EP3014100B1 - Soupape de distribution - Google Patents

Soupape de distribution Download PDF

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Publication number
EP3014100B1
EP3014100B1 EP14721358.1A EP14721358A EP3014100B1 EP 3014100 B1 EP3014100 B1 EP 3014100B1 EP 14721358 A EP14721358 A EP 14721358A EP 3014100 B1 EP3014100 B1 EP 3014100B1
Authority
EP
European Patent Office
Prior art keywords
outflow opening
control valve
slot
valve
valve according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP14721358.1A
Other languages
German (de)
English (en)
Other versions
EP3014100A1 (fr
Inventor
Dominik Kuhnke
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3014100A1 publication Critical patent/EP3014100A1/fr
Application granted granted Critical
Publication of EP3014100B1 publication Critical patent/EP3014100B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • 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
    • 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
    • F02M2547/008—Means for influencing the flow rate out of or into a control chamber, e.g. depending on the position of the needle

Definitions

  • the invention relates to a control valve for a fuel injector, in particular a common rail fuel injector, with the features of the preamble of claim 1. Furthermore, the invention relates to a fuel injector with such a control valve.
  • Control valves of the aforementioned type are regularly used in fuel injectors, which have a hubbewegliche nozzle needle for releasing and closing at least one injection port.
  • the control valve serves to control the lifting movement of the nozzle needle. Opens the control valve, a control chamber is relieved, so that acting in the closing direction of the nozzle needle control pressure decreases in the control chamber and opens the nozzle needle.
  • the actuation of the control valve is usually carried out by means of an actuator, such as a Magnetaktors or a piezoelectric actuator.
  • a fuel injector with a control valve for controlling an at least one injection opening releasing or occluding injection valve member shows.
  • the control valve comprises a liftable valve piston, which cooperates sealingly with a valve seat designed as a flat seat. If the valve piston is sealingly seated on the flat seat, a control pressure which acts on the injection valve member in the closing direction builds up in the control chamber.
  • the valve piston Upon actuation of the control valve by means of an electromagnet, the valve piston lifts off the valve seat and a connection of the control chamber is made with a low pressure area. As a result, the control pressure in the control chamber and thus the injection valve member acting in the closing direction decreases Force.
  • the injection valve member opens and releases the at least one injection opening in this way.
  • the provision of the valve piston takes place by means of the spring force of a spring after completion of the energization of the electromagnet. This in turn results in the increase of the control pressure in the control chamber, so that also the injection valve member is returned to its sealing seat and the at least one injection port closes again.
  • a fast-switching control valve is advantageous in order to bring about rapid relief of the control chamber.
  • the advantage here is a reduced stroke of the liftable closing element of the control valve.
  • a sufficiently large outflow cross-section must be ensured.
  • the diameter of a discharge opening located within the valve seat can be increased.
  • this also increases the area formed on the valve closing element, which comes to lie within the diameter of the valve seat, and is acted upon in the closed position of the control valve by the control pressure of the control chamber.
  • the result is an increase in the force acting on the valve closing element in the opening direction hydraulic force. This can be counteracted by the spring force of a spring is increased, which acts on the valve closing element in the closing direction. To open the valve but then larger magnetic forces are required, which in turn adversely affects the switching time of the control valve.
  • an injection device with an electromagnetic valve for connecting a pressure control chamber with a low-pressure chamber comprises a plate member and a movable member with flat contact and sealing surfaces. In at least one contact surface, a groove-shaped fuel relief passage is provided.
  • the present invention has the object to provide a fast-switching control valve for a fuel injector, which has at least one optimized in terms of reduced switching forces and / or low strokes discharge opening. Furthermore, a control valve with an increased life is to be provided.
  • control valve with the features of claim 1 is proposed.
  • Advantageous developments of the invention can be found in the dependent claims.
  • a fuel injector is specified with such a control valve.
  • the proposed control valve comprises a valve piece with a discharge opening formed inside a valve seat designed as a flat seat, and a lift-movable valve closing element sealingly cooperating with the valve seat.
  • the outflow opening is slit-shaped and has a length L which is greater than a width B of the outflow opening.
  • the length L corresponds essentially to a diameter D or a radius R of a circular area within which the outflow opening and at least one further outlet opening connected to the outflow opening and / or separated from the outflow opening are arranged.
  • the slot-shaped outflow opening in comparison to a circular outflow opening has the advantage that it has a large outflow circumference at the same time small area. Accordingly, the valve closing element is subjected to a smaller hydraulic force via the slot-shaped outflow opening, with the same outflow circumference, so that the shifting forces can be reduced. Alternatively or additionally, the stroke of the valve closing element can be reduced because a fast discharge of the control chamber is ensured via the outflow circumference.
  • an unfavorable length / width ratio (L / B >> 1) of the slit-shaped outflow opening can lead to stresses in the valve piece which occur in particular at the ends in the longitudinal direction of the outflow opening (notch stress).
  • notch stress notch stress
  • the at least one further outflow opening can be connected to the slot-like outflow opening or formed as a separate outflow opening. It has been found that the load on the valve piece can be reduced by this measure. This in turn leads to an increase in the service life of the control valve.
  • the at least one further outflow opening is likewise slot-shaped and has a longitudinal axis A ', which is inclined relative to a longitudinal axis A of the first slot-shaped outflow opening.
  • a plurality of slit-like Outflow openings arranged in a cross or star shape. The arrangement may be such that two or more slit-like outflow openings intersect.
  • the strength-increasing effect is achieved by avoiding a voltage-generating widening of the slot-shaped outflow openings, since in the vicinity of other pressure-loaded slots by the expansion of a supporting effect on the highly loaded notch radius is achieved.
  • the effect can already be detected by arranging a further slot-like outflow opening within the circular area predetermined by the first outflow opening.
  • the at least one further outflow opening is arranged at one end of the slot-like outflow opening within the circular area.
  • the further discharge opening arranged at the end leads to an enlargement of the notch radius, so that a stress relief is achieved.
  • the further outflow opening arranged at one end of the slot-shaped outflow opening may, for example, be circular and have a diameter d which is greater than the width B of the slot-like outflow opening.
  • the further outflow opening arranged at one end of the slot-shaped outflow opening can be slot-shaped and have an arcuate course. Also by this measure, a stress relief is achieved by increasing the notch radius. At the same time, the further outflow opening has an optimized geometry. The arcuate course ensures the arrangement of the further slot-shaped outflow opening within the specified circular area.
  • the effect of the voltage reduction is here in particular in the approximation to the voltage-ideal circular shape with internal pressure.
  • an arcuate course of the further outflow opening which is offset slightly inwards relative to the circular shape, proves to be particularly advantageous with regard to the avoidance of notch stresses.
  • the arcuate course of the further outflow opening follows the shape of an ellipse with two half-axes a, b, wherein the shorter half-axis a coincides with the length L of the slit-like outflow opening defining the circular area.
  • Within the approximate circular shape thus an approximately hydrostatic stress state, so that stresses occur substantially only radially outward of the arcuate course, where they are much smaller due to the large radius.
  • the half-axis a is less than a quarter of the length L of the slot-like outflow opening, at the end of which it is arranged. By this measure, a sufficient mechanical strength of the valve piece is further ensured.
  • the half-axis ratio a / b is 0.8 to 0.9. This ensures that a plurality of slot-shaped outflow openings, which are each arranged at one end of a slot-shaped radially extending outflow opening and have a curved course, a sufficient web width remains in order not to jeopardize the mechanical strength of the valve piece.
  • valve seat formed as a flat seat is released and is formed by at least one web, which follows an outer contour of an outflow opening.
  • the discharge opening is therefore limited by the web. Due to the release, the fluid exiting via the outflow openings can flow off almost without pressure. As a result, an additional opening force acting on the valve closing element is avoided.
  • the sealing surface of the valve seat is reduced, so that an improved sealing effect is achieved.
  • control valve is preferably used to control the lifting movement of a nozzle needle of the fuel injector.
  • the Indian FIG. 1 illustrated fuel injector has a nozzle body 25 and a holding body 26 which are axially braced by means of a clamping nut, not shown.
  • the nozzle body 25 and the holding body 26 are penetrated by a high-pressure bore 24, in which a nozzle needle 20 for releasing or closing of injection openings 27 is received in a liftable manner.
  • the high-pressure bore 24 is connected via a feed line 28 to a high-pressure accumulator 29, via which the high-pressure bore 24 is supplied under high pressure fuel.
  • the high-pressure bore 24 is delimited by a valve piece 1, which is inserted into the holding body 26, of a control valve for controlling the lifting movement of the nozzle needle 20.
  • the valve piece 1 seals the high-pressure bore 24 from a low-pressure chamber 10, which is formed within a valve body 11 of the control valve.
  • a low-pressure chamber 10 Via a bore 15 of the valve body 11, in which a valve closing element 4 of the control valve is received liftable, and a receiving space 19, in which a cooperating with an electromagnet 13 for actuating the control valve armature 12 is arranged, the low-pressure chamber 10 is connected to a return line 30 ,
  • a sealing sleeve 22 is supported, in which one end of the nozzle needle 20 is received in such a way that a control chamber 16 is formed, which is connected via an inlet throttle 18 with the high-pressure bore 24.
  • a control chamber 16 In the closed position of the control valve therefore also prevails in the control chamber 16 high pressure, which exerts an acting on an end face 21 of the nozzle needle 20 in the closing direction compressive force.
  • the nozzle needle 20 is acted upon by the spring force of a spring 23 in the closing direction.
  • a relief of the control chamber 16 is effected, so that the force acting on the end face 21 of the nozzle needle 20 closing pressure is reduced and the nozzle needle 20 lifts from its seat.
  • the nozzle needle 20 releases the injection openings 27 in this way.
  • the discharge of the control chamber 16 is effected by opening the control valve, so that the control chamber 16 is connected to the low-pressure chamber 10.
  • the electromagnet 13 is energized. About the magnetic force of the electromagnet 13 of the arranged in the receiving space 19 armature 12 which is fixedly connected to the valve closing element 4 of the control valve, pulled in the direction of the electromagnet 13, so that the valve closing element 4 lifts from a formed in the valve piece 1 valve seat 2 and an outflow opening 3 releases, via which the required to relieve the control chamber 16 connection with the low-pressure chamber 10 is made.
  • the energization of the electromagnet 13 is stopped. The armature 12 and the valve closing element 4 are then placed back on the spring force of a spring 14 to its original position. In the closed position of the control valve, the control chamber 16 is filled via the inlet throttle 18 again with fuel, so that the pressure in the control chamber 16 increases again.
  • valve closure member 4 has a circular sealing surface 8, which is formed flat according to the valve seat 2.
  • At least one further outflow opening 6, 6 ' is provided according to the invention, which is formed within a circular area 5 which is defined by the slot-shaped outflow opening 3 and thus likewise comes to lie within the sealing surface 8 of the valve closing element 4.
  • the at least one further outflow opening 6, 6 'voltages in the valve piece 1 are counteracted, so that the load capacity of the valve piece 1 increases.
  • a first preferred embodiment is in the FIG. 2 shown. It shows a in the fuel injector according to the FIG. 1 insertable valve piece 1 of a control valve according to the invention in plan view.
  • the further outflow opening 6 is here also slit-shaped and forms with the outflow opening 3 a cross, which comes to rest within the circular area 5, which is defined by the length L of the outflow opening 3. Because the length L corresponds to the diameter D of the circular surface 5.
  • the longitudinal axes A and A 'of the two slot-shaped outflow openings 3, 6 are orthogonal to each other, so that the two outflow openings 3, 6 intersect in the middle.
  • FIG. 3 A modification of the embodiment of FIG. 2 is in the FIG. 3 shown.
  • a circular outflow opening 6 is arranged at the ends of the two slot-shaped outflow openings 3, 6, whose diameter d is greater than the width B of the slot-shaped outflow openings 3, 6 is selected.
  • the circular outflow openings 6 cause a relief of the valve piece 1, as notch stresses is counteracted.
  • FIGS. 2 and 3 Further modifications of the embodiments of FIGS. 2 and 3 are possible if - as in the FIGS. 4 and 5 shown - a plurality of slot-shaped outflow openings 3, 6 6 'are arranged in a star shape.
  • the star-shaped slot-shaped outflow openings 3, 6, 6 ' can be connected via an intersection region or arranged at a distance from a center of the circular surface 5 so that there is no intersection.
  • the number of slot-shaped outflow openings 3, 6, 6 ' can be varied and / or circular outflow openings 6 at the respective ends of the slot-shaped outflow openings 3, 6, 6' according to the embodiment of FIG. 3 be provided.
  • FIG. 6 Another, particularly preferred embodiment is in the FIG. 6 shown.
  • the slot-shaped outflow opening 3 is combined with each end arranged C-shaped outflow openings 6.
  • the C-shaped outflow openings 6 also form slots, which also extend arcuately.
  • the arch form follows the shape of an ellipse, which is defined by the half-axes a, b (see FIG. 8 ).
  • the shorter half-axis a coincides with the length L of the slot-shaped outflow opening 3, where a is less than a quarter of the length L.
  • the ratio of the semi-axes a / b in the present case is 0.8. This has the consequence that the arcuate course of the C-shaped outflow openings 6 is offset in relation to a circle 5 delimiting the circular line inwards.
  • This measure has an increasing strength, because stresses occur substantially on the outside of the C-shaped outflow openings 6 and thus on the large radii, which are less critical with respect to stresses (see FIG. 9 ).
  • FIG. 7 A modification of the embodiment of FIG. 6 is in the FIG. 7 shown.
  • the length L of the slot-shaped outflow opening 3 here corresponds to the radius R of the circular surface 5.
  • Respectively at the same angular distance from each other two further slot-shaped outflow openings 6 are arranged, so that the outflow openings 3, 6 give a star shape.
  • Each of the outflow openings 3, 6 has at its end a C-shaped outflow opening 6 for relieving the valve piece 1.
  • the ends of the C-shaped outflow openings 6 are compared with the circle 5 delimiting circular line inwardly offset by the amount i in order to increase the strength of the valve piece 1.
  • valve seat 2 is formed here by webs 7, which limit the outflow openings 3, 6, 6 '.
  • the webs 7 thus follow the outer contours of the outflow openings 3, 6, 6 '.
  • the webs 7 are released over a lowered portion 9 of the valve piece 1. Via the lowered region 9, the fuel exiting via the outflow openings 3, 6, 6 'can flow off almost without pressure.
  • the surface of the lowered portion 9 is larger than a cooperating with the valve seat 2 sealing surface 8 of a valve closing element 4 selected (in the FIG. 10 not shown).
  • the effect of the exemption of the valve seat 2 is based on the Figures 11 and 12 explained in more detail.
  • the valve seat 2, which is formed by webs 7, has a discharge opening 3 limiting web surface with a web width s on. This is followed by the lowered portion 9 of the valve piece 1, whereby the webs 7 are released.
  • the fuel exiting via the outflow circumference of the outflow opening 3 can flow over the lowered area 9 largely free of pressure.
  • the sealing surface 8 of the valve closing element 4 is therefore not acted upon by an additional pressure force acting in the opening direction when it lifts off from the valve seat 2, 7 with a reduced stroke h.
  • the closing force F required to close the control valve can thus be reduced.
  • FIG. 12 In the FIG. 12 are shown in the region of the valve seat 2 applied pressures.
  • the pressure prevails p1.
  • p4 (p1 + p3) / 2).
  • the decrease in region 9 ensures that the pressure p3 approximately corresponds to the pressure p4.

Landscapes

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

Claims (11)

  1. Soupape de commande pour un injecteur de carburant, en particulier un injecteur de carburant à rampe commune, comprenant un organe de soupape (1) avec un ouverture d'écoulement (3) réalisée à l'intérieur d'un siège de soupape (2) réalisé en tant que siège plat, ainsi qu'un élément de fermeture de soupape (4) à mouvement de levage coopérant de manière hermétique avec le siège de soupape (2),
    caractérisée en ce que l'ouverture d'écoulement (3) est réalisée en forme de fente et présente une longueur (L) qui est supérieure à une largeur (B) de l'ouverture d'écoulement (3), la longueur (L) correspondant essentiellement à un diamètre (D) ou à un rayon (R) d'une surface circulaire (5) à l'intérieur de laquelle sont disposées l'ouverture d'écoulement (3) et au moins une ouverture d'écoulement (6, 6') connectée à l'ouverture d'écoulement (3) et/ou séparée de l'ouverture d'écoulement (3).
  2. Soupape de commande selon la revendication 1,
    caractérisée en ce que l'au moins une ouverture d'écoulement supplémentaire (6, 6') est en forme de fente et possède un axe longitudinal (A') qui est incliné par rapport à un axe longitudinal (A) de l'ouverture d'écoulement (3).
  3. Soupape de commande selon la revendication 2,
    caractérisée en ce que les ouvertures d'écoulement de type fente (3, 6, 6') sont disposées en forme de croix ou en forme d'étoile.
  4. Soupape de commande selon l'une quelconque des revendications précédentes,
    caractérisée en ce que l'au moins une ouverture d'écoulement supplémentaire (6) est disposée au niveau d'une extrémité de l'ouverture d'écoulement de type fente (3).
  5. Soupape de commande selon l'une quelconque des revendications précédentes, caractérisée en ce que l'au moins une ouverture d'écoulement supplémentaire (6) est en forme circulaire et possède un diamètre (d) qui est supérieur à la largeur (B) de l'ouverture d'écoulement de type fente (3).
  6. Soupape de commande selon l'une quelconque des revendications 1 à 4,
    caractérisée en ce que l'au moins une ouverture d'écoulement supplémentaire (6) est en forme de fente et possède une allure de forme courbe.
  7. Soupape de commande selon la revendication 6,
    caractérisée en ce que l'allure de forme courbe de l'ouverture d'écoulement supplémentaire (6) suit la forme d'une ellipse avec deux demi-axes (a, b), le demi-axe plus court (a) coïncidant avec la longueur (L) de l'ouverture d'écoulement de type fente (3).
  8. Soupape de commande selon la revendication 7,
    caractérisée en ce que le demi-axe (a) est inférieur à un quart de la longueur (L) de l'ouverture d'écoulement de type fente (3).
  9. Soupape de commande selon la revendication 7 ou 8,
    caractérisée en ce que le rapport des demi-axes (a/b) est de 0,8 à 0,9.
  10. Soupape de commande selon l'une quelconque des revendications précédentes,
    caractérisée en ce que le siège de soupape (2) réalisé sous forme de siège plat (2) est dégagé et est réalisé par au moins une nervure (7) qui suit un contour extérieur d'une ouverture d'écoulement (3, 6, 6').
  11. Injecteur de carburant comprenant une soupape de commande selon l'une quelconque des revendications précédentes.
EP14721358.1A 2013-06-25 2014-04-30 Soupape de distribution Not-in-force EP3014100B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310212140 DE102013212140A1 (de) 2013-06-25 2013-06-25 Steuerventil
PCT/EP2014/058919 WO2014206606A1 (fr) 2013-06-25 2014-04-30 Soupape de distribution

Publications (2)

Publication Number Publication Date
EP3014100A1 EP3014100A1 (fr) 2016-05-04
EP3014100B1 true EP3014100B1 (fr) 2017-07-19

Family

ID=50639520

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14721358.1A Not-in-force EP3014100B1 (fr) 2013-06-25 2014-04-30 Soupape de distribution

Country Status (4)

Country Link
EP (1) EP3014100B1 (fr)
CN (1) CN105492755B (fr)
DE (1) DE102013212140A1 (fr)
WO (1) WO2014206606A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10310597B2 (en) 2013-09-03 2019-06-04 Tobii Ab Portable eye tracking device
DE102015111813B4 (de) * 2015-07-21 2017-03-02 Kendrion (Villingen) Gmbh Sitzventil
CN114790957B (zh) * 2022-04-29 2023-11-21 中国北方发动机研究所(天津) 一种滑阀式共轨喷油器

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Publication number Priority date Publication date Assignee Title
US3731880A (en) * 1971-10-08 1973-05-08 Gen Motors Corp Ball valve electromagnetic fuel injector
US4887769A (en) * 1987-06-26 1989-12-19 Hitachi, Ltd. Electromagnetic fuel injection valve
DE59606610D1 (de) * 1995-06-02 2001-04-26 Ganser Hydromag Ag Zuerich Brennstoffeinspritzventil für Verbrennungskraftmaschinen
JP3584554B2 (ja) * 1995-07-26 2004-11-04 株式会社デンソー 蓄圧式燃料噴射装置
JP3719468B2 (ja) * 1996-09-02 2005-11-24 株式会社デンソー 蓄圧式燃料噴射装置
ITTO20010970A1 (it) * 2001-10-12 2003-04-12 Fiat Ricerche Inettore di combustibile per un motore a combustione interna.
DE102006049050A1 (de) * 2006-10-18 2008-04-30 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff
DE102008005532A1 (de) * 2008-01-22 2009-07-23 Robert Bosch Gmbh Kraftstoffinjektor, dessen Steuerventilelement einen Stützbereich aufweist

Non-Patent Citations (1)

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Title
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Also Published As

Publication number Publication date
WO2014206606A1 (fr) 2014-12-31
EP3014100A1 (fr) 2016-05-04
CN105492755A (zh) 2016-04-13
CN105492755B (zh) 2018-08-14
DE102013212140A1 (de) 2015-01-08

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