EP2123898A1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2123898A1
EP2123898A1 EP09100198A EP09100198A EP2123898A1 EP 2123898 A1 EP2123898 A1 EP 2123898A1 EP 09100198 A EP09100198 A EP 09100198A EP 09100198 A EP09100198 A EP 09100198A EP 2123898 A1 EP2123898 A1 EP 2123898A1
Authority
EP
European Patent Office
Prior art keywords
control valve
valve element
fuel injector
pressure
sealing edge
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.)
Granted
Application number
EP09100198A
Other languages
German (de)
English (en)
Other versions
EP2123898B1 (fr
Inventor
Nadja Eisenmenger
Hans-Christoph Magel
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 EP2123898A1 publication Critical patent/EP2123898A1/fr
Application granted granted Critical
Publication of EP2123898B1 publication Critical patent/EP2123898B1/fr
Ceased 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
    • 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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0043—Two-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided

Definitions

  • the invention relates to a fuel injector, in particular a common rail injector, for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • a fuel injector which is servo-controlled by means of a control valve.
  • the control valve has a sleeve-shaped control valve element, which is formed conically at its front side facing its control valve seat, wherein the control valve seat is formed by an annular edge of a stepped bore.
  • a disadvantage of the known fuel injector is the heavy load on the linear seat edge, which is formed by two mutually perpendicular surfaces. This causes significant wear during operation.
  • the invention has for its object to propose a fuel injector with a sleeve-shaped control valve member having control valve that on the one hand in a simple manner and on the other hand guarantees a relatively low wear in the seating area.
  • the invention is based on the idea to provide on the control valve element as a sealing surface for cooperation with the axially opposite control valve seat, a sealing edge which is arranged between two angularly mutually, preferably in the axial direction adjacent, in particular conical, conical surfaces (annular surfaces), of which one extends into the high pressure region of the fuel injector and the other into the low pressure region.
  • a sealing edge which is arranged between two angularly mutually, preferably in the axial direction adjacent, in particular conical, conical surfaces (annular surfaces), of which one extends into the high pressure region of the fuel injector and the other into the low pressure region.
  • the position of the sealing edge in contrast to the prior art is well defined, which can be realized in a simple manner in the closed position in the axial direction pressure compensated control valve.
  • a trained according to the concept of the invention fuel injector has a good tightness - even at very high pressures of over 2000 bar - on.
  • a trained according to the concept of the invention fuel injector is not only advantageous over a fuel injector in which the control valve element is formed a conical surface, but also with respect to a fuel injector, in which the sleeve-shaped control valve member is provided at the end with a part spherical surface, there two angle to each other extending, in particular axially, between a sealing edge forming conical surfaces are easier to manufacture and on the other lead to a defined position of the sealing edge. Also, two straight, conical surfaces can be metrologically better checked than a spherical shape.
  • a further advantage is that the high-pressure side conical surface of the sections of double-conical Control valve seat member in the region of the fuel inlet to the control valve seat together with the seat of the control valve seat limited in the direction of the sealing edge tapered inlet gap. This results in a protection of the sealing edge against particles in the fuel, since arriving (larger) particles are partially stopped first in the inlet gap to the sealing edge and thus kept away from the sealing edge.
  • a disadvantage of the provision of a high-pressure-side conical surface is that it creates negative flow forces which have a negative effect on the switching behavior. In particular, the opening speed and the switching accuracy are reduced.
  • Acceptable to good flow properties while ensuring good particle destruction properties and a sufficient support of the sealing edge according to the invention achieved in that the radial extent of the high pressure side cone surface corresponds to a maximum of 15%, preferably not more than 10%, of the diameter of the sealing edge.
  • the diameter of the high-pressure-side boundary line is understood to mean the sealing edge flaking off during operation of the fuel injector due to wear.
  • the radial extent of the high-pressure-side conical surface is to be understood as meaning the (radial) width of the axial projection surface of the conical surface on the high-pressure side.
  • this diameter of the sealing edge is 3 mm or less and as a result the radial extent of the high-pressure side conical surface amounts to a maximum of 450 ⁇ m, preferably between 30 ⁇ m and 300 ⁇ m.
  • the diameter of the sealing edge is less than 2 mm and as a result the radial extent of the sealing edge is less than 300 ⁇ m, preferably between 30 ⁇ m and 200 ⁇ m.
  • control valve element is in the closed state, at least approximately pressure-balanced in the axial direction, which means that the control valve element is designed such that act on this in its closed position no or only very small hydraulic forces.
  • This axial pressure balance can be achieved, for example, with a sleeve-shaped control valve element.
  • a sleeve-shaped control valve element is understood to mean a control valve element which has a, preferably centric, continuous opening or a continuous, if necessary also formed as a stepped bore channel, wherein in the channel, as will be explained later, a pressure pin can be added which axially closes the channel and which is preferably a separate component from the valve body having the control valve seat.
  • a pressure-compensated in the axial direction control valve element can alternatively be realized with a bolt-shaped control valve (without through-hole), for example by this is provided with an annular groove-shaped, edge-side valve chamber, which are effective in both axial directions pressure application surfaces.
  • the sealing edge formed by a double cone cooperates with an internal cone-shaped control valve seat.
  • An internal cone-shaped control valve seat like the double-cone control valve element, is characterized by a simple and accurate manufacturability.
  • the combination of a sealing edge formed between two conical surfaces with an internal cone-shaped control valve seat offers the possibility of compensating for angular tolerances between the control valve element and the valve body having the control valve seat.
  • this comparatively inexpensive producible, multi-part control valve bodies feasible.
  • good inflow conditions to the control valve seat are realized without a sharp fuel diversion in a region between an outlet throttle and the control valve seat.
  • control valve seat is formed on the same valve body, which also limits a control chamber which, preferably directly, cooperates with an adjustable in the axial direction injection valve element.
  • the control chamber can be connected by means of the control valve with a low pressure region of the injector or separated therefrom, wherein when acting in the low pressure region control chamber due to the decreasing pressure in the control chamber acting on the injection valve element force is achieved in the opening direction.
  • the fuel injector in which act on the control valve element in its closed position no or at most minimal forces in the opening direction.
  • a pressure-compensated in its closed position in the axial direction of the control valve element can be realized in a sleeve-shaped control valve element, that the inner guide diameter is performed with the control valve element on an inner, to be explained later, pressure pin, the sealing edge diameter, with which the control valve element at its control valve seat is applied.
  • an embodiment is preferred in which no exact axial pressure balance is realized in the closed position, but in which acts on the control valve member a "small" hydraulic closing force. This can be realized by providing a small closing pressure stage, for example, by the inner guide diameter is chosen to be slightly larger than the sealing edge diameter.
  • the proposed sealing edge in combination with a control valve element, which is guided with its inner circumference on a pressure pin which seals the channel formed in the control valve element in the axial direction upwards.
  • This pressure pin is preferably designed as a separate component from the valve body having the control valve seat, which component is preferably accommodated loosely within the control valve element.
  • this pressure pin is acted upon by the fuel flowing out of the control chamber in the axial direction in the direction away from the control valve seat, preferably such that the pressure pin is supported on an injector component, preferably on an injector cover in the axial direction.
  • a possibly provided pressure pin essentially only has the function of sealing the inner control valve element channel in the axial direction upward.
  • an embodiment is preferred in which the sleeve-shaped control valve element is guided with its outer circumference on the component on which the control valve seat is also formed.
  • the component is also the component that radially outwardly delimits the control chamber.
  • an embodiment is preferable in which the sleeve-shaped control valve member does not have a continuous central channel (inner channel), but in which in the control valve element a, preferably concentric, stepped bore is realized, wherein an upper, remote from the control valve seat portion of the stepped bore a larger diameter than the lower bore portion.
  • the larger diameter section preferably serves to guide the control valve element on a (loose) pressure pin.
  • the injection valve element is formed low pressure stage.
  • axial channels realized on the outer circumference of the injection valve element are designed as throttle channels in order to throttle the fuel flowing axially from an internal high-pressure storage chamber (minirail) in the direction of a nozzle chamber.
  • Fig. 1 is designed as a common-rail injector fuel injector 1 for injecting fuel into a combustion chamber, not shown, also shown an internal combustion engine, also not shown.
  • a high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail). In this fuel, especially diesel or gasoline, under high pressure, of about 2000 bar in this embodiment, stored.
  • the fuel injector 1 is connected, among other fuel injectors, not shown, via a supply line 5.
  • the supply line 5 discharges into a high-pressure reservoir 6 which acts as a mini-rail for minimizing the pressure oscillation and flows into the high pressure reservoir 6 in the axial direction into the combustion chamber of the internal combustion engine during an injection process.
  • the fuel injector 1 is connected via an injector return port 7 to a return line 8 to the reservoir 3. Via the return line 8, a later to be explained control amount of fuel from the fuel injector 1 to flow to the reservoir 3 and are fed from there from the high pressure circuit again.
  • an injector body 9 Within an injector body 9 is a two-part injection valve element 10 in this embodiment, which may also be made in one piece if necessary, in the axial direction adjustable.
  • the injection valve element 10 is guided within a nozzle body 11 at its outer periphery.
  • This nozzle body 11 is screwed by means of a union nut, not shown, with the injector body 9.
  • the injection valve element 10 has at its tip 12 a closing surface 13 (sealing surface), with which the injection valve element 10 can be brought into a tight contact with an injection valve element seat 14 formed inside the nozzle body 11.
  • a closing surface 13 closing surface
  • fuel can flow from the high-pressure reservoir 6 through axial passages 17 formed in a guide section 16 on the outer circumference into an annular space 18 (nozzle space) radially formed between the injection valve element 10 and the nozzle body 11 in the drawing plane the injection valve element seat 14 to flow past the nozzle hole assembly 15 and there are injected substantially under the high pressure (rail pressure) standing in the combustion chamber.
  • sleeve-shaped portion 20 of a valve body 21, a control chamber 22 is limited, via a radially extending in the sleeve-shaped portion 20 of the valve body 21 inlet throttle 23 with high-pressure fuel from the high-pressure reservoir 6 is supplied.
  • the sleeve-shaped portion 20 with the control chamber 22 enclosed therein is enclosed radially on the outside by high-pressure fuel, so that an annular guide gap 24 is comparatively fuel-tight radially between the sleeve-shaped portion 20 and the injection valve element 10.
  • the control chamber 22 is connected via an arranged in the valve body 21, axial flow channel 25 with outlet throttle 26 with a valve chamber 27, which is radially outwardly of an axially adjustable, sleeve-shaped control valve element 28th a pressure-balanced in the axial direction in the closed state control valve 29 (servo-valve) is limited.
  • fuel can flow into a low-pressure region 30 of the fuel injector 1 and from there to the injector return port 7, when the sleeve-shaped control valve element 28, which is firmly connected to an anchor plate 31, lifted from its control valve seat formed on the valve body 21, ie the Control valve 29 is open.
  • an electromagnetic actuator 32 is provided with an electromagnet 33 which cooperates with the armature plate 31 which is arranged in an anchor plate space 34 and subsequently with the sleeve-shaped control valve element 28.
  • the electromagnetic actuator 32 raises the control valve element 28 from its arranged on the valve body 21, formed in this embodiment as an inner cone-shaped inner cone, control valve seat 35 from.
  • the flow cross sections of the inlet throttle 23 and the outlet throttle 26 are matched to one another such that when open control valve 29, a net outflow of fuel (fuel control amount) from the control chamber 22 in the low pressure region 30 of the fuel injector 1 and from there via the Injektor Weglaufan gleich 7 and Return line 8 results in the reservoir 3.
  • the pressure in the control chamber 22 drops rapidly, whereby the injection valve element 10 lifts off from an injection valve element seat 14, so that fuel can flow out of the high-pressure reservoir 6 through the nozzle hole arrangement 15.
  • the energization of the electromagnetic actuator 32 is interrupted, whereby the sleeve-shaped control valve element 28 is adjusted with a control spring 36 which is supported on the armature plate 31 in the drawing plane down to its control valve seat 35.
  • the fuel flowing in through the inlet throttle 23 into the control chamber 22 provides for a rapid pressure increase in the control chamber 22 and thus for a force acting on the injection valve element 10 Closing force.
  • the resulting closing movement of the injection valve element 10 is assisted by a closing spring 37, which is supported at one end on a circumferential collar 38 and at the other end on the lower, annular end face 39 of the sleeve-shaped section 20 of the valve body 21 in the plane of the drawing.
  • a loose pressure pin 42 is accommodated, which is designed as a separate component from the valve body 21.
  • the purpose of the cylindrical pressure pin 42 is to seal up the valve chamber 27 formed by the stepped bore 40 in the axial direction in order to prevent fuel from the drainage channel 25 from flowing into the low-pressure region 30 when the control valve element 28 is closed.
  • the pressure pin 42 further serves to guide the control valve element 28 at its inner periphery formed by the stepped bore 40 and the portion 41.
  • the sleeve-shaped, in the closed state in the axial direction pressure balanced control valve element 28 is guided on its outer circumference 43.
  • a guide section 44 protruding upward in the plane of the drawing is provided on the valve body 21, which surrounds the control valve element 28 radially on the outside.
  • the control valve seat 35 was made through the guide portion 44 of the valve body 21 in the axial direction. Holes 45 are radially introduced into the guide section 44, via which fuel flowing out of the outlet channel 25 when the control valve element 28 is open can flow radially outwards into the anchor plate space 34.
  • a radial channel 48 is introduced through the fuel into an annular chamber 49 in a support ring 46 which delimits the armature plate space 34 and carries the electromagnet arrangement 47 of the electromagnetic actuator 32 can flow, both the support ring 46 and Also, the solenoid assembly 47 radially encloses the outside.
  • a radial passage 50 which is axially spaced from the radial passage 48, the fuel from the annular chamber 49 can again flow radially inward toward the injector return port 7 and from there via the return line 8 to the reservoir 3.
  • Fig. 2 the sleeve-shaped control valve element 28 is shown in an enlarged view, wherein in the sleeve-shaped control valve element 28, the stepped bore 40 is introduced, which forms a closed by the pressure pin 42 through-channel.
  • the pressure pin 42 which is supported axially on a cover 51 of the fuel injector 1 has the function of sealing a formed inside the control valve element 28 valve chamber 27 in the axial direction upwards.
  • an inner channel 52 leads from the axial direction of the drawing plane below, wherein the inner channel 52 is formed by a lower surface in the drawing plane 53 of the stepped bore 40.
  • the diameter of the inner channel 52 is less than the diameter of the upper plane in the plane of the drawing 41 of the stepped bore 40th
  • annular sealing edge 54 is formed, which forms the line of contact or intersection of two axially adjacent, each cone-shaped conical surfaces 55, 56, wherein the two conical conical surfaces 55, 56 one another Cone angle (here cone angle) have. It is in the drawing plane lower conical surface 55 to a high pressure side and the axially immediately adjacent in the drawing plane upper conical surface 56 to a low-pressure side conical surface.
  • the lower in the drawing plane, high-pressure side Cone surface 55 in this case has a larger cone angle ⁇ , as in the drawing plane, axially adjacent, upper, low-pressure side cone surface 50 whose cone angle ⁇ is smaller.
  • a cone angle is understood to mean the angle between two diametrically opposite surface sections of the respective annular conical surface.
  • the sealing edge 54 formed axially between the conical surfaces 55, 56 cooperates in its closed position with the internal conical control valve seat 35, which is formed on the valve body 21.
  • the cone angle of the inner cone-shaped control valve seat 35 is smaller than the cone angle ⁇ between the lower in the drawing plane conical surfaces 55 and greater than the cone angle ⁇ between the upper in the drawing plane conical surfaces 56th
  • the radial extent R (here 150 ⁇ m) of the high-pressure side cone surface 55 a maximum of 15%, preferably not more than 10% of the diameter D I (here 2 mm) of the sealing edge 54 corresponds to negative flow influences of high pressure side conical surface 55 to minimize.
  • the high pressure applied within the control valve element 28 is the innermost diameter of the sealing edge 54, which is not ideally linear due to wear. In the case of a fuel injector 1 with external high pressure, it would be the act extreme diameter of the sealing edge 54.
  • Axially between the radially inner, high-pressure side conical surface 55 and the inner conical control valve seat 35 is formed in the radial direction to the sealing edge 54 tapered inlet gap 57, which in addition to a formed between the conical surface 55 and the inner channel 52 edge 58 for comminution contained in the fuel Contributes particles.
  • the diameter of the valve chamber 27, and thus the upper portion 41 of the stepped bore 40 must be the same size as the diameter D I of the sealing edge 54.
  • the diameter of the valve chamber 27 (something) must be selected larger than the diameter D I of the sealing edge 54 between the conical surfaces 55, 56th
  • a particle 59 is shown in the transition between the drainage channel 25 and the sealing edge 54.
  • a particle 59 of this size does not flow directly to the sealing edge 54, but usually initially remains in the inlet gap 57 and is crushed during a closing movement of the control valve element 28 between the control valve element 28 and the high-pressure side conical surface 55. Alternatively, the particle is smashed by striking against the inlet gap 57 bounding edges and surfaces.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP20090100198 2008-05-21 2009-03-23 Injecteur de carburant Ceased EP2123898B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200810001913 DE102008001913A1 (de) 2008-05-21 2008-05-21 Kraftstoff-Injektor

Publications (2)

Publication Number Publication Date
EP2123898A1 true EP2123898A1 (fr) 2009-11-25
EP2123898B1 EP2123898B1 (fr) 2011-09-28

Family

ID=41110777

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20090100198 Ceased EP2123898B1 (fr) 2008-05-21 2009-03-23 Injecteur de carburant

Country Status (2)

Country Link
EP (1) EP2123898B1 (fr)
DE (1) DE102008001913A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2541036A1 (fr) * 2011-06-29 2013-01-02 Robert Bosch Gmbh Vanne de commande, procédé de fabrication d'une vanne de commande et injecteur de carburant doté d'une vanne de commande
EP3006723A1 (fr) * 2014-10-08 2016-04-13 Robert Bosch Gmbh Soupape d'injection de carburant
CN113464337A (zh) * 2021-06-16 2021-10-01 中船动力研究院有限公司 船用柴油机共轨喷油器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111502880A (zh) * 2020-03-17 2020-08-07 成都威特电喷有限责任公司 一种防止动态泄漏的电控高压燃油喷射装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5934643A (en) * 1995-12-23 1999-08-10 Lucas Industries Valve arrangement
EP1253314A2 (fr) 1995-12-05 2002-10-30 Denso Corporation Electrovanne et soupape d'injection de combustible pour un moteur à combustion interne
EP1600627A1 (fr) * 2004-05-15 2005-11-30 L'orange Gmbh Soupape de régulation
WO2006067015A1 (fr) * 2004-12-22 2006-06-29 Robert Bosch Gmbh Injecteur de systeme d'injection de carburant d'un moteur a combustion interne
WO2008155260A1 (fr) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Soupape de commande pour un injecteur de carburant, et injecteur de carburant

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1253314A2 (fr) 1995-12-05 2002-10-30 Denso Corporation Electrovanne et soupape d'injection de combustible pour un moteur à combustion interne
US5934643A (en) * 1995-12-23 1999-08-10 Lucas Industries Valve arrangement
EP1600627A1 (fr) * 2004-05-15 2005-11-30 L'orange Gmbh Soupape de régulation
WO2006067015A1 (fr) * 2004-12-22 2006-06-29 Robert Bosch Gmbh Injecteur de systeme d'injection de carburant d'un moteur a combustion interne
WO2008155260A1 (fr) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Soupape de commande pour un injecteur de carburant, et injecteur de carburant

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2541036A1 (fr) * 2011-06-29 2013-01-02 Robert Bosch Gmbh Vanne de commande, procédé de fabrication d'une vanne de commande et injecteur de carburant doté d'une vanne de commande
EP3006723A1 (fr) * 2014-10-08 2016-04-13 Robert Bosch Gmbh Soupape d'injection de carburant
CN113464337A (zh) * 2021-06-16 2021-10-01 中船动力研究院有限公司 船用柴油机共轨喷油器

Also Published As

Publication number Publication date
EP2123898B1 (fr) 2011-09-28
DE102008001913A1 (de) 2009-11-26

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