EP1047871B1 - Systeme d'injection de carburant pour moteurs a combustion interne - Google Patents
Systeme d'injection de carburant pour moteurs a combustion interne Download PDFInfo
- Publication number
- EP1047871B1 EP1047871B1 EP99939946A EP99939946A EP1047871B1 EP 1047871 B1 EP1047871 B1 EP 1047871B1 EP 99939946 A EP99939946 A EP 99939946A EP 99939946 A EP99939946 A EP 99939946A EP 1047871 B1 EP1047871 B1 EP 1047871B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- injection system
- fuel injection
- valve piston
- fuel
- 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
Links
Images
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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
-
- 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
- F02M63/0045—Three-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
- 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
- F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
-
- 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
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/24—Fuel-injection apparatus with sensors
Definitions
- the invention relates to a fuel injection system for Internal combustion engines according to the preamble of claim 1.
- a such is known from EP 0 778 413.
- Valve piston opening from in a radial plane on the circumference of the Valve piston arranged control openings controlled. Furthermore are in this area - for example - EP 0 299 337 and DE 195 49 108.4 known.
- the invention is based on a so-called common rail System (CR system).
- CR system common rail System
- the peculiarity of such CR systems is that the amount of fuel required by a High pressure pump on a variable from each Operating state of the engine dependent pressure brought must become.
- the high-pressure pump is dependent on the engine speed driven what z. B. can be done by camshaft drive.
- the possible delivery rate of the high pressure pump is designed so that in an excess amount of fuel in each operating condition, i. H. more than the rail is required to build the desired pressure can.
- Removable solution according to the invention is for a generic CR system a fuel metering unit created that is capable of the high pressure pump of the CR system which in the respective operating state of the Internal combustion engine desired amount of fuel exactly to meter.
- Electromagnet 10 with integrated control valve 11.
- electromagnet 10 essentially a magnet coil 12, an armature 13 with armature bolts 14 and a magnetic pot 15 which holds the magnet coil 12 and the armature 13 partially encloses.
- the entire assembly electromagnet 10 with integrated Control valve 11 is in a (not shown) High pressure fuel pump arranged.
- the magnetic pot 15 also serves as a sealing element magnetic yoke and as a fastening element (16) of the Electromagnet 10 in the high pressure pump.
- the solenoid 12 is after it in the magnet housing 15th is completely overmolded.
- By the age of 17 overmolding is an optimal heat transfer from the coil 12 to the housing 15 guaranteed. one This can cause overheating in critical operating states be counteracted.
- the extrusion coating 17 also leads to a good vibration and shake resistance, which makes a Attachment of the fuel metering unit 10, 11 highly stressed areas, e.g. B. the high pressure fuel pump, in terms of vibrations, temperature and environmental pollution is made possible.
- the coating 17 of the solenoid 12 in cooperation with two sealing points 18, 19 ensures that the contact points of the coil 12 to the Plug lugs (not shown) are "dry".
- Magnet coil winding and contact points are thus in front Corrosive media attacks optimally protected.
- the control valve 11 has a valve housing 22, which in a flange-like widening 23 merges, which at the same time the front end of the electromagnet housing 15 forms.
- the axial bore 24 takes one displaceable sleeve-shaped valve piston 25, in whose interior 26 a compression spring 27 is arranged.
- the Compression spring 27 is supported on the front on a bottom 28 of the Valve piston 25 and on the back of one in the Axial bore 24 of the valve housing 22 located Spring plate 29 from.
- a paragraph 30 on the inner wall of the Valve piston 25 ensures that the compression spring 27 largely non-contact from the inner wall in the Valve piston 25 is.
- the valve piston head is on the outside 28 and thus the valve piston 25 with the front end of the anchor bolt 14 in plant.
- Valve housings 22 are also several radially directed Control openings arranged (see also Fig. 2 to 4), one of which can be seen in FIG. 1 and numbered 32 is.
- the control opening 32 stands with the low pressure area the (not shown) high pressure pump in hydraulic Operatively connected.
- Fig. 2 shows a variant in of the three control openings - with 32, 34 and 35 designated, are provided. 3, result from the special design of the middle Control opening 32 two control areas of the control valve 11, on the one hand, an area 1 with a correspondingly smaller amount Fuel delivery and on the other an area 2 with in Dependence on the valve piston stroke (magnetic stroke) linearly strong increasing fuel delivery (see FIG. 4).
- the Range 1 low fuel delivery
- engine idling up to assigned to the lower partial load.
- Area 2 (strong increasing fuel delivery) corresponds to the medium partial load to full load of the internal combustion engine.
- Area 1 is characterized in that initially only the opening area of the slot-shaped part 36 of FIG Control opening 32, plotted over the stroke of the valve piston 25 (or the anchor bolt 14), a flat characteristic has. This is numbered 37 in FIG. 4. This is good controllability of the idle and the lower Partial load of the internal combustion engine possible. This is achieved due to the narrow, rounded design of the slot-shaped part 36 of the control opening 32. Manufactured this narrow slot 36 can be eroded, Punching or laser cutting.
- Area 2 is characterized in that the opening area - in this case all three control openings 32, 34 and 35 involved (FIG. 2) - plotted over the stroke of the valve piston 25 or the anchor bolt 14 has a steep characteristic curve, cf. Curve sections 38, 39, 40 in Fig. 4. This ensures that a correspondingly large opening area is available after a defined stroke. A short overall length and a low energy expenditure of the electromagnet 10 are thus possible.
- large control opening areas can also be provided by a correspondingly wide slot or a control opening of correspondingly large diameter or also by several slots or bores with suitable geometries distributed around the circumference of the valve housing 22 (e.g. triangular shape).
- the fuel meter in question is for various vehicle types (cars, commercial vehicles, special vehicles, Ships etc.), provided that they are with internal combustion engines operated, equally applicable.
- the required Adaptation can be done in a simple manner via the design the opening areas of the valve control openings (e.g. 32, 34, 35 in Fig. 2) accomplish.
- the minimum that can be achieved Dead volume ensures exact metering of the required Fuel quantity and quick response times to changing Quantity requirement of the high pressure pump or the internal combustion engine.
- Fig. 5 shows four parallel Magnetic characteristics 41 to 44 with different magnetic currents as a parameter.
- the spring characteristic (shown in dashed lines) is numbered 45.
- Control points result in each case the interfaces of the spring characteristic 45 with the Magnetic characteristics 41 to 44.
- a high spring stiffness (high c-value the compression spring 27) is advantageous. This will correspondingly steep transitions between the magnetic characteristic (41 or 42 or 43 or 44) and the spring characteristic 45 reached. This leads to stable control points.
- the control of the electromagnet 10 takes place pulse width modulated.
- An optimized control frequency gives movement ripple of the armature 13 and thus the Valve piston 25.
- the setting process is as follows performed. First, the electromagnet 10 with a defined current applied. Then the Insert spring plate 29 into valve bore 24 so far until it comes out of the control opening (e.g. 32, Fig. 1) defined volume flow results. In this position the Spring plate 29 fixed, e.g. B. by the spring plate 29 as Press-in part is formed or the valve housing 22 of is plastically deformed on the outside. It makes sense to do this Valve set point in the range of minimum fuel flow rates because this makes the tolerance sensitive Idle range is exactly realizable.
- the solenoid 12 is included a stage 46 has been designed. This allows the inner Space of the electromagnet 10 can be optimally used.
- the Working air gap of the electromagnet 10 was for reasons the magnetic force optimization placed in the middle of the coil 12. Due to the non-contact guidance of the compression spring 37 in Inside the valve piston 25, the spring and Magnetic hysteresis can be kept to a minimum, so that an exact fuel metering is guaranteed.
- the entire control valve 11 and the electromagnet 10 are kraftstoffgeflutet.
- the control valve 11 is thus hydraulic balanced. Interferences do not affect the Metering out.
- the flooded electromagnet 10 acts as hydraulic cushion that both interference and counteracts fretting.
- valve piston 25 47 is opened in the valve housing 22.
- Control opening 32 via a recess 48 on the cylindrical
- the circumference of the valve piston 25 with the radial bore 47 hydraulically connected.
- the radial bore 47 can - through a channel 49 - e.g. B. connected to the suction side of the pre-feed pump his.
- the edge of the spring plate 29 on the valve side designed as an axial sealing seat 51, which with the End face 52 of the valve piston 25 on the spring plate side cooperates sealingly.
- the annular sealing seat 51 can z. B. as an elastomer flat sealing seat or as a steel cone seat be trained.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
Claims (11)
- Système d'injection de carburant pour des moteurs à combustion interne comportant une conduite de distribution et une pompe à haute pression entraínée en fonction du régime du moteur pour générer la pression et le débit de carburant nécessaires dans la conduite de répartition pour l'état de fonctionnement respectif du moteur à combustion interne, ainsi qu'une vanne de régulation à commande électromagnétique munie d'une unité de dosage de carburant installée dans la pompe à haute pression, une entrée (31) relié au côté de refoulement d'une pompe amont et une sortie (32, 34, 35) reliée à la zone basse pression de la pompe haute pression ainsi qu'un piston de vanne (25) sollicité en position d'ouverture par un ressort de compression (27), ce piston étant actionné par un goujon d'induit (14) de l'électro-aimant (10) vers la position de fermeture contre l'action développée par le ressort de compression avec au moins un orifice de commande radial (32, 34, 35) et de préférence plusieurs orifices prévus dans la paroi du boitier de vanne (22) et en coopération avec la région basse pression de la pompe à haute pression,
caractérisé en ce que
les ouvertures de commande sont formées et/ou installées pour qu'en fonction de la course du piston de vanne, on obtienne au moins deux régions de commande,
les surfaces d'ouverture des orifices de commande tracées en fonction de la course du piston de vanne comportent dans une première région de commande (région 1) une caractéristique plate (37) dont la pente est faible et dans une seconde région de commande, plage (2) une caractéristique pentue (38, 39, 40) avec une pente importante. - Système d'injection de carburant selon la revendication 1,
caractérisé en ce que
la vanne de régulation (11) fait suite axialement au boítier (15) de l'électro-aimant (10) et comporte un boítier (22) dont la face frontale comporte une ouverture axiale (31) coopérant avec le côté de pression de la pompe d'alimentation amont. - Système d'injection de carburant selon l'une des revendications 1 ou 2,
caractérisé en ce qu'
au début de la course du piston de vanne, on a une première région de commande (région 1) associée au ralenti et à la plage des charges inférieures du moteur à combustion interne et pour la suite de la course du piston de vanne, on a une seconde région de commande (région 2) correspondant à la charge partielle et à la charge maximale du moteur à combustion interne pour les orifices de commande (32, 34, 35). - Système d'injection de carburant selon l'une ou plusieurs des revendications 1 à 3,
caractérisé en ce que
les caractéristiques (41 - 44) de l'électro-aimant (10) sont opposées à la caractéristique (45) du ressort de compression (27) sollicitées par le piston de vanne (25). - Système d'injection de carburant selon l'une des revendications précédentes,
caractérisé en ce que
l'électro-aimant (10) est commandé avec modulation de largeur d'impulsion par un capteur de pression - carburant installé dans la conduite distributrice (rampe commune). - Système d'injecaion de carburant selon l'une des revendications précédentes,
caractérisé en ce que
le piston de vanne (25) est en forme de manchon et dans son volume intérieur (26) il loge le ressort de compression (27) le sollicitant en position d'ouverture ; et
le ressort de compression (27) s'appuie par son côté arrière contre un plateau à ressort (27) prévu dans le perçage (24) du boítier de vanne (22). - Système d'injection de carburant selon la revendication 6,
caractérisé en ce que
la vanne de régulation (11) est réglable par un coulissement axial correspondant suivi du blocage du plateau de ressort (29) dans le perçage de vanne (24). - Système d'injection de carburant selon l'une des revendications précédentes,
caractérisé en ce que
l'ensemble de l'unité de dosage de carburant (10, 11) est intégrée directement dans la pompe à haute pression de préférence par vissage et à la fois la vanne de régulation (11) et l'électro-aimant (10) sont baignés par le carburant. - Système d'injection de carburant selon la revendication 8,
caractérisé en ce que
la bobine (12) de l'électro-aimant (10) placée dans le boítier d'électro-aimant (15) en forme de pot est complètement enrobée par injection d'une enveloppe de matière plastique (17). - Système d'injection de carburant selon l'une des revendications précédentes,
caractérisé en ce que
le piston de vanne (25) possède à sa surface périphérique cylindrique, un lamage (48) et le boítier de vanne (22) comporte un perçage radial (47) relié au côté aspiration de la pompe de pré alimentation, de façon qu'en position de fermeture du piston de vanne (25), les ouvertures de commande radiales (32) soient reliées par le lamage (48) du piston de vanne au perçage radial (47) du boítier de vanne (22) par une liaison hydraulique. - Système d'injection de carburant selon l'une des revendications précédentes,
caractérisé en ce que
le bord du plateau à ressort (29) tourné vers le piston de vanne (25) comporte un siège d'étanchéité (51) axial, qui coopère en position de fermeture du piston de vanne (25) avec le bord (52) de celui-ci tourné vers le plateau à ressort (29) par une coopération étanche.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19853103A DE19853103A1 (de) | 1998-11-18 | 1998-11-18 | Kraftstoffeinspritzsystem für Brennkraftmaschinen |
DE19853103 | 1998-11-18 | ||
PCT/DE1999/001848 WO2000029742A1 (fr) | 1998-11-18 | 1999-06-25 | Systeme d'injection de carburant pour moteurs a combustion interne |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1047871A1 EP1047871A1 (fr) | 2000-11-02 |
EP1047871B1 true EP1047871B1 (fr) | 2004-01-28 |
Family
ID=7888157
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99939946A Expired - Lifetime EP1047871B1 (fr) | 1998-11-18 | 1999-06-25 | Systeme d'injection de carburant pour moteurs a combustion interne |
Country Status (5)
Country | Link |
---|---|
US (1) | US6446606B1 (fr) |
EP (1) | EP1047871B1 (fr) |
JP (1) | JP4358445B2 (fr) |
DE (2) | DE19853103A1 (fr) |
WO (1) | WO2000029742A1 (fr) |
Families Citing this family (44)
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JP2002004977A (ja) * | 2000-06-26 | 2002-01-09 | Denso Corp | 流量制御装置 |
DE10146740A1 (de) | 2001-09-22 | 2003-04-10 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
JP4841772B2 (ja) * | 2001-09-28 | 2011-12-21 | いすゞ自動車株式会社 | コモンレール式燃料噴射制御装置 |
DE10149746C1 (de) * | 2001-10-09 | 2003-05-28 | Siemens Ag | Verfahren zur Herstellung einer Rohrfeder sowie Aktoreinheit mit einer solchen Rohrfeder |
JP3630304B2 (ja) * | 2001-10-15 | 2005-03-16 | 株式会社ボッシュオートモーティブシステム | 燃料液流量調節弁、及び該燃料液流量調節弁を備えた内燃機関の燃料噴射システム |
JP2003120468A (ja) * | 2001-10-15 | 2003-04-23 | Bosch Automotive Systems Corp | 燃料液流量調節弁、及び該燃料液流量調節弁を備えた内燃機関の燃料噴射システム |
JP2005299683A (ja) * | 2001-11-27 | 2005-10-27 | Bosch Corp | 液体の流量制御弁および可動子のためのアンカー |
EP1321663A3 (fr) | 2001-12-19 | 2003-07-02 | Robert Bosch Gmbh | Dispositif d'injection de combustible pour moteur à combustion interne |
DE10205187A1 (de) | 2002-02-08 | 2003-08-21 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
DE10205811A1 (de) * | 2002-02-13 | 2003-08-21 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
DE10206236B4 (de) | 2002-02-15 | 2019-06-19 | Robert Bosch Gmbh | Kraftstoffeinpritzeinrichtung für eine Brennkraftmaschine |
DE10218021A1 (de) * | 2002-04-23 | 2003-11-06 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
WO2004007950A2 (fr) * | 2002-07-11 | 2004-01-22 | Siemens Automotive Hydraulics Sa | Dispositif de controle de debit d'une pompe a injection directe d'essence |
DE10242219A1 (de) * | 2002-09-12 | 2004-03-25 | Robert Bosch Gmbh | Kraftstoffzumesseinheit für eine Kraftstoffeinspritzanlage |
DE10244551A1 (de) | 2002-09-25 | 2004-04-08 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
DE10247145A1 (de) * | 2002-10-09 | 2004-04-22 | Robert Bosch Gmbh | Durchflussregeleinrichtung, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine |
DE10251014A1 (de) * | 2002-11-02 | 2004-05-19 | Robert Bosch Gmbh | Kraftstoffzumesseinheit für Kraftstoffeinspritzanlagen von Brennkraftmaschinen |
DE10257134A1 (de) * | 2002-12-06 | 2004-06-24 | Robert Bosch Gmbh | Vorrichtung zur Aufrechterhaltung eines Solldruckes im Kraftstoff-Hochdruckspeicher eines Speichereinspritzsystems |
DE10305947A1 (de) | 2003-02-12 | 2004-08-26 | Robert Bosch Gmbh | Expansionsorgan für eine Klimaanlage |
WO2004092575A1 (fr) * | 2003-04-11 | 2004-10-28 | Bosch Automotive Systems Corporation | Vanne de reglage de debit de combustible liquide, et systeme d'injection de combustible d'un moteur a combustion interne comportant une vanne de reglage de debit de combustible liquide |
DE10324010A1 (de) * | 2003-05-27 | 2004-12-16 | Robert Bosch Gmbh | Einrichtung zur Einstellung eines veränderlichen Durchflussquerschnitts |
US7387109B2 (en) * | 2003-10-21 | 2008-06-17 | Robert Bosch Gmbh | High-pressure fuel pump for an internal combustion engine |
EP1852603B1 (fr) * | 2004-09-24 | 2009-04-29 | Denso Corporation | Vanne de contrôle de flux |
US7819637B2 (en) * | 2004-12-17 | 2010-10-26 | Denso Corporation | Solenoid valve, flow-metering valve, high-pressure fuel pump and fuel injection pump |
JP2007092714A (ja) * | 2005-09-30 | 2007-04-12 | Denso Corp | 調量弁およびそれを用いた燃料噴射ポンプ |
US20070246015A1 (en) * | 2006-04-19 | 2007-10-25 | Alejandro Moreno | Solenoid-operated valve with coil for sensing plunger position |
DE102006061558A1 (de) * | 2006-12-27 | 2008-07-03 | Robert Bosch Gmbh | Kraftstoff-Fördereinrichtung für eine Brennkraftmaschine |
DE102007026833A1 (de) * | 2007-06-06 | 2008-12-11 | Hydraulik-Ring Gmbh | Volumenstromsteuerventil |
DE102007044001B4 (de) | 2007-09-14 | 2019-08-01 | Robert Bosch Gmbh | Verfahren zur Steuerung eines Kraftstoffeinspritzsystems einer Brennkraftmaschine |
DE102007050297A1 (de) | 2007-10-22 | 2009-04-23 | Robert Bosch Gmbh | Verfahren zur Steuerung eines Kraftstoffeinspritzsystems einer Brennkraftmaschine |
JP5157976B2 (ja) * | 2009-03-13 | 2013-03-06 | 株式会社デンソー | 流量制御電磁弁 |
US8585014B2 (en) * | 2009-05-13 | 2013-11-19 | Keihin Corporation | Linear solenoid and valve device using the same |
DE102009028501A1 (de) | 2009-08-13 | 2011-02-17 | Robert Bosch Gmbh | Kraftstoffzumesseinrichtung für eine Kraftstoffeinspritzanlage |
JP2011077355A (ja) * | 2009-09-30 | 2011-04-14 | Keihin Corp | リニアソレノイド及びそれを用いたバルブ装置 |
IT1398734B1 (it) * | 2010-03-04 | 2013-03-18 | Bosch Gmbh Robert | Impianto per l'alimentazione di carburante ad un motore a combustione interna |
DE102011051656A1 (de) | 2011-07-07 | 2013-01-10 | Hydraulik-Ring Gmbh | Schwenkmotorversteller |
DE102011087701A1 (de) * | 2011-12-05 | 2013-06-06 | Robert Bosch Gmbh | Niederdruckeinheit für eine Pumpe, insbesondere eine Kraftstoffhochdruckpumpe einer Kraftstoffeinspritzeinrichtung |
DE102012106134A1 (de) * | 2012-07-09 | 2014-01-09 | Svm Schultz Verwaltungs-Gmbh & Co. Kg | Ventil |
CN103075285A (zh) * | 2013-02-05 | 2013-05-01 | 李正富 | 高压共轨燃油计量阀 |
WO2015043637A1 (fr) * | 2013-09-26 | 2015-04-02 | Robert Bosch Gmbh | Ensemble doseur |
DE102013224296A1 (de) * | 2013-11-27 | 2015-05-28 | Robert Bosch Gmbh | Elektrische Steckvorrichtung zum Anschluss einer Magnetspule und/oder eines Sensorelements |
US9739203B2 (en) * | 2014-05-15 | 2017-08-22 | Hamilton Sundstrand Corporation | Fuel metering valve and method of managing fuel in a metering valve |
DE102014220757A1 (de) * | 2014-10-14 | 2016-04-14 | Robert Bosch Gmbh | Elektromagnetisch betätigbares Saugventil, Hochdruckpumpe mit einem solchen Saugventil sowie Verfahren zur Verbindung eines solchen Saugventils mit einem Gehäuseteil einer Hochdruckpumpe |
DE102018212882A1 (de) * | 2018-08-02 | 2020-02-06 | Robert Bosch Gmbh | Fluidventilvorrichtung |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2042541C3 (de) * | 1970-08-27 | 1973-09-27 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspntzanlage fur Fahrzeuggasturbinen |
US4462372A (en) * | 1982-09-30 | 1984-07-31 | Jackson Maurus E | Fuel injection system |
CH674243A5 (fr) * | 1987-07-08 | 1990-05-15 | Dereco Dieselmotoren Forschung | |
US5092299A (en) * | 1990-11-30 | 1992-03-03 | Cummins Engine Company, Inc. | Air fuel control for a PT fuel system |
US5701873A (en) * | 1993-11-08 | 1997-12-30 | Eidgenoessische Technische Hochschule Laboratorium Fuer Verbrennungsmotoren Und Verbrennungstechnik | Control device for a filling-ratio adjusting pump |
US5639066A (en) * | 1995-06-15 | 1997-06-17 | Applied Power Inc. | Bidirectional flow control valve |
DE19540021A1 (de) * | 1995-10-27 | 1997-04-30 | Bosch Gmbh Robert | Ventil zum dosierten Einleiten von aus einem Brennstofftank einer Brennkraftmaschine verflüchtigtem Brennstoffdampf |
FR2741672A1 (fr) * | 1995-11-29 | 1997-05-30 | Lucas Ind Plc | Systeme d'alimentation de carburant |
DE19549108A1 (de) * | 1995-12-29 | 1997-07-03 | Bosch Gmbh Robert | System zur Kraftstoffhochdruckerzeugung für ein in Brennkraftmaschinen eingesetztes Kraftstoffeinspritzsystem |
-
1998
- 1998-11-18 DE DE19853103A patent/DE19853103A1/de not_active Withdrawn
-
1999
- 1999-06-25 EP EP99939946A patent/EP1047871B1/fr not_active Expired - Lifetime
- 1999-06-25 DE DE59908419T patent/DE59908419D1/de not_active Expired - Lifetime
- 1999-06-25 US US09/600,418 patent/US6446606B1/en not_active Expired - Fee Related
- 1999-06-25 WO PCT/DE1999/001848 patent/WO2000029742A1/fr active IP Right Grant
- 1999-06-25 JP JP2000582707A patent/JP4358445B2/ja not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JP2002530568A (ja) | 2002-09-17 |
DE59908419D1 (de) | 2004-03-04 |
DE19853103A1 (de) | 2000-05-25 |
WO2000029742A1 (fr) | 2000-05-25 |
JP4358445B2 (ja) | 2009-11-04 |
EP1047871A1 (fr) | 2000-11-02 |
US6446606B1 (en) | 2002-09-10 |
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