EP1252433B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1252433B1
EP1252433B1 EP00993183A EP00993183A EP1252433B1 EP 1252433 B1 EP1252433 B1 EP 1252433B1 EP 00993183 A EP00993183 A EP 00993183A EP 00993183 A EP00993183 A EP 00993183A EP 1252433 B1 EP1252433 B1 EP 1252433B1
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EP
European Patent Office
Prior art keywords
control valve
valve element
control
space
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00993183A
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German (de)
French (fr)
Other versions
EP1252433A2 (en
Inventor
Friedrich Boecking
Wolfgang Stoecklein
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1252433A2 publication Critical patent/EP1252433A2/en
Application granted granted Critical
Publication of EP1252433B1 publication Critical patent/EP1252433B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/025—Hydraulically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
    • 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

Definitions

  • the invention relates to a fuel injection valve for Internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection valve is known from DE 197 32 802 A known.
  • This fuel injection valve is part of a Storage fuel injection system.
  • the fuel injector has an axially displaceable guided injection valve member, is controlled by the at least one injection opening and the having a pressure chamber limiting pressure shoulder.
  • the Pressure chamber becomes pressurized fuel from a High-pressure fuel source supplied by the Injection valve member against a closing force for opening the at least one injection opening can be lifted from a valve seat.
  • Control valve provided by a by a piezoelectric actuator generated actuating force against a restoring force movable Control valve member having the in one with a pressure source
  • the control pressure chamber is controlled by the prevailing pressure that controls the Injection valve member at least indirectly in its closing direction applied.
  • the control valve member is the control pressure chamber connectable with a relief space and the control valve member acts with at least one sealing surface with at least one valve seat together, over which the connection of the control pressure space with the Relief space is controlled.
  • the control valve has two in the Movement direction of the control valve member spaced from each other Valve seats on and the control valve member is between two Closing positions movable, in which there are each with a Sealing surface rests against one of the valve seats and the control pressure chamber is separated from the discharge space.
  • control valve member At between his two Closed positions arranged control valve member is the Control pressure chamber connected to the discharge chamber.
  • the Control valve member is piston-shaped and the two Sealing surfaces are on opposite outer sides of the Control valve member arranged. In this training of Control valve member is a large space for the control valve required.
  • the fuel injection valve according to the invention with the features according to claim 1 has the advantage that the control valve with compact design can be performed.
  • FIG. 1 shows a Storage fuel injection system in schematic Representation
  • Figure 2 shows a fuel injection valve of the Storage fuel injection system in a longitudinal section according to a first embodiment
  • Figure 3 the Fuel injection valve in longitudinal section according to a modified embodiment
  • Figure 4 the Fuel injection valve in longitudinal section according to a second embodiment.
  • FIG. 1 A schematically illustrated in Figure 1 Storage fuel injection system has a high-pressure pump 10 on, by the fuel from a storage tank 12 below High pressure is conveyed into a memory 14.
  • the memory 14 is formed as a so-called rail, from the lines To dissipate fuel injection valves 16 which at a Internal combustion engine are arranged.
  • each Fuel injection valve 16 has a control valve 18, by opening and closing the Fuel injection valve 16 is controlled.
  • the Storage fuel injection system also has a Control device 20, the signals over various Operating parameters of the internal combustion engine are supplied and by depending on the control valves 18 of the Fuel injection valves 16 to open or close be controlled.
  • a fuel injection valve 16 with associated control valve 18 according to a first Embodiment shown.
  • the Fuel injection valve 16 has a valve body 22 in which an injection valve member 24 axially displaceable is guided.
  • the valve body 22 has at its the Combustion chamber of the engine facing end at least one, preferably a plurality of injection openings 26 on.
  • the injection valve member 24 has at its the Combustion chamber facing end an example, for example conical sealing surface 28, which with a in Valve body 22 formed valve seat 30 cooperates, from which discharge the injection openings 26.
  • an injection valve member 24 surrounding annular space 32 formed with a pressure chamber 34 is connected, which in turn connected to the memory 14 is, so that in the pressure chamber 34 of the high-pressure pump 10th generated pressure prevails.
  • the injection valve member 24 has a pressure shoulder 34 arranged in the pressure chamber 34, via the pressure prevailing in the pressure chamber 34 pressure in Opening direction 38 of the injection valve member 24 acting Exercise power on this.
  • On injection valve member 24 engages a biased closing spring 40, through which the Injection valve member 24 opposite to that in the pressure chamber 34 prevailing pressure on this in the opening direction 38th acting force is applied in the closing direction.
  • the Injection valve member 24 By the pressure prevailing in the pressure chamber 34 is the Injection valve member 24 against the force of the closing spring 40th movable in the opening direction 38 and gives the Injection openings 26 free, through the fuel in the Combustion chamber of the internal combustion engine is injected. to End of the injection, the injection valve member 24th in the closing direction with its sealing surface 28 in the Valve seat 30 is pressed against the valve body 22, so that the Injection openings 26 are closed.
  • a closing piston 42 arranged, which is part of the control valve 18.
  • the closing piston 42 is at least approximately coaxial arranged to the injection valve member 24 and in a bore 44 in a housing part 46 of the control valve 18 axially slidably guided.
  • the closing piston 42 defines a hole in the bore 44 Control pressure chamber 48, via a channel 49, in which a Throttle 50 is arranged, connected to the memory 14 is.
  • the bore 44 faces away from the closing piston 42 stepped formed and has a portion 44a with reduced diameter and then this again an enlarged diameter portion 44b.
  • From the side facing away from the control pressure chamber 48 side is in the Sections 44a, b of the bore 44 a nozzle 52 is inserted, essentially a slightly smaller diameter than has the portion 44 a of the bore and with his End portion is arranged in section 44a.
  • the nozzle 52 is at least approximately coaxial with the closing piston 42 arranged.
  • the nozzle 52 has an annular collar 53, whose diameter is slightly smaller than the diameter of the Section 44b of the bore 44 and the section 44b is arranged.
  • the nozzle 52 is located with its annular collar 53rd at the transition between the sections 44a and 44b of Bore 44 formed annular shoulder and is thus in Direction of its longitudinal axis to the control pressure chamber 48 back established.
  • the housing part 46 is followed by a Washer 54, which has a bore 55, whose Diameter larger than the diameter of the nozzle 52 however, smaller than the diameter of the annular collar 53 is.
  • the Washer 54 is between the housing part 46 and a clamped further housing part 56, so that by this the Stutzen 52 via its annular collar 53 in the direction of his Longitudinal axis is also set away from the control pressure chamber 48.
  • a flow channel 58 is formed, which the control pressure chamber 48 limiting the front end of the Stutzens 52 goes out and on the lateral surface of the nozzle 52nd near the end remote from the control pressure chamber 48 end empties.
  • the flow channel 58 has, for example, starting from the front end of the nozzle 52 is an approximately parallel to Longitudinal axis of the nozzle 52 extending portion 58 a and an approximately perpendicular to this extending portion 58b on, which opens on the lateral surface of the nozzle 52.
  • a throttle 59 may be arranged to to limit the flow.
  • the nozzle 52 At its the control pressure chamber 48 remote end region, the nozzle 52 a for example, conical chamfer 60, which as a first valve seat of the control valve 18 is used.
  • the housing part 56 of the control valve 18 has a bore 61, in which the nozzle 52 with its the control pressure chamber 48 remote area protrudes.
  • a Control valve member 62 guided tightly displaceable, as a Hollow piston is formed, in which the nozzle 52nd protrudes.
  • the control valve member 62 has to Washer 54 toward a hole 63, whose Diameter is only slightly larger than the diameter of the through the bore 63 passing through nozzle 52.
  • To the Bore 63 is then in the control valve member 62 a opposite the bore 63 extended pressure space 64th formed in which the flow channel 58 of the nozzle 52nd empties.
  • Control valve member 62 has a bore 65 with a smaller Diameter than the bore 63, which at the the Intermediate disc 54 remote from the front end of the Control valve member 62 opens.
  • the transition from the pressure chamber 64 to the bore 65 extends with an example conical Bevel 66.
  • the bore 63, the pressure chamber 64 and the Bore 65 in the control valve member 62 are at least approximately arranged coaxially with each other.
  • the chamfer 66 serves as first sealing surface of the control valve member 62, with the Bevel 60 on the nozzle 52 as the first valve seat interacts.
  • the bore 65 forms a discharge channel, through which the pressure chamber 64 with the outside of the Control valve member 62 is connected.
  • the control valve member 62 has at its the intermediate disc 54 opposite end portion one opposite to the diameter of the guided in the bore 61 area of Control valve member 62 in the reduced diameter approach 68th up, which ends with an example tapered bevel 69, which is a second Sealing surface on the control valve member 62 forms.
  • an annular shoulder 70 is formed at the control valve member 62 .
  • the bore 61 is as Sack bore formed and between the bottom 71 of the Bore 61 and the annular shoulder 70 of the control valve member 62nd a prestressed return spring 72 is arranged through the control valve member 62 to the washer 54 out is pressed.
  • the bottom 71 of the bore 61 has a at least approximately coaxial with the control valve member 62 arranged recess 73, the edge 74, for example is conically tapered and a second Valve seat forms, with which the second sealing surface forming chamfer 69 on the control valve member 62nd interacts.
  • the control valve member 62 with the Approach 68 is limited in the bore 61 an annular space 75, the connected via a channel 76 with a discharge space is than, for example, the storage tank 12 can serve.
  • the diameters of the first valve seat 60 and the second Valve seat 74, where the control valve member 62 with its first sealing surface 66 and with its second Sealing surface 69 comes to rest, are at least approximately same size.
  • control valve member 62 By the control valve member 62 is in the bore 61 for Washer 54 toward a working space 78 limited.
  • the Bore 61 may be in the region of the annular space 75 and / or in the Area of the working space 78 slightly larger in diameter be compared to the area in which the control valve member 62nd is guided in the bore 61.
  • the working space 78 is over a hydraulic ratio with a piezoelectric actuator 80th connected.
  • the piezo actuator 80 is controlled by the controller 20 is activated and changes depending on one at this applied electrical voltage its length.
  • the Piezoactuator 80 is disposed in a cylinder 81 and causes in its change in length compression or Relaxation of a cylinder 81 arranged Hydraulic volume.
  • the hydraulic transmission is thereby achieved that that influenced by the piezoelectric actuator 80 Hydraulic volume to a diameter in relation to the Piezoaktor 80 reduced piston 82 acts, the at a Length change of the piezoelectric actuator 80 by a ratio the diameter of the piezoactuator 80 to the diameter of the Piston 82 enlarged stroke executes.
  • the piston 82 is at least approximately coaxial with the piezoelectric actuator 80 and arranged in a cylinder 83 corresponding in diameter slidably guided.
  • a Workspace 84 limited, the one in diameter smaller channel 85 in the housing part 56 with the working space 78th connected is.
  • the piezoelectric actuator 80 and the piston 82 can arbitrarily on the circumference of the housing part 56 of the control valve 18th be arranged and with their longitudinal axes approximately perpendicular to Longitudinal axis of the control valve 18 or as in Figure 2 represented as desired to the longitudinal axis of the control valve inclined.
  • the second sealing surface 69 is located on the control valve member 62 then not in contact with the second valve seat 74, so that the bore 65 of the control valve member 62 with the annular space 75th and over this with the serving as a discharge space Storage tank 12 is connected. From the control pressure chamber 48 can in this open position of the control valve 18th Fuel through the flow channel 58, the pressure chamber 64 and serving as a discharge channel bore 65 in the Discharge relief space, whereby the pressure in the Control pressure chamber 48 decreases.
  • the injection valve member 24 may in this case by the on his pressure shoulder 36 acting pressure of the memory 14 against the force of Closing spring 40 and against that of the control pressure chamber 48th prevailing reduced pressure generated force in Opening direction 38 are moved and gives the Injection openings 28 free, so that injected fuel becomes.
  • the pressure in the working space 78 so be set that the control valve 18 in his is kept open position, in this neither with its first sealing surface 66 at the first valve seat 60 at Stub 52 rests still with its second sealing surface 69 on second valve seat 74 on the bottom 71 of the bore 61 abuts and thus the fuel injection valve 16 remains open. It can also be provided that by appropriate Activation of the piezoelectric actuator 80, the control valve member 62 without Motion interruption from its first closed position in its second closed position is moved or vice versa. at the movement of the control valve member 62 is carried out no Reversal of direction of movement, but this is only in one Direction moves.
  • the control valve 18 is only open briefly, so that accordingly the Fuel injector 16 is opened only briefly. This allows, for example, a Pre-fuel injection, at a low Fuel quantity before the actual fuel injection is injected.
  • By appropriate control of the Piezoaktors 78 of the control valve 18 via the Control device 20 may be the time of opening, the Duration of opening and the size of the opening stroke of the Fuel injection valve 16 can be determined.
  • the Fuel injection valve can initially only briefly and / or be opened with a small opening stroke for the Pre-injection, then closed and then for the main injection for a long time and / or with larger opening stroke to be opened. It can also be one certain course of the injection can be achieved in the For example, the fuel injector initially only is opened with a small opening stroke and subsequently opened with a larger opening stroke. It can also be any other course of injection be achieved.
  • the pressure acts on the front end of the control valve member 62 adjacent to the Bore 65 on a same sized ring surface as inside the control valve member 62 adjacent to the bore 65, so that compensate for the resulting pressure forces.
  • a Movement of the control valve member 62 by the piezoelectric actuator 80 generated pressure in the working space 78 thus does not have against the pressure in the control pressure chamber 48 done so that of the Piezoelectric actuator 80 generates only relatively small actuating forces need and the piezoelectric actuator 80 and the hydraulic Translation to be carried out with small dimensions can.
  • the control valve 18 is according to FIG above-explained first embodiment modified embodiment shown, wherein the basic structure of the control valve 18 according to the modified version is the same as the first Embodiment and below only the additional Characteristics are explained.
  • the nozzle 52 is in the bore 63 of the control valve member 62 as close as possible, so that the bore 63 is a sealing area through which the Pressure chamber 64 in the control valve member 62 from the working space 78th is disconnected.
  • the control valve member 62 has in its Bore 63 has a circumferential annular groove 88, which has a or a plurality of approximately radial bores 89 with an in Outer jacket of the control valve member 62 formed annular groove 90 is connected.
  • the groove 91 may instead of in the outer jacket of the Control valve member 62 also in the bore 61 of the Housing part 56 may be formed.
  • About the annular grooves 88 and 90 may also be a filling of the work spaces 78 and 84th the hydraulic transmission of the control valve 18 take place.
  • control valve 18 according to a second Embodiment illustrated, in turn, the basic structure is the same as the first Embodiment, however, the effective directions of the Piezo actuator generated actuating force and the return spring are reversed.
  • the control valve member 162 has the bore 63, through which the nozzle 52 protrudes into the pressure chamber 64, from which the bore 65 discharges.
  • the recess 73 is formed and the control valve member 162 has the projection 68 on.
  • the bore 161 is as Stepped bore formed and faces the washer 54 toward a larger diameter section 161a and toward its bottom 71 a smaller portion 161b Diameter.
  • control valve member 162 is in his outside diameter also formed stepped and has an area 162a with a larger diameter, the in the section 161 a of the bore 161 is arranged and a Area 162b of smaller diameter, in the section 161b of the bore 161 is arranged.
  • a biased return spring 172 arranged through which the Control valve member 162 to the bottom 71 of the bore 161 out is pressed.
  • Due to the larger diameter area 162a of the control valve member 162 is in section 161a of Bore 161 defines a working space 178, which has a Channel 185 with the hydraulic transmission of the piezoelectric actuator 80 is connected.
  • the from the control valve member 162 in the section 161a of the bore 161 limited to the intermediate disc 54 out Room 188 in which the return spring 172 is arranged is via a channel 189 with a discharge space, for example, the storage tank 12, connected.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The inventive fuel injection valve (16) comprises an injection valve element (24) via which at least one injection opening (26) is controlled. The movement of the injection valve element (24) is influenced by a control valve (18) which comprises a control valve element (62), said control valve element controlling the pressure in a control pressure space (48), and which can be moved by an adjusting force generated by a piezo actuator (80) thus controlling a connection of the control pressure space (48) to a pressure release space (12). The control valve (18) comprises two valve seats (60, 74) which are interspaced in the direction of movement of the control valve element (62), and with which the control valve element (62) interacts via a respective sealing surface (66, 69) arranged thereon so that the control valve element (62) has two closing positions in which the control pressure space (48) is separated from the pressure release space (12). When the control valve element (62) is not located in one of both closing positions, the control pressure space (48) is connected to the pressure release space (12). The fuel injection valve (16) can be momentarily opened by moving the control valve element (62) between both closing positions thereof.

Description

Die Erfindung betrifft ein Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Anspruchs 1.The invention relates to a fuel injection valve for Internal combustion engine according to the preamble of claim 1.

Ein solches Kraftstoffeinspritzventil ist durch die DE 197 32 802 A bekannt. Dieses Kraftstoffeinspritzventil ist Bestandteil eines Speicherkraftstoffeinspritzsystems. Das Kraftstoffeinspritzventil weist ein axial verschiebbar geführtes Einspritzventilglied auf, durch das wenigstens eine Einspritzöffnung gesteuert wird und das eine einen Druckraum begrenzende Druckschulter aufweist. Dem Druckraum wird unter Druck stehender Kraftstoff von einer Kraftstoffhochdruckquelle zugeführt, durch den das Einspritzventilglied entgegen einer Schließkraft zur Öffnung der wenigstens einen Einspritzöffnung von einem Ventilsitz abhebbar ist. Es ist ein die Bewegung des Einspritzventilglieds beeinflussendes Steuerventil vorgesehen, das ein durch eine von einem Piezoaktor erzeugte Stellkraft gegen eine Rückstellkraft bewegbares Steuerventilglied aufweist, das den in einem mit einer Druckquelle verbundenen Steuerdruckraum herrschenden Druck steuert, der das Einspritzventilglied zumindest mittelbar in seiner Schließrichtung beaufschlagt. Durch das Steuerventilglied ist der Steuerdruckraum mit einem Entlastungsraum verbindbar und das Steuerventilglied wirkt mit wenigstens einer Dichtfläche mit wenigstens einem Ventilsitz zusammen, über den die Verbindung des Steuerdruckraums mit dem Entlastungsraum gesteuert wird. Das Steuerventil weist zwei in der Bewegungsrichtung des Steuerventilglieds zueinander beabstandete Ventilsitze auf und das Steuerventilglied ist zwischen zwei Schließstellungen bewegbar, in denen es jeweils mit einer Dichtfläche an einem der Ventilsitze anliegt und der Steuerdruckraum vom Entlastungsraum getrennt ist. Bei zwischen seinen beiden Schließstellungen angeordnetem Steuerventilglied ist der Steuerdruckraum mit dem Entlastungsraum verbunden. Das Steuerventilglied ist kolbenförmig ausgebildet und die beiden Dichtflächen sind an einander abgewandten Außenseiten des Steuerventilglieds angeordnet. Bei dieser Ausbildung des Steuerventilglieds ist ein großer Bauraum für das Steuerventil erforderlich.Such a fuel injection valve is known from DE 197 32 802 A known. This fuel injection valve is part of a Storage fuel injection system. The fuel injector has an axially displaceable guided injection valve member, is controlled by the at least one injection opening and the having a pressure chamber limiting pressure shoulder. the Pressure chamber becomes pressurized fuel from a High-pressure fuel source supplied by the Injection valve member against a closing force for opening the at least one injection opening can be lifted from a valve seat. It is a movement influencing the movement of the injection valve member Control valve provided by a by a piezoelectric actuator generated actuating force against a restoring force movable Control valve member having the in one with a pressure source The control pressure chamber is controlled by the prevailing pressure that controls the Injection valve member at least indirectly in its closing direction applied. By the control valve member is the control pressure chamber connectable with a relief space and the control valve member acts with at least one sealing surface with at least one valve seat together, over which the connection of the control pressure space with the Relief space is controlled. The control valve has two in the Movement direction of the control valve member spaced from each other Valve seats on and the control valve member is between two Closing positions movable, in which there are each with a Sealing surface rests against one of the valve seats and the control pressure chamber is separated from the discharge space. At between his two Closed positions arranged control valve member is the Control pressure chamber connected to the discharge chamber. The Control valve member is piston-shaped and the two Sealing surfaces are on opposite outer sides of the Control valve member arranged. In this training of Control valve member is a large space for the control valve required.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den Merkmalen gemäß Anspruch 1 hat den Vorteil, dass das Steuerventil mit kompaktem Aufbau ausgeführt werden kann. The fuel injection valve according to the invention with the features according to claim 1 has the advantage that the control valve with compact design can be performed.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen des erfindungsgemäßen Kraftstoffeinspritzventils angegeben. Durch die Ausbildung gemäß Anspruch 2 ergibt sich auf das Steuerventilglied keine Kraft durch den Druck im Steuerdruckraum, wodurch nur eine geringe vom Piezoaktor zu erzeugende Stellkraft für die Bewegung des Steuerventilglieds erforderlich ist und der Piezoaktor mit geringen Abmessungen ausgeführt werden kann.In the dependent claims are advantageous Embodiments and developments of the invention Fuel injection valve specified. Through the training according to claim 2 results on the control valve member no Force due to the pressure in the control pressure chamber, which causes only one low to be generated by the piezoelectric actuator for the Movement of the control valve member is required and the Piezoelectric actuator with small dimensions can be performed.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein Speicherkraftstoffeinspritzsystem in schematischer Darstellung, Figur 2 ein Kraftstoffeinspritzventil des Speicherkraftstoffeinspritzsystems in einem Längsschnitt gemäß einem ersten Ausführungsbeispiel, Figur 3 das Kraftstoffeinspritzventil im Längsschnitt gemäß einer modifizierten Ausführung und Figur 4 das Kraftstoffeinspritzventil im Längsschnitt gemäß einem zweiten Ausführungsbeispiel.Two embodiments of the invention are in the Drawing shown and in the following description explained in more detail. 1 shows a Storage fuel injection system in schematic Representation, Figure 2 shows a fuel injection valve of the Storage fuel injection system in a longitudinal section according to a first embodiment, Figure 3 the Fuel injection valve in longitudinal section according to a modified embodiment and Figure 4 the Fuel injection valve in longitudinal section according to a second embodiment.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Ein in Figur 1 schematisch dargestelltes Speicherkraftstoffeinspritzsystem weist eine Hochdruckpumpe 10 auf, durch die Kraftstoff aus einem Vorratstank 12 unter Hochdruck in einen Speicher 14 gefördert wird. Der Speicher 14 ist als sogenanntes Rail ausgebildet, von dem Leitungen zu Kraftstoffeinspritzventilen 16 abführen, die an einer Brennkraftmaschine angeordnet sind. Jedes Kraftstoffeinspritzventil 16 weist ein Steuerventil 18 auf, durch das das Öffnen und Schließen des Kraftstoffeinspritzventils 16 gesteuert wird. Das Speicherkraftstoffeinspritzsystem weist außerdem eine Steuereinrichtung 20 auf, der Signale über verschiedene Betriebsparameter der Brennkraftmaschine zugeführt werden und durch die abhängig hiervon die Steuerventile 18 der Kraftstoffeinspritzventile 16 zu deren Öffnen oder Schließen angesteuert werden.A schematically illustrated in Figure 1 Storage fuel injection system has a high-pressure pump 10 on, by the fuel from a storage tank 12 below High pressure is conveyed into a memory 14. The memory 14 is formed as a so-called rail, from the lines To dissipate fuel injection valves 16 which at a Internal combustion engine are arranged. each Fuel injection valve 16 has a control valve 18, by opening and closing the Fuel injection valve 16 is controlled. The Storage fuel injection system also has a Control device 20, the signals over various Operating parameters of the internal combustion engine are supplied and by depending on the control valves 18 of the Fuel injection valves 16 to open or close be controlled.

In Figur 2 ist ein Kraftstoffeinspritzventil 16 mit zugehörigem Steuerventil 18 gemäß einem ersten Ausführungsbeispiel dargestellt. Das Kraftstoffeinspritzventil 16 weist einen Ventilkörper 22 auf, in dem ein Einspritzventilglied 24 axial verschiebbar geführt ist. Der Ventilkörper 22 weist an seinem dem Brennraum der Brennkraftmaschine zugewandten Endbereich wenigstens eine, vorzugsweise mehrere Einspritzöffnungen 26 auf. Das Einspritzventilglied 24 weist an seinem dem Brennraum zugewandten Endbereich eine beispielsweise etwa kegelförmige Dichtfläche 28 auf, die mit einem im Ventilkörper 22 ausgebildeten Ventilsitz 30 zusammenwirkt, von dem aus die Einspritzöffnungen 26 abführen. Im Ventilkörper 22 ist ein das Einspritzventilglied 24 umgebender Ringraum 32 ausgebildet, der mit einem Druckraum 34 verbunden ist, der wiederum mit dem Speicher 14 verbunden ist, so daß im Druckraum 34 der von der Hochdruckpumpe 10 erzeugte Druck herrscht. Das Einspritzventilglied 24 weist eine im Druckraum 34 angeordnete Druckschulter 36 auf, über die der im Druckraum 34 herrschende Druck eine in Öffnungsrichtung 38 des Einspritzventilglieds 24 wirkende Kraft auf dieses ausübt. Am Einspritzventilglied 24 greift eine vorgespannte Schließfeder 40 an, durch die das Einspritzventilglied 24 entgegen der durch den im Druckraum 34 herrschenden Druck auf dieses in Öffnungsrichtung 38 wirkenden Kraft in Schließrichtung beaufschlagt ist. Durch den im Druckraum 34 herrschenden Druck ist das Einspritzventilglied 24 gegen die Kraft der Schließfeder 40 in Öffnungsrichtung 38 bewegbar und gibt dabei die Einspritzöffnungen 26 frei, durch die Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt wird. Zur Beendung der Einspritzung wird das Einspritzventilglied 24 in Schließrichtung mit seiner Dichtfläche 28 in den Ventilsitz 30 am Ventilkörper 22 gepresst, so daß die Einspritzöffnungen 26 verschlossen werden.In Figure 2, a fuel injection valve 16 with associated control valve 18 according to a first Embodiment shown. The Fuel injection valve 16 has a valve body 22 in which an injection valve member 24 axially displaceable is guided. The valve body 22 has at its the Combustion chamber of the engine facing end at least one, preferably a plurality of injection openings 26 on. The injection valve member 24 has at its the Combustion chamber facing end an example, for example conical sealing surface 28, which with a in Valve body 22 formed valve seat 30 cooperates, from which discharge the injection openings 26. in the Valve body 22 is an injection valve member 24 surrounding annular space 32 formed with a pressure chamber 34 is connected, which in turn connected to the memory 14 is, so that in the pressure chamber 34 of the high-pressure pump 10th generated pressure prevails. The injection valve member 24 has a pressure shoulder 34 arranged in the pressure chamber 34, via the pressure prevailing in the pressure chamber 34 pressure in Opening direction 38 of the injection valve member 24 acting Exercise power on this. On injection valve member 24 engages a biased closing spring 40, through which the Injection valve member 24 opposite to that in the pressure chamber 34 prevailing pressure on this in the opening direction 38th acting force is applied in the closing direction. By the pressure prevailing in the pressure chamber 34 is the Injection valve member 24 against the force of the closing spring 40th movable in the opening direction 38 and gives the Injection openings 26 free, through the fuel in the Combustion chamber of the internal combustion engine is injected. to End of the injection, the injection valve member 24th in the closing direction with its sealing surface 28 in the Valve seat 30 is pressed against the valve body 22, so that the Injection openings 26 are closed.

Im Bereich des dem Brennraum abgewandten Endes des Einspritzventilglieds 24 ist ein Schließkolben 42 angeordnet, der Teil des Steuerventils 18 ist. Der Schließkolben 42 kann einstückig mit dem Einspritzventilglied 24 ausgebildet sein oder als separates Teil. Der Schließkolben 42 ist zumindest annähernd koaxial zum Einspritzventilglied 24 angeordnet und in einer Bohrung 44 in einem Gehäuseteil 46 des Steuerventils 18 axial verschiebbar geführt.In the region of the combustion chamber facing away from the end of Injection valve member 24 is a closing piston 42 arranged, which is part of the control valve 18. Of the Closing piston 42 may be integral with the Injection valve member 24 may be formed or as a separate Part. The closing piston 42 is at least approximately coaxial arranged to the injection valve member 24 and in a bore 44 in a housing part 46 of the control valve 18 axially slidably guided.

Der Schließkolben 42 begrenzt in der Bohrung 44 einen Steuerdruckraum 48, der über einen Kanal 49, in dem eine Drossel 50 angeordnet ist, mit dem Speicher 14 verbunden ist. Dem Schließkolben 42 abgewandt ist die Bohrung 44 gestuft ausgebildet und weist einen Abschnitt 44a mit verringertem Durchmesser und an diesen anschließend wieder einen Abschnitt 44b mit vergrößertem Durchmesser auf. Von der dem Steuerdruckraum 48 abgewandten Seite her ist in die Abschnitte 44a,b der Bohrung 44 ein Stutzen 52 eingesetzt, der im wesentlichen einen etwas kleineren Durchmesser als der Abschnitt 44a der Bohrung aufweist und mit seinem Endbereich im Abschnitt 44a angeordnet ist. Der Stutzen 52 ist zumindest annähernd koaxial zum Schließkolben 42 angeordnet. Der Stutzen 52 weist einen Ringbund 53 auf, dessen Durchmesser etwas kleiner ist als der Durchmesser des Abschnitts 44b der Bohrung 44 und der im Abschnitt 44b angeordnet ist. Der Stutzen 52 liegt mit seinem Ringbund 53 an der am Übergang zwischen den Abschnitten 44a und 44b der Bohrung 44 gebildeten Ringschulter an und ist damit in Richtung seiner Längsachse zum Steuerdruckraum 48 hin festgelegt. An das Gehäuseteil 46 schließt sich eine Zwischenscheibe 54 an, die eine Bohrung 55 aufweist, deren Durchmesser größer als der Durchmesser des Stutzens 52 jedoch kleiner als der Durchmesser des Ringbunds 53 ist. Die Zwischenscheibe 54 ist zwischen dem Gehäuseteil 46 und einem weiteren Gehäuseteil 56 eingespannt, so daß durch diese der Stutzen 52 über seinen Ringbund 53 in Richtung seiner Längsachse auch vom Steuerdruckraum 48 weg festgelegt ist. The closing piston 42 defines a hole in the bore 44 Control pressure chamber 48, via a channel 49, in which a Throttle 50 is arranged, connected to the memory 14 is. The bore 44 faces away from the closing piston 42 stepped formed and has a portion 44a with reduced diameter and then this again an enlarged diameter portion 44b. From the side facing away from the control pressure chamber 48 side is in the Sections 44a, b of the bore 44 a nozzle 52 is inserted, essentially a slightly smaller diameter than has the portion 44 a of the bore and with his End portion is arranged in section 44a. The nozzle 52 is at least approximately coaxial with the closing piston 42 arranged. The nozzle 52 has an annular collar 53, whose diameter is slightly smaller than the diameter of the Section 44b of the bore 44 and the section 44b is arranged. The nozzle 52 is located with its annular collar 53rd at the transition between the sections 44a and 44b of Bore 44 formed annular shoulder and is thus in Direction of its longitudinal axis to the control pressure chamber 48 back established. The housing part 46 is followed by a Washer 54, which has a bore 55, whose Diameter larger than the diameter of the nozzle 52 however, smaller than the diameter of the annular collar 53 is. The Washer 54 is between the housing part 46 and a clamped further housing part 56, so that by this the Stutzen 52 via its annular collar 53 in the direction of his Longitudinal axis is also set away from the control pressure chamber 48.

Im Stutzen 52 ist ein Strömungskanal 58 ausgebildet, der von dem den Steuerdruckraum 48 begrenzenden Stirnende des Stutzens 52 ausgeht und an der Mantelfläche des Stutzens 52 nahe von dessen dem Steuerdruckraum 48 abgewandten Ende mündet. Der Strömungskanal 58 weist beispielsweise ausgehend vom Stirnende des Stutzens 52 einen etwa parallel zur Längsachse des Stutzens 52 verlaufenden Abschnitt 58a und einen etwa rechtwinklig zu diesem verlaufenden Abschnitt 58b auf, der an der Mantelfläche des Stutzens 52 mündet. Im Strömungskanal 58 kann eine Drossel 59 angeordnet sein, um den Durchfluß zu begrenzen. An seinem dem Steuerdruckraum 48 abgewandten Endbereich weist der Stutzen 52 eine beispielsweise konische Anschrägung 60 auf, die als ein erster Ventilsitz des Steuerventils 18 dient.In the nozzle 52, a flow channel 58 is formed, which the control pressure chamber 48 limiting the front end of the Stutzens 52 goes out and on the lateral surface of the nozzle 52nd near the end remote from the control pressure chamber 48 end empties. The flow channel 58 has, for example, starting from the front end of the nozzle 52 is an approximately parallel to Longitudinal axis of the nozzle 52 extending portion 58 a and an approximately perpendicular to this extending portion 58b on, which opens on the lateral surface of the nozzle 52. in the Flow passage 58, a throttle 59 may be arranged to to limit the flow. At its the control pressure chamber 48 remote end region, the nozzle 52 a for example, conical chamfer 60, which as a first valve seat of the control valve 18 is used.

Das Gehäuseteil 56 des Steuerventils 18 weist eine Bohrung 61 auf, in die der Stutzen 52 mit seinem dem Steuerdruckraum 48 abgewandten Bereich hineinragt. In der Bohrung 61 ist ein Steuerventilglied 62 dicht verschiebbar geführt, das als ein Hohlkolben ausgebildet ist, in den der Stutzen 52 hineinragt. Das Steuerventilglied 62 weist zur Zwischenscheibe 54 hin eine Bohrung 63 auf, deren Durchmesser nur wenig größer ist als der Durchmesser des durch die Bohrung 63 hindurchtretenden Stutzens 52. An die Bohrung 63 anschließend ist im Steuerventilglied 62 ein gegenüber der Bohrung 63 erweiterter Druckraum 64 ausgebildet, in dem der Strömungskanal 58 des Stutzens 52 mündet. An den Druckraum 64 schließt sich im Steuerventilglied 62 eine Bohrung 65 mit kleinerem Durchmesser als die Bohrung 63 an, die an dem der Zwischenscheibe 54 abgewandten Stirnende des Steuerventilglieds 62 mündet. Der Übergang vom Druckraum 64 zur Bohrung 65 verläuft mit einer beispielsweise konischen Anschrägung 66. Die Bohrung 63, der Druckraum 64 und die Bohrung 65 im Steuerventilglied 62 sind zumindest annähernd koaxial zueinander angeordnet. Die Anschrägung 66 dient als erste Dichtfläche des Steuerventilglieds 62, die mit der Anschrägung 60 am Stutzen 52 als erstem Ventilsitz zusammenwirkt. Die Bohrung 65 bildet einen Abströmkanal, durch den der Druckraum 64 mit der Außenseite des Steuerventilglieds 62 verbunden ist.The housing part 56 of the control valve 18 has a bore 61, in which the nozzle 52 with its the control pressure chamber 48 remote area protrudes. In the bore 61 is a Control valve member 62 guided tightly displaceable, as a Hollow piston is formed, in which the nozzle 52nd protrudes. The control valve member 62 has to Washer 54 toward a hole 63, whose Diameter is only slightly larger than the diameter of the through the bore 63 passing through nozzle 52. To the Bore 63 is then in the control valve member 62 a opposite the bore 63 extended pressure space 64th formed in which the flow channel 58 of the nozzle 52nd empties. At the pressure chamber 64 closes in Control valve member 62 has a bore 65 with a smaller Diameter than the bore 63, which at the the Intermediate disc 54 remote from the front end of the Control valve member 62 opens. The transition from the pressure chamber 64 to the bore 65 extends with an example conical Bevel 66. The bore 63, the pressure chamber 64 and the Bore 65 in the control valve member 62 are at least approximately arranged coaxially with each other. The chamfer 66 serves as first sealing surface of the control valve member 62, with the Bevel 60 on the nozzle 52 as the first valve seat interacts. The bore 65 forms a discharge channel, through which the pressure chamber 64 with the outside of the Control valve member 62 is connected.

Das Steuerventilglied 62 weist an seinem der Zwischenscheibe 54 abgewandten Endbereich einen gegenüber dem Durchmesser des in der Bohrung 61 geführten Bereichs der Steuerventilglieds 62 im Durchmesser verringerten Ansatz 68 auf, der sich zu seinem Ende hin mit einer beispielsweise konischen Anschrägung 69 verjüngt, die eine zweite Dichtfläche am Steuerventilglied 62 bildet. Durch den im Durchmesser verringerten Ansatz 68 ist am Steuerventilglied 62 eine Ringschulter 70 gebildet. Die Bohrung 61 ist als Sackbohrung ausgebildet und zwischen dem Boden 71 der Bohrung 61 und der Ringschulter 70 des Steuerventilglieds 62 ist eine vorgespannte Rückstellfeder 72 angeordnet, durch die das Steuerventilglied 62 zur Zwischenscheibe 54 hin gedrückt wird. Der Boden 71 der Bohrung 61 weist eine zumindest annähernd koaxial zum Steuerventilglied 62 angeordnete Vertiefung 73 auf, der Rand 74 beispielsweise konisch angeschrägt ausgebildet ist und einen zweiten Ventilsitz bildet, mit dem die die zweite Dichtfläche bildende Anschrägung 69 am Steuerventilglied 62 zusammenwirkt. Durch das Steuerventilglied 62 mit dessen Ansatz 68 wird in der Bohrung 61 ein Ringraum 75 begrenzt, der über einen Kanal 76 mit einem Entlastungsraum verbunden ist, als der beispielsweise der Vorratstank 12 dienen kann.The control valve member 62 has at its the intermediate disc 54 opposite end portion one opposite to the diameter of the guided in the bore 61 area of Control valve member 62 in the reduced diameter approach 68th up, which ends with an example tapered bevel 69, which is a second Sealing surface on the control valve member 62 forms. By the im Diameter reduced shoulder 68 is at the control valve member 62 an annular shoulder 70 is formed. The bore 61 is as Sack bore formed and between the bottom 71 of the Bore 61 and the annular shoulder 70 of the control valve member 62nd a prestressed return spring 72 is arranged through the control valve member 62 to the washer 54 out is pressed. The bottom 71 of the bore 61 has a at least approximately coaxial with the control valve member 62 arranged recess 73, the edge 74, for example is conically tapered and a second Valve seat forms, with which the second sealing surface forming chamfer 69 on the control valve member 62nd interacts. By the control valve member 62 with the Approach 68 is limited in the bore 61 an annular space 75, the connected via a channel 76 with a discharge space is than, for example, the storage tank 12 can serve.

Die Durchmesser des ersten Ventilsitzes 60 und des zweiten Ventilsitzes 74, an denen das Steuerventilglied 62 mit seiner ersten Dichtfläche 66 bzw. mit seiner zweiten Dichtfläche 69 zur Anlage kommt, sind zumindest annähernd gleich groß.The diameters of the first valve seat 60 and the second Valve seat 74, where the control valve member 62 with its first sealing surface 66 and with its second Sealing surface 69 comes to rest, are at least approximately same size.

Durch das Steuerventilglied 62 wird in der Bohrung 61 zur Zwischenscheibe 54 hin ein Arbeitsraum 78 begrenzt. Die Bohrung 61 kann im Bereich des Ringraums 75 und/oder im Bereich des Arbeitsraums 78 im Durchmesser etwas vergrößert sein gegenüber dem Bereich, in dem das Steuerventilglied 62 in der Bohrung 61 geführt ist. Der Arbeitsraum 78 ist über eine hydraulische Übersetzung mit einem Piezoaktor 80 verbunden. Der Piezoaktor 80 wird von der Steuereinrichtung 20 angesteuert und ändert abhängig von einer an diesem anliegenden elektrischen Spannung seine Länge. Der Piezoaktor 80 ist in einem Zylinder 81 angeordnet und bewirkt bei seiner Längenänderung eine Verdichtung bzw. Entspannung eines im Zylinder 81 angeordneten Hydraulikvolumens. Die hydraulische Übersetzung ist dadurch erreicht, daß das vom Piezoaktor 80 beeinflußte Hydraulikvolumen auf einen im Durchmesser gegenüber dem Piezoaktor 80 verkleinerten Kolben 82 wirkt, der bei einer Längenänderung des Piezoaktors 80 einen um das Verhältnis des Durchmessers des Piezoaktors 80 zum Durchmesser des Kolbens 82 vergrößerten Hub ausführt. Der Kolben 82 ist zumindest annähernd koaxial zum Piezoaktor 80 angeordnet und in einem im Durchmesser entsprechenden Zylinder 83 verschiebbar geführt. Durch den Kolben 82 wird ein Arbeitsraum 84 begrenzt, der über einen im Durchmesser kleineren Kanal 85 im Gehäuseteil 56 mit dem Arbeitsraum 78 verbunden ist. Der Piezoaktor 80 sowie der Kolben 82 können beliebig am Umfang des Gehäuseteils 56 des Steuerventils 18 angeordnet sein und mit ihren Längsachsen etwa senkrecht zur Längsachse des Steuerventils 18 oder wie in Figur 2 dargestellt beliebig zur Längsachse des Steuerventils geneigt. By the control valve member 62 is in the bore 61 for Washer 54 toward a working space 78 limited. The Bore 61 may be in the region of the annular space 75 and / or in the Area of the working space 78 slightly larger in diameter be compared to the area in which the control valve member 62nd is guided in the bore 61. The working space 78 is over a hydraulic ratio with a piezoelectric actuator 80th connected. The piezo actuator 80 is controlled by the controller 20 is activated and changes depending on one at this applied electrical voltage its length. Of the Piezoactuator 80 is disposed in a cylinder 81 and causes in its change in length compression or Relaxation of a cylinder 81 arranged Hydraulic volume. The hydraulic transmission is thereby achieved that that influenced by the piezoelectric actuator 80 Hydraulic volume to a diameter in relation to the Piezoaktor 80 reduced piston 82 acts, the at a Length change of the piezoelectric actuator 80 by a ratio the diameter of the piezoactuator 80 to the diameter of the Piston 82 enlarged stroke executes. The piston 82 is at least approximately coaxial with the piezoelectric actuator 80 and arranged in a cylinder 83 corresponding in diameter slidably guided. By the piston 82 is a Workspace 84 limited, the one in diameter smaller channel 85 in the housing part 56 with the working space 78th connected is. The piezoelectric actuator 80 and the piston 82 can arbitrarily on the circumference of the housing part 56 of the control valve 18th be arranged and with their longitudinal axes approximately perpendicular to Longitudinal axis of the control valve 18 or as in Figure 2 represented as desired to the longitudinal axis of the control valve inclined.

Nachfolgend wird die Funktion des Kraftstoffeinspritzventils 16 und des Steuerventils 18 erläutert. Wenn der Piezoaktor 80 nicht aktiviert ist, so herrscht im Arbeitsraum 78 ein geringer Druck und das Steuerventilglied 62 wird durch die Rückstellfeder 72 mit seiner ersten Dichtfläche 66 in Anlage am ersten Ventilsitz 60 am Stutzen 52 gehalten. Das Steuerventilglied 62 befindet sich hierbei in einer ersten Schließstellung. Der Druckraum 64 im Steuerventilglied 62 ist somit vom Entlastungsraum, der durch den Vorratstank 12 gebildet ist, getrennt und aus dem Steuerdruckraum 48 kann durch den Kanal 58 und den Druckraum 64 kein Kraftstoff abströmen. Aus diesem Grund herrscht im Steuerdruckraum 48 derselbe Druck wie im Speicher 14, der auf den Schließkolben 42 wirkt und über diesen auf das Einspritzventilglied 24 wirkt und dieses in seiner Schließstellung hält, in der das Einspritzventilglied 24 mit seiner Dichtfläche 28 am Ventilsitz 30 anliegt und die Einspritzöffnungen 28 verschließt, so daß kein Kraftstoff eingespritzt wird.The following is the function of the fuel injection valve 16 and the control valve 18 explained. When the piezo actuator 80 is not activated, so prevails in the working space 78 a low pressure and the control valve member 62 is replaced by the Return spring 72 with its first sealing surface 66 in Appendix held at the first valve seat 60 on the nozzle 52. The Control valve member 62 is here in a first Closed position. The pressure chamber 64 in the control valve member 62nd is thus from the discharge space through the storage tank 12th is formed, separated and from the control pressure chamber 48 can through the channel 58 and the pressure chamber 64 no fuel flow out. For this reason prevails in the control pressure chamber 48th the same pressure as in the reservoir 14, which is on the closing piston 42 acts and on this on the injection valve member 24th acts and holds this in its closed position in which the Injection valve member 24 with its sealing surface 28 am Valve seat 30 abuts and the injection openings 28th closes, so that no fuel is injected.

Wenn der Piezoaktor 80 von der Steuereinrichtung 20 angesteuert wird, so vergrößert sich dessen Länge und durch den Kolben 82 wird Hydraulikvolumen aus dem Arbeitsraum 84 über den Kanal 85 in den Arbeitsraum 78 verdrängt, wo der Druck ansteigt, bis die von diesem auf das Steuerventilglied 62 ausgeübte Kraft die Vorspannung der Rückstellfeder 72 überwinden kann und das Steuerventilglied 62 von der Zwischenscheibe 54 weg bewegt wird. Die erste Dichtfläche 66 des Steuerventilglieds 62 hebt dabei vom ersten Ventilsitz 60 am Stutzen 52 ab, so daß der Druckraum 64 im Steuerventilglied 62 mit der Bohrung 65 verbunden ist. Die zweite Dichtfläche 69 am Steuerventilglied 62 befindet sich dann noch nicht in Anlage am zweiten Ventilsitz 74, so daß die Bohrung 65 des Steuerventilglieds 62 mit dem Ringraum 75 und über diesen mit dem als Entlastungsraum dienenden Vorratstank 12 verbunden ist. Aus dem Steuerdruckraum 48 kann in dieser geöffneten Stellung des Steuerventils 18 Kraftstoff durch den Strömungskanal 58, den Druckraum 64 und die als Abströmkanal dienende Bohrung 65 in den Entlastungsraum abströmen, wodurch der Druck im Steuerdruckraum 48 sinkt. Das Einspritzventilglied 24 kann in diesem Fall durch den auf seine Druckschulter 36 wirkenden Druck des Speichers 14 gegen die Kraft der Schließfeder 40 und gegen die von dem im Steuerdruckraum 48 herrschenden verringerten Druck erzeugte Kraft in Öffnungsrichtung 38 bewegt werden und gibt die Einspritzöffnungen 28 frei, so daß Kraftstoff eingespritzt wird.When the piezoelectric actuator 80 from the controller 20 is driven, so its length and increases the piston 82 is hydraulic volume from the working space 84th displaced via the channel 85 into the working space 78, where the Pressure rises until the latter from this to the control valve member 62 applied force the bias of the return spring 72nd can overcome and the control valve member 62 of the Washer 54 is moved away. The first sealing surface 66 of the control valve member 62 lifts from the first valve seat 60 at the nozzle 52, so that the pressure chamber 64 in Control valve member 62 is connected to the bore 65. The second sealing surface 69 is located on the control valve member 62 then not in contact with the second valve seat 74, so that the bore 65 of the control valve member 62 with the annular space 75th and over this with the serving as a discharge space Storage tank 12 is connected. From the control pressure chamber 48 can in this open position of the control valve 18th Fuel through the flow channel 58, the pressure chamber 64 and serving as a discharge channel bore 65 in the Discharge relief space, whereby the pressure in the Control pressure chamber 48 decreases. The injection valve member 24 may in this case by the on his pressure shoulder 36 acting pressure of the memory 14 against the force of Closing spring 40 and against that of the control pressure chamber 48th prevailing reduced pressure generated force in Opening direction 38 are moved and gives the Injection openings 28 free, so that injected fuel becomes.

Wenn der durch den Piezoaktor 80 erzeugte Druck im Arbeitsraum 78 weiter erhöht wird, so wird das Steuerventilglied 62 weiter verschoben, bis es mit seiner zweiten Dichtfläche 69 am zweiten Ventilsitz 74 am Boden 71 der Bohrung 61 zur Anlage kommt. Das Steuerventilglied 62 befindet sich hierbei in einer zweiten Schließstellung. In diesem Fall ist die Bohrung 65 im Steuerventilglied 62 vom Ringraum 75 getrennt, so daß aus dem Steuerventilglied 62 durch die Bohrung 65 kann Kraftstoff abströmen kann und im Steuerdruckraum 48 der hohe Druck des Speichers 14 herrscht, durch den über den Schließkolben 42 das Einspritzventilglied 24 in seine Schließstellung bewegt wird und in dieser gehalten wird.When the pressure generated by the piezoactuator 80 in the Workspace 78 is further increased, so will the Control valve member 62 further shifted until it with his second sealing surface 69 on the second valve seat 74 on the floor 71st the bore 61 comes to rest. The control valve member 62 is here in a second closed position. In In this case, the bore 65 in the control valve member 62 of Annullly 75 separated, so that from the control valve member 62nd through the bore 65, fuel can flow out and in Control pressure chamber 48, the high pressure of the memory 14 prevails, by the over the closing piston 42, the injection valve member 24 is moved to its closed position and in this is held.

Durch entsprechende Ansteuerung des Piezoaktors 80 über die Steuereinrichtung 20 kann der Druck im Arbeitsraum 78 derart eingestellt werden, daß das Steuerventil 18 in seiner geöffneten Stellung gehalten wird, in der dieses weder mit seiner ersten Dichtfläche 66 am ersten Ventilsitz 60 am Stutzen 52 anliegt noch mit seiner zweiten Dichtfläche 69 am zweiten Ventilsitz 74 am Boden 71 der Bohrung 61 anliegt und somit das Kraftstoffeinspritzventil 16 geöffnet bleibt. Es kann auch vorgesehen werden, daß durch entsprechende Aktivierung des Piezoaktors 80 das Steuerventilglied 62 ohne Bewegungsunterbrechung von seiner ersten Schließstellung in seine zweite Schließstellung bewegt wird oder umgekehrt. Bei der Bewegung des Steuerventilglieds 62 erfolgt dabei keine Bewegungsrichtungsumkehr, sondern dieses wird nur in einer Richtung bewegt. Das Steuerventil 18 wird dabei nur kurzzeitig geöffnet, so daß entsprechend auch das Kraftstoffeinspritzventil 16 nur kurzzeitig geöffnet wird. Dies ermöglicht beispielsweise eine Kraftstoffvoreinspritzung, bei der eine geringe Kraftstoffmenge vor der eigentlichen Kraftstoffeinspritzung eingespritzt wird. Durch entsprechende Ansteuerung des Piezoaktors 78 des Steuerventils 18 über die Steuereinrichtung 20 kann der Zeitpunkt der Öffnung, die Dauer der Öffnung und die Größe des Öffnungshubs des Kraftstoffeinspritzventils 16 bestimmt werden. Das Kraftstoffeinspritzventil kann zunächst nur kurzzeitig und/oder mit geringem Öffnungshub geöffnet werden für die Voreinspritzung, danach geschlossen werden und anschließend für die Haupteinspritzung für längere Zeit und/oder mit größerem Öffnungshub geöffnet werden. Es kann auch ein bestimmter Verlauf der Einspritzung erzielt werden, bei der beispielsweise das Kraftstoffeinspritzventil zunächst nur mit einem geringen Öffnungshub geöffnet wird und anschließend mit einem größeren Öffnungshub geöffnet wird. Es kann auch ein beliebiger anderer Verlauf der Einspritzung erzielt werden.By appropriate control of the piezoelectric actuator 80 via the Control device 20, the pressure in the working space 78 so be set that the control valve 18 in his is kept open position, in this neither with its first sealing surface 66 at the first valve seat 60 at Stub 52 rests still with its second sealing surface 69 on second valve seat 74 on the bottom 71 of the bore 61 abuts and thus the fuel injection valve 16 remains open. It can also be provided that by appropriate Activation of the piezoelectric actuator 80, the control valve member 62 without Motion interruption from its first closed position in its second closed position is moved or vice versa. at the movement of the control valve member 62 is carried out no Reversal of direction of movement, but this is only in one Direction moves. The control valve 18 is only open briefly, so that accordingly the Fuel injector 16 is opened only briefly. This allows, for example, a Pre-fuel injection, at a low Fuel quantity before the actual fuel injection is injected. By appropriate control of the Piezoaktors 78 of the control valve 18 via the Control device 20 may be the time of opening, the Duration of opening and the size of the opening stroke of the Fuel injection valve 16 can be determined. The Fuel injection valve can initially only briefly and / or be opened with a small opening stroke for the Pre-injection, then closed and then for the main injection for a long time and / or with larger opening stroke to be opened. It can also be one certain course of the injection can be achieved in the For example, the fuel injector initially only is opened with a small opening stroke and subsequently opened with a larger opening stroke. It can also be any other course of injection be achieved.

Wenn sich das Steuerventilglied 62 in seiner ersten Schließstellung befindet, in der dessen erste Dichtfläche 66 am ersten Ventilsitz 60 am Stutzen 52 anliegt, so wirkt der Druck des Steuerdruckraums 48 im Druckraum 64, wobei sich jedoch keine resultierende Kraft auf das Steuerventilglied 62 ergibt, da der Druck allseitig den Druckraum 64 beaufschlagt. Wenn sich das Steuerventilglied 62 in seiner zweiten Schließstellung befindet, in der dessen zweite Dichtfläche 69 am zweiten Ventilsitz 74 am Boden 71 der Bohrung 61 anliegt, so ergibt sich durch den im Druckraum 64 und der Bohrung 65 herrschenden Druck des Steuerdruckraums 48 ebenfalls keine resultierende Kraft, da die Durchmesser der beiden Ventilsitze 60 und 74 gleich groß sind. Der Druck wirkt am Stirnende des Steuerventilglieds 62 neben der Bohrung 65 auf eine gleich große Ringfläche wie innerhalb des Steuerventilglieds 62 neben der Bohrung 65, so daß sich die hierbei entstehenden Druckkräfte ausgleichen. Eine Bewegung des Steuerventilglieds 62 durch den vom Piezoaktor 80 erzeugten Druck im Arbeitsraum 78 muß somit nicht gegen den Druck im Steuerdruckraum 48 erfolgen, so daß vom Piezoaktor 80 nur relativ geringe Stellkräfte erzeugt zu werden brauchen und der Piezoaktor 80 sowie die hydraulische Übersetzung mit geringen Abmessungen ausgeführt werden können.When the control valve member 62 in its first Closed position is located in the first sealing surface 66th on the first valve seat 60 abuts the nozzle 52, so does the Pressure of the control pressure chamber 48 in the pressure chamber 64, wherein but no resultant force on the control valve member 62 results because the pressure on all sides of the pressure chamber 64th applied. When the control valve member 62 in its second closed position is located in the second Sealing surface 69 on the second valve seat 74 at the bottom 71 of Bore 61 is applied, it is clear from the pressure in the space 64th and the bore 65 prevailing pressure of the control pressure chamber 48 also no resulting force as the diameters the two valve seats 60 and 74 are the same size. The pressure acts on the front end of the control valve member 62 adjacent to the Bore 65 on a same sized ring surface as inside the control valve member 62 adjacent to the bore 65, so that compensate for the resulting pressure forces. A Movement of the control valve member 62 by the piezoelectric actuator 80 generated pressure in the working space 78 thus does not have against the pressure in the control pressure chamber 48 done so that of the Piezoelectric actuator 80 generates only relatively small actuating forces need and the piezoelectric actuator 80 and the hydraulic Translation to be carried out with small dimensions can.

In Figur 3 ist das Steuerventil 18 gemäß einer gegenüber dem vorstehend erläuterten ersten Ausführungsbeispiel modifizierten Ausführung dargestellt, wobei der grundsätzliche Aufbau des Steuerventils 18 gemäß der modifizierten Ausführung gleich ist wie beim ersten Ausführungsbeispiel und nachfolgend nur die zusätzlichen Merkmale erläutert werden. Der Stutzen 52 ist in der Bohrung 63 des Steuerventilglieds 62 möglichst dicht geführt, so daß die Bohrung 63 einen Dichtbereich darstellt, durch den der Druckraum 64 im Steuerventilglied 62 vom Arbeitsraum 78 getrennt ist. Das Steuerventilglied 62 weist in seiner Bohrung 63 eine umlaufende Ringnut 88 auf, die über eine oder mehrere etwa radiale Bohrungen 89 mit einer im Außenmantel des Steuerventilglieds 62 ausgebildete Ringnut 90 verbunden ist. Von der Ringnut 90 führt eine im Außenmantel des Steuerventilglieds 62 ausgebildete beispielsweise etwa axial verlaufende Nut 91 in den Ringraum 75, über den eine Verbindung mit dem Entlastungsraum in Form des Vorratstanks hergestellt ist. Wenn sich das Steuerventilglied 62 in einer seiner Schließstellungen befindet, so herrscht im Druckraum 64 derselbe Hochdruck wie im Steuerdruckraum 48, wobei eventuell durch den zwischen dem Stutzen 52 und der Bohrung 63 vorhandenen Ringspalt Kraftstoff aus dem Druckraum 64 abströmt. Diese abströmende Leckmenge an Kraftstoff wird über die Ringnut 88, die Bohrung 89, die Ringnut 90 und die Nut 91 in den Entlastungsraum abgeführt und kann nicht in den Arbeitsraum 78 gelangen. Die Nut 91 kann anstelle im Außenmantel des Steuerventilglieds 62 auch in der Bohrung 61 des Gehäuseteils 56 ausgebildet sein. Über die Ringnuten 88 und 90 kann außerdem eine Befüllung der Arbeitsräume 78 und 84 der hydraulischen Übersetzung des Steuerventils 18 erfolgen.In FIG. 3, the control valve 18 is according to FIG above-explained first embodiment modified embodiment shown, wherein the basic structure of the control valve 18 according to the modified version is the same as the first Embodiment and below only the additional Characteristics are explained. The nozzle 52 is in the bore 63 of the control valve member 62 as close as possible, so that the bore 63 is a sealing area through which the Pressure chamber 64 in the control valve member 62 from the working space 78th is disconnected. The control valve member 62 has in its Bore 63 has a circumferential annular groove 88, which has a or a plurality of approximately radial bores 89 with an in Outer jacket of the control valve member 62 formed annular groove 90 is connected. From the annular groove 90 performs an im Outer jacket of the control valve member 62 formed For example, approximately axially extending groove 91 in the annulus 75, via which a connection with the relief space in the form of the storage tank is made. If that is Control valve member 62 in one of its closed positions is located, then prevails in the pressure chamber 64, the same high pressure as in the control pressure chamber 48, possibly by the between the nozzle 52 and the bore 63 existing annular gap Fuel flows from the pressure chamber 64. This outflowing Leakage of fuel is via the annular groove 88, the Bore 89, the annular groove 90 and the groove 91 in the Discharge space dissipated and can not enter the work space 78 arrive. The groove 91 may instead of in the outer jacket of the Control valve member 62 also in the bore 61 of the Housing part 56 may be formed. About the annular grooves 88 and 90 may also be a filling of the work spaces 78 and 84th the hydraulic transmission of the control valve 18 take place.

In Figur 4 ist das Steuerventil 18 gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem wiederum der grundsätzliche Aufbau gleich ist wie beim ersten Ausführungsbeispiel, jedoch die Wirkrichtungen der vom Piezoaktor erzeugten Stellkraft und der Rückstellfeder umgekehrt sind. Das Steuerventilglied 162 weist die Bohrung 63 auf, durch die der Stutzen 52 in den Druckraum 64 ragt, von dem die Bohrung 65 abführt. Am Boden 71 der Bohrung 161 ist die Vertiefung 73 ausgebildet und das Steuerventilglied 162 weist den Ansatz 68 auf. Die Bohrung 161 ist als Stufenbohrung ausgebildet und weist zu der Zwischenscheibe 54 hin einen Abschnitt 161a mit größerem Durchmesser auf und zu ihrem Boden 71 hin einen Abschnitt 161b mit kleinerem Durchmesser. Entsprechend ist das Steuerventilglied 162 in seinem Außendurchmesser ebenfalls gestuft ausgebildet und weist einen Bereich 162a mit größerem Durchmesser auf, der im Abschnitt 161a der Bohrung 161 angeordnet ist und einen Bereich 162b mit kleinerem Durchmesser, der im Abschnitt 161b der Bohrung 161 angeordnet ist. Zwischen einer durch einen Absatz am Steuerventilglied 162 gebildeten Ringschulter 170 und der Zwischenscheibe 54 ist eine vorgespannte Rückstellfeder 172 angeordnet, durch die das Steuerventilglied 162 zum Boden 71 der Bohrung 161 hin gedrückt wird. Durch den im Durchmesser größeren Bereich 162a des Steuerventilglieds 162 wird im Abschnitt 161a der Bohrung 161 ein Arbeitsraum 178 begrenzt, der über einen Kanal 185 mit der hydraulischen Übersetzung des Piezoaktors 80 verbunden ist. Der vom Steuerventilglied 162 im Abschnitt 161a der Bohrung 161 zur Zwischenscheibe 54 hin begrenzte Raum 188, in dem die Rückstellfeder 172 angeordnet ist, ist über einen Kanal 189 mit einem Entlastungsraum, beispielsweise dem Vorratstank 12, verbunden.In Figure 4, the control valve 18 according to a second Embodiment illustrated, in turn, the basic structure is the same as the first Embodiment, however, the effective directions of the Piezo actuator generated actuating force and the return spring are reversed. The control valve member 162 has the bore 63, through which the nozzle 52 protrudes into the pressure chamber 64, from which the bore 65 discharges. At the bottom 71 of the bore 161 the recess 73 is formed and the control valve member 162 has the projection 68 on. The bore 161 is as Stepped bore formed and faces the washer 54 toward a larger diameter section 161a and toward its bottom 71 a smaller portion 161b Diameter. Accordingly, the control valve member 162 is in his outside diameter also formed stepped and has an area 162a with a larger diameter, the in the section 161 a of the bore 161 is arranged and a Area 162b of smaller diameter, in the section 161b of the bore 161 is arranged. Between a through a shoulder formed on the control valve member 162 Ring shoulder 170 and the washer 54 is a biased return spring 172 arranged through which the Control valve member 162 to the bottom 71 of the bore 161 out is pressed. Due to the larger diameter area 162a of the control valve member 162 is in section 161a of Bore 161 defines a working space 178, which has a Channel 185 with the hydraulic transmission of the piezoelectric actuator 80 is connected. The from the control valve member 162 in the section 161a of the bore 161 limited to the intermediate disc 54 out Room 188 in which the return spring 172 is arranged is via a channel 189 with a discharge space, for example, the storage tank 12, connected.

Nachfolgend wird die Funktion des Steuerventils 18 gemäß dem zweiten Ausführungsbeispiel erläutert. Wenn der Piezoaktor 80 von der Steuereinrichtung 20 nicht aktiviert ist, so wird durch die Rückstellfeder 172 das Steuerventilglied 162 mit seiner zweiten Dichtfläche 69 gegen den zweiten Ventilsitz 74 am Boden 71 der Bohrung gepresst und befindet sich in seiner zweiten Schließstellung. Wenn der Piezoaktor 80 aktiviert ist, so wird durch den erhöhten Druck im Arbeitsraum 178 das Steuerventilglied 162 gegen die Vorspannung der Rückstellfeder 172 zur Zwischenscheibe 54 hin verschoben. Bei ausreichend hohem Druck im Arbeitsraum 178 gelangt das Steuerventilglied 162 mit seiner ersten Dichtfläche 66 in Anlage am ersten Ventilsitz 60 und wird in seiner ersten Schließstellung gehalten. In seiner zweiten Schließstellung, in der sich das Steuerventilglied 162 bei nicht aktiviertem Piezoaktor 80 befindet, ist das Volumen der Bohrung 65 im Steuerventilglied 162 ebenfalls vom hohen Druck im Steuerdruckraum 48 beaufschlagt. Im Gegensatz hierzu befindet sich das Steuerventilglied 62 gemäß dem ersten Ausführungsbeispiel bei nicht aktiviertem Piezoaktor 80 in seiner ersten Schließstellung, in der nur der Druckraum 64 im Steuerventilglied 62 vom hohen Druck im Steuerdruckraum 48 beaufschlagt ist, während das Volumen der Bohrung 65 mit dem Entlastungsraum verbunden ist. Durch das beim Steuerventil 18 gemäß dem zweiten Ausführungsbeispiel vorhandene größere vom hohen Druck im Steuerdruckraum 48 beaufschlagte Volumen kann das dynamische Verhalten des Steuerventils 18 insbesondere bei kurzen Voreinspritzzeiten beeinflußt werden.Hereinafter, the function of the control valve 18 according to the second embodiment explained. When the piezo actuator 80 is not activated by the controller 20 is so by the return spring 172, the control valve member 162 with its second sealing surface 69 against the second valve seat 74 pressed on the bottom 71 of the hole and is located in its second closed position. When the piezoelectric actuator 80 is activated, so by the increased pressure in the Working space 178 the control valve member 162 against the Bias of the return spring 172 to the washer 54th postponed. At sufficiently high pressure in the working space 178, the control valve member 162 comes with its first Sealing surface 66 in abutment with the first valve seat 60 and is in kept its first closed position. In his second Closed position in which the control valve member 162 at is not activated piezoelectric actuator 80 is the volume the bore 65 in the control valve member 162 also from the high Pressure in the control pressure chamber 48 acted upon. In contrast this is the control valve member 62 according to the first embodiment with not activated piezoelectric actuator 80 in its first closed position, in which only the Pressure chamber 64 in the control valve member 62 from the high pressure in Control pressure chamber 48 is applied, while the volume of the Bore 65 is connected to the discharge chamber. By the at the control valve 18 according to the second embodiment existing larger of the high pressure in the control pressure chamber 48 applied volume can be the dynamic behavior of the Control valve 18, especially for short Voreinspritzzeiten to be influenced.

Claims (8)

  1. Fuel injection valve for internal combustion engines, in particular as a component of an accumulator-type fuel injection system, having an injection valve element (24) which is guided in an axially displaceable fashion and by means of which at least one injection opening (26) is controlled and which has a pressure shoulder (36) which bounds a pressure space (34), wherein pressurized fuel is fed to the pressure space (34) from a high-pressure fuel source (10; 14) by means of which the injection valve element (24) can be lifted off from a valve seat (30) counter to a closing force in order to open the at least one injection opening (26), and having a control valve (18) which influences the movement of the injection valve element (24) and which has a control valve element (62; 162) which can be moved counter to a restoring force by an actuating force which is generated by a piezo-actuator (80), said control valve element (62; 162) controlling the pressure prevailing in a control pressure space (48) which is connected to a pressure source (10; 14) and loading the injection valve element (24) at least indirectly in its closing direction, wherein the control pressure space (48) can be connected to a relief space (12) by means of the control valve element (62; 162) and the control valve element (62; 162) interacts with at least one sealing face (66, 69) with at least one valve seat (60, 74) via which the connection of the control pressure space (48) to the relief space (12) is controlled, wherein the control valve (18) has two valve seats (60, 74) which are spaced apart from one another in the direction of movement of the control valve element (62; 162), wherein the control valve element (62; 162) can be moved between two closed positions in which it respectively bears with a sealing face (66, 69) against one of the valve seats (60, 74) and the control pressure space (48) is separated from the relief space (12), and wherein the control pressure space (48) is connected to the relief space (12) when the control valve element (62; 162) is arranged between its two closed positions, characterized in that the control valve element (62; 162) is embodied as a hollow piston, wherein the first sealing face (66) is arranged inside the control valve element (62; 162) and the second sealing face (69) is arranged on the outside of the control valve element (62; 162).
  2. Fuel injection valve according to Claim 1, characterized in that the two valve seats (60, 74) have cross-sectional faces which are at least approximately of the same size.
  3. Fuel injection valve according to Claim 1 or 2, characterized in that a connector (52), in which a duct (58) which leads to the control pressure space (48) is formed, projects into the control valve element (62; 162), said duct (58) opening into a pressure space (64) in the control valve element (62; 162), the connection of which pressure space (64) to the relief space (12) is controlled by the control valve element (62; 162).
  4. Fuel injection valve according to Claim 3, characterized in that the first sealing face (66) which is formed within the control valve element (62; 162) interacts with the end region of the connector (52) which serves as a first valve seat (60), and a connection of the pressure space (64) to an outflow duct (65) which is formed in the control valve element (62; 162) is controlled by means of said sealing face (66).
  5. Fuel injection valve according to Claim 4, characterized in that the second sealing face (69) which is arranged on the outside of the control valve element (62, 162) is arranged in the region of the mouth of the outflow duct (65) and interacts with the second valve seat (74) which is arranged on a housing part (56) of the control, valve (16) and a connection of the outflow duct (65) to the relief space (12) is controlled by means of said second sealing face (69).
  6. Fuel injection valve according to one of Claims 3 to 5, characterized in that the actuating force which is generated by the piezo-actuator (80) is amplified by a hydraulic transformer which has a working space (78) which is bounded by the control valve element (62), in that a sealing region (63) by means of which the pressure space (64) is separated from the working space (78) is provided between the connector (52) and the control valve element (62), and in that the sealing region (63) has a connection (88, 89, 90, 91) to a relief space (12).
  7. Fuel injection valve according to one of Claims 4 to 6, characterized in that the control valve element (62) is loaded in the direction of the first valve seat (60) on the connector (52) by the restoring force.
  8. Fuel injection valve according to Claim 5 or 6, characterized in that the control valve element (162) is loaded in the direction of the second valve seat (74) on the housing part (56) by the restoring force.
EP00993183A 1999-11-11 2000-11-10 Fuel injection valve for internal combustion engines Expired - Lifetime EP1252433B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19954288 1999-11-11
DE19954288A DE19954288A1 (en) 1999-11-11 1999-11-11 Fuel injection valve for fitting to internal combustion engines has an injection valve element to control injection openings, a control valve to affect movement in injection valve elements and a valve element for regulating pressure
PCT/DE2000/004011 WO2001038712A2 (en) 1999-11-11 2000-11-10 Fuel injection valve for internal combustion engines

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EP1252433A2 EP1252433A2 (en) 2002-10-30
EP1252433B1 true EP1252433B1 (en) 2005-08-31

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EP (1) EP1252433B1 (en)
JP (1) JP2003515045A (en)
KR (1) KR100717522B1 (en)
CZ (1) CZ295475B6 (en)
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KR100717522B1 (en) 2007-05-14
WO2001038712A2 (en) 2001-05-31
WO2001038712A3 (en) 2001-12-27
US6581850B1 (en) 2003-06-24
JP2003515045A (en) 2003-04-22
CZ20012468A3 (en) 2002-11-13
KR20010101466A (en) 2001-11-14
CZ295475B6 (en) 2005-08-17
DE19954288A1 (en) 2001-05-17
DE50011086D1 (en) 2005-10-06
EP1252433A2 (en) 2002-10-30

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