the volume of the compensation chamber 37 varies according to the distance 36.

Der Innenraum 24 ist über einen Verbindungskanal 38 mit dem Ausgleichsraum 37 verbunden. Hierbei weist der Verbindungskanal 38 eine Drossel 39 auf. Der Verbindungskanal 38 ist daher als gedrosselter Verbindungskanal 38 ausgestaltet. Somit besteht über den gedrosselten Verbindungskanal 38 eine gedrosselte Verbindung zwischen dem Innenraum 24 und dem Ausgleichsraum 37. Der Innenraum 24, der Verbindungskanal 38 und der Ausgleichsraum 37 sind mit einem Druckfluid 40 gefüllt. Das Druckfluid 40 kann beispielsweise durch ein Trafoöl gebildet sein. Über den gedrosselten Verbindungskanal 38 ist nach und nach ein Ausgleich zwischen dem Innenraum 24 und dem Ausgleichsraum 37 in beiden Richtungen ermöglicht. Dieser Ausgleich erfolgt auf Grund der Drossel 39 relativ langsam. Der Aktorkörper 18 wird zum Betätigen der Düsennadel 7 geladen und wieder entladen beziehungsweise entladen und dann wieder geladen. Hierdurch wirkt das Aktormodul 2 auf die Düsennadel 7 ein, wie es durch den Doppelpfeil 41 veranschaulicht ist. Hierbei überträgt sich die Kraft und der Hub des Aktorkörpers 18 auf den Aktorkopf 19. Der Aktorkopf 19 steht bei nicht verschwindendem Abstand 36 allerdings nur mittels des im Ausgleichsraum 37 vorgesehenen Druckfluids 40 in Wirkverbindung mit dem Druckbolzen 29. Die auf den Aktorkopf 19 wirkende Aktorkraft und der diesbezügliche Aktorhub übertragen sich somit über das Druckfluid 40 auf den Druckbolzen 29. Von dem Druckbolzen 29 kommt es zu einer direkten oder mittelbaren Übertragung auf die Düsennadel 7. Die Drossel 39 verhindert bei dieser Übertragung, dass auf Grund des Aktorhubs eine deutliche Menge des Druckfluids 40 aus dem Ausgleichsraum 37 in den Innenraum 24 der Dichthülse 23 verdrängt wird. Somit können die Aktorkraft und der Hub des Aktorkörpers 18 zumindest im Wesentlichen auf den Druckbolzen 29 übertragen werden. Somit ist ein im Wesentlichen ungedämpftes Übertragen der Kraft und des Hubs von dem Aktorkörper 18 auf den Druckbolzen 29 ermöglicht.The interior 24 is connected via a connecting channel 38 with the compensation chamber 37. Here, the connecting channel 38 has a throttle 39. The connecting channel 38 is therefore designed as a throttled connecting channel 38. Thus, there is a throttled connection between the interior 24 and the compensation chamber 37 via the throttled connection channel 38. The interior 24, the connection channel 38 and the compensation chamber 37 are filled with a pressure fluid 40. The pressurized fluid 40 may be formed, for example, by a transformer oil. About the throttled connection channel 38 is gradually a balance between the interior 24 and the compensation chamber 37 allows in both directions. This compensation is due to the throttle 39 is relatively slow. The actuator body 18 is charged to actuate the nozzle needle 7 and again discharged or discharged and then reloaded. As a result, the actuator module 2 acts on the nozzle needle 7, as illustrated by the double arrow 41. In this case, the force and the stroke of the actuator body 18 transmits to the actuator head 19. The actuator head 19 is at non-disappearing distance 36, however, only by means provided in the expansion chamber 37 pressure fluid 40 in operative connection with the pressure pin 29. The force acting on the actuator head 19 Aktorkraft and The related Aktorhub thus transferred via the pressure fluid 40 to the pressure pin 29. From the pressure pin 29 there is a direct or indirect transfer to the nozzle needle 7. The throttle 39 prevents this transfer, that due to the Aktorhubs a significant amount of the pressurized fluid 40 is displaced from the expansion chamber 37 into the interior 24 of the sealing sleeve 23. Thus, the actuator force and the stroke of the actuator body 18 can be transmitted at least substantially to the pressure pin 29. Thus, a substantially undamped transmission of the force and the stroke of the actuator body 18 on the pressure pin 29 is made possible.

Im Betrieb des Brennstoffeinspritzventils 1 kommt es auf Grund des häufigen Ladens und Entladens des Aktorkörpers 18 und der damit verbundenen mechanischen Betätigung zu einer Erwärmung des Aktorkörpers 18. Die Wärme des Aktorkörpers 18 wird hierbei unter anderem über das Druckfluid 40 im Innenraum 24 abgeführt. Hierdurch erwärmt sich auch das Druckfluid 40 im Innenraum 24. Der keramische Werkstoff des piezoelektrischen Aktorkörpers 18 hat einen negativen Temperaturausdehnungskoeffizienten. Durch die Erwärmung kommt es daher zu einer Verkürzung des Aktorkörpers 18 entlang der Längsachse 30. Das Druckfluid 40 hat einen positiven Temperaturausdehnungskoeffizienten, so dass sich das Volumen des Druckfluids 40 im Innenraum 24 vergrößert. Dies bedeutet einen gewissen Druckanstieg des Druckfluids 40 im Innenraum 24. Hierdurch kommt es nach und nach zu einem Ausgleich, bei dem das Druckfluid 40 aus dem Innenraum 24 über den Verbindungskanal 38 in den Ausgleichsraum 37 fließt. Dieser Ausgleich erfolgt solange, bis im Innenraum 24 und im Ausgleichsraum 37 zumindest näherungsweise der gleiche Druck des Druckfluids 40 herrscht. Das Druckfluid ist inkompressibel. Bei dem Ausgleich hat sich die Menge des Druckfluids 40 im Ausgleichsraum 37 vergrößert. Somit ist es bei dem Ausgleich zu einer Volumenvergrößerung des Ausgleichsraums 37 gekommen. Hierdurch hat sich der Abstand 36 zwischen den Stirnflächen 34, 35 vergrößert. Da sich der Aktorkörper 18 bei der Temperaturerhöhung verkürzt, der Abstand 36 aber vergrößert hat, kommt es im Ergebnis zu einer zumindest teilweisen Kompensation. Hierdurch bleibt die Gesamtlänge des Aktormoduls 2 auch bei Temperaturerhöhungen zumindest näherungsweise konstant. Entsprechendes gilt für Temperatursenkungen.During operation of the fuel injection valve 1, due to the frequent charging and discharging of the actuator body 18 and the associated mechanical actuation, the actuator body 18 heats up. The heat of the actuator body 18 is dissipated in the interior 24, inter alia via the pressure fluid 40. As a result, the pressure fluid 40 in the interior 24 also heats up. The ceramic material of the piezoelectric actuator body 18 has a negative coefficient of thermal expansion. As a result of the heating, the actuator body 18 is shortened along the longitudinal axis 30. The pressurized fluid 40 has a positive coefficient of thermal expansion, so that the volume of the pressurized fluid 40 in the interior space 24 increases. This means a certain pressure increase of the pressure fluid 40 in the interior space 24. As a result, it gradually comes to a balance in which the pressure fluid 40 flows from the interior 24 via the connecting channel 38 in the expansion chamber 37. This compensation takes place until at least approximately the same pressure of the pressure fluid 40 prevails in the interior 24 and in the compensation chamber 37. The pressurized fluid is incompressible. In the compensation, the amount of pressurized fluid 40 in the expansion chamber 37 has increased. Thus, it has come in the balance to an increase in volume of the expansion chamber 37. As a result, the distance 36 between the end faces 34, 35 has increased. Since the actuator body 18 is shortened during the temperature increase, but the distance 36 has increased, the result is at least partial compensation. As a result, the total length of the actuator module 2 remains at least approximately constant even with temperature increases. The same applies to temperature reductions.

Vorzugsweise befindet sich im Ausgangszustand von beispielsweise 20 °C bereits eine gewisse Menge des Druckfluids 40 im Ausgleichsraum 37. Hierbei kann ein definierter Abstand 36 bei einer Temperatur von beispielsweise 20 °C vorgegeben sein. Dies ermöglicht auch bei Temperatursenkungen unter 20 °C, beispielsweise wenn das Brennstoffeinspritzventil 1 bei niedrigen Umgebungstemperaturen in Betrieb genommen wird, einen Ausgleich über den gesamten Einsatzbereich.Preferably, in the initial state of, for example, 20 ° C already a certain amount of the pressure fluid 40 in the expansion chamber 37. In this case, a defined distance 36 may be predetermined at a temperature of for example 20 ° C. This allows even at temperature drops below 20 ° C, for example, when the fuel injector 1 is operated at low ambient temperatures, a balance over the entire application area.

In diesem Ausführungsbeispiel ist der Aktorkörper 18 an seiner Außenseite von einer Isolationsschicht 45 umgeben. Die Isolationsschicht 45 ist hierbei als gelartige Isolationsschicht 45 ausgestaltet. Beispielsweise kann die Isolationsschicht 45 auf der Basis eines Isolationsgels gebildet sein. Solch ein Isolationsgel kann durch einen Werkstoff mit einem Backbone (Grundgerüst) aus Perfluorpolyether und Vernetzungsgruppen aus Silizium gebildet sein. Speziell kann das Isolationsgel aus einer Werkstoffgruppe gewählt sein, die unter dem Namen Sifel bekannt ist.In this embodiment, the actuator body 18 is surrounded on its outer side by an insulating layer 45. The insulation layer 45 is configured here as a gel-like insulation layer 45. For example, the insulating layer 45 may be formed on the basis of an insulating gel. Such an insulating gel may be formed by a material having a backbone of perfluoropolyether and silicon crosslinking groups. Specifically, the isolation gel can be selected from a group of materials known under the name Sifel.

Fig. 2 zeigt ein Aktormodul 2 eines Brennstoffeinspritzventils 1 in einer schematischen Schnittdarstellung entsprechend einem zweiten Ausführungsbeispiel. In diesem Ausführungsbeispiel ist zwischen einer Außenseite 46 des Aktorkopfs 19 und der Dichthülse 23, die die Führungshülse 28 umfasst, eine Schweißnaht 25 gebildet, die abschnittsweise unterbrochen ist. Hierdurch sind zwischen der Führungshülse 28 und der Außenseite 46 des Aktorkopfs 19 ein oder mehrere Verbindungsstellen 47 gebildet, die als Verbindungsspalt 47 ausgestaltet sind. Über diese Verbindungsstellen 47 ist eine gedrosselte Verbindung zwischen dem Innenraum 24 und dem Ausgleichsraum 37 gebildet. Somit kann Druckfluid 40 aus dem Innenraum 24 über die Verbindungsstelle 47 in den Ausgleichsraum 37 gelangen, wie es durch eine Strömungslinie 48 veranschaulicht ist, und umgekehrt. Fig. 2 shows an actuator module 2 of a fuel injection valve 1 in a schematic sectional view according to a second embodiment. In this embodiment, a weld 25 is formed between an outer side 46 of the actuator head 19 and the sealing sleeve 23, which includes the guide sleeve 28, which is interrupted in sections. As a result, 19 one or more connection points 47 are formed between the guide sleeve 28 and the outer side 46 of the actuator head, which are configured as a connecting gap 47. About these connection points 47 a throttled connection between the interior 24 and the compensation chamber 37 is formed. Thus, pressure fluid 40 from the interior 24 via the connection point 47 in the Compensation space 37, as illustrated by a flow line 48, and vice versa.

Somit können temperaturbedingte Längenänderungen des Aktorkörpers 18 durch einen nach und nach erfolgenden Austausch von Druckfluid 40 zwischen dem Innenraum 24 und dem Ausgleichsraum 37 ausgeglichen werden.Thus, temperature-induced changes in length of the actuator body 18 can be compensated by a successively taking place exchange of pressurized fluid 40 between the interior 24 and the compensation chamber 37.

Somit ist über den Ausgleichsraum 37 eine Art hydraulischer Koppler gebildet. Hierbei ist der Hub, der durch den Abstand 36 gegeben ist, durch die Ausdehnung des Druckfluids 40 im Innenraum 24 bestimmt. Die als Wellbalg ausgestaltete metallische Dichthülse 23 nimmt während der Betätigung auftretende Längenänderungen auf. Dadurch ist eine gute Haltbarkeit gewährleistet. Durch die Kompensation der temperaturbedingten Längenänderungen des Aktorkörpers 18 kann das Aktormodul 2 je nach Anwendungsfall auch ohne weitere thermische Ausgleichskomponenten in ein Brennstoffeinspritzventil 1 oder dergleichen eingebaut werden.Thus, a kind of hydraulic coupler is formed over the compensation chamber 37. Here, the stroke, which is given by the distance 36, determined by the expansion of the pressure fluid 40 in the interior 24. The configured as a bellows metallic sealing sleeve 23 receives occurring during operation length changes. This ensures good durability. Due to the compensation of the temperature-induced changes in length of the actuator body 18, the actuator module 2 can be installed depending on the application without further thermal compensation components in a fuel injector 1 or the like.

In Bezug auf die Temperaturkompensation sind mehrere Abstimmmöglichkeiten gegeben. Beispielsweise kann ein Querschnitt des Ausgleichsraums 37 vorgegeben sein. Dies wird über die radiale Erstreckung der Stirnflächen 34, 35 beziehungsweise die Durchmesser des Übergangsstücks 19 und des Druckbolzens 29 erreicht. Ferner kann ein Druckfluid 40 mit einem gewissen Temperaturausdehnungskoeffizienten gewählt werden. Hierdurch kann innerhalb gewisser Grenzen ein Druckfluid 40 mit einem gewissen Temperaturausdehnungskoeffizienten gewählt werden. Außerdem kann das Volumen des Innenraums 24 durch die Ausgestaltung der Dichthülse 23, insbesondere eines mittleren Querschnitts der Dichthülse 23, vorgegeben sein. Somit kann in Bezug auf den vorgegebenen Aktorkörper 18 eine zumindest weitgehende Kompensation von temperaturbedingten Längenänderungen des Aktorkörpers 18 erfolgen. Ferner kann die Wirkung der Drossel 39 beziehungsweise der Drosselwirkung einer oder mehrerer Verbindungsstellen 47 an den jeweiligen Anwendungsfall angepasst sein. Da in der Regel Temperaturänderungen im Betrieb des Brennstoffeinspritzventils 1 relativ langsam erfolgen, kann die Drosselwirkung in der Regel relativ ausgeprägt sein. Hierdurch wird ein diesbezüglicher Wirkungsgradverlust des Aktormoduls 2 zumindest weitgehend verhindert.With regard to the temperature compensation, several tuning options are given. For example, a cross section of the compensation chamber 37 may be predetermined. This is achieved via the radial extent of the end faces 34, 35 or the diameters of the transition piece 19 and the pressure pin 29. Further, a pressurized fluid 40 having a certain coefficient of thermal expansion can be selected. As a result, within certain limits, a pressurized fluid 40 with a certain coefficient of thermal expansion can be selected. In addition, the volume of the inner space 24 by the configuration of the sealing sleeve 23, in particular a central cross section of the sealing sleeve 23, be predetermined. Thus, in relation to the given actuator body 18, an at least substantial compensation of temperature-induced changes in length of the actuator body 18 can take place. Furthermore, the effect of the throttle 39 or the throttle effect of one or more connection points 47 can be adapted to the respective application. As a rule, temperature changes occur during operation of the fuel injection valve 1 is relatively slow, the throttle effect can be relatively pronounced in the rule. As a result, a related loss of efficiency of the actuator module 2 is at least largely prevented.

Je nach Ausgestaltung des Aktormoduls 2 kann eine Druckfeder 17 hinsichtlich ihrer Federkonstante und/oder Vorspannung auch schwächer ausgelegt sein oder ganz entfallen. Hierfür kann beispielsweise die Dichthülse 23 eine Vorspannung zwischen den beiden Übergangsstücken 19, 20 aufbringen. Dies ist in der Fig. 2 veranschaulicht.Depending on the configuration of the actuator module 2, a compression spring 17 may be designed to be weaker in terms of their spring constant and / or bias or omitted entirely. For this purpose, for example, the sealing sleeve 23 a bias between the two transition pieces 19, 20 apply. This is in the Fig. 2 illustrated.

Außerdem kann die über den Ausgleichsraum 37 erfolgende Kompensation auch im Bereich des Aktorfußes 20 erfolgen. Prinzipiell ist auch eine Ausgestaltung denkbar, bei der sowohl am Aktorkopf 19 als auch am Aktorfuß 20 jeweils ein Ausgleichsraum 47 vorgesehen ist.In addition, the compensation taking place via the compensation chamber 37 can also take place in the area of the actuator foot 20. In principle, a configuration is also conceivable in which a compensation chamber 47 is provided both on the actuator head 19 and on the actuator base 20.

Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt.The invention is not limited to the described embodiments.

Claims (11)

  1. Actuator module (2), in particular for fuel injection valves, having a piezoelectric actuator body (18), having at least one transition piece (19) joined to the actuator body (18), and having a sealing sleeve (23) which seals off an interior space (24), wherein the actuator body (18) is arranged in the interior space (24), characterized in that a thrust pin (29) is provided which delimits a compensation chamber (37) between the transition piece (19) and the thrust pin (29), wherein the interior space (24) is filled with a pressure fluid (40), wherein the interior space (24) is connected to the compensation chamber (37), wherein the connection of the interior space (24) to the compensation chamber (37) is in the form of a throttled connection, and wherein the thrust pin (29) is movable along a longitudinal axis (30) in order to permit a change in volume of the compensation chamber (37).
  2. Actuator module according to Claim 1,
    characterized
    in that a guide sleeve (28) is provided, in which guide sleeve the thrust pin (29) is guided, and in that the compensation chamber (37) is delimited by the transition piece (19), by the guide sleeve (28) and by the thrust pin (29) guided in the guide sleeve (28).
  3. Actuator module according to Claim 2,
    characterized
    in that the sealing sleeve (23) has a hollow cylindrical portion (28) which forms the guide sleeve (28).
  4. Actuator module according to one of Claims 1 to 3,
    characterized
    in that the transition piece (19) has at least one throttled connecting duct (38) which connects the interior space (24) of the sealing sleeve (23) to the compensation chamber (37), and in that the throttled connection between the interior space (24) and the compensation chamber (37) comprises at least the throttled connecting duct.
  5. Actuator module according to one of Claims 1, 3 or 4,
    characterized
    in that a guide sleeve (28) is provided which is connected to the transition piece (19) and in which the thrust pin (29) is guided, in that at least one throttled connecting point (47) is formed between the guide sleeve (28) and an outer side (46) of the transition piece (19), and in that the throttled connection between the interior space (24) and the compensation chamber (37) comprises at least the throttled connecting point (47).
  6. Actuator module according to Claim 5,
    characterized
    in that the throttled connecting point (47) is formed by a throttled connecting gap (47) in a weld seam (25) which is encircling in segment form and which connects the guide sleeve (28) to the transition piece (19).
  7. Actuator module according to one of Claims 1 to 6,
    characterized
    in that the pressure fluid (40) is at least substantially based on a transformer oil.
  8. Actuator module according to one of Claims 1 to 7,
    characterized
    in that the actuator body (18) is surrounded by a gel-like insulation layer (45) based on at least one material with a backbone of perfluoropolyether and crosslinking groups of silicon.
  9. Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, autoignition internal combustion engines, having a piezoelectric actuator module (2) according to one of Claims 1 to 8, and having a valve closing body (6) which can be actuated by the actuator module (2) and which interacts with a valve seat surface (5) to form a sealing seat.
  10. Fuel injection valve according to Claim 9, characterized in that the transition piece (19) is formed as an actuator head (19), and in that the actuator head (19) transmits an actuator force of the actuator body (18) to the thrust pin (29) via the pressure fluid (40) arranged in the compensation chamber (37).
  11. Fuel injection valve according to Claim 9,
    characterized
    in that the transition piece (20) is formed as an actuator foot (20), and in that the actuator foot (20) is supported on the thrust pin via the pressure fluid (40) arranged in the compensation chamber, wherein the thrust pin is supported at least indirectly on a valve housing (3).
EP20100181972 2009-11-03 2010-09-29 Actuator module and fuel injection valve Not-in-force EP2317117B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910046356 DE102009046356A1 (en) 2009-11-03 2009-11-03 Actuator module and fuel injector

Publications (2)

Publication Number Publication Date
EP2317117A1 EP2317117A1 (en) 2011-05-04
EP2317117B1 true EP2317117B1 (en) 2012-12-26

Family

ID=43530941

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20100181972 Not-in-force EP2317117B1 (en) 2009-11-03 2010-09-29 Actuator module and fuel injection valve

Country Status (2)

Country Link
EP (1) EP2317117B1 (en)
DE (1) DE102009046356A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013219225A1 (en) * 2013-09-25 2015-03-26 Continental Automotive Gmbh Piezo injector for direct fuel injection

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19940055C1 (en) * 1999-08-24 2001-04-05 Siemens Ag Dosing valve
DE10310297A1 (en) * 2003-03-10 2004-09-23 Robert Bosch Gmbh Fuel injector
DE10336327B4 (en) 2003-08-07 2016-03-17 Robert Bosch Gmbh Injector for fuel injection systems of internal combustion engines, in particular direct injection diesel engines
DE102004060533A1 (en) * 2004-12-16 2006-06-29 Robert Bosch Gmbh Hydraulic coupler for use in fuel injecting valve, has pressure retaining unit in compensation area or in connection channel, where unit designed elastically provides restoring force on fluids of compensation area and connection channel
DE102007053423A1 (en) * 2007-11-09 2009-05-14 Robert Bosch Gmbh Piezoelectric actuator module

Also Published As

Publication number Publication date
EP2317117A1 (en) 2011-05-04
DE102009046356A1 (en) 2011-05-05

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