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EP1576277A1 - Actionneur magnetique exempt d'impulsions rebondissantes pour des soupapes d'injection - Google Patents

Actionneur magnetique exempt d'impulsions rebondissantes pour des soupapes d'injection

Info

Publication number
EP1576277A1
EP1576277A1 EP03785564A EP03785564A EP1576277A1 EP 1576277 A1 EP1576277 A1 EP 1576277A1 EP 03785564 A EP03785564 A EP 03785564A EP 03785564 A EP03785564 A EP 03785564A EP 1576277 A1 EP1576277 A1 EP 1576277A1
Authority
EP
European Patent Office
Prior art keywords
face
damping
solenoid valve
magnetic
magnetic core
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.)
Withdrawn
Application number
EP03785564A
Other languages
German (de)
English (en)
Inventor
Michael Mennicken
Joachim Boltz
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE10305985A external-priority patent/DE10305985A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1576277A1 publication Critical patent/EP1576277A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/166—Selection of particular materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0635—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • Actuators such as piezo actuators or solenoid valves are used in fuel injection valves. By actuating the actuators, the pressure relief of a control chamber is initiated, whereby an injection valve opens, so that fuel can be injected into the combustion chamber of an expansion engine. Solenoid valves, however, have the property of tending to bounce, which means that the quantity map, i. H. the injection quantity can be changed in relation to the actuation duration so that it is only of limited suitability for reproductions or compensation functions.
  • EP 0 562 046 B1 discloses an actuating and valve arrangement with damping for an electronically controlled injection unit.
  • the actuating and valve arrangement for a hydraulic unit has an electrically excitable electromagnetic arrangement with a fixed stator and a moving armature.
  • the anchor includes a first and a second surface.
  • the first and second surfaces of the armature define first and second cavities, the first surface of the armature facing the stator.
  • a valve is provided which is connected to the armature.
  • the valve is capable of delivering hydraulic actuating fluid to the injector from a sump.
  • a damping fluid can be collected there with respect to one of the cavities of the electromagnet arrangement and can be discharged from there again.
  • DE 101 23 910.6 relates to a fuel injection device. This is used on an internal combustion engine.
  • the combustion chambers of the internal combustion engine are supplied with fuel via fuel injectors.
  • the fuel injectors in turn are acted upon by a high pressure source; the fuel injection device further comprises a pressure booster which has a movable pressure booster piston.
  • the fuel hole pressure in the high-pressure space can be varied by filling a rear space of a pressure transmission device with fuel or by emptying this rear space of the fuel translator of fuel.
  • the stroke is limited by stop sleeves, to name an example.
  • the stroke of the solenoid valve can be limited by the two seats. With such solenoid valves, bouncing can occur at the first, upper seat. The same applies to a valve that is open when de-energized and has only one seat.
  • stop sleeves are accommodated in the magnetic core, they surround a closing spring which acts on the magnetic armature.
  • a stop sleeve can be used to precisely set a residual air gap between the magnetic core and the armature or its armature plate.
  • the armature strikes an end face of the stop sleeve, which is referred to as armature bouncing.
  • the anchor bouncing on the stop sleeve has an effect on the quantity map, i. H. the injection quantity of fuel, based on the activation duration of a solenoid coil of a solenoid valve actuating a fuel injector.
  • the impact of anchor bouncing on the quantity field is desirable if, for example, a pre-injection quantity plateau is desired for a pre-injection phase in the combustion chamber.
  • a quantity map which has a pre-injection quantity plateau, is extremely unfavorable.
  • the anchor bounce influencing the quantity map of a fuel injector is considerably reduced by generating a surface that builds up a damping force. If only the end face of a stop sleeve and the end face of a magnetic core were available as a surface generating a damping force in the case of solutions used hitherto, a targeted increase in damping can be achieved with the solution proposed according to the invention.
  • the damping surface formed on the side of the magnetic core facing the magnetic armature is made of non-magnetic material, such as plastic. Plastic material has the advantage that it can be easily processed. This material can either be glued to the magnetic core or cast on it.
  • the easy machinability of the plastic material also offers the advantage that the damping behavior can be set in a targeted manner by forming an angle with respect to the flat end face of the magnet armature. In principle, all those materials can be used to manufacture the damping surface that have no or only minor effects on the magnetic circuit.
  • the damping surface can extend on the end face of the magnetic core facing the magnet armature both parallel to it and in a damping setting angle relative to the end face of the magnet anchor.
  • the desired damping behavior can be set by selecting the damping adjustment angle.
  • a hydraulic damping space that opens outwards in the radial direction it can also increasingly narrow towards the outside when viewed in the radial direction, based on the axis of symmetry of the magnet coil and the magnet core.
  • An undesired, premature outflow of the damping fluid (such as fuel) from the hydraulic damping space can be achieved by forming a nose-shaped projection on the outer radius of the hydraulic damping space.
  • the nose-shaped projection acts as a throttle element and, when the magnet armature moves upward, throttles the current of the actuating fluid, such as fuel or diesel fuel from the hydraulic damping chamber when the magnet analyzer is opened.
  • the actuating fluid such as fuel or diesel fuel from the hydraulic damping chamber when the magnet analyzer is opened.
  • FIG. 1 shows a Ma netventil, the stroke is limited by a stop sleeve.
  • FIG. 2 shows a magnetic valve designed according to the invention with a magnetic core that has a surface that generates a damping force,
  • FIG. 3 shows a magnetic core with an external stop sleeve
  • FIG. 4 pressure distributions in the hydraulic damping space in the case of the filling variants according to FIGS. 2 and 3,
  • Figure 5 shows the comparison according to the execution variants of FIGS. 2 and 3 adjusting damping forces
  • Figure 6 shows an embodiment variant of a magnetic core without a stop sleeve.
  • Figure 1 shows a solenoid valve according to the prior art, the stroke is limited by a stop sleeve.
  • a solenoid valve 1 which is used to actuate a fuel projector for self-igniting internal combustion engines, comprises a magnetic core 2.
  • a magnetic coil 3 is embedded in the magnetic core 2.
  • the magnetic core 2 comprises a first end face 4 and a second end face 5 facing a magnet armature 10.
  • a bore 6 is formed in the magnetic core 2, in which a stop sleeve 7 is embedded.
  • an end face 8 is formed, which forms a stop for an end face 12 of an anchor plate 11 of the magnetic anchor 10.
  • the stop sleeve 7 surrounds a closing spring 9 which acts on the end face 12 of the magnetic connector 10 in the closing direction.
  • the end face 12 of the magnet connector 10 is formed on its anchor plate 11.
  • the armature 10 is designed as a one-piece armature, i.e. Anlcerplatte 11 and anchor bolt of the magnet armature 10 form a component.
  • the anchor plate 11 of the magnet armature 10 can also be designed to be displaceable on the anchor bolt. In this case, i.e. in the case of a two-part magnetic armature, the anchor plate 11 is acted upon by a spring element which surrounds the anchor bolt.
  • Reference number 13 denotes a residual air gap, which characterizes the distance between the second end face 5 of the magnetic core 2 and the end face 12 of the armature plate 11 of the magnet anchor 10.
  • the magnet coil 3 is embedded in the lower region of the magnet core 2, an annular space 14 being configured between the underside of the magnet coil and the second end face 5 of the magnet core 2.
  • the annularly configured free space 14 between the underside of the magnet coil 3 and the end face 12 of the anlcer plate 11 of the magnet analyzer 10 exceeds the residual air gap 13; the distance between the magnetic coil 3 and the top 12 of the armature plate 11 is identified by reference numeral 15.
  • the ITub of the solenoid valve 1 is limited by the stop sleeve 7, that is to say the end face 8 of the stop sleeve 7 acts as a stop surface for the end face 12 of the anchor plate 11 of the magnetic armature 10 if the solenoid valve is due to a Excitation of the magnetic coil 3 opens and moves upwards - in the direction of the stop sleeve 7.
  • the remaining air gap 13 between the second end face 5 of the magnetic core 2 and the end face 12 of the anchor plate 11 can be set precisely.
  • the fuel volume controlled from a control chamber of the fuel injector is subject to fluctuations, which leads to inaccuracies with regard to the generation of a lifting movement - be it a closing movement - of an injection valve member provided in the fuel injector.
  • FIG. 2 shows a magnetic valve designed according to the invention with a magnetic core that has a surface that generates a damping force.
  • the magnetic core 2 shown in FIG. 2 shows a magnetic core 2, which is shown in half-section with respect to its axis of symmetry.
  • the magnetic core 2 shown in FIG. 2 comprises a first end face 4 and a second end face 5.
  • the magnet coil 3 is let into the interior of the magnet core 2.
  • the bore 6 is also formed, in which the stop sleeve 7 is received.
  • the diameter of the bore 6 of the magnetic core 2 is identical to an outer diameter 28 of the stop sleeve 7.
  • the stop sleeve 7 in turn comprises a closing spring 9, of which only a Windmig is shown in section here, which acts on a magnet armature 10 shown only partially in FIG. 2 in the closing direction.
  • the outlet gap 18 for fuel is formed between the end face 8 of the stop sleeve 7 and the end face 12 of the armature plate 11 of the magnet armature 10 when the magnet armature 10 is opened.
  • the outlet gap 18, which runs in a ring between the end face 8 of the stop sleeve 7 and the end face 12 of the anchor plate 11 of the magnet armature 10 opens into a hydraulic damping space 31 which extends in the radial direction.
  • the hydraulic damping space 31 is delimited on the side of the magnet anchor 2 on its second end face 5 by a damping surface 20 which extends from the outer diameter 28 of the stop sleeve 7 to the circumference 27 of the magnetic core 2. Furthermore, the hydraulic damping space 31 is delimited by the end face 12 of the armature plate 11 of the magnet armature 10.
  • the damping surface 20 on the armature side consists of a non-magnetic material 16, such as plastic material, in order not to impair the magnetic properties of the solenoid valve 1.
  • the achievable damping force can be set by the geometry of the damping surface 20, which counteracts one of the opening movements of the armature plate 11 of the magnetic armature 10.
  • the damping surface 20, which delimits the hydraulic damping space 31 can be at a constant distance 15, i.e. Fuel emerging parallel to the end face 12 of the anchor plate 11 and the end face 8 of the stop sleeve 7 enters the hydraulic damping chamber 31.
  • the hydraulic damping chamber 31 has a constant cross section which extends in the radial direction.
  • the damping surface 20 can be formed at an angle 17 on the second end face 5 of the magnetic core 2. In this embodiment variant, the distance between the
  • Magnetic armature 10 generates counteracting damping force, which is higher compared to the damping force that only through the end face 8 of the stop sleeve 7 (see
  • a hydraulic damping space 31 consists in attaching a nose-shaped projection 32 to the damping surface 20 on the second end face 5 of the magnetic core 2.
  • This nose-shaped projection 32 on the second end face 5 of the magnetic core 2 causes the fuel volume flowing out of the hydraulic damping chamber 31 to throttle when the anchor plate 11 of the magnetic core 10 is opened, which means that the fuel volume flowing onto the magnetic armature 10, i.e. whose armature plate 1 1, acting damping force can be increased, since the throttle point between the end face 12 of the armature plate 11 and the nose-shaped projection 32 becomes smaller and smaller during the opening movement of the magnet armature 10. Due to the reduction in the throttling point, i.e. the distance between the face
  • the outflow opening for the fuel volume flowing out of the damping space is identified by reference numeral 35.
  • the damping surface 20, which is made of a non-magnetic material 16, can be both glued to the second end face 5 of the magnetic core 2 and cast on the second end face 5 of the magnetic core 2. If the damping surface 20 is made from a non-magnetic material 16, such as plastic material, for example, by machining the damping surface 20 appropriately, grinding work can be specifically set to the angle 17 that significantly influences the damping behavior.
  • the damping surface 20 on the second end face 5 of the magnetic core 2 comprises a first annular surface section 21, which extends from the outer radius 28 of the stop sleeve 7 to the inner radius 25 of the magnetic coil 3 within the magnetic core 2.
  • the damping surface 20 further comprises a second annular surface section 22, which extends from the inner radius 25 of the magnet coil 3 to its outer radius 26, and a third ring surface section 23, which extends from the outer radius 26 of the magnet coil 3 within the magnet core 2 to the outer periphery 27 of the magnet core 2 ,
  • the already mentioned, throttle effect-developing nose-shaped projection 32 can be formed on the damping surface 20, which delimits the annularly configured hydraulic damping space 31, which with the end face 12 of the anchor plate 11 delimits an outflow opening 35, the opening cross section of which from the flow path and the speed of movement of the magnetic analyzer 10 depends.
  • the magnetic coil 3 is accommodated in an annularly configured recess 24.
  • the recess 24 defines a first edge 33 and a second edge 34 on the second end face 5 of the magnetic core 2.
  • the damping surface 20 can be glued or cast into the annular space delimited by the first edge 33 and the second edge 34, so that it is cast is fixed in the radial direction.
  • a step 29 of the damping surface 20 with respect to the second end face 5 of the magnetic core 2 is achieved by the first edge 33.
  • the gradation and the fixation of the damping surface 20 on the second end face 5 of the magnetic core 2 by the first edge 33 and the second edge 34 in the radial direction have the effect that the damping surface 20 of the magnetic core 2 is accommodated in a stationary manner and when the outlet gap 18 is shot in the hydraulic damping space 31 entering fuel volume remains reliably in its position and does not migrate outward in the radial direction.
  • the with respect to the second end face 5 of the magnetic core 2nd According to the illustration in FIG. 2, the step 29 or 30 of the hydraulic damping surface 20 is particularly effective if the damping surface 20 is made of a non-magnetic material 16, such as a plastic material, cast on the second end surface 5 of the magnetic core 2.
  • the nose-shaped projection 32 of the damping surface 20 is attached to the second end face 5 of the magnetic core 2, preferably above the outer edge of the armature plate 11 of the magnet armature 10.
  • a throttle is formed during the opening movement of the armature plate 11 in the direction of the nose-shaped projection 32, which decreases continuously during the opening movement of the magnet armature 10 or the armature plate 11, so that the flowing fluid 31 when the magnet armature 10 or the armature plate 11 opens is forced to flow out a continuously decreasing cross-section in the radial direction.
  • the damping lcraft achievable with reference number 19 is significantly higher than if the fuel volume flows freely from the hydraulic damping space 31 in the radial direction.
  • the magnetic properties of the solenoid valve 1 remain unchanged due to the formation of the damping surface 20 which delimits the hydraulic damping space 31 and the damping lcraft 19 takes place on a non-magnetic material 16.
  • the damping surface 20 is located in the residual air gap 13 between the second end face 5 of the magnetic core 2 and the end face 12 of the anchor plate 11 of the magnetic anchor 10 (see illustration according to FIG. 1).
  • the surface producing the damping force 19 can be designed in such a way that a targeted reinforcement of the damping lcraft 19 is achieved. If a non-magnetic material 16 such as e.g. Potting plastic, the bouncing behavior of the magnet armature 10 or the armature plate 11 can be set in a targeted manner by simple grinding work by adjusting the angle 17.
  • a non-magnetic material 16 such as e.g. Potting plastic
  • Fig. 3 shows a magnetic core with an external stop sleeve.
  • the magnetic core 2 comprises a first, upper end face and a second lower end face 5.
  • a magnetic coil 3 is accommodated in the magnetic core 2 in the recess 24.
  • the magnetic core 2 as shown in FIG. 3 is surrounded by a stop sleeve 7 which surrounds the outer circumference 27 of the magnetic core 2.
  • the end face of the stop sleeve 7 is identified by reference number 8.
  • Below the Magnet core 2 is the anchor plate 11 of a Magnetanlcer.
  • the anchor plate 11 has an end face 12.
  • On the second end face 5 of the magnetic core 2 a non-magnetic filler material 16 is accommodated, the damping face 20 of which, together with the end face 12 of the anchor plate 11, delimits the hydraulic damping space 31.
  • the non-magnetic filler material 16 extends on the second end face 5 of the magnetic core 2 via a first ring surface section 21, a second ring surface section 22 adjoining this and a third ring surface section 23.
  • the non-magnetic filler material 16 has a first step 29 and a second stage 30 and can be cast or glued to the second end face 5 of the magnetic core 2.
  • the stages 29 and 30 of the non-magnetic filler 16 form a first edge 33 and a second edge 34 which engage in the Ausnel tion 24 of the magnetic core 2 and the non-magnetic filler 16 relative to the magnetic core 2 positively secure in the radial direction ,
  • the non-magnetic filler material 16 is arranged on the second end face 5 of the magnetic core 2 in such a way that a damping adjustment angle 17 results which is the reverse of the damping adjustment angle 17 as shown in FIG. 2.
  • the hydraulic damping space 31 thus narrows in the radial direction in the direction of the stop sleeve 7 surrounding the magnetic core 2 in its outer circumference 27.
  • the outer radius of the stop sleeve 7 according to the illustration in FIG. 3 is - with reference to the line of symmetry - identified by reference number 28.2.
  • the damping force 19, which results from the inflow of fuel into the outwardly narrowing hydraulic damping chamber 31 according to the variant in FIG. 3, is indicated by reference number 19.
  • the distance 15 denotes the gap height through which fuel flows into the hydraulic damping space 15 from the inside of the hydraulic damping space 31.
  • Fig. 4 are compared pressure distributions in the hydraulic damping chamber according to the variants in Figs. 2 and 3.
  • a first course of the pressure distribution 40 is established, which, seen in the radial direction of the hydraulic damping chamber 31, is the first maximum lying further inside 41 honors.
  • the maximum 41 lies approximately within the first annular surface section 21 as shown in FIG. 2.
  • a second course of the redistribution 42 which is characterized by a second maximum 43.
  • the second maximum 43 of the embodiment variant according to FIG. 3 lies within the third annular surface section 23; accordingly, where the hydraulic damping space 31 is most narrowed.
  • FIG. 5 shows a comparison of the damping force curves which occur in accordance with the embodiment variants in FIGS. 2 and 3.
  • the level of the damping force which arises in the hydraulic damping chamber 31 according to the first damping force curve 44 lies considerably below the damping force level of the damping lcraft 19 according to the second damping force curve 45 which can be achieved with the embodiment variant according to FIG. 3 increasing stroke taking into account the residual air gap decreases steadily and at the maximum stroke of the armature plate 1 1 in the direction of the magnetic core 2 assumes its minimum.
  • An estimate of the damping force profiles 44, 45 can be determined for simple geometries using the lubrication gap theory.
  • FIG. 6 shows an embodiment variant of a magnetic core which is designed without a stop sleeve.
  • the non-magnetic filler material 16 is poured or glued into the openings of the recess 24 on the second end face 5 of the magnetic core 2 and, in relation to the end face 12 of the armature plate 11, represents a flat damping surface 20.
  • the non-magnetic filler material 16 according to the embodiment variant shown in FIG. 6 also comprises a first step 29 and a second step 30.
  • the step of the non-magnetic filler material 16 results in a first edge 33 and a second edge 34 with which the non-magnetic filler material 16 is positively attached to the underside of the recess 24 on the second end face 5 of the magnetic core 2.
  • the hydraulic damping chamber 31 has a cross-section which runs constantly outward in the radial direction with respect to the line of symmetry shown.
  • the hydraulic damping space 31 runs through the annular surface sections 21, 22 and 23 at a constant height.
  • the hydraulic damping space 31 is only effective when there is pure liquid in the hydraulic damping space 31. If there is air or an air / liquid mixture, for example foam, the achievable hydraulic damping, in particular the first and second damping force profiles 44 and 45 shown in FIG. 5, is severely impaired.
  • the quantity map of a fuel injector can be significantly improved, in particular bring about a plateau-free quantity map. If a characteristic curve for a certain high pressure level has a pre-injection plateau within a characteristic curve field and if the actuation duration is changed within this pre-injection plateau, the amount of fuel injected into the combustion chamber of the self-igniting internal combustion engine remains constant.
  • the characteristic curves for fuel pressures within a characteristic curve field that result from the solution proposed according to the invention run in a strictly monotonically increasing manner, ie without a pre-injection plateau. This in turn means that with a longer activation time, more and more fuel is injected into the combustion chamber of the combustion machine. This is the basic prerequisite for zero quantity calibration of a fuel projector. A plateau-free quantity map is particularly helpful for zero quantity calibration of the fuel injector while the vehicle is running. Furthermore, the design of a hydraulic damping space 31 proposed according to the invention between the second end face 5 of the magnetic core 2 and the end face 12 of the armature plate 11 of the magnet anchor 10 allows noise reduction when operating a fuel projector.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne une électrovanne servant à actionner un injecteur de carburant et comprenant un noyau magnétique (2) dans lequel est logée une bobine magnétique (3). Un ressort de fermeture (9) agit sur l'armature d'aimant (10) dans le sens de fermeture. Une fente de sortie (18) pour un fluide d'actionnement est formée entre une face frontale (8), orientée vers l'armature d'aimant (10), de la douille de butée (7) et l'armature d'aimant (10). Cette fente de sortie (18) débouche dans une chambre d'amortissement hydraulique (31) qui est délimitée par une face frontale (12) de l'armature d'aimant (10) et par une surface d'amortissement (20) en matériau non magnétique (16).
EP03785564A 2002-12-13 2003-12-12 Actionneur magnetique exempt d'impulsions rebondissantes pour des soupapes d'injection Withdrawn EP1576277A1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10258442 2002-12-13
DE10258442 2002-12-13
DE10305985A DE10305985A1 (de) 2002-12-13 2003-02-13 Prellerfreier Magnetsteller für Einspritzventile
DE10305985 2003-02-13
PCT/DE2003/004111 WO2004055357A1 (fr) 2002-12-13 2003-12-12 Actionneur magnetique exempt d'impulsions rebondissantes pour des soupapes d'injection

Publications (1)

Publication Number Publication Date
EP1576277A1 true EP1576277A1 (fr) 2005-09-21

Family

ID=32598065

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03785564A Withdrawn EP1576277A1 (fr) 2002-12-13 2003-12-12 Actionneur magnetique exempt d'impulsions rebondissantes pour des soupapes d'injection

Country Status (4)

Country Link
US (1) US7354027B2 (fr)
EP (1) EP1576277A1 (fr)
JP (1) JP2006509964A (fr)
WO (1) WO2004055357A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007285124A (ja) * 2006-04-12 2007-11-01 Mitsubishi Electric Corp 燃料噴射弁
US20090267008A1 (en) * 2007-09-14 2009-10-29 Cummins Intellectual Properties, Inc. Solenoid actuated flow control valve including stator core plated with non-ferrous material
US20100007224A1 (en) * 2008-07-08 2010-01-14 Caterpillar Inc. Precision ground stator assembly for solenoid actuator and fuel injector using same
JP5048617B2 (ja) * 2008-09-17 2012-10-17 日立オートモティブシステムズ株式会社 内燃機関用の燃料噴射弁
US8316826B2 (en) * 2009-01-15 2012-11-27 Caterpillar Inc. Reducing variations in close coupled post injections in a fuel injector and fuel system using same
AT508049B1 (de) * 2009-03-17 2016-01-15 Bosch Gmbh Robert Vorrichtung zum einspritzen von kraftstoff in den brennraum einer brennkraftmaschine
DE102010037922A1 (de) * 2010-10-01 2012-04-05 Contitech Vibration Control Gmbh Aktor
US8436704B1 (en) * 2011-11-09 2013-05-07 Caterpillar Inc. Protected powder metal stator core and solenoid actuator using same
DE102012214920A1 (de) * 2012-08-22 2014-02-27 Continental Automotive Gmbh Dämpfungsoberfläche an Ventilkomponenten
DE102012215448B3 (de) * 2012-08-31 2013-12-12 Continental Automotive Gmbh Injektor zur Krafteinspritzung in eine Brennkraftmaschine
DE102012217322A1 (de) 2012-09-25 2014-06-12 Robert Bosch Gmbh Einspritzventil
CN104033300B (zh) * 2014-06-19 2016-09-07 中国第一汽车股份有限公司无锡油泵油嘴研究所 一种燃料喷射阀
CN108138715B (zh) * 2015-10-15 2022-02-25 大陆汽车有限公司 具有防弹跳装置的燃料喷射阀、燃烧发动机和车辆
CN114635818A (zh) * 2022-03-09 2022-06-17 哈尔滨工程大学 一种利用柔性液压阻尼实现共轨喷油器稳定喷射的高速电磁阀
KR102844819B1 (ko) * 2023-08-31 2025-08-11 주식회사 현대케피코 댐핑 면적 확장형 인젝터

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2098192C (fr) * 1991-10-11 2004-11-16 Thomas G. Ausman Positionneur et valve pour un systeme d'injection a commande electronique
US5238224A (en) * 1992-08-20 1993-08-24 Siemens Automotive L.P. Dry coil
JPH0849624A (ja) * 1994-06-01 1996-02-20 Zexel Corp 電磁式燃料噴射弁の燃料侵入防止装置
JPH09317596A (ja) * 1996-05-24 1997-12-09 Denso Corp 燃料噴射弁
JPH09310650A (ja) * 1996-05-22 1997-12-02 Denso Corp 燃料噴射弁
US5918818A (en) * 1996-05-22 1999-07-06 Denso Corporation Electromagnetically actuated injection valve
DE19707666C2 (de) * 1997-02-26 1999-12-02 Ford Global Tech Inc Elektromagnetventil, insbesondere für Heizungsanlagen in Kraftfahrzeugen
JPH1144275A (ja) * 1997-07-03 1999-02-16 Zexel Corp 燃料噴射装置用ソレノイドバルブ
JP2000265919A (ja) * 1999-03-16 2000-09-26 Bosch Automotive Systems Corp 電磁式燃料噴射弁
DE10131201A1 (de) * 2001-06-28 2003-01-16 Bosch Gmbh Robert Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine
JP2003156169A (ja) * 2001-09-04 2003-05-30 Denso Corp 電磁式流体制御装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004055357A1 *

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US20060113503A1 (en) 2006-06-01
US7354027B2 (en) 2008-04-08

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