EP1155233B1 - Mecanisme de regulation permettant de commander une augmentation de pression de carburant, destine a un injecteur de carburant - Google Patents

Mecanisme de regulation permettant de commander une augmentation de pression de carburant, destine a un injecteur de carburant Download PDF

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Publication number
EP1155233B1
EP1155233B1 EP00916758A EP00916758A EP1155233B1 EP 1155233 B1 EP1155233 B1 EP 1155233B1 EP 00916758 A EP00916758 A EP 00916758A EP 00916758 A EP00916758 A EP 00916758A EP 1155233 B1 EP1155233 B1 EP 1155233B1
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EP
European Patent Office
Prior art keywords
pressure
valve
fuel
actuator
valve piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00916758A
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German (de)
English (en)
Other versions
EP1155233A1 (fr
Inventor
Ulrich Augustin
Reda Rizk
Raimondo Giavi
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.)
Siemens AG
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Siemens AG
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Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP1155233A1 publication Critical patent/EP1155233A1/fr
Application granted granted Critical
Publication of EP1155233B1 publication Critical patent/EP1155233B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive

Definitions

  • the invention relates to a control element for controlling a Pressure boosting of fuel for a fuel injector according to the preamble of claim 1.
  • a control element for controlling a Pressure boosting of fuel for a fuel injector according to the preamble of claim 1.
  • Such a regulatory body is known from US 5,682,858 A.
  • a pressure booster with a movable piston arranged the pressure booster in a low-pressure side control room and a high-pressure side work space divided.
  • the High-pressure side working space of the booster is connected to a Fuel line in a fuel injector in front of an injection nozzle connected.
  • the low-pressure side control room is about a trained in the fuel injector electromagnetically actuated control element with a pressure accumulator in Connection.
  • the electromagnetically actuated control element is so trained that in the initial state when not energized is, the governing organ the flow connection between the Pressure accumulator and the low-pressure side control chamber of Pressure booster interrupts and the control room depressurized holds. In this operating state, the working space fills of the booster via the fuel line with fuel.
  • control element By energizing the control element is then switched, that the flow connection between the accumulator and opened the low-pressure side control chamber of the booster and the piston in the pressure intensifier control room side with the pressure in the pressure accumulator is applied. He is in the Control chamber adjusting pressure is thereby from the piston in the pressure booster increased many times to those in the workspace passed fuel located in the booster.
  • JP-A-59141764 is a control element for a Fuel injector known, having a pressure booster with a low-pressure side control chamber and a high-pressure side Working space has.
  • An electromagnetically operated Actuator of the control element in turn actuates a valve piston, in a first position the working space with a pressure supply and in a second position with a non-pressurized Drain opening connects.
  • a similar control organ also shows US-A-4170974, but here the valve piston is not electromagnetic, but is servohydraulisch actuated.
  • Object of the present invention is therefore a Control element for controlling a pressure boost of fuel for a fuel injector in such a way that a Ensures simple and reliable control function and in particular large variations of the fuel injectors in Injection behavior can be avoided.
  • the control element according to the invention is in a pressure line in a fuel injector, which has a low pressure side Control chamber of a pressure booster in the fuel injector with a pressure supply connects, arranged and has a Actuator, a valve chamber and one in the valve chamber movably arranged spring-loaded valve piston.
  • a flow connection through the Valve chamber between a connected to the pressure supply Inlet opening and a first drain opening, the connected to the control room of the booster ago.
  • the valve piston Located in the switching position caused by the actuator the valve piston, however, in a position in which a Flow connection through the valve chamber between the first Outlet opening to the control room in the pressure booster is connected and a second drain port, the pressure-less held is made.
  • control element In the control element according to the invention is only for the start of injection an injection nozzle in the fuel injector a Control of the valve piston in the control element necessary. Of the Injection of the injection nozzle, however, is automatic finished as soon as the whole, in a working space of the booster upstream fuel is injected. The Switching times in the control element thus have no influence on the Time at which the injection is terminated. The automatic End of the injection in the inventive design of the regulatory body continues to ensure a high intrinsic safety in case of possible malfunction of the regulatory body. In addition, the injection quantity of only in the combustion chamber the pressure booster sucked fuel determined. Manufacturing tolerances of the injector in the fuel injector therefore have no influence on the Einspritzmengenzuflop.
  • control element has two cone-shaped valve seats on which alternately the valve piston with a its two conical sealing surfaces depending on Switching state rests.
  • the actuator is driven piezoelectrically, resulting in high Switching speeds and thus improved efficiency of the control element.
  • the fuel injector shown in Figures 1 and 2 with pressure boosting is particularly suitable for use with Diesel engines.
  • the fuel injector is essentially from a trained as a 3/2-way valve control element 2, a pressure booster 3, an injection nozzle 4 and a Check valve 5 together, preferably together in a housing are arranged.
  • the pressure booster 3 in the fuel injector has a Housing 31, in which a two-stage cylindrical inner bore is trained.
  • the housing 31 is also axially movable a punch 34th arranged, which consists of a control piston 341 and a working piston 342 composed.
  • the control piston 341 is doing guided in the control chamber bore 311 and is against the Control chamber bore 311 sealed. Similar to the control piston 341, the working piston 342 in the working space bore 312 guided and is sealed against the working space bore 312.
  • a compression spring 36 arranged on one side against a Stage between the control chamber bore 311 and the working space bore 312 is supported and with her other side on Control piston 341 is applied. Since the punch 34 is shorter than the Inner bore of the housing 31 is formed between the end face of the control piston 341 and the housing 31 a Control chamber 32 and between the end face of the working piston 342 and the housing 31, a working space 33 is formed. Of the Working space 33 is connected to a fuel supply line 37 and a Injection line 41 in communication, via which the injection nozzle 4 is connected to a fuel supply.
  • a housing 21 in which a cylindrical valve chamber 22 is provided is, consisting of a first bore portion 221 and a second bore portion 222, wherein the second Bore portion 222 has a larger inner diameter than the first bore portion 221 has. Furthermore, the valve chamber 22 a beveled transition region 323 between the first bore portion 221 and the second bore portion 222 on.
  • an inlet opening 211, a first drain opening 213, a second drain opening 214 and a Leakage opening 215 introduced.
  • the inlet opening 211 opens in the region of the second Bore portion 222 of the valve chamber 22 in the vicinity of the transition region 223 provided in a housing 21 Ring groove 212 and is further via an inlet 11 to a Pressure supply 1 connected to a medium, preferably Oil or fuel, with a regulated pressure of about 200 bar from a supply switch 12 feeds.
  • the first drainage opening 213 opens in the first bore section 221 of the valve chamber 22 and is via a pressure line 38 to the control room 32 of the booster 3 connected.
  • the second drainage opening 214 opens into the valve chamber 22 in the area of a End portion of the second bore portion 222 and connected to the reservoir 12, wherein the connection is designed without pressure.
  • valve piston 23 In the valve chamber 22 of the 3/2-way valve is still a valve piston 23 is arranged, which has a first cylindrical Section 231, which in the first bore section 221 of the Valve chamber 22 is guided, and a second cylindrical Section 232, in the second bore portion 222 of the valve chamber 22 is guided, has. Between the first cylindrical Section 231 and the second cylindrical section 232 of the valve piston 23 is still a bevelled Transition region 233 formed whose inclination the slope of the transition region 223 between the first Bore portion 221 and the second bore portion 222nd in the valve chamber 22 corresponds.
  • the valve piston 23 has in its first cylindrical Section 231 has an annular groove 234, which extends to the transition region 233 extends and the first drain opening 213 opposite.
  • a two-stage blind bore 24 provided in which an inner Bore portion 241 has a smaller diameter than an outer one Bore portion 242 has and a transition region 243 between the bore sections with a chamfer is provided.
  • the inner bore portion 241 of the blind bore 24 is also through a throttle bore 25, the through the first cylindrical portion 231 of the valve piston 23 extends, with the annular groove 234 around the valve piston 23 connected.
  • a lid 26 extends to the housing 21 of the 3/2-way valve 2 continue with a bolt 27 in the blind hole 24 in the valve piston 23, wherein a bolt tip 271 conical and the conical inclination of the slope of the transition area 243 between the inner bore portion 241 and the outer bore portion 242 of the blind bore 24 corresponds.
  • the bolt 27 is designed so that between its outer wall and the inner wall of the valve piston 23 in the outer Bore portion 242 of the blind bore 24 an annular gap remains.
  • valve piston 23 sits in its idle state with the Transition region 243 of the blind bore 24 on the bolt head 271 on, whereby the connection between the inner bore section 241 and the outer bore portion 242 of Blind hole 24 is interrupted.
  • this position of the valve piston 23 is an annular gap between the end face of the Valve piston 23 and a stop on the lid 26 is formed, the connection between the annular gap around the bolt 27th and the second outlet port 214.
  • a stamp-shaped armature 28 is further provided, the extends into a arranged on the housing 21 head portion 29 and a magnetic coil 291 is arranged opposite.
  • a compression spring 292 On the armature 28 bears the holding force of a compression spring 292, which is supported on the head portion 29.
  • this first cylindrical Section also opens the leakage opening 215, the is connected to the reservoir 12, wherein the connection is kept depressurized.
  • the 3/2-way valve 2 is in its rest position shown.
  • the solenoid 291 is de-energized and the valve piston 23 is replaced by that on the armature 28 load-holding force of the compression spring 292 with its transition region 243 in the blind bore 24 on the bolt head 271 of the bolt 27 is pressed.
  • this position of the valve piston 23 is an annular gap between the tapered transition region 223 in the valve chamber 22 and the corresponding bevelled Transition region 233 formed on the valve piston 23, so that a flow connection between the inlet opening 211 and the first drain opening 213 via the annular groove 212, the annular gap between the transition region 223 in the Valve chamber 22 and the transition region 233 on the valve piston 23 and the annular groove 234 is formed.
  • the pressure supply 1 ensures a regulated pressure of the medium, preferably in the range of about 200 bar.
  • a regulated pressure of the medium preferably in the range of about 200 bar.
  • the punch 34 in the pressure booster 3 is located in its extended position, where the control room volume maximum, the working space volume, however, is minimal.
  • the injection process is then powered by energizing the solenoid 291 prepared.
  • the energized solenoid 291 pulls the armature 28 against the holding force of the compression spring 292 at. This shifts the connected to the armature 28 Valve piston 23 from its initial position, in which the Transition region 243 of the blind bore 24 on the bolt tip 271 is seated, in the direction of the head portion 29 in a Position in which the transition region 243 on the valve piston 23rd at the transition region 223 of the valve chamber 22 abuts. hereby becomes the flow connection from the inlet opening 211 closed to the first drain opening 213 through the valve chamber 22, so that the supply of the control chamber 32 in the pressure booster 3 interrupted with the pressurized medium becomes.
  • the time course of the filling phase is from the in the fuel supply 37 prevailing supply pressure, the holding force of the compression spring 36 and the flow velocity determined by the throttle bore 25.
  • the filling phase of the working space 33 is automatically terminated as soon as the compression spring 36, the control piston 341 of the punch 34th pushed back to its rest position and the control room volume is minimal.
  • the start of injection into a combustion chamber of an internal combustion engine is caused by the interruption of the power supply the solenoid 291 set.
  • the compression spring 292 pushes then the armature 28 and thus the valve piston 23 in the 3/2-way valve 2 back to its original position, in which the Transition region 243 in the blind bore 24 on the bolt tip 271 is seated and so the flow connection between the first drain opening 213 and the second drain opening 214 is interrupted again via the 3/2-way valve. simultaneously raises the transition region 233 on the valve piston 23 from Transition region 223 of the valve chamber 22 and the flow connection through the 3/2-way valve between the inlet opening 211 and the first drain opening 213 opens.
  • the pressure in the control chamber 32 of the booster 3 then rises on the pressure prevailing in the pressure supply 1 of the medium at.
  • This pressure of the medium is about the punch 34 a multiple amplified located in the working space 33 Fuel passed.
  • This fuel pressure the preferably in the range of about 1500 bar, stands over the injection line 41 to the injection nozzle 4, wherein the Check valve 5 prevents fuel return.
  • the high fuel pressure in the injection line 41 causes that the injection nozzle 4 opens and fuel in the combustion chamber of the internal combustion engine is injected.
  • the control piston 341 of the punch 34 by the pressure prevailing in the control chamber 32 pressure pushed away the medium against the holding force of the compression spring 36, so that the control chamber 32 fills with medium.
  • the control piston 341 Working piston 342 presses firmly connected to the control piston 341 Working piston 342 the fuel from the working space 33rd in the injection nozzle 4 and thus in the combustion chamber of the internal combustion engine.
  • FIG. 2 shows a second embodiment of the 3/2-way valve executed control element 3, wherein the actuator instead of electromagnetically driven piezoelectrically.
  • the actuator instead of electromagnetically driven piezoelectrically.
  • a piezoelectric actuator ensures a higher Switching speed of the 3/2-way valve, which causes the Injection of the injection nozzle can be controlled better.
  • valve piston 23 in the blind bore 24 an additional Shoulder 61 which supports the compression spring 292 is.
  • This compression spring 292 is arranged around the bolt 27 around and strikes the lid 26 with its other end.
  • Farther is in front of the shoulder 61 has a through hole 63 in Valve piston 23 is provided, which the blind bore 24 in the valve piston 23 with the second drain opening 214 in each position of the valve piston 23 connects.
  • the valve chamber 22 additionally has in front of the first cylindrical Section 231 of the valve piston 23 a control chamber 64, which has a throttle bore 65 and a side channel 66 is in communication with the inlet opening 211.
  • the control chamber 64 in the valve chamber 22 is defined by an intermediate member 67 from the head portion 29, in which a piezoelectric actuator 68 is arranged, separated.
  • Through the intermediate member 67 extends through a Through hole 69, in which a valve seat 70 is formed is, on which a valve ball 71, loaded by a spring 72, seated.
  • the valve ball 71 is still on a Plunger 73, which is arranged in the through hole 69, with the piezoelectric actuator 68 in connection.
  • the through hole 69 also has in the adjacent to the control room 64 section a throttle point 74 on.
  • Head portion 29 is further provided the leakage opening 215, which is in communication with the pre-tank 12 and is kept depressurized.
  • FIG. 2 shows the starting position of the 3/2-way valve 2 with not actuated piezoelectric actuator 68.
  • the valve ball 71 sits on the valve seat 70 in the through hole 69, so that the connection from the control room 64 via the through hole 69, the head portion 29th closed to the leakage opening 215.
  • the 3/2-way valve shown in Figure 2 solves the same Injection process of the injection nozzle 4 off, as related shown with the 3/2-way valve shown in Figure 1 is.
  • the embodiment shown in Figure 2 at which is used as the drive of the piezoelectric actuator 68, can be however, with respect to the electromagnetic shown in FIG Drive to achieve faster switching times.
  • the control element 2 basically has the Advantage that when using such a control element in a Accumulator injection system the injected fuel quantity exclusively by the timing of the filling phase of the pressure booster 3 determined with fuel becomes.
  • the inevitable manufacturing tolerances of the injector 4 thus have no effect on the Einspritzmengenzuflop.
  • the complete emptying ensures of the pressure booster 3 of fuel during injection for an automatic end of injection, regardless of the switching speed of the governing organ 2. This sharp injection end ensures good combustion values of the internal combustion engine.
  • the design of the control element 2 with two conical valve seats also allows easy production and a high functional reliability of the control element.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (4)

  1. Dispositif de réglage (2) pour commander une amplification de pression de carburant pour un injecteur de carburant de véhicule à moteur, dispositif qui comprend un amplificateur de pression (3) présentant un espace de commande (32) côté basse pression et un espace de travail (33) côté haute pression,
    l'espace de commande (32) étant relié par une conduite de pression (11, 38) à une alimentation en pression (1) contenant un fluide pressurisé,
    l'espace de travail (33) étant connecté à une conduite d'injection de carburant (41, 37),
    le dispositif de réglage étant placé dans la conduite de pression (11, 38) entre l'alimentation de pression (1) et l'espace de commande (32) de l'amplificateur de pression (3) et comprenant
    un actionneur (291, 68),
    une ouverture d'amenée (211) reliée à l'alimentation de pression (1),
    une première ouverture d'écoulement (213) reliée à l'amplificateur de pression (3),
    une deuxième ouverture d'écoulement (214) maintenue sans pression, et
    un piston de soupape (23) commandé par ressort et disposé de façon mobile dans une chambre de soupape (22),
    le piston de soupape (23) étant en connexion fonctionnelle (28, 64, 69, 70, 71, 72, 73, 74) avec l'actionneur (291, 68) et étant commuté entre une position dans laquelle une communication de fluide est établie dans la chambre de soupape (22) entre l'ouverture d'amenée (211) et la première ouverture d'écoulement (213), et une position dans laquelle une communication de fluide est établie dans la chambre de soupape (22) entre la première ouverture d'écoulement (213) et la deuxième ouverture d'écoulement (214),
    le piston de soupape (23) commandé par ressort se trouvant à l'état de repos où il n'est pas actionné par l'actionneur (211, 68), dans la position dans laquelle une communication de fluide est établie dans la chambre de soupape (22) entre l'ouverture d'amenée (211) et la première ouverture d'écoulement (213),
    et se trouvant dans la position de commutation déclenchée par l'actionneur dans laquelle une communication de fluide est établie dans la chambre de soupape (22) entre la première ouverture d'écoulement (213) et la deuxième ouverture d'écoulement (214),
       caractérisé en ce que
    un boítier (21) comporte un alésage interne cylindrique à deux échelons à titre de chambre de soupape (22) dans laquelle un premier siège de soupape conique (223) est formé dans la région de transition des échelons,
    le boítier (21) comprenant en plus un dispositif de couvercle (26, 27) faisant saillie dans la chambre de soupape (22), dispositif sur lequel un deuxième siège de soupape conique (271) est formé,
    le piston de soupape (23) présentant une forme externe cylindrique à deux échelons dans laquelle une première surface de joint conique (233) est formée dans la région de transition des échelons,
    le piston de soupape (23) présentant en outre un alésage borgne (24) dans lequel une deuxième surface de joint conique (243) est formée,
    la deuxième surface de joint conique (243) du piston de soupape (23) étant en appui, dans sa position de repos, sur le deuxième siège de soupape conique (271) dans le dispositif de couvercle (26, 27), et
    la première surface de joint conique (233) du piston de soupape (23) étant en appui, dans sa position commutée, sur le premier siège de soupape conique (223) dans la région de transition des échelons.
  2. Dispositif de réglage selon la revendication 1, caractérisé en ce qu'un étranglement (25) est prévu dans la communication de fluide entre la première ouverture d'écoulement (213) et la deuxième ouverture d'écoulement (214).
  3. Dispositif de réglage selon la revendication 1 ou 2, caractérisé en ce que l'actionneur est un actionneur à commande électromagnétique comprenant une bobine magnétique (291) qui est apte à exercer une force magnétique sur une armature (28) fixée au piston de soupape (23).
  4. Dispositif de réglage selon la revendication 1 ou 2, caractérisé en ce que l'actionneur est un actionneur piézo-électrique (68) apte à actionner une soupape (70, 71, 72) qui commande une pression hydraulique du fluide sur le piston de soupape (23) dans un espace de commande (64).
EP00916758A 1999-02-24 2000-02-24 Mecanisme de regulation permettant de commander une augmentation de pression de carburant, destine a un injecteur de carburant Expired - Lifetime EP1155233B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19907952 1999-02-24
DE19907952 1999-02-24
PCT/DE2000/000518 WO2000050764A1 (fr) 1999-02-24 2000-02-24 Mecanisme de regulation permettant de commander une augmentation de pression de carburant, destine a un injecteur de carburant

Publications (2)

Publication Number Publication Date
EP1155233A1 EP1155233A1 (fr) 2001-11-21
EP1155233B1 true EP1155233B1 (fr) 2005-01-19

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EP00916758A Expired - Lifetime EP1155233B1 (fr) 1999-02-24 2000-02-24 Mecanisme de regulation permettant de commander une augmentation de pression de carburant, destine a un injecteur de carburant

Country Status (4)

Country Link
US (1) US6463914B2 (fr)
EP (1) EP1155233B1 (fr)
DE (1) DE50009281D1 (fr)
WO (1) WO2000050764A1 (fr)

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DE10216153A1 (de) * 2002-04-12 2003-10-23 Hydraulik Ring Gmbh Drosselventil,insbesondere für Diesel-Hochdruckpumpen von Einspritzvorrichtung in Kraftfahrzeugen
WO2005078271A1 (fr) * 2004-02-11 2005-08-25 Mazrek Ltd Mecanisme d'actionnement destine a une pompe-injecteur a entrainement hydraulique pour moteurs thermiques
JP4003770B2 (ja) * 2004-10-01 2007-11-07 トヨタ自動車株式会社 燃料噴射装置
US7464697B2 (en) * 2005-08-19 2008-12-16 The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency High-pressure fuel intensifier system
JP2008045486A (ja) * 2006-08-16 2008-02-28 Yanmar Co Ltd 蓄圧式燃料噴射装置
DE102008041384A1 (de) * 2008-08-20 2010-02-25 Robert Bosch Gmbh Vorrichtung zur Versorgung einer Verbrennungskraftmaschine mit Treibstoff
JP5337911B2 (ja) * 2011-08-01 2013-11-06 トヨタ自動車株式会社 燃料供給装置
DE102013205624B4 (de) * 2013-03-28 2015-07-09 Continental Automotive Gmbh Ventil zum Einblasen von gasförmigen Kraftstoffen für eine Brennstoffmaschine
DE102014106715B4 (de) * 2014-05-13 2024-05-16 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor
DE102015106315B4 (de) * 2015-04-24 2021-09-16 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Betätigungseinrichtung für Umschaltventile eines Verbrennungsmotors und Verbrennungsmotor
US11261836B1 (en) * 2021-03-09 2022-03-01 Ford Global Technologies, Llc Fuel system check valve

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JPS49108427A (fr) * 1973-02-19 1974-10-15
US3961612A (en) * 1974-08-22 1976-06-08 Diesel Kiki Kabushiki Kaisha Fuel injection device for diesel engines
JPS51101628A (fr) * 1975-01-24 1976-09-08 Diesel Kiki Co
DE2558789A1 (de) * 1975-12-24 1977-07-14 Bosch Gmbh Robert Hochdruck-kraftstoffeinspritzeinrichtung fuer dieselmotoren
DE2806788A1 (de) 1978-02-17 1979-08-23 Bosch Gmbh Robert Pumpe-duese fuer brennkraftmaschinen
US4219154A (en) 1978-07-10 1980-08-26 The Bendix Corporation Electronically controlled, solenoid operated fuel injection system
JPS59141764A (ja) * 1983-02-03 1984-08-14 Nissan Motor Co Ltd 燃料噴射装置
JPS59188070A (ja) * 1983-04-08 1984-10-25 Isuzu Motors Ltd 増圧プランジヤ式燃料噴射装置
US5779149A (en) 1996-07-02 1998-07-14 Siemens Automotive Corporation Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke
US5682858A (en) 1996-10-22 1997-11-04 Caterpillar Inc. Hydraulically-actuated fuel injector with pressure spike relief valve

Also Published As

Publication number Publication date
EP1155233A1 (fr) 2001-11-21
US6463914B2 (en) 2002-10-15
US20020000219A1 (en) 2002-01-03
WO2000050764A1 (fr) 2000-08-31
DE50009281D1 (de) 2005-02-24

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