EP1290335B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP1290335B1
EP1290335B1 EP01933624A EP01933624A EP1290335B1 EP 1290335 B1 EP1290335 B1 EP 1290335B1 EP 01933624 A EP01933624 A EP 01933624A EP 01933624 A EP01933624 A EP 01933624A EP 1290335 B1 EP1290335 B1 EP 1290335B1
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EP
European Patent Office
Prior art keywords
valve
valve piece
piece
fuel
opening
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
EP01933624A
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German (de)
French (fr)
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EP1290335A1 (en
Inventor
Patrick Mattes
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1290335A1 publication Critical patent/EP1290335A1/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
    • 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
    • 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
    • F02M47/027—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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to a fuel injection valve with the Features of claim 1.
  • Such a fuel injector which also as Injector is referred to, for example, from DE 196 50 865 A1 known and used in fuel injection systems, which are equipped with a high-pressure fuel accumulator are.
  • Valve needle over a valve piston from in a control pressure chamber prevailing fuel pressure in the closing direction.
  • the control pressure chamber is in one in the valve housing used valve piece and arranged with a Inlet throttle provided inlet channel and one with an outlet throttle provided drain channel with a high-pressure fuel connection or a low-pressure fuel connection connected. Drain throttle and inlet throttle are both arranged in the same valve piece inserted into the valve housing.
  • valve member of a control valve which as a drive, for example, a magnetic actuator or Piezosteller has
  • the drain channel can be closed and opened and the fuel pressure in the control pressure chamber for the individual operations of the valve needle can be controlled.
  • the opening speed of the valve needle is when the valve is open Drain channel through the flow difference between Inlet throttle and outlet throttle and thus ultimately by Fixed size ratio of inlet and outlet throttle certainly.
  • a disadvantage of the known fuel injection valve is that both the inlet throttle and the Flow restrictor with great precision in the same component getting produced. Are the geometric dimensions of a the chokes are not within the required accuracy, so the entire valve piece must be manufactured again.
  • inlet throttle and outlet throttle in the same valve piece in addition, complex and the manufacturing committee accordingly high.
  • the known fuel injection valve opens a section of the inlet channel arranged in the valve body, from which a pressure hole leading to the injection opening branches into an annular space surrounding the valve piece, which Annulus is connected to the inlet throttle.
  • the disadvantage here is that for the inlet channel in the Valve body drilled in the area of the pressure hole leads to a critical drilling intersection that occurs at the high Pressing in the inlet channel to impair the function can lead.
  • EPC describes a fuel injection valve proposed for internal combustion engines, in which the Inlet throttle and the outlet throttle on separate components are trained.
  • the inlet throttle is in one Guide sleeve for the control piston introduced in one piece. A simple replacement of the inlet throttle is therefore not possible.
  • Flow rate between inlet throttle and outlet throttle simply replace the second valve piece with the inlet throttle without the first containing the control pressure chamber Valve piece must be removed.
  • the fuel injector does not have to be completely disassembled here that a simple adjustment of the fuel flow between Inlet and outlet throttle by adjusting and replacing of the second valve piece is possible.
  • the interchangeable Inlet throttle thus allows easy readjustment of the Injection valve in case of quantity deviations in the test field.
  • first valve piece trained opening extending radially to the valve member branches off from the control pressure chamber and the second valve piece in a coaxial with the opening of the first valve piece outwardly extending mounting hole of the valve housing is inserted and with an end portion in which the Inlet channel opens into the opening of the first valve piece is introduced. This ensures that second valve piece in a very easy to assemble manner the mounting hole of the valve housing can be replaced can.
  • the second valve piece which include a seal that connects between the first valve piece and the second valve piece seals.
  • the inner wall forms the opening formed in the first valve piece a preferably conical seat for one on the Outer wall of the second valve piece formed sealing edge.
  • connection piece provided anyway for the high-pressure fuel connection the injection valve can be advantageous at the same time can be used as a tensioning part, which at least indirectly the second valve piece against the first valve piece biases.
  • a spring element clamped which is the sealing edge of the second valve piece presses against a conical seat of the valve piece.
  • a drill waste can advantageously be avoided if one arranged in the valve housing, the injection opening pressure bore supplying the fuel to be injected, preferably in the area of the spring element into which the opens the second valve piece receiving bore.
  • the second valve piece in one piece with the connecting piece for the high-pressure fuel connection trained and with a seat seal Mistake.
  • a gradation surrounding the inlet channel is on provided the outer wall of the second valve piece, by which is an annular contact surface for a sealing ring is formed, which faces away from the bearing surface Side is pressed against the first valve piece.
  • the high pressure connection is made via a hole, which between the inlet throttle and that of the control pressure chamber inlet facing away from the inlet channel into the inlet channel opens out and the inlet channel with one in the valve housing arranged pressure hole, which connects the injection opening supplied with the fuel to be injected.
  • Fig. 1a and Fig. 1b is a section through an electrical controlled fuel injection valve according to the state of the Technology shown, such as from DE 196 50th 865 A1 is known.
  • a fuel injector is intended for use in a fuel injection system, which are equipped with a high-pressure fuel accumulator is continuous by a high pressure feed pump is supplied with high-pressure fuel and from there Fuel under injection pressure via individual electrically controlled Injectors supplied to the internal combustion engine can be.
  • the fuel injector shown in Figures 1a and 1b 1 has a valve housing 4 a longitudinal bore 5 in which, for example, as a push rod formed, piston-like part 6 is arranged, that at one end via a pressure piece 67 on an in acts on a nozzle body 65 arranged valve needle 60, which by the closing force of a nozzle spring 63 and the Pressure force of the part 6 at least one injection opening 7 in Nozzle body 65 closes.
  • the nozzle body is by means of a Spiral spring pin 66 and a nozzle nut 64 with connected to the valve body.
  • On the valve needle 60 is known in Way, a pressure shoulder 68 formed in a Pressure chamber 61 of the nozzle body 65 is arranged.
  • the Pressure chamber 61 is under high pressure via a pressure bore 8 standing fuel supplied. With an opening stroke movement of part 6, the valve needle 60 by the high pressure of fuel constantly attacking the pressure shoulder 68 in the pressure chamber 61 against the closing force of the spring 63 raised. By then connected to the pressure chamber 61 Injection opening 7 is used to inject the fuel in the combustion chamber of the internal combustion engine. By lowering the Part 6 becomes the valve needle 60 in the closing direction of the spring force the spring 63 in the valve seat 62 of the injection valve pressed and the injection process ends.
  • part 6 is on its end opposite the valve needle 60 in one Cylinder bore 11 out, which is introduced into a valve piece 12 which is inserted into the valve housing 4.
  • a control pressure chamber 14 which via an inlet channel 16 connected to a high-pressure fuel connection 3 is.
  • the inlet channel 16 is essentially in three parts educated.
  • One radially through the wall of the valve piece 12 leading bore, the inner walls of which are part of their length form an inlet throttle 15, with one the valve piece annular space 20 surrounding the circumference is permanently connected, which annulus in turn via one in the inlet channel inserted fuel filter 42 in constant communication with the high-pressure fuel connection 3 in the valve housing 4 screw-in connecting piece 9 stands.
  • the Annular space 20 is connected to longitudinal bore 5 via a sealing ring 39 sealed.
  • the control pressure chamber is via the inlet channel 16 14 the high prevailing in the high-pressure fuel accumulator Exposed to fuel pressure.
  • Coaxial to part 6 branches out the control pressure chamber 14 a running in the valve piece 12 Bore from that provided with a discharge throttle 18 Forms drain channel 17, which opens into a relief chamber 19, which is connected to a fuel low pressure connection 10 which, in turn, is not shown in FIG Way with a fuel return of the injection valve 1 connected is.
  • the outlet channel 17 exits the valve piece 12 takes place in the area of a countersunk cone Part 21 of the outer end face of the valve piece 12.
  • the valve piece 12 is in a flange region 22 firmly clamped to the valve housing 4 via a screw member 23.
  • a valve seat 24 is formed in the conical part 21, with which a control valve member 25 of the injection valve controlling solenoid valve 30 cooperates.
  • the control valve member 25 is in shape with a two-part anchor an anchor bolt 27 and an anchor plate 28 coupled, which armature with an electromagnet 29 of the solenoid valve 30 works together.
  • the anchor plate is under the influence of them inert mass against the preload of a return spring 35 dynamically slidably mounted on the anchor bolt and is by this return spring at rest against a stop ring 26 pressed on the anchor bolt.
  • the return spring 35 is fixed to the housing via a flange 32 of the anchor bolt leading slider 34 from that with this Flange between valve piece 12 and screw 23 in the valve body is firmly clamped.
  • the anchor bolt and with it the armature disk and that connected to the anchor bolt Control valve member 25 are constantly housed by one supporting closing spring 31 acted upon in the closing direction, so that the control valve member 25 normally in Close position is present on valve seat 24.
  • the anchor plate 28 is electromagnets by the electromagnet attracted and thereby the drain channel 17 to the relief space 19 open.
  • an annular shoulder 33 on the anchor bolt 27 Between the control valve member 25 and the Anchor plate 28 is an annular shoulder 33 on the anchor bolt 27, when the electromagnet is excited on the flange 32 stops and so the opening stroke of the control valve member 25th limited.
  • To set the opening stroke is between Flange 32 and valve piece 12 inserted a shim 38.
  • the opening and closing of the valve needle is as follows Controlled by the solenoid valve.
  • control pressure chamber 14 In the closed position of the control valve member 25 is the control pressure chamber 14 closed to the discharge side 19 so that there via the inlet duct 15 provided with the inlet throttle 16 the high pressure builds up very quickly, which also in the High-pressure fuel accumulator pending.
  • About the area of the The end face 13 generates the pressure in the control pressure chamber 14 Closing force on part 6 and the related Valve needle 60, which is larger than that on the other hand in Opening direction due to the high pressure Forces.
  • the control pressure chamber 14 by opening the solenoid valve open to the relief side 19, builds up the pressure in the small volume of the control pressure chamber 14 very quickly, since this is via the inlet throttle 15 of the High pressure side is disconnected.
  • FIGS. 2 and 3 are two embodiments for a fuel injector according to the invention shown.
  • the partial representation in FIGS. 2 and 3 is limited on the parts deviating from FIGS. 1a and 1b. Same Parts have been given the same reference numbers.
  • a second Valve piece 40 as an essentially cylindrical insert formed, which in a receiving bore 46 of the Valve housing 4 is used.
  • the outside diameter of the cylindrical second valve piece 40 is slightly smaller formed as the inner diameter of the receiving bore 46.
  • the front end facing the control pressure chamber 14 48 of the second valve piece 40 has a circumferential sealing edge 53, which is connected to the first valve piece 12 trained seat 55 cooperates, as below is still described.
  • the second valve piece has 40 has an axial bore which has a section 16a of the inlet channel 16 forms. A section narrowed in cross section the inner wall of the in the second valve piece 40 formed section 16a of the inlet channel forms the inlet throttle 15 out.
  • the inlet throttle is in a known manner introduced into the second valve piece 40, which like that first valve piece 12 made of metal, for example can be.
  • first and second valve piece but also made of different materials become.
  • the first valve piece 12 differs from that in Fig. 1a shown valve piece 12 in that in place of the section of the inlet duct having the inlet throttle 15 16 an opening 45 is provided in the first valve piece which is radial to the cylinder bore 11 laterally extends from the control pressure chamber 14.
  • the inner wall 55 The opening 45 forms one starting from the control pressure chamber 14 tapered outward widening in diameter Seat for the second valve piece 40.
  • the second Valve piece 40 is with the end portion 48 in the receiving bore 46 used such that the sealing edge 53 on the conical seat 55 and the end portion 48th of the second valve piece 40 with the outlet opening of the inlet channel 16 faces the control pressure chamber 14.
  • the connecting piece 9 has on its second valve piece 12 facing side a stepped annular surface 51, from the from a cylindrical projection 52 of the connecting piece 9 protrudes toward the second valve piece 40.
  • a Spring element 56 arranged, for example a plate spring or coil spring.
  • the connecting piece 9 is in a threaded bore the valve housing 4 screwed and pressed with the projection 52 engaging in the receiving bore 46 the spring element 56 against the second valve piece 40, which hereby with the sealing edge 53 in the conical seat 55 is pressed.
  • a slid over the protrusion 52 on the annular surface 51 is sealing ring 41 pressed and sealed at the same time against the valve housing 4 the valve housing against the connecting piece.
  • the pressure chamber 61 with fuel supplying pressure bore 8 opens in the area of the spring element 56 into the receiving bore 46.
  • the under High-pressure fuel comes from the high-pressure fuel accumulator from the fuel filter first into the Part of the inlet channel 16, which is arranged in the connecting piece 9 and from there on the one hand through the gaps of the spring element 56 in the receiving bore 46 and Pressure bore 8 and the other through section 16a of the second valve piece 40 and the inlet throttle 15 in the Control pressure chamber 14.
  • the spring element 56 it is also possible on the spring element 56 to do without, and the second valve piece 40 immediately with the screwed connector 9 against that to bias the first valve piece 12.
  • the projection 52 of the connecting piece 9 can then be used to connect the pressure bore 8 with the inlet channel a radially opening into the inlet channel 16 have side hole.
  • first valve piece surrounding the opening 45 12 and the end face 48 of the second valve piece 40 just design and the second valve piece 40 with a Sealing ring against the flat part of the outer wall of the first Press valve piece 12. In this case, this applies second valve piece 40 not in the opening 45 of the first Valve piece.
  • FIG. 3 Another embodiment is shown in FIG. 3. at In this embodiment, the second valve piece 40 made in one piece with the connecting piece 9 made of metal.
  • this embodiment results from that the cylindrical projection 52 of the connecting piece 9 from 2 is somewhat extended and has a further gradation, which has an annular bearing surface 57 for one forms another sealing ring 54, for example a Viton seal.
  • the sealing ring 54 becomes 9 when screwing in the connecting piece the threaded bore of the valve housing 4 against the outer wall of the first valve piece 12 pressed, whereby the control pressure chamber 14 is sealed.
  • transverse bore 58 in the inlet channel 16 a, which the inlet channel with the in the valve housing 4 arranged pressure hole 8 connects.
  • this transverse bore 58 is approximately coaxial with the pressure bore 8 introduced into the connecting piece 3.

Abstract

The invention relates to a fuel injection valve (1) for internal combustion engines, comprising a valve housing (4) with an axially movable valve member for opening and closing an injection opening (7) of the injection valve, and a part (6) which acts in the closing direction of the valve member (60) and which is guided in a bore (11) of a first valve piece with the end facing away from the injection opening (7), said valve piece being introduced into the valve housing (4), and which closes a control pressure chamber (14) in the first valve piece (12) with this end. According to the invention, at least the section of the delivery channel (16) that is provided with the delivery throttle (15) is situated on the second valve piece (40) introduced into the valve housing, said second valve piece being connected to an opening (45) configured in the first valve piece in such a way that the section of the delivery channel of the second valve piece (40) that is provided with the delivery throttle (15) opens out into the control pressure chamber of the first valve piece.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Kraftstoffeinspritzventil mit den Merkmalen des Anspruchs 1.The invention relates to a fuel injection valve with the Features of claim 1.

Ein derartiges Kraftstoffeinspritzventil, welches auch als Injektor bezeichnet wird, ist beispielsweise aus der DE 196 50 865 A1 bekannt und wird in Kraftstoffeinspritzanlagen verwandt, die mit einem Kraftstoffhochdruckspeicher ausgerüstet sind. Bei dem bekannten Kraftstoffeinspritzventil wird eine Ventilnadel über einen Ventilkolben von in einem Steuerdruckraum herrschenden Kraftstoffdruck in Schließrichtung belastet. Der Steuerdruckraum ist in einem in das Ventilgehäuse eingesetzten Ventilstück angeordnet und über einen mit einer Zulaufdrossel versehenen Zulaufkanal und einen mit einer Ablaufdrossel versehenen Ablaufkanal mit einem Kraftstoffhochdruckanschluß beziehungsweise einem Kraftstoffniederdruckanschluß verbunden. Ablaufdrossel und Zulaufdrossel sind beide im selben in das Ventilgehäuse eingesetzten Ventilstück angeordnet. Mit einem Ventilglied eines Steuerventils, welches als Antrieb beispielsweise einen Magnetsteller oder einen Piezosteller hat, kann der Ablaufkanal geschlossen und geöffnet werden und der Kraftstoffdruck im Steuerdruckraum für die einzelnen Betätigungsvorgänge der Ventilnadel gesteuert werden. Die Öffnungsgeschwindigkeit der Ventilnadel wird bei geöffnetem Ablaufkanal durch den Durchflußunterschied zwischen Zulaufdrossel und Ablaufdrossel und damit letztlich durch das fest eingestellte Größenverhältnis von Zulauf- und Ablaufdrossel bestimmt. Nachteilig bei dem bekannten Kraftstoffeinspritzventil ist, daß sowohl die Zulaufdrossel als auch die Ablaufdrossel mit sehr großer Präzision im gleichen Bauteil hergestellt werden. Liegen die geometrischen Abmessungen einer der Drosseln nicht innerhalb der geforderten Genauigkeit, so muß das ganze Ventilstück neu gefertigt werden. Da der Zulaufkanal und der Ablaufkanal etwa senkrecht zueinander in den Steuerdruckraum einmünden, ist die präzise Herstellung von Zulaufdrossel und Ablaufdrossel im gleichen Ventilstück darüber hinaus aufwendig und der Fertigungsausschuß entsprechend hoch. Bei dem bekannten Kraftstoffeinspritzventil mündet ein im Ventilkörper angeordneter Abschnitt des Zulaufkanals, von dem eine zur Einspritzöffnung führende Druckbohrung abzweigt, in einen das Ventilstück umgebenden Ringraum, welcher Ringraum mit der Zulauförossel in Verbindung steht. Nachteilig hierbei ist, daß die für den Zulaufkanal in den Ventilkörper eingebrachte Bohrung im Bereich der Druckbohrung zu einer kritischen Bohrverschneidung führt, die bei den hohen Drücken im Zulaufkanal zu Funktionsbeeinträchtigungen führen kann.Such a fuel injector, which also as Injector is referred to, for example, from DE 196 50 865 A1 known and used in fuel injection systems, which are equipped with a high-pressure fuel accumulator are. In the known fuel injection valve Valve needle over a valve piston from in a control pressure chamber prevailing fuel pressure in the closing direction. The control pressure chamber is in one in the valve housing used valve piece and arranged with a Inlet throttle provided inlet channel and one with an outlet throttle provided drain channel with a high-pressure fuel connection or a low-pressure fuel connection connected. Drain throttle and inlet throttle are both arranged in the same valve piece inserted into the valve housing. With a valve member of a control valve, which as a drive, for example, a magnetic actuator or Piezosteller has, the drain channel can be closed and opened and the fuel pressure in the control pressure chamber for the individual operations of the valve needle can be controlled. The opening speed of the valve needle is when the valve is open Drain channel through the flow difference between Inlet throttle and outlet throttle and thus ultimately by Fixed size ratio of inlet and outlet throttle certainly. A disadvantage of the known fuel injection valve is that both the inlet throttle and the Flow restrictor with great precision in the same component getting produced. Are the geometric dimensions of a the chokes are not within the required accuracy, so the entire valve piece must be manufactured again. Because the inlet channel and the drain channel approximately perpendicular to each other in the control pressure chamber is the precise manufacture of inlet throttle and outlet throttle in the same valve piece in addition, complex and the manufacturing committee accordingly high. In the known fuel injection valve opens a section of the inlet channel arranged in the valve body, from which a pressure hole leading to the injection opening branches into an annular space surrounding the valve piece, which Annulus is connected to the inlet throttle. The disadvantage here is that for the inlet channel in the Valve body drilled in the area of the pressure hole leads to a critical drilling intersection that occurs at the high Pressing in the inlet channel to impair the function can lead.

In der EP 1 118 765 A2 gemäss Artikel 54(3) EPÜ wird ein Brennstoffeinspritzventil für Verbrennungskraftmaschinen vorgeschlagen, bei dem die Zulaufdrossel und die Ablaufdrossel an getrennten Bauteilen ausgebildet sind. Die Zulaufdrossel ist dabei in eine Führungshülse für den Steuerkolben einstückig eingebracht. Ein einfacher Austausch der Zulaufdrossel ist daher nicht möglich.EP 1 118 765 A2 in accordance with Article 54 (3) EPC describes a fuel injection valve proposed for internal combustion engines, in which the Inlet throttle and the outlet throttle on separate components are trained. The inlet throttle is in one Guide sleeve for the control piston introduced in one piece. A simple replacement of the inlet throttle is therefore not possible.

Vorteile der ErfindungAdvantages of the invention

Durch das erfindungsgemäße Kraftstoffeinspritzventil mit den Merkmalen des Anspruchs 1 werden die oben beschriebenen Nachteile vermieden. Dies wird durch ein unabhängig von dem ersten Ventil stück hersgestelltes zweites Ventilstück erreicht, an dem der mit der Zulaufdrossel versehene Abschnitt des Zulaufkanals angeordnet ist und das mit einer an dem ersten Ventilstück angeordneten Öffnung derart verbunden ist, daß der mit der Zulaufdrossel versehene Abschnitt des Zulaufkanals des zweiten Ventilstücks in den Steuerdruckraum des ersten Ventilstücks einmündet. Da die Zulaufdrossel und die Ablaufdrossel in zwei getrennte Bauteile eingebracht werden, können diese wesentlich einfacher und unabhängig voneinander mit der erforderlichen Genauigkeit hergestellt werden und der Fertigungsausschuß verringert werden. Vorteilhaft kann bei einer Nachjustage des Injektors bei festgestellten Abweichungen vom vorgegebenen Mengendurchfluß zwischen Zulaufdrossel und Ablaufdrossel einfach das zweite Ventilstück mit der Zulaufdrossel ausgetauscht werden, ohne daß das erste den Steuerdruckraum beinhaltende Ventilstück ausgebaut werden muß. Das Kraftstoffeinspritzventil muß hierbei nicht völlig zerlegt werden, so daß eine einfache Abstimmung des Kraftstoffdurchflusses zwischen Zulauf- und Ablaufdrossel durch Anpassen und Auswechseln des zweiten Ventilstücks möglich ist. Die auswechselbare Zulaufdrossel erlaubt somit eine einfache Nachjustage des Einspritzventils bei Mengenabweichungen im Prüffeld.By the fuel injector according to the invention with the Features of claim 1 are the above described disadvantages avoided. This is done by an independent second manufactured from the first valve piece Reached valve piece on which the one provided with the inlet throttle Section of the inlet channel is arranged and with an opening arranged on the first valve piece such is connected that the section provided with the inlet throttle of the inlet channel of the second valve piece in the Control pressure chamber of the first valve piece opens. Since the Inlet throttle and the outlet throttle in two separate components introduced, they can be much easier and independently of one another with the required accuracy are produced and the manufacturing committee is reduced become. Can be advantageous when readjusting the injector if deviations from the specified are found Flow rate between inlet throttle and outlet throttle simply replace the second valve piece with the inlet throttle without the first containing the control pressure chamber Valve piece must be removed. The fuel injector does not have to be completely disassembled here that a simple adjustment of the fuel flow between Inlet and outlet throttle by adjusting and replacing of the second valve piece is possible. The interchangeable Inlet throttle thus allows easy readjustment of the Injection valve in case of quantity deviations in the test field.

Weiterentwicklungen und vorteilhafte Ausführungen der Erfindung werden durch die in den Unteransprüchen enthaltenen Merkmale ermöglicht.Further developments and advantageous embodiments of the invention are covered by those in the subclaims Features.

Besonders vorteilhaft ist, wenn die in dem ersten Ventilstück ausgebildete Öffnung radial zum Ventilglied verlaufend aus dem Steuerdruckraum abzweigt und das zweite Ventilstück in eine sich koaxial zu der Öffnung des ersten Ventilstücks nach außen erstreckende Aufnahmebohrung des Ventilgehäuses eingesetzt ist und mit einem Endabschnitt, in welchen der Zulaufkanal einmündet, in die Öffnung des ersten Ventilstücks eingeführt ist. Hierdurch wird erreicht, daß das zweite Ventilstück in sehr einfach zu montierender Weise in der Aufnahmebohrung des Ventilgehäuses ausgetauscht werden kann. It is particularly advantageous if that in the first valve piece trained opening extending radially to the valve member branches off from the control pressure chamber and the second valve piece in a coaxial with the opening of the first valve piece outwardly extending mounting hole of the valve housing is inserted and with an end portion in which the Inlet channel opens into the opening of the first valve piece is introduced. This ensures that second valve piece in a very easy to assemble manner the mounting hole of the valve housing can be replaced can.

Es sind verschiedene Ausführungsformen des zweiten Ventilstücks möglich, welche eine Dichtung umfassen, die die Verbindung zwischen dem ersten Ventilstück und dem zweiten Ventilstück abdichtet.There are various embodiments of the second valve piece possible, which include a seal that connects between the first valve piece and the second valve piece seals.

In einem vorteilhaften Ausführungsbeispiel bildet die Innenwandung der in dem ersten Ventilstück ausgebildeten Öffnung eine vorzugsweise konusförmige Sitzfläche für eine an der Außenwandung des zweiten Ventilstücks ausgebildete Dichtkante.In an advantageous embodiment, the inner wall forms the opening formed in the first valve piece a preferably conical seat for one on the Outer wall of the second valve piece formed sealing edge.

Der ohnehin vorgesehene Anschlußstutzen für den Kraftstoffhochdruckanschluß des Enspritzventils kann vorteilhaft zugleich als Spannteil verwandt werden, welches zumindest mittelbar das zweite Ventilstück gegen das erste Ventilstück vorspannt. In einem Ausführungsbeispiel ist zwischen dem Anschlußstutzen und dem zweiten Ventilstück ein Federelement eingespannt, welches die Dichtkante des zweiten Ventilstücks gegen eine konusförmige Sitzfläche des Ventilstücks preßt.The connection piece provided anyway for the high-pressure fuel connection the injection valve can be advantageous at the same time can be used as a tensioning part, which at least indirectly the second valve piece against the first valve piece biases. In one embodiment is between the connection piece and the second valve piece a spring element clamped, which is the sealing edge of the second valve piece presses against a conical seat of the valve piece.

Vorteilhaft kann ein Bohrverschnitt vermieden werden, falls eine in dem Ventilgehäuse angeordnete, die Einspritzöffnung mit dem einzuspritzenden Kraftstoff versorgende Druckbohrung, vorzugsweise im Bereich des Federelementes, in die das zweite Ventilstück aufnehmende Aufnahmebohrung einmündet.A drill waste can advantageously be avoided if one arranged in the valve housing, the injection opening pressure bore supplying the fuel to be injected, preferably in the area of the spring element into which the opens the second valve piece receiving bore.

In einem zweiten Ausführungsbeispiel ist das zweite Ventilstück einstückig mit dem Anschlußstutzen für den Kraftstoffhochdruckanschluß ausgebildet und mit einer Sitzdichtung versehen. Eine den Zulaufkanal umgebende Abstufung ist an der Außenwandung des zweiten Ventilstücks vorgesehen, durch welche eine ringförmige Auflagefläche für einen Dichtring ausgebildet wird, der mit seiner von der Auflagefläche abgewandten Seite gegen das erste Ventilstück gepreßt wird. Der Hochdruckanschluß erfolgt in diesem Fall über eine Bohrung, welche zwischen der Zulaufdrossel und dem vom Steuerdruckraum abgewandten Einlaß des Zulaufkanals in den Zulaufkanal einmündet und den Zulaufkanal mit einer in dem Ventilgehäuse angeordneten Druckbohrung verbindet, welche die Einspritzöffnung mit dem einzuspritzenden Kraftstoff versorgt.In a second embodiment, the second valve piece in one piece with the connecting piece for the high-pressure fuel connection trained and with a seat seal Mistake. A gradation surrounding the inlet channel is on provided the outer wall of the second valve piece, by which is an annular contact surface for a sealing ring is formed, which faces away from the bearing surface Side is pressed against the first valve piece. The In this case, the high pressure connection is made via a hole, which between the inlet throttle and that of the control pressure chamber inlet facing away from the inlet channel into the inlet channel opens out and the inlet channel with one in the valve housing arranged pressure hole, which connects the injection opening supplied with the fuel to be injected.

Zeichnungendrawings

Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung erläutert. Es zeigt

  • Fig. 1a einen Schnitt durch den oberen Teil eines aus dem Stand der Technik bekannten Kraftstoffeinspritzventils mit Magnetsteller,
  • Fig. 1b einen Schnitt durch den unteren Teil des bekannten Kraftstoffeinspritzventils aus Fig. 1a,
  • Fig. 2 einen Teilschnitt aus einem ersten Ausführungsbeispiel eines erfindungsgemäßen Kraftstoffeinspritzventils und
  • Fig. 3 einen Teilschnitt aus einem zweiten Ausführungsbeispiel eines erfindungsgemäßen Kraftstoffeinspritzventils.
    • Exemplary embodiments of the invention are illustrated in the drawings and are explained in the description below. It shows
  • 1a shows a section through the upper part of a fuel injection valve with magnetic actuator known from the prior art,
  • 1b shows a section through the lower part of the known fuel injection valve from Fig. 1a,
  • Fig. 2 is a partial section from a first embodiment of a fuel injection valve according to the invention and
  • Fig. 3 is a partial section from a second embodiment of a fuel injection valve according to the invention.

    • Beschreibung der AusführungsbeispieleDescription of the embodiments

    In Fig. 1a und Fig. 1b ist ein Schnitt durch ein elektrisch gesteuertes Kraftstoffeinspritzventil nach dem Stand der Technik dargestellt, wie es beispielsweise aus der DE 196 50 865 A1 bekannt ist. Ein solches Kraftstoffeinspritzventil ist zur Verwendung in einer Kraftstoffeinspritzanlage bestimmt, die mit einem Kraftstoffhochdruckspeicher ausgerüstet ist, der durch eine Hochdruckförderpumpe kontinuierlich mit Hochdruckkraftstoff versorgt wird und von dem aus dieser Kraftstoff unter Einspritzdruck über einzelne elektrisch gesteuerte Einspritzventile der Brennkraftmaschine zugeführt werden kann. Das in den Figuren 1a und 1b gezeigte Kraftstoffeinspritzventil 1 weist dabei ein Ventilgehäuse 4 mit einer Längsbohrung 5 auf, in der ein zum Beispiel als Druckstange ausgebildetes, kolbenartiges Teil 6 angeordnet ist, das an seinem einen Ende über ein Druckstück 67 auf eine in einem Düsenkörper 65 angeordnete Ventilnadel 60 einwirkt, welche durch die Schließkraft einer Düsenfeder 63 und die Druckkraft des Teils 6 wenigstens eine Einspritzöffnung 7 im Düsenkörper 65 verschließt. Der Düsenkörper ist mittels eines Spiralspannstiftes 66 und einer Düsenspannmutter 64 mit dem Ventilkörper verbunden. An der Ventilnadel 60 ist in bekannter Weise eine Druckschulter 68 ausgebildet, die in einem Druckraum 61 des Düsenkörpers 65 angeordnet ist. Der Druckraum 61 wird über eine Druckbohrung 8 mit unter Hochdruck stehendem Kraftstoff versorgt. Bei einer Öffnungshubbewegung des Teiles 6 wird die Ventilnadel 60 durch den ständig an der Druckschulter 68 angreifenden Kraftstoffhochdruck im Druckraum 61 entgegen der Schließkraft der Feder 63 angehoben. Durch die dann mit dem Druckraum 61 verbundene Einspritzöffnung 7 erfolgt die Einspritzung des Kraftstoffs in den Brennraum der Brennkraftmaschine. Durch Absenken des Teiles 6 wird die Ventilnadel 60 in Schließrichtung der Federkraft der Feder 63 in den Ventilsitz 62 des Einspritzventils gedrückt und der Einspritzvorgang beendet.In Fig. 1a and Fig. 1b is a section through an electrical controlled fuel injection valve according to the state of the Technology shown, such as from DE 196 50th 865 A1 is known. Such a fuel injector is intended for use in a fuel injection system, which are equipped with a high-pressure fuel accumulator is continuous by a high pressure feed pump is supplied with high-pressure fuel and from there Fuel under injection pressure via individual electrically controlled Injectors supplied to the internal combustion engine can be. The fuel injector shown in Figures 1a and 1b 1 has a valve housing 4 a longitudinal bore 5 in which, for example, as a push rod formed, piston-like part 6 is arranged, that at one end via a pressure piece 67 on an in acts on a nozzle body 65 arranged valve needle 60, which by the closing force of a nozzle spring 63 and the Pressure force of the part 6 at least one injection opening 7 in Nozzle body 65 closes. The nozzle body is by means of a Spiral spring pin 66 and a nozzle nut 64 with connected to the valve body. On the valve needle 60 is known in Way, a pressure shoulder 68 formed in a Pressure chamber 61 of the nozzle body 65 is arranged. The Pressure chamber 61 is under high pressure via a pressure bore 8 standing fuel supplied. With an opening stroke movement of part 6, the valve needle 60 by the high pressure of fuel constantly attacking the pressure shoulder 68 in the pressure chamber 61 against the closing force of the spring 63 raised. By then connected to the pressure chamber 61 Injection opening 7 is used to inject the fuel in the combustion chamber of the internal combustion engine. By lowering the Part 6 becomes the valve needle 60 in the closing direction of the spring force the spring 63 in the valve seat 62 of the injection valve pressed and the injection process ends.

    Wie am besten in Fig. 1a zu erkennen ist, wird das Teil 6 an seinem der Ventilnadel 60 gegenüber liegenden Ende in einer Zylinderbohrung 11 geführt, die in einem Ventilstück 12 eingebracht ist, welches in das Ventilgehäuse 4 eingesetzt ist. In der Zylinderbohrung 11 schließt die Stirnseite 13 des Teiles 6 einen Steuerdruckraum 14 ein, der über einen Zulaufkanal 16 mit einem Kraftstoffhochdruckanschluß 3 verbunden ist. Der Zulaufkanal 16 ist im wesentlichen dreiteilig ausgebildet. Eine radial durch die Wand des Ventilstücks 12 führende Bohrung, deren Innenwände auf einem Teil ihrer Länge eine Zulaufdrossel 15 ausbilden, ist mit einem das Ventilstück umfangsseitig umgebenden Ringraum 20 ständig verbunden, welcher Ringraum wiederum über einen in den Zulaufkanal eingeschobenen Kraftstoffilter 42 in ständiger Verbindung mit dem Kraftstoffhochdruckanschluß 3 eines in das Ventilgehäuse 4 einschraubbaren Anschlußstutzens 9 steht. Der Ringraum 20 ist über einen Dichtring 39 zur Längsbohrung 5 abgedichtet. Über den Zulaufkanal 16 ist der Steuerdruckraum 14 dem im Kraftstoffhochdruckspeicher herrschenden hohen Kraftstoffdruck ausgesetzt. Koaxial zum Teil 6 zweigt aus dem Steuerdruckraum 14 eine im Ventilstück 12 verlaufende Bohrung ab, die einen mit einer Ablaufdrossel 18 versehenen Ablaufkanal 17 bildet, der in einen Entlastungsraum 19 einmündet, der mit einem Kraftstoffniederdruckanschluß 10 verbunden ist, welcher wiederum in nicht weiter dargestellter Weise mit einem Kraftstoffrücklauf des Einspritzventils 1 verbunden ist. Der Austritt des Ablaufkanals 17 aus dem Ventilstück 12 erfolgt im Bereich eines kegelförmig angesenkten Teiles 21 der außenliegenden Stirnseite des Ventilstückes 12. Das Ventilstück 12 ist dabei in einem Flanschbereich 22 fest über ein Schraubglied 23 mit dem Ventilgehäuse 4 verspannt.As best seen in Fig. 1a, part 6 is on its end opposite the valve needle 60 in one Cylinder bore 11 out, which is introduced into a valve piece 12 which is inserted into the valve housing 4. In the cylinder bore 11, the end face 13 of the Part 6 a control pressure chamber 14, which via an inlet channel 16 connected to a high-pressure fuel connection 3 is. The inlet channel 16 is essentially in three parts educated. One radially through the wall of the valve piece 12 leading bore, the inner walls of which are part of their length form an inlet throttle 15, with one the valve piece annular space 20 surrounding the circumference is permanently connected, which annulus in turn via one in the inlet channel inserted fuel filter 42 in constant communication with the high-pressure fuel connection 3 in the valve housing 4 screw-in connecting piece 9 stands. The Annular space 20 is connected to longitudinal bore 5 via a sealing ring 39 sealed. The control pressure chamber is via the inlet channel 16 14 the high prevailing in the high-pressure fuel accumulator Exposed to fuel pressure. Coaxial to part 6 branches out the control pressure chamber 14 a running in the valve piece 12 Bore from that provided with a discharge throttle 18 Forms drain channel 17, which opens into a relief chamber 19, which is connected to a fuel low pressure connection 10 which, in turn, is not shown in FIG Way with a fuel return of the injection valve 1 connected is. The outlet channel 17 exits the valve piece 12 takes place in the area of a countersunk cone Part 21 of the outer end face of the valve piece 12. The valve piece 12 is in a flange region 22 firmly clamped to the valve housing 4 via a screw member 23.

    In dem kegelförmigen Teil 21 ist ein Ventilsitz 24 ausgebildet, mit dem ein Steuerventilglied 25 eines das Einspritzventil steuernden Magnetventils 30 zusammen wirkt. Das Steuerventilglied 25 ist mit einem zweiteiligen Anker in Form eines Ankerbolzens 27 und einer Ankerscheibe 28 gekoppelt, welcher Anker mit einem Elektromagneten 29 des Magnetventils 30 zusammen wirkt. Die Ankerplatte ist unter Einwirkung ihrer trägen Masse gegen die Vorspannkraft einer Rückholfeder 35 dynamisch verschiebbar auf dem Ankerbolzen gelagert und wird durch diese Rückholfeder im Ruhezustand gegen einen Anschlagring 26 am Ankerbolzen gedrückt. Die Rückholfeder 35 stützt sich gehäusefest über einen Flansch 32 eines den Ankerbolzen führenden Gleitstücks 34 ab, das mit diesem Flansch zwischen Ventilstück 12 und Schraubteil 23 im Ventilgäuse fest eingespannt ist. Der Ankerbolzen und mit ihm die Ankerscheibe und das mit dem Ankerbolzen verbundene Steuerventilglied 25 sind ständig durch eine sich gehäusefest abstützende Schließfeder 31 in Schließrichtung beaufschlagt, so daß das Steuerventilglied 25 normalerweise in Schließstellung am Ventilsitz 24 anliegt. Bei Erregung des Elektromagneten wird die Ankerplatte 28 vom Elektromagneten angezogen und dabei der Ablaufkanal 17 zum Entlastungsraum 19 hin geöffnet. Zwischen dem Steuerventilglied 25 und der Ankerplatte 28 befindet sich eine Ringschulter 33 am Ankerbolzen 27, die bei erregtem Elektromagneten am Flansch 32 anschlägt und so den Öffnungshub des Steuerventilglieds 25 begrenzt. Zur Einstellung des Öffnungshubes ist zwischen Flansch 32 und Ventilstück 12 eine Einstellscheibe 38 eingelegt. Das Öffnen und Schließen der Ventilnadel wird in folgender Weise durch das Magnetventil gesteuert. In Schließstellung des Steuerventilgliedes 25 ist der Steuerdruckraum 14 zur Entlastungsseite 19 hin verschlossen, so daß sich dort über den mit der Zulaufdrossel 15 versehenen Zulaufkanal 16 sehr schnell der hohe Druck aufbaut, der auch in dem Kraftstoffhochdruckspeicher ansteht. Über die Fläche der Stirnseite 13 erzeugt der Druck im Steuerdruckraum 14 eine Schließkraft auf das Teil 6 und die damit in Verbindung stehende Ventilnadel 60, die größer ist als die andererseits in Öffnungsrichtung in Folge des anstehenden Hochdrucks wirkenden Kräfte. Wird der Steuerdruckraum 14 durch Öffnen des Magnetventils zur Entlastungsseite 19 hin geöffnet, baut sich der Druck in dem geringen Volumen des Steuerdruckraumes 14 sehr schnell ab, da dieser über die Zulaufdrossel 15 von der Hochdruckseite abgekoppelt ist. Infolgedessen überwiegt die auf die Ventilnadel in Öffnungsrichtung wirkende Kraft aus dem an der Ventilnadel anstehenden Kraftstoffhochdruck, so daß diese nach oben bewegt und dabei die wenigstens eine Einspritzöffnung 7 zur Einspritzung geöffnet wird. Schließt jedoch das Magnetventil 30 den Ablaufkanal 17, kann der Druck im Steuerdruckraum 14 durch den über den Zulaufkanal 16 nachfließenden Kraftstoff dennoch sehr schnell wieder aufgebaut werden, so daß die ursprüngliche Schließkraft ansteht und die Ventilnadel des Kraftstoffeinspritzventils schließt. Natürlich kann an Stelle des mit dem Steuerventilglied 25 zusammenwirkenden Magnetstellers auch ein Piezosteller oder eine Kombination aus Piezosteller und Magnetsteller oder ein anderes Stellglied verwandt werden.A valve seat 24 is formed in the conical part 21, with which a control valve member 25 of the injection valve controlling solenoid valve 30 cooperates. The control valve member 25 is in shape with a two-part anchor an anchor bolt 27 and an anchor plate 28 coupled, which armature with an electromagnet 29 of the solenoid valve 30 works together. The anchor plate is under the influence of them inert mass against the preload of a return spring 35 dynamically slidably mounted on the anchor bolt and is by this return spring at rest against a stop ring 26 pressed on the anchor bolt. The return spring 35 is fixed to the housing via a flange 32 of the anchor bolt leading slider 34 from that with this Flange between valve piece 12 and screw 23 in the valve body is firmly clamped. The anchor bolt and with it the armature disk and that connected to the anchor bolt Control valve member 25 are constantly housed by one supporting closing spring 31 acted upon in the closing direction, so that the control valve member 25 normally in Close position is present on valve seat 24. When the The anchor plate 28 is electromagnets by the electromagnet attracted and thereby the drain channel 17 to the relief space 19 open. Between the control valve member 25 and the Anchor plate 28 is an annular shoulder 33 on the anchor bolt 27, when the electromagnet is excited on the flange 32 stops and so the opening stroke of the control valve member 25th limited. To set the opening stroke is between Flange 32 and valve piece 12 inserted a shim 38. The opening and closing of the valve needle is as follows Controlled by the solenoid valve. In the closed position of the control valve member 25 is the control pressure chamber 14 closed to the discharge side 19 so that there via the inlet duct 15 provided with the inlet throttle 16 the high pressure builds up very quickly, which also in the High-pressure fuel accumulator pending. About the area of the The end face 13 generates the pressure in the control pressure chamber 14 Closing force on part 6 and the related Valve needle 60, which is larger than that on the other hand in Opening direction due to the high pressure Forces. The control pressure chamber 14 by opening the solenoid valve open to the relief side 19, builds up the pressure in the small volume of the control pressure chamber 14 very quickly, since this is via the inlet throttle 15 of the High pressure side is disconnected. As a result, the prevails force acting on the valve needle in the opening direction the high fuel pressure at the valve needle, so that this moves up and the at least one Injection opening 7 is opened for injection. closes however, the solenoid valve 30 the drain channel 17, the Pressure in the control pressure chamber 14 through the via the inlet channel 16 fuel flowing in again very quickly be built up so that the original closing force is applied and the valve needle of the fuel injector closes. Of course, instead of using the control valve member 25 interacting magnetic actuator also a piezo actuator or a combination of a piezo actuator and a magnetic actuator or another actuator can be used.

    In den Figuren 2 und 3 sind zwei Ausführungsbeispiele für ein erfindungsgemäßes Kraftstoffeinspritzventil dargestellt. Die Teildarstellung in Fig. 2 und Fig. 3 beschränkt sich dabei auf die von Fig. 1a und 1b abweichenden Teile. Gleiche Teile wurden mit gleichen Bezugsziffern versehen.In Figures 2 and 3 are two embodiments for a fuel injector according to the invention shown. The partial representation in FIGS. 2 and 3 is limited on the parts deviating from FIGS. 1a and 1b. Same Parts have been given the same reference numbers.

    Bei dem ersten Ausführungsbeispiel in Fig. 2 ist ein zweites Ventilstück 40 als im wesentlichen zylinderförmiges Einlegeteil ausgebildet, welches in eine Aufnahmebohrung 46 des Ventilgehäuses 4 eingesetzt ist. Der Außendurchmesser des zylinderförmigen zweiten Ventilstücks 40 ist etwas kleiner ausgebildet, als der Innendurchmesser der Aufnahmebohrung 46. Das dem Steuerdruckraum 14 zugewandte stirnseitige Ende 48 des zweiten Ventilstücks 40 weist eine umlaufende Dichtkante 53 auf, welche mit einer an dem ersten Ventilstück 12 ausgebildeten Sitzfläche 55 zusammenwirkt, wie weiter unten noch beschrieben wird. Weiterhin weist das zweite Ventilstück 40 eine axiale Bohrung auf, welche einen Abschnitt 16a des Zulaufkanals 16 bildet. Ein im Querschnitt verengter Abschnitt der Innenwandung des in dem zweiten Ventilstück 40 ausgebildeten Abschnitts 16a des Zulaufkanals bildet die Zulaufdrossel 15 aus. Die Zulaufdrossel wird in bekannter Weise in das zweite Ventilstück 40 eingebracht, welches wie das erste Ventilstück 12 beispielsweise aus Metall gefertigt sein kann. Prinzipiell können das erste und zweite Ventilstück aber auch aus unterschiedlichen Materialien gefertigt werden. Das erste Ventilstück 12 unterscheidet sich von dem in Fig. 1a gezeigten Ventilstück 12 dadurch, daß an Stelle des die Zulaufdrossel 15 aufweisenden Abschnitts des Zulaufkanals 16 eine Öffnung 45 in dem ersten Ventilstück vorgesehen ist, welche sich radial zur Zylinderbohrung 11 seitlich aus dem Steuerdruckraum 14 erstreckt. Die Innenwandung 55 der Öffnung 45 bildet eine sich ausgehend vom Steuerdruckraum 14 nach außen im Durchmesser erweiternde, konusförmige Sitzfläche für das zweite Ventilstück 40 aus. Das zweite Ventilstück 40 ist mit dem Endabschnitt 48 in die Aufnahmebohrung 46 derart eingesetzt, daß die Dichtkante 53 an der konusförmigen Sitzfläche 55 anliegt und der Endabschnitt 48 des zweiten Ventilstücks 40 mit der Austrittsöffnung des Zulaufkanals 16 dem Steuerdruckraum 14 zugewandt ist. Der Anschlußstutzen 9 weist an seiner dem zweiten Ventilstück 12 zugewandten Seite eine abgestufte Ringfläche 51 auf, von der aus ein zylindrischer Vorsprung 52 des Anschlußstutzens 9 zum zweiten Ventilstück 40 hin absteht. Zwischen dem zweiten Ventilstück 40 und dem zylindrischen Vorsprung 52 ist ein Federelement 56 angeordnet, beispielsweise eine Tellerfeder oder Schraubenfeder. Der Anschlußstutzen 9 wird in eine Gewindebohrung des Ventilgehäuses 4 eingeschraubt und preßt mit dem in die Aufnahmebohrung 46 eingreifenden Vorsprung 52 das Federelement 56 gegen das zweite Ventilstück 40 an, welches hierdurch mit der Dichtkante 53 in die konische Sitzfläche 55 gepreßt wird. Ein über den Vorsprung 52 geschobener, an der Ringfläche 51 anliegender Dichtring 41 wird gleichzeitig gegen das Ventilgehäuse 4 angedrückt und dichtet das Ventilgehäuse gegen den Anschlußstutzen ab. Eine in dem Ventilgehäuse 4 angeordnete, den Druckraum 61 mit Kraftstoff versorgende Druckbohrung 8 mündet im Bereich des Federelementes 56 in die Aufnahmebohrung 46 ein. Der unter Hochdruck stehende Kraftstoff gelangt vom Kraftstoffhochdruckspeicher aus über den Kraftstoffilter zunächst in den Teil des Zulaufkanals 16, welcher im Anschlußstutzen 9 angeordnet ist, und von dort einerseits durch die Zwischenräume des Federelementes 56 in die Aufnahmebohrung 46 und die Druckbohrung 8 und andererseits durch den Abschnitt 16a des zweiten Ventilstücks 40 und die Zulaufdrossel 15 in den Steuerdruckraum 14. In Abweichung von dem hier dargestellten Ausführungsbeispiel ist es auch möglich, auf das Federelement 56 zu verzichten, und das zweite Ventilstück 40 unmittelbar mit dem eingeschraubten Anschlußstutzen 9 gegen das erste Ventilstück 12 vorzuspannen. Der Vorsprung 52 des Anschlußstutzens 9 kann dann zur Verbindung der Druckbohrung 8 mit dem Zulaufkanal eine in den Zulaufkanal 16 radial einmündende seitliche Bohrung aufweisen. Auch ist es möglich, den die Öffnung 45 umgebenden Bereich des ersten Ventilstücks 12 und die Stirnseite 48 des zweiten Ventilstücks 40 eben auszugestalten und das zweite Ventilstück 40 mit einem Dichtungsring gegen den ebenen Teil der Außenwandung des ersten Ventilstücks 12 anzudrücken. In diesem Fall greift das zweite Ventilstück 40 nicht in die Öffnung 45 des ersten Ventilstücks ein.In the first embodiment in Fig. 2 is a second Valve piece 40 as an essentially cylindrical insert formed, which in a receiving bore 46 of the Valve housing 4 is used. The outside diameter of the cylindrical second valve piece 40 is slightly smaller formed as the inner diameter of the receiving bore 46. The front end facing the control pressure chamber 14 48 of the second valve piece 40 has a circumferential sealing edge 53, which is connected to the first valve piece 12 trained seat 55 cooperates, as below is still described. Furthermore, the second valve piece has 40 has an axial bore which has a section 16a of the inlet channel 16 forms. A section narrowed in cross section the inner wall of the in the second valve piece 40 formed section 16a of the inlet channel forms the inlet throttle 15 out. The inlet throttle is in a known manner introduced into the second valve piece 40, which like that first valve piece 12 made of metal, for example can be. In principle, the first and second valve piece but also made of different materials become. The first valve piece 12 differs from that in Fig. 1a shown valve piece 12 in that in place of the section of the inlet duct having the inlet throttle 15 16 an opening 45 is provided in the first valve piece which is radial to the cylinder bore 11 laterally extends from the control pressure chamber 14. The inner wall 55 The opening 45 forms one starting from the control pressure chamber 14 tapered outward widening in diameter Seat for the second valve piece 40. The second Valve piece 40 is with the end portion 48 in the receiving bore 46 used such that the sealing edge 53 on the conical seat 55 and the end portion 48th of the second valve piece 40 with the outlet opening of the inlet channel 16 faces the control pressure chamber 14. The connecting piece 9 has on its second valve piece 12 facing side a stepped annular surface 51, from the from a cylindrical projection 52 of the connecting piece 9 protrudes toward the second valve piece 40. Between the second Valve piece 40 and the cylindrical projection 52 is a Spring element 56 arranged, for example a plate spring or coil spring. The connecting piece 9 is in a threaded bore the valve housing 4 screwed and pressed with the projection 52 engaging in the receiving bore 46 the spring element 56 against the second valve piece 40, which hereby with the sealing edge 53 in the conical seat 55 is pressed. A slid over the protrusion 52 on the annular surface 51 is sealing ring 41 pressed and sealed at the same time against the valve housing 4 the valve housing against the connecting piece. One in arranged the valve housing 4, the pressure chamber 61 with fuel supplying pressure bore 8 opens in the area of the spring element 56 into the receiving bore 46. The under High-pressure fuel comes from the high-pressure fuel accumulator from the fuel filter first into the Part of the inlet channel 16, which is arranged in the connecting piece 9 and from there on the one hand through the gaps of the spring element 56 in the receiving bore 46 and Pressure bore 8 and the other through section 16a of the second valve piece 40 and the inlet throttle 15 in the Control pressure chamber 14. In deviation from that shown here Embodiment, it is also possible on the spring element 56 to do without, and the second valve piece 40 immediately with the screwed connector 9 against that to bias the first valve piece 12. The projection 52 of the connecting piece 9 can then be used to connect the pressure bore 8 with the inlet channel a radially opening into the inlet channel 16 have side hole. It is also possible the area of the first valve piece surrounding the opening 45 12 and the end face 48 of the second valve piece 40 just design and the second valve piece 40 with a Sealing ring against the flat part of the outer wall of the first Press valve piece 12. In this case, this applies second valve piece 40 not in the opening 45 of the first Valve piece.

    Ein weiteres Ausführungsbeispiel ist in Fig. 3 gezeigt. Bei diesem Ausführungsbeispiel ist das zweite Ventilstück 40 einstückig mit dem Anschlußstutzen 9 aus Metall gefertigt. Im Prinzip ergibt sich dieses Ausführungsbeispiel dadurch, daß der zylindrische Vorsprung 52 des Anschlußstutzens 9 aus Fig. 2 etwas verlängert wird und eine weiter Abstufung aufweist, welche eine ringförmige Auflagefläche 57 für einen weiteren Dichtring 54 bildet, beispielsweise eine Viton-Dichtung. Von der Auflagefläche 57 steht ein weiterer zylindrischer Vorsprung ab, der mit seiner Stirnseite 48 in die Öffnung 45 des ersten Ventilstücks 12 eingreift. Der Dichtring 54 wird beim Einschrauben des Anschlußstutzens 9 in die Gewindebohrung des Ventilgehäuses 4 gegen die Außenwandung des ersten Ventilstücks 12 gepreßt, wodurch der Steuerdruckraum 14 abgedichtet wird. Zwischen der Zulaufdrossel 15 und dem vom Steuerdruckraum 14 abgewandten Einlaß 3 des Zulaufkanals 16 mündet eine Querbohrung 58 in den Zulaufkanal 16 ein, welche den Zulaufkanal mit der in dem Ventilgehäuse 4 angeordneten Druckbohrung 8 verbindet. Vorzugsweise ist diese Querbohrung 58 in etwa koaxial zu der Druckbohrung 8 in den Anschlußstutzen 3 eingebracht.Another embodiment is shown in FIG. 3. at In this embodiment, the second valve piece 40 made in one piece with the connecting piece 9 made of metal. In principle, this embodiment results from that the cylindrical projection 52 of the connecting piece 9 from 2 is somewhat extended and has a further gradation, which has an annular bearing surface 57 for one forms another sealing ring 54, for example a Viton seal. There is another cylindrical one from the support surface 57 Projection from the end face 48 in the Opening 45 of the first valve piece 12 engages. The sealing ring 54 becomes 9 when screwing in the connecting piece the threaded bore of the valve housing 4 against the outer wall of the first valve piece 12 pressed, whereby the control pressure chamber 14 is sealed. Between the inlet throttle 15 and the inlet 3 of the inlet channel facing away from the control pressure chamber 14 16 opens a transverse bore 58 in the inlet channel 16 a, which the inlet channel with the in the valve housing 4 arranged pressure hole 8 connects. Preferably this transverse bore 58 is approximately coaxial with the pressure bore 8 introduced into the connecting piece 3.

    Claims (12)

    1. Fuel injection valve (1) for internal combustion engines having a valve housing (4) and having a valve element (60) which moves axially in order to open and close an injection opening (7) in the injection valve, and having a part (6) which acts in the closing direction of the valve element (60), is guided by its end (13), which faces away from the injection opening (7), in a bore (11) in a first valve piece (12) which is inserted into the valve housing (4), and, by means of this end (13) encloses a control pressure area (14) in the first valve piece (12), which control pressure area (14) can be connected to a fuel low-pressure connection (10) via an inlet channel (16), which is provided with at least one inlet throttle (15) and has a fuel high-pressure connection (3) and via an outlet channel (17) which can be closed by a moving control valve element (25) and has an outlet throttle (28), in which case the injection process can be controlled via the fuel pressure that is controlled by the control valve element (25) in the control pressure area (14), with at least one section (16a) which is provided with the inlet throttle (15) of the inlet channel (16) being arranged on a second valve piece (40), which is inserted into the valve housing (4) and is connected with an opening (45) formed in the first valve piece (12) such that the section (16a) of the inlet channel (16) of the second valve piece (40) which is provided with the inlet throttle (15) opens into the control pressure area (14) in the first valve piece (12), with the second valve piece (40) being inserted into a retaining bore (46), which extends outwards, in the valve housing (4).
    2. Fuel injection valve according to Claim 1, characterized in that the opening (45) which is formed in the first valve piece (12) branches away from the control pressure area (14) running radially with respect to the axis of the bore (11), and in that the second valve piece (40) is inserted into a retaining bore (46) (which extends outwards coaxially with respect to the opening (45) of the first valve piece (12)) in the valve housing (4), and has an end section (48), into which the inlet channel (16) opens, which is inserted in the opening (45) in the first valve piece (12).
    3. Fuel injection valve according to Claim 1 or 2, characterized in that a seal (53, 54) is provided and seals the connection between the first valve piece (12) and the second valve piece (40).
    4. Fuel injection valve according to Claim 3, characterized in that a connecting stub (9) (which has the fuel high-pressure connection (3) and can be attached to the valve housing (4)) of the injection valve (1) forms a clamping part which at least indirectly prestresses the second valve piece (40) against the first valve piece (12).
    5. Fuel injection valve according to Claim 4, characterized in that the inner wall (55) of the opening (45) which is formed in the first valve piece (12) forms a seating surface for a sealing edge (53) which is formed on the outer wall of the second valve piece (40).
    6. Fuel injection valve according to Claim 5, characterized in that the seating surface (55) is conical.
    7. Fuel injection valve according to Claim 5, characterized in that a spring element (56) is clamped between the connecting stub (9) and the second valve piece (40) and presses the sealing edge (53) of the second valve piece (40) against the seating surface (55).
    8. Fuel injection valve according to Claim 7, characterized in that a pressure bore (8), which is arranged in the valve housing (4) and supplies the injection opening (7) with the fuel to be injected, opens, preferably in the area of the spring element (56), into the retaining bore (46) which holds the second valve piece (40).
    9. Fuel injection valve according to Claim 4,
      characterized in that the second valve piece (40) is formed integrally with the connecting stub (9), which has the fuel high-pressure connection (3) and can be attached to the valve housing (4).
    10. Fuel injection valve according to Claim 9, characterized in that a step, which surrounds the inlet channel (16), is provided on the outer wall of the second valve piece (40), by means of which an annular bearing surface (57) is formed for a sealing ring (54) which is used for sealing and whose side facing away from the bearing surface (57) is pressed against the first valve piece (12), sealing the opening (45) in the control pressure area (14).
    11. Fuel injection valve according to Claim 9 or 10, characterized in that a bore (58) opens into the inlet channel (16) between the inlet throttle (15) and the inlet (3) of the inlet channel (16) facing away from the control pressure area (14) and connects the inlet channel to a pressure bore (8) which is arranged in the valve housing (4) and supplies the injection opening (7) with the fuel to be injected.
    12. Fuel injection valve according to Claim 11, characterized in that the bore (58) which opens into the inlet channel (16) is introduced into the connecting stub (3) coaxially with respect to the pressure bore (8).
    EP01933624A 2000-05-23 2001-04-24 Fuel injection valve Expired - Lifetime EP1290335B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    DE10025497A DE10025497A1 (en) 2000-05-23 2000-05-23 Fuel injector
    DE10025497 2000-05-23
    PCT/DE2001/001540 WO2001090565A1 (en) 2000-05-23 2001-04-24 Fuel injection valve

    Publications (2)

    Publication Number Publication Date
    EP1290335A1 EP1290335A1 (en) 2003-03-12
    EP1290335B1 true EP1290335B1 (en) 2004-10-27

    Family

    ID=7643242

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP01933624A Expired - Lifetime EP1290335B1 (en) 2000-05-23 2001-04-24 Fuel injection valve

    Country Status (9)

    Country Link
    US (1) US20040069863A1 (en)
    EP (1) EP1290335B1 (en)
    JP (1) JP2003534492A (en)
    KR (1) KR20020019555A (en)
    CN (1) CN1380939A (en)
    BR (1) BR0106657A (en)
    CZ (1) CZ2002201A3 (en)
    DE (2) DE10025497A1 (en)
    WO (1) WO2001090565A1 (en)

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    DE10216622B3 (en) * 2002-04-15 2004-01-08 Siemens Ag One-piece control module for a fuel injector
    DE10257641B4 (en) * 2002-07-29 2009-08-20 Robert Bosch Gmbh Fuel injector with and without pressure boosting with controllable needle speed and method for its control
    DE102004022428A1 (en) * 2004-05-06 2005-12-01 Siemens Ag Injection valve for internal combustion engines
    EP1612398B1 (en) * 2004-06-30 2006-10-04 C.R.F. Società Consortile per Azioni Fuel injector comprising a force-balanced control valve
    JP4716142B2 (en) * 2008-09-16 2011-07-06 株式会社デンソー Fuel injection device
    EP2295784B1 (en) * 2009-08-26 2012-02-22 Delphi Technologies Holding S.à.r.l. Fuel injector
    DE102011081176A1 (en) * 2011-08-18 2013-02-21 Robert Bosch Gmbh Valve for metering a flowing medium
    US9644589B2 (en) * 2013-11-20 2017-05-09 Stanadyne Llc Debris diverter shield for fuel injector
    CN113123909A (en) * 2021-05-24 2021-07-16 中国重汽集团重庆燃油喷射系统有限公司 Compressing sleeve for high-pressure common rail system

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    EP1118765A2 (en) * 2000-01-19 2001-07-25 CRT Common Rail Technologies AG Fuel injector for internal combustion engines

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    US2391808A (en) * 1942-08-19 1945-12-25 Continental Motors Corp Fuel atomizer
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    US4709679A (en) * 1985-03-25 1987-12-01 Stanadyne, Inc. Modular accumulator injector
    DE4237469B4 (en) * 1992-11-06 2004-05-13 Robert Bosch Gmbh Fuel injection device, in particular pump nozzle for internal combustion engines
    CH689282A5 (en) * 1994-03-29 1999-01-29 Christian Dipl-Ing Eth Mathis Injection valve for a particular intended as a diesel engine internal combustion engine.
    FI101738B1 (en) * 1996-01-30 1998-08-14 Waertsilae Nsd Oy Ab Injector device
    DE19650865A1 (en) 1996-12-07 1998-06-10 Bosch Gmbh Robert magnetic valve
    IT1295462B1 (en) * 1997-10-02 1999-05-12 Elasis Sistema Ricerca Fiat FUEL INJECTOR WITH ELECTROMAGNETIC CONTROL FOR INTERNAL COMBUSTION ENGINES.
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    EP1118765A2 (en) * 2000-01-19 2001-07-25 CRT Common Rail Technologies AG Fuel injector for internal combustion engines

    Also Published As

    Publication number Publication date
    US20040069863A1 (en) 2004-04-15
    KR20020019555A (en) 2002-03-12
    CZ2002201A3 (en) 2003-06-18
    JP2003534492A (en) 2003-11-18
    DE10025497A1 (en) 2001-11-29
    EP1290335A1 (en) 2003-03-12
    WO2001090565A1 (en) 2001-11-29
    BR0106657A (en) 2002-04-02
    DE50104303D1 (en) 2004-12-02
    CN1380939A (en) 2002-11-20

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