EP0451227B1 - Pompe d'injection de carburant - Google Patents

Pompe d'injection de carburant Download PDF

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Publication number
EP0451227B1
EP0451227B1 EP90914055A EP90914055A EP0451227B1 EP 0451227 B1 EP0451227 B1 EP 0451227B1 EP 90914055 A EP90914055 A EP 90914055A EP 90914055 A EP90914055 A EP 90914055A EP 0451227 B1 EP0451227 B1 EP 0451227B1
Authority
EP
European Patent Office
Prior art keywords
pump
closing
valve
fuel injection
suction conduit
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
EP90914055A
Other languages
German (de)
English (en)
Other versions
EP0451227A1 (fr
Inventor
Heinz Nothdurft
Reinhard Trunk
Kurt Sprenger
Carlos Alvarez-Avila
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 EP0451227A1 publication Critical patent/EP0451227A1/fr
Application granted granted Critical
Publication of EP0451227B1 publication Critical patent/EP0451227B1/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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric 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
    • F02M63/02—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
    • F02M63/0205—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 for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/0215—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 for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits

Definitions

  • the invention is based on a fuel injection pump according to the preamble of claim 1.
  • a fuel injection pump known from DE-A1-31 42 750
  • the valve member is acted upon in the closing direction by a stationary supporting spring, so that when the electromagnet of the solenoid valve is fully excited, the closing part and the closing member counter to the force of the weaker closing spring of the valve member and the force of the stronger return spring of the closing part can be adjusted.
  • the weaker closing spring is designed so that it holds the valve member in its position closing the bore in the closing part when the electromagnet is not energized.
  • the valve member can now be brought into the open position against the force of the closing spring by partial excitation of the electromagnet, so that a quantity of fuel defined by the bore flows to the pump workspace of the fuel injection pump for emergency operation.
  • the closing part when it is used for the purpose of interrupting the fuel supply to the pump work space and thus stopping the internal combustion engine by its return spring when the magnet is not energized Is brought closed position, is acted upon by a pressure surge from the pump work space in the course of the remaining delivery stroke of the fuel injection pump and after opening the connection between the suction line and the pump work space.
  • This pressure surge can lead to the closing part being lifted off its seat and that a refilling process of the pump work space can now take place briefly via the suction line.
  • This quantity flowing into the pump work space can continue to be injected during the next delivery stroke of the pump piston, and the purpose of the solenoid valve serving to shut off is therefore not achieved.
  • the internal combustion engine can fail.
  • the solenoid valve according to the invention with the characterizing features of claim 1 has the advantage that an opening of the closing part and thus a correspondingly large fuel flow to the pump work space is prevented, since the pressure surge via the opening valve member, which releases only a small overflow cross section, is reduced.
  • FIG. 1 shows a partial longitudinal section through a fuel injection pump, in which the solenoid valve according to the invention is used
  • FIG. 2 shows a partial section through FIG. 1 along II-II
  • FIG. 3 shows a longitudinal section through the solenoid valve according to the invention in an enlarged view.
  • a cylinder liner 2 is inserted in a housing 1, in the cylinder bore 3 of which a pump piston 4 is set into a reciprocating movement and at the same time rotating movement by a drive and cam drive of the fuel injection pump (not shown) as shown by the arrows in the drawing.
  • the pump piston 4 includes in the cylinder bore 3 at the end a pump working chamber 6 which is supplied with fuel during the suction stroke of the pump piston via longitudinal grooves 8, which serve as filling grooves, which extend from the end face 7 of the pump piston.
  • FIG. 2 which shows a section along line II-II through FIG.
  • the filling grooves 8 are distributed around the circumferential surface of the pump piston at uniform angular intervals. Two grooves are shown in FIG. 2, corresponding to four suction strokes per pump piston revolution for supplying four injection nozzles alternately through this distributor fuel injection pump.
  • one of the filling grooves 8 is connected to a suction line 10 which opens laterally into the cylinder bore 3 and is connected to a pump suction chamber 11 which is enclosed in the housing of the fuel injection pump.
  • the pump suction chamber 11 supplied by a fuel feed pump 12 from a fuel reservoir 14 with fuel, which is preferably under speed-dependent pressure, additionally controlled by a pressure control valve 15, which is parallel to the fuel feed pump 12, which is driven in speed synchronism with the fuel injection pump.
  • the end of the pump piston opposite the pump working chamber 6 protrudes into said pump suction chamber 11 and is connected there to the drive (not shown).
  • An annular slide 17 is slidably arranged on the outer surface of the pump piston, which can be displaced in a known manner by a regulator of known design, not shown here, via a regulator lever 18 and thereby controls the outlet opening of a transverse bore 19 in the pump piston.
  • the transverse bore 19 is connected to a longitudinal channel 20 in the pump piston, which enters axially at the end face 7 of the pump piston and ends as a blind bore.
  • a radial bore 21 branches off from this longitudinal channel and leads to a distributor opening, here a distributor groove 22, on the lateral surface of the pump piston.
  • injection lines 23 branch off from the cylinder bore, each leading to an injection valve 25, for example via a pressure valve.
  • Such injection lines are distributed around the circumference of the cylinder bore 3 according to the number of injection valves to be supplied, in this case four, in that the pump piston performs four delivery strokes per revolution.
  • the latter sucks fuel from the pump suction chamber 11 via the filling groove 8, which is then covered with the suction line, so that the pump working chamber 6 is filled with fuel at the beginning of the following delivery stroke.
  • the ring slide 17 then closes the outlets of the transverse bore 19, so that during the subsequent delivery stroke of the pump piston and after the filling groove in the pump work chamber has been closed again the fuel is brought to high pressure, which is then fed via the longitudinal channel 20 and one of the injection lines 23 to the corresponding fuel injection valve and is injected.
  • the transverse bore emerges from the overlap at a stroke predetermined by the ring slide 17, so that the pump working space is now relieved via the longitudinal bore 20 and the transverse bore 19 to the pump suction space, the delivery pressure of the pump piston falls below the opening pressure of the injection valve and thus the high pressure injection is interrupted.
  • a solenoid valve 27 is also provided in the suction line 10, the closing part 28 of which cooperates with a valve seat 29 designed as a flat seat, on which the closing part 28 engages when the solenoid valve is de-energized by the force of a return spring is coming.
  • the valve seat is located at the transition from a stepped bore part 31 with a small diameter, on the pump work chamber side, to the stepped bore part 30 with a large diameter of a stepped bore, which receives the solenoid valve used from the outside. From the stepped bore part 30 with a large diameter, the suction line 10 leads further to the pump suction chamber 11.
  • the stepped bore part 31 with a small diameter opens into a recess 32 in the cylinder liner 2, from which a suction line piece 33 with a rectangular cross section opens into the cylinder bore 3.
  • the solenoid valve 27 is shown in detail in FIG. 3.
  • a solenoid 39 and a guide sleeve 40 surrounded by it, into which a magnetic core 41 is immersed, are arranged.
  • An armature 42 which is loaded by the return spring 43, is displaceable in the guide sleeve 40.
  • the valve housing 38 is on the side of the solenoid valve facing away from the armature closed by a plastic part 44 through which the power supply line 45 leads to the solenoid 39.
  • the space between the valve housing 38 and the solenoid 39 is filled with a synthetic resin in order to prevent the vibrations transmitted by the internal combustion engine from causing parts of the valve, in particular the electrical connection, to become detached.
  • the core 41 and the armature 42 are conical on the facing end faces in order to obtain a favorable magnetic force transmission for large strokes necessary for the use of the solenoid valve.
  • the armature also serves as a valve part, in which its end projecting out of the guide sleeve 40 into the stepped bore part 30 with a larger diameter is designed as a closing part 28.
  • a hat-shaped cap 47 made of elastic sealing material is vulcanized onto this end of the armature 42, which comes into abutment with its circumferential outer edge 48 on the front side on the valve seat 29 when the armature with the closing part 28 with the solenoid coil de-energized by the force of the return spring 43 in the closed position brought.
  • the armature 42 has a bore 50 which extends through the end face of the cap 47 coaxially to the stepped bore part 31 and which opens out into the receiving bore 53 with a larger diameter via a conical valve seat 52, which can also be spherical.
  • This receiving bore continues with essentially the same diameter until it emerges at the conically shaped end face of the armature opposite the core 41.
  • the return spring 43 is arranged, which is supported on the face on the correspondingly conical core, there on a shoulder, and on the other hand on a sleeve pressed into the receiving bore 53.
  • This sleeve which can also be fixed in the receiving bore in another way, is to be referred to as an intermediate spring plate 55, since a closing spring 57 is supported on the latter on the other side, which, designed as a compression spring, supports it the other end comes to rest on a spring plate 58 which is displaceable within the receiving bore 53.
  • the spring plate has a recess 60 on its end face facing the bore 50, in which a ball 61, which serves as a valve member, is centered. The ball 61, on the other hand, comes to rest in the closed position on the conical valve seat 52 between the receiving bore 53 and the bore 50.
  • the spring plate 58 is advantageously made of plastic and has on the side of the closing spring 57 a pin 63 which projects through a central opening 64 in the intermediate spring plate 55 and is guided there.
  • the intermediate spring plate 55 On its circumference, the intermediate spring plate 55 has recesses 67, so that when the intermediate spring plate or the armature is adjusted, fuel is throttled and the movement cannot flow past the intermediate spring plate.
  • Cross openings 66 branch off from the receiving bore 53, via which the parts of the suction line 10 upstream and downstream of the valve seat 29 are connected when the valve member 61 is lifted off, even when the closing part 28 is in the closed position and via the armature 42 when the closing part 28 is opened the fuel that it displaces can flow off.
  • the small mass of ball 61 and spring plate 58 with a correspondingly dimensioned closing spring allows a very brief low-hysteresis opening and reclosing of the bore 50 or the connection between the suction line parts. This prevents large amounts of fuel from overflowing from the pump work chamber to equalize the pressure, even if the valve member had been brought into the open position due to momentary pressure surges. In any case, it is prevented that the closing part 28 controlling the substantially larger diameter of the stepped bore part 31 is lifted off its seat. This reduces the risk of the internal combustion engine going through. The danger of the internal combustion engine running through exists in particular when the ring slide 17 is displaced in a very high position towards the pump work space and, for. B.
  • the fuel can be injected again during the subsequent pressure stroke, in particular if the pump work space cannot be relieved via the ring slide.
  • the pressure surge can in turn cause the closing portion 28 to open, followed by pressure equalization and a reflow of fuel to the pump work space as previously described.

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

Abstract

Une électrovanne servant à la coupure d'une conduite d'aspiration de carburant (10) pour l'alimentation en carburant d'un espace de travail d'une pompe d'injection de carburant, présente sur la partie de fermeture (28) un trou (50) entrant par le devant et pouvant être obturé au moyen d'un élément de soupape (61) sous l'effet d'un ressort de fermeture (57). En présence d'à-coups de pression dans le tronçon de la conduite d'aspiration (31) obturée par la partie de fermeture (28) et menant vers l'espace de travail de la pompe, la partie de fermeture (28) et toute la section de la partie de la conduite d'aspiration (31) ne s'ouvrent pas, mais uniquement la section du trou (50). Ce trou, après avoir été ouvert, est rapidement refermé par l'élément de soupape (61) à faible masse, de façon que seulement de faibles quantités de carburant puissent passer à travers le trou (50) en vue de l'égalisation de pression.

Claims (5)

  1. Pompe d'injection de carburant servant à alimenter des moteurs à combustion interne avec un piston de pompe (4) délimitant une chambre de travail (6) de la pompe, avec une conduite d'admission (10, 31, 32, 33) reliant la chambre de travail (6) de la pompe d'injection de carburant à une source d'alimentation en carburant (11) et pouvant être bloquée par une électrovanne (27) pour arrêter l'injection du carburant pendant la course d'admission du piston de pompe (4) en pouvant s'écouler en direction de la chambre de travail (6) de la pompe, l'électrovanne présentant une bobine d'électroaimant (39), un noyau magnétique (41) et une armature (42) servant en même temps comme partie de l'électrovanne, partie qui possède une pièce de fermeture (28), qui peut être maintenue en position fermée sur un siège de soupape (29) par un ressort de rappel (43) s'appuyant à poste fixe, siège qui subdivise la conduite d'admission en une partie de conduite d'admission (31, 32, 33) allant du siège de soupape à la chambre de travail de la pompe d'injection de carburant, et une partie de conduite d'admission (10) allant de la source d'alimentation en carburant (11) de la pompe d'injection de carburant au siège de soupape (29), alors que l'organe de fermeture (28), en position de fermeture, est actionné par la pression régnant dans la partie de la conduite d'admission (31, 32, 33) conduisant à la chambre de travail (6) de la pompe d'injection de carburant, à l'encontre de la force du ressort de rappel (43), et peut être mis en position d'ouverture par l'armature (42), la pièce de fermeture (28) présentant un alésage (50) qui relie ensemble les deux parties de la conduite d'admission, alésage qui peut être fermé par un organe de soupape (61) actionné par un ressort de fermeture (57) sollicité par la pression dans la partie (31, 32, 33) de la conduite d'admission allant à la chambre de travail de la pompe (6), à l'encontre de la force du ressort de fermeture (57), pompe d'injection de carburant caractérisée en ce que le ressort de fermeture (57) s'appuie dans la pièce de fermeture et l'organe de soupape s'ouvre sous l'action de coups de bélier qui surviennent dans la partie (31, 32, 33) de la conduite d'admission allant à la chambre de travail (6) de la pompe, avant que ceux-ci ne soient en position d'ouvrir la pièce de fermeture (28) à l'encontre de la force du ressort de rappel (43).
  2. Electrovanne selon la revendication 1, caractérisée en ce que l'alésage (50) est, dans la pièce de fermeture (28), un alésage axial qui débouche, par l'intermédiaire d'un siège de soupape (52) conique ou sphérique, dans un alésage de réception (53) dans lequel l'organe de soupape (61) et le ressort de fermeture (57) sont disposés, électrovanne dans laquelle l'alésage de réception (53) pénètre axialement dans la pièce de fermeture (28) et l'armature (42) et présente une cuvette intermédiaire de ressort (55) insérée de façon fixe, qui sert d'une part de point d'appui au ressort de rappel s'appuyant sur le noyau fixe (41) de l'électroaimant de l'électrovanne, et d'autre part de point d'appui au ressort de fermeture (57).
  3. Electrovanne selon la revendication 2, caractérisée en ce que l'organe de soupape (61) est une bille qui s'appuie sur un évidement (60) formé dans une coupelle de ressort (58), qui présente par ailleurs un téton (63) et que l'on fait passer à travers une ouverture médiane (64) de la cuvette intermédiaire de ressort (55).
  4. Electrovanne selon la revendication 3, caractérisée en ce que la coupelle de ressort est en matière plastique.
  5. Electrovanne selon l'une des revendications 2 à 4, caractérisée en ce que la cuvette intermédiaire de ressort (55) est enfoncée par pressage dans l'alésage de réception qui est relié par l'intermédiaire d'une ouverture transversale (66) à la conduite d'admission (10).
EP90914055A 1989-10-20 1990-09-28 Pompe d'injection de carburant Expired - Lifetime EP0451227B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE3934953 1989-10-20
DE3934953A DE3934953A1 (de) 1989-10-20 1989-10-20 Magnetventil, insbesondere fuer kraftstoffeinspritzpumpen
PCT/DE1990/000740 WO1991005950A1 (fr) 1989-10-20 1990-09-28 Electrovanne, en particulier pour pompes d'injection de carburant

Publications (2)

Publication Number Publication Date
EP0451227A1 EP0451227A1 (fr) 1991-10-16
EP0451227B1 true EP0451227B1 (fr) 1994-12-14

Family

ID=6391833

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90914055A Expired - Lifetime EP0451227B1 (fr) 1989-10-20 1990-09-28 Pompe d'injection de carburant

Country Status (7)

Country Link
US (1) US5150688A (fr)
EP (1) EP0451227B1 (fr)
JP (1) JP3145108B2 (fr)
DE (2) DE3934953A1 (fr)
ES (1) ES2066225T3 (fr)
RU (1) RU2018758C1 (fr)
WO (1) WO1991005950A1 (fr)

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EP0928893A2 (fr) 1998-01-12 1999-07-14 Robert Bosch Gmbh Electrovanne
US6148796A (en) * 1998-01-12 2000-11-21 Robert Bosch Gmbh Switching magnet for a high pressure pump

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RU2184870C2 (ru) * 2000-10-04 2002-07-10 Гундоров Валентин Михайлович Электромагнитная форсунка для двигателя внутреннего сгорания
DE10216154A1 (de) * 2002-04-12 2003-10-23 Hydraulik Ring Gmbh Druckbegrenzungsventil, insbesondere für Diesel-Hochdruckpumpen von Einspritzvorrichtungen in Kraftfahrzeugen
US7537024B2 (en) * 2003-07-29 2009-05-26 Societe Bic Fuel cartridge with connecting valve
DE102010027745A1 (de) * 2010-04-14 2011-10-20 Robert Bosch Gmbh Hochdruckpumpe
RU2465506C1 (ru) * 2011-06-22 2012-10-27 Закрытое акционерное общество "Барнаульский котельный завод" (ЗАО "БКЗ") Регулирующий клапан
DE102012206604A1 (de) * 2012-04-20 2013-10-24 Hyptec Gmbh Elektromagnetisches Ventil für ein Behälterventil einer Kraftstoffversorgungsanlage
DE102018206334A1 (de) * 2018-04-25 2019-10-31 Robert Bosch Gmbh Kraftstofffördereinrichtung für kryogene Kraftstoffe
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DE3144361A1 (de) * 1981-11-07 1983-05-19 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen
JPS59211757A (ja) * 1983-05-16 1984-11-30 Nippon Soken Inc 内燃機関の燃料制御装置
US4412519A (en) * 1982-09-13 1983-11-01 General Motors Corporation Diesel fuel distributor type injection pump
JPH0650090B2 (ja) * 1983-05-17 1994-06-29 日産自動車株式会社 分配型燃料噴射ポンプの燃料遮断弁
JPH0692743B2 (ja) * 1985-04-01 1994-11-16 日本電装株式会社 流体制御用電磁弁
US4617959A (en) * 1985-10-04 1986-10-21 Nippondenso Co., Ltd. Check valve assembly for pipeline system
KR910009542B1 (ko) * 1985-12-24 1991-11-21 가부시끼가이샤 나니와 세이사꾸쇼 수도꼭지
JPH07107372B2 (ja) * 1986-09-04 1995-11-15 株式会社日本自動車部品総合研究所 燃料噴射ポンプ
JPS63223351A (ja) * 1987-03-13 1988-09-16 Nippon Soken Inc 内燃機関の燃料噴射ポンプの制御方法
DE3711744A1 (de) * 1987-04-07 1988-10-27 Bosch Gmbh Robert Verfahren und vorrichtung zur steuerung der kraftstoffeinspritzmenge
DE3715614A1 (de) * 1987-05-11 1988-11-24 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
JPH01295085A (ja) * 1988-05-20 1989-11-28 Kimura Koki Kk 比例式電動二方弁
DE3819996A1 (de) * 1988-06-11 1989-12-14 Bosch Gmbh Robert Hydraulische steuereinrichtung insbesondere fuer kraftstoffeinspritzanlagen von brennkraftmaschinen

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0928893A2 (fr) 1998-01-12 1999-07-14 Robert Bosch Gmbh Electrovanne
US6138986A (en) * 1998-01-12 2000-10-31 Robert Bosh Gmbh Solenoid valve for a fuel injection system for a vehicle
US6148796A (en) * 1998-01-12 2000-11-21 Robert Bosch Gmbh Switching magnet for a high pressure pump

Also Published As

Publication number Publication date
US5150688A (en) 1992-09-29
WO1991005950A1 (fr) 1991-05-02
EP0451227A1 (fr) 1991-10-16
DE59008029D1 (de) 1995-01-26
ES2066225T3 (es) 1995-03-01
JP3145108B2 (ja) 2001-03-12
JPH04502502A (ja) 1992-05-07
DE3934953A1 (de) 1991-04-25
RU2018758C1 (ru) 1994-08-30

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