EP2206912A2 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2206912A2
EP2206912A2 EP09169850A EP09169850A EP2206912A2 EP 2206912 A2 EP2206912 A2 EP 2206912A2 EP 09169850 A EP09169850 A EP 09169850A EP 09169850 A EP09169850 A EP 09169850A EP 2206912 A2 EP2206912 A2 EP 2206912A2
Authority
EP
European Patent Office
Prior art keywords
fuel injector
volume
valve element
fuel
injection valve
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
EP09169850A
Other languages
German (de)
English (en)
Other versions
EP2206912B1 (fr
EP2206912A3 (fr
Inventor
Matthias Burger
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 EP2206912A2 publication Critical patent/EP2206912A2/fr
Publication of EP2206912A3 publication Critical patent/EP2206912A3/fr
Application granted granted Critical
Publication of EP2206912B1 publication Critical patent/EP2206912B1/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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

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.
  • Hub-controlled common rail injectors whose injection valve element is servo-operated are known. Piezo and solenoid valves are used as pressure actuators, with which the servo circuit is controlled. For rapid needle closure, a permanent low pressure stage is often provided which exerts a permanent, closing hydraulic force on the needle. The disadvantage is the high leakage, which occurs between the high pressure and the low pressure stage. Leakage inevitably leads to the requirement for higher pump performance and thus to sacrifice in the efficiency of the system. This situation is problematic especially at high pressures. For this reason, the latest injectors are designed leak-free for highest injection pressures.
  • leak-free fuel injectors do not have a permanent low-pressure stage acting in the closing direction, which eliminates the leaks caused thereby. Due to the elimination of the low pressure stage, two-piece injection valve elements of the type that are used in practice for use fuel injectors used with low-pressure stage, no longer be used.
  • the invention has for its object to provide a simply constructed fuel injector, in which the coupling of the at least two injection valve element parts is realized with the lowest possible number of components.
  • the invention is based on the idea to introduce two relatively adjustable parts of the injection valve element into one another, so as to be able to dispense with a separate guide sleeve, as used in the prior art, as well as a spring-loaded spring the spring sleeve.
  • the at least, preferably exclusively two-part, construction has the advantage that the production of the individual injection valve element parts in total is less complicated and thus less expensive than the production of a one-piece long injection valve element.
  • existing production lines can be maintained and the existing logistics, which is aligned with a multi-part injection valve element.
  • the invention has also recognized that it would result in a solution with in-run injector element parts to a constant increase in the Kopplervolumens in operation of the fuel injector, if the coupler volume would be connected exclusively via a guide gap between the two parts with a Injektorvolumen, since the flow resistance of the guide gap is proportional to the applied pressure difference , The fact that the flow resistance of such a guide gap is linearly related to the magnitude of the pressure difference between the coupler volume and injector volume would cause much fuel to be drawn from the injector volume upon opening the fuel injector due to the very low pressure in the coupler volume and emptying the Kopplervolumens during the closing process due to the available (short) time would no longer be possible.
  • the coupler volume is additionally or alternatively connected to a guide gap via at least one throttle arrangement with the injector volume in a fuel injector designed according to the concept of the invention, wherein the throttle arrangement is designed such that the fuel volume flow flowing through it ( Flow volume flow) is not proportional to the pressure difference between the coupler volume and injector volume as a guide gap behaves, but disproportionately.
  • the flow volume flow passing through the throttle assembly does not increase to the same extent as a pressure difference between the volume of the coupler and the injector volume, ie, the flow volume flow and the pressure difference are not linearly related.
  • the flow volume flow increase becomes smaller and smaller with increasing pressure difference.
  • the flow volume flow is proportional to the root of the pressure difference between injector volume and coupler volume.
  • the throttle arrangement is to provide at least one, preferably only one, realized in particular in the first or second part, throttle bore, the throttle bore very particularly preferably in the manner of a drain throttle from a control chamber as in known servo-circuit fuel injectors is.
  • the throttle bore is preferably a stepped bore with a diameter step, which preferably leads to the formation of a turbulent, cavitating flow within the throttle bore.
  • the above-mentioned diameter stage is a possibility for realizing a degressive ratio between flow volume flow and pressure difference between the coupler volume and injector volume.
  • any throttle stages in particular hydraulically sharp-edged throttle stages, can be realized for this purpose, preferably with a small longitudinal extension in the flow direction.
  • the longitudinal extension of the at least one throttle stage is designed such that a turbulent flow is formed.
  • a hydraulically sharp-edged throttle stage while a length to hydraulic diameter ratio is less than or equal to 10 to understand.
  • the following applies to the hydraulic diameter of an annular gap reactor D Hyd 4 ⁇ perfused cross section flowed through Berandungsus ,
  • the boundary length in this equation is the sum of the inner and the outer boundary length.
  • the throttle arrangement comprises a plurality of hydraulically connected in series (arranged) throttles.
  • the throttles are formed radially between the two injection valve element parts, preferably in the guide region, with which the two parts are guided into one another.
  • the throttles are designed in such a way, ie have such a small extent in the flow direction, that the guide length is so small that forms a turbulent flow.
  • the flow volume flow would be by the throttle arrangement proportional to the pressure difference between the coupler volume and injector volume, which should be avoided.
  • One possibility for forming the throttle arrangement is to provide a plurality of axially juxtaposed (parallel) grooves on one of the injection valve element parts, wherein the throttles are formed radially between the webs delimiting the grooves and the other injection valve element part.
  • the webs Preferably, the webs, at least approximately, sharp-edged to realize a minimum guide length and thus to force the formation of a turbulent flow.
  • it is very particularly preferred to dispense with a throttle bore in the injection valve element parts.
  • the hydraulic coupler is designed as a joint, which allows a certain pivotability of the two hydraulically coupled injection valve element parts to compensate in this way tolerance-related angular errors and inclinations.
  • a particularly preferred possibility for forming such a pivot joint is to contour the guided injection valve element part in the region of the guide in order to allow a relative pivoting.
  • the fuel injector is leak-free except for leaks which may have been realized in the region of the control valve element.
  • a low-pressure stage acting on the injection valve element in the closing direction on the injection valve element is dispensed with.
  • Fig. 1 is a trained as a common rail injector fuel injector 1 for injecting fuel into a combustion chamber, not shown, also shown an internal combustion engine of a motor vehicle.
  • 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, stored in this embodiment about 2000bar.
  • the fuel injector 1 is connected via other, not shown, fuel injectors via a supply line 5.
  • the supply line 5 opens into an annular space 6 radially between a valve body 7 and an injector body 8 (housing part).
  • the high-pressure fuel can flow essentially unthrottled in the axial direction in the plane of the drawing down into a pressure space 11 acting as a mini-rail for pressure oscillation minimization.
  • the fuel flows directly through axial passages 13 into a nozzle chamber 14 (annular space) also belonging to the injector volume 12 and out of this through at least one injection hole 15 into the combustion chamber of the internal combustion engine.
  • the fuel injector 1 is connected via an injector return port 16 to a return line 17. About the return line 17 can be explained later on a control amount of fuel from the fuel injector 1 to the reservoir 3 drain and be fed from there from the high pressure circuit again.
  • a two-part injection valve element 18 in this exemplary embodiment is arranged to be adjustable in the axial direction.
  • the injection valve element 18 projects with its lower, designed as a nozzle needle first part 19 in a stepped bore 20 of a nozzle body 21 into it.
  • the first part 19 is guided axially displaceably with a guide portion 22.
  • the axial channels 13 are formed by bevels 9 in the guide section 22 radially between the first part 19 and the nozzle body 21.
  • the nozzle body 21 is screwed by means of a union nut, not shown, with the injector body 8.
  • the first part 19 (nozzle needle) of the injection valve element 18 is guided in an end blind bore 23 of a second part 24 (control rod) of the injection valve element 18.
  • the injection valve element 18 has a closing surface 26 (sealing surface) on a (lower) tip 25 formed on the first part 19, with which the injection valve element 18 can be brought into tight contact with an injection valve element seat 27 formed inside the nozzle body 21.
  • the injection valve element 18 abuts against its injection valve element seat 27, ie is in a closed position, the fuel outlet from the at least one injection hole 15 is blocked. If, on the other hand, it is lifted off its injection valve element seat 27, fuel can flow from the pressure chamber 11 via the axial channels 13 and the annular chamber 14 to the injection valve element seat 27 to the injection hole 15 where it is injected substantially under high pressure (rail pressure) into the combustion chamber become.
  • a control chamber 29 is limited, which extends over a radially extending in the sleeve-shaped portion of the valve body 7 inlet throttle 30 with high-pressure fuel from the Annulus 6 is supplied.
  • the sleeve-shaped portion with control chamber 29 enclosed therein is enclosed radially on the outside with high-pressure fuel, so that an annular Guide gap 31 radially between the sleeve-shaped portion of the valve body 7 and the injection valve element 18, here the second part 24, is comparatively fuel-tight.
  • the control chamber 29 is connected via a, extending perpendicularly in the valve body 7 axial channel 32 with outlet throttle 33 with a valve chamber 34 radially outwardly of an axially adjustable, sleeve-shaped control valve element 35 of a pressure-balanced in the axial direction in the closed state control valve 36 (servo valve) is limited.
  • fuel can flow into a low-pressure region 37 of the fuel injector 1 and thence to the injector return port 16 when the sleeve-shaped control valve element 35 is lifted from its control valve element seat 38 formed on the valve body 7, i. when the control valve 36 is open.
  • an electromagnetic actuator 39 is provided with an electromagnet 40 which cooperates with an integrally formed with the control valve element 35 anchor plate 41 and subsequently with the sleeve-shaped control valve element 35.
  • the electromagnetic actuator 39 raises the control valve element 35 from its formed on the valve body 7, designed in this embodiment as a flat seat control valve element seat 38 from.
  • the flow cross-sections of the inlet throttle 30 and the outlet throttle 33 are matched to one another such that when open control valve 36, a net outflow of fuel (control amount) from the control chamber 29 in the low pressure region 37 of the fuel injector 1 and from there via the Injektor Weglaufan gleich 16 and Return line 17 results in the reservoir 3.
  • the pressure in the control chamber 29 decreases rapidly, whereby the injection valve element 18, more precisely the first part 19, lifts off from its injection valve element seat 27 so that fuel can flow out of the injector volume 12 through the injection hole 15 into the combustion chamber.
  • the energization of the electromagnetic actuator 39 is interrupted, whereby the sleeve-shaped control valve element 35 is adjusted by means of a control spring 42 which is supported on the armature plate 41 in the drawing plane down on its control valve element seat 38.
  • the fuel flowing in through the inlet throttle 30 into the control chamber 29 provides for a rapid pressure increase in the control chamber 29 and thus for a force acting on the injection valve element 18 closing force.
  • the resulting closing movement of the injection valve element 18 is assisted by a closing spring 43, which is supported at one end on a circumferential collar 44 of the second part 24 and at the other end on a lower, annular end side 45 of the valve body 7.
  • a loose pressure pin 47 is accommodated, which is designed as a separate component from the valve body 7.
  • the purpose of the cylindrical pressure pin 47 is to seal the valve chamber 34 in the axial direction in order to prevent fuel from the control chamber 29 being able to flow into the low-pressure region 37 when the control valve element 35 is closed, except for an unavoidable amount of leakage.
  • the pressure pin 47 also serves to guide the control valve element 35 at its inner periphery formed by the bore 46.
  • Fig. 1 results, it is in the fuel injector 1 to a so-called leak-free injector, which has no leakage except for a leak in the region of the control valve 36, since no permanent, acting on the injection valve element 18 in the closing direction low pressure stage is provided.
  • the first part 19 is guided into the second part 24 of the injection valve element 18 and guided on the inner circumference of the blind hole 23.
  • a hydraulic coupler volume 50 is formed, which couples the movement of the parts 19, 24. How to get out Fig. 1 results, the coupler volume 50 is hydraulically connected to the Injektorvolumen 12 via a consisting of a single throttle bore 51 throttle assembly 52.
  • the pressure in the coupler volume 50 drops rapidly and the opening force is transmitted to the first part 19 due to the suction effect in the sequence of its injection valve element seat 27 lifts. Due to the aforementioned negative pressure in the coupler volume 50, this increases because fuel from the injector 12 via the throttle assembly 52 in a range between axially the end face 48 of the first part 19 and the bottom 49 of the blind hole 23 flows.
  • the throttle arrangement 52 is designed such that the filling or the increase of the coupler volume 50 does not lead to any functionally relevant change in the maximum stroke of the injection valve element 18. This can also be realized in the case of a multiple injection.
  • the fit between the first part 19 and the inner circumference of the blind hole 23 is dimensioned so that the volume flow occurring here compared to the flow volume flow through the throttle assembly 52 is negligible - so the guide gap 53 is to be described as substantially hydraulic tight.
  • Fig. 1 is the first part 19 formed in the region of the guide gap 53 and thus formed as a pivot joint, so as to be able to compensate for angular errors and inclinations between the nozzle-side guide and the guide of the injection valve element 18 in the valve body 7.
  • FIG. 2 shown embodiment of a fuel injector 1 substantially corresponds to the embodiment according to Fig. 1 , so as to avoid repetition in terms of similarities to the preceding description of the figures as well as on Fig. 1 is referenced. In the following, only differences to the preceding embodiment are explained essentially.
  • a throttle bore for connecting the coupler volume 50 to the injector volume 12 has been dispensed with.
  • the coupler volume 50 is also formed between the bottom 49 of the blind bore 23 and the upper side 48 in the plane of the drawing of the first part 19 of the injection valve element 18.
  • the throttle arrangement 52 is realized in the region of a guide 54 between the outer circumference of the first part 19 and the inner circumference of the blind bore 23.
  • the throttle arrangement 52 comprises in the exemplary embodiment shown a number of throttles 55 arranged one behind the other in the axial direction.
  • the throttles 55 are each formed between an annular web 56 with a radially tapered outer edge and the inner circumference of the blind bore 23.
  • the axial extent of the webs 56 in a voltage applied to the inner circumference of the blind hole 23 area is so short that can form a turbulent flow, with the result that the flow rate through the throttle assembly 52 only disproportionately increases with increasing pressure difference between the coupler volume 50 and 12 injector.
  • the two adjacent in the axial direction, annular webs 56 define between them a groove 57 (circumferential groove) on the outer periphery of the first part 19.
  • a groove 57 (circumferential groove) on the outer periphery of the first part 19.
  • the first part 19 in the region of the guide 54 formed somewhat spherical, so that the first part 19 is pivotable relative to the second part 24 within certain limits, so that angle errors can be compensated.

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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)
EP09169850A 2009-01-13 2009-09-09 Injecteur de carburant Not-in-force EP2206912B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009000181A DE102009000181A1 (de) 2009-01-13 2009-01-13 Kraftstoff-Injektor

Publications (3)

Publication Number Publication Date
EP2206912A2 true EP2206912A2 (fr) 2010-07-14
EP2206912A3 EP2206912A3 (fr) 2010-07-21
EP2206912B1 EP2206912B1 (fr) 2011-08-03

Family

ID=42124568

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09169850A Not-in-force EP2206912B1 (fr) 2009-01-13 2009-09-09 Injecteur de carburant

Country Status (4)

Country Link
US (1) US8302888B2 (fr)
EP (1) EP2206912B1 (fr)
AT (1) ATE519031T1 (fr)
DE (1) DE102009000181A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012130452A1 (fr) * 2011-03-31 2012-10-04 Fuechslin Raphael Soupape d'injection
CN104533683A (zh) * 2014-11-26 2015-04-22 中国北方发动机研究所(天津) 一种高压共轨喷油器滑阀结构
WO2016020469A1 (fr) * 2014-08-08 2016-02-11 Continental Automotive Gmbh Dispositif d'étranglement pour commander une quantité de carburant à alimenter par un injecteur de carburant et système d'injection

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012220657A1 (de) 2012-11-13 2014-05-15 Robert Bosch Gmbh Brennstoffeinspritzventil
JP6145652B2 (ja) * 2014-01-06 2017-06-14 株式会社Ｓｏｋｅｎ 燃料噴射弁
GB201412086D0 (en) * 2014-07-08 2014-08-20 Delphi International Operations Luxembourg S.�.R.L. Fuel injector for an internal combustion engine
US11506162B2 (en) * 2020-11-17 2022-11-22 Caterpillar Inc. Trapped volume split check assembly in fuel injector
DE102021200154A1 (de) * 2021-01-11 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoffeinspritzvorrichtung

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT232490Y1 (it) * 1994-07-01 2000-01-10 Elasis Sistema Ricerca Fiat Dispositivo di registrazione della corsa dell'otturatore per un iniettore di combustibile
ATE226279T1 (de) * 1998-03-26 2002-11-15 Mtu Friedrichshafen Gmbh Hochdruck-kolbenzylindereinheit
DE10104618A1 (de) * 2001-02-02 2002-08-08 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE50214476D1 (de) * 2001-07-03 2010-07-15 Crt Common Rail Tech Ag Brennstoffeinspritzventil für Verbrennungskraftmaschinen
DE102004024527A1 (de) * 2004-05-18 2005-12-15 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung
DE102005026514B4 (de) * 2005-02-18 2008-12-24 Robert Bosch Gmbh Einspritzdüse
DE102005059169A1 (de) * 2005-12-12 2007-06-14 Robert Bosch Gmbh Kraftstoffinjektor mit direkt betätigbarem Einspritzventilglied
RU2438035C2 (ru) * 2006-03-03 2011-12-27 Ганзер-Хюдромаг Аг Инжекторный клапан для топлива для двигателя внутреннего сгорания (варианты)
DE102006036780A1 (de) * 2006-08-07 2008-02-21 Robert Bosch Gmbh Krafstoffinjektor mit direkter Nadelsteuerung und Servoventil-Unterstützung
DE102007014359A1 (de) * 2006-09-01 2008-03-06 Robert Bosch Gmbh Injektor für eine Kraftstoffeinspritzanlage
DE102007001363A1 (de) * 2007-01-09 2008-07-10 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff in Brennräume von Brennkraftmaschinen
DE102008040680A1 (de) * 2008-07-24 2010-01-28 Robert Bosch Gmbh Kraftstoff-Injektor

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012130452A1 (fr) * 2011-03-31 2012-10-04 Fuechslin Raphael Soupape d'injection
WO2016020469A1 (fr) * 2014-08-08 2016-02-11 Continental Automotive Gmbh Dispositif d'étranglement pour commander une quantité de carburant à alimenter par un injecteur de carburant et système d'injection
US20170226974A1 (en) * 2014-08-08 2017-08-10 Continental Automotive Gmbh Throttle device for controlling an amount of fuel to be supplied to a fuel injection nozzle, as well as an injection device
US10240566B2 (en) * 2014-08-08 2019-03-26 Continental Automotive Gmbh Throttle device for controlling an amount of fuel to be supplied to a fuel injection nozzle, as well as an injection device
CN104533683A (zh) * 2014-11-26 2015-04-22 中国北方发动机研究所(天津) 一种高压共轨喷油器滑阀结构

Also Published As

Publication number Publication date
EP2206912B1 (fr) 2011-08-03
DE102009000181A1 (de) 2010-07-15
US20100175665A1 (en) 2010-07-15
ATE519031T1 (de) 2011-08-15
EP2206912A3 (fr) 2010-07-21
US8302888B2 (en) 2012-11-06

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