EP1047871A1 - Kraftstoffeinspritzsystem für brennkraftmaschinen - Google Patents
Kraftstoffeinspritzsystem für brennkraftmaschinenInfo
- Publication number
- EP1047871A1 EP1047871A1 EP99939946A EP99939946A EP1047871A1 EP 1047871 A1 EP1047871 A1 EP 1047871A1 EP 99939946 A EP99939946 A EP 99939946A EP 99939946 A EP99939946 A EP 99939946A EP 1047871 A1 EP1047871 A1 EP 1047871A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- injection system
- fuel injection
- valve
- fuel
- control
- 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
Links
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.
- 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 must be brought to a variable pressure depending on the respective operating state of the internal combustion engine by means of a high-pressure pump.
- the high pressure pump is driven depending on the engine speed. B. can be done by camshaft drive.
- the possible delivery rate of the high pressure pump is designed so that in each
- pressure control valve which is arranged in the high pressure area behind the high pressure pump. Because of this Pressure regulating valve divides the high-tension fuel flow, namely in the direction of the rail, for increasing / maintaining pressure, and in the direction of the fuel tank. The latter partial flow is the overflow quantity, which also means a corresponding loss of efficiency.
- the solution according to the invention which can be gathered from the characterizing part of patent claim 1, creates a fuel metering unit for a generic CR system which is capable of precisely metering the amount of fuel desired in the respective operating state of the internal combustion engine to the high pressure pump of the CR system.
- Such an exact metering of the amount of fuel required to the high-pressure pump on the low-pressure side avoids the unnecessarily compressed overcurrents that occur in the prior art up to now. This leads to improved efficiency and thus to fuel savings. Further refinements and advantages of the invention can be found in patent claims 2 to 16.
- Fig. 1 shows an embodiment of a
- Fuel metering unit in vertical longitudinal section,
- FIG. 2 shows a variant of a control valve of the fuel metering unit according to FIG. 1 with three control openings (shown in development over the circumference),
- FIG. 3 shows the detail “A” from FIG. 2, in a separate representation,
- FIG. 4 shows a diagram in which the opening area of the control opening according to FIG. 3 is plotted over the magnetic stroke
- FIG. 5 shows a diagram containing the characteristics of the electromagnet and a pressure spring actuating the control valve
- FIG. 6 shows a variant of a fuel metering unit which is somewhat modified (and shown reduced in size) compared to FIG. 1, in a vertical longitudinal section,
- FIG. 7 shows the detail "B" (arrow) from FIG. 6, in an enlarged view compared to FIG. 6, and FIG. 8 shows a modification of the detail "C" from FIG. 7.
- the electromagnet 10 essentially consists of a magnet coil 12, an armature 13 with armature bolts 14 and a magnet pot 15 which partially encloses the magnet coil 12 and the armature 13 .
- the entire electromagnet assembly 10 with integrated control valve 11 is arranged in a high-pressure fuel pump (not shown).
- the magnet pot 15 serves as a sealing element, as a magnetic yoke and as a fastening element (16) of the electromagnet 10 in the high pressure pump.
- the magnetic coil 12 is completely encapsulated after it has been inserted into the magnetic housing 15.
- the encapsulation designated 17 ensures optimal heat transfer from the coil 12 to the housing 15.
- the encapsulation 17 leads to good vibration and vibration resistance, as a result of which the fuel metering unit 10, 11 is fastened at highly stressed points, for. B. the high-pressure fuel pump, in relation to vibrations, temperature and environmental pollution is made possible.
- the encapsulation 17 of the magnetic coil 12 in cooperation with two sealing points 18, 19 ensures that the contact points of the coil 12 with the connector lugs (not shown) are “dry”. Magnet coil winding and contact points are thus optimally protected against attacks by corrosive media.
- the control valve 11 has a valve housing 22 which merges into a flange-like widening 23, which at the same time forms the front end of the electromagnet housing 15.
- An axial bore 24 is formed in the valve housing 22 and is arranged coaxially with the armature bolt 14 of the electromagnet 10.
- the axial bore 24 receives a displaceable sleeve-shaped valve piston 25, in the interior 26 of which a compression spring 27 is arranged.
- Compression spring 27 is supported on the front on a bottom 28 of the valve piston 25 and on the rear on a spring plate 29 located in the axial bore 24 of the valve housing 22.
- a shoulder 30 on the inner wall of the valve piston 25 ensures that the compression spring 27 is largely contact-free from the inner wall in the valve piston 25.
- the valve piston head 28 and thus the valve piston 25 are in contact with the front end of the anchor bolt 14.
- An opening 31 connects the interior 26 of the valve piston 25 to a prefeed pump (not shown) of the fuel injection system.
- a plurality of radially directed control openings are arranged in the valve housing 22 (see also FIGS. 2 to 4), one of which can be seen in FIG. 1 and is numbered 32.
- the control opening 32 stands with the low pressure area the high pressure pump (not shown) in hydraulic operative connection.
- the opening 31 would then be hydraulically connected to the low-pressure region of the high-pressure pump, while the control opening 32 would be connected to the pressure side of the prefeed pump and would thus form the feed into the metering unit.
- valve piston 25 and anchor bolt 14 - shows the control valve 11 in the open position, in which the control opening 32 is completely released by the valve piston 25.
- the control valve 11 is shown in the fully closed position.
- the magnetic force of the energized electromagnet 10 acts on the armature pin 14 on the valve piston 25 and moves it against the resistance of the compression spring 27 into said closed position of the control valve 11.
- the compression spring 27 is able to actuate the valve piston 25 in the open position (upper half of FIG.
- FIG. 2 shows a variant in which a total of three control openings - designated 32, 34 and 35, are provided.
- the special design of the central control opening 32 results in two control areas of the control valve 11, on the one hand an area 1 with a correspondingly low fuel delivery and on the other hand an area 2 with a linearly strong dependence on the valve piston stroke (magnetic stroke) increasing fuel delivery (see FIG. 4).
- Area 1 (low fuel delivery) is assigned to engine idling up to the lower partial load.
- Area 2 corresponds to the average partial load up to the full load of the internal combustion engine.
- Area 1 is therefore characterized in that initially only the opening area of the slit-shaped part 36 of the control opening 32, plotted over the stroke of the valve piston 25 (or the armature pin 14), has a flat characteristic curve. This is numbered 37 in FIG. 4. This is a good controllability of the idle and the lower
- Partial load of the internal combustion engine possible. This is achieved by the narrow, rounded design of the slot-shaped part 36 of the control opening 32.
- This narrow slot 36 can be produced by eroding, 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 after a defined stroke a correspondingly large opening area is available. Thus, a short construction length and a low energy expenditure of the electromagnet 10 are 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 a plurality of slots or bores distributed around the circumference of the valve housing 22 with suitable geometries (e.g. triangular shape).
- the fuel metering unit in question is equally applicable to different types of vehicles (cars, commercial vehicles, special vehicles, ships, etc.), provided they are operated with internal combustion engines.
- the required adaptation can be accomplished in a simple manner by designing the opening areas of the valve control openings (for example 32, 34, 35 m in FIG. 2).
- Dead volume ensures exact metering of the required amount of fuel and quick reaction times to changing volume requirements 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 parameters.
- the spring characteristic (shown in dashed lines) is numbered 45. Control points each arise at the interfaces of the spring characteristic 45 with the magnetic characteristics 41 to 44.
- This characteristic assignment is achieved by a special magnetic core geometry and optimized material thicknesses on the magnet armature 13 and the magnet housing 15.
- a high spring stiffness (high c-value of the compression spring 27) is essential Advantage.
- Correspondingly steep transitions between the magnetic characteristic (41 or 42 or 43 or 44) and the spring characteristic 45 are achieved. This leads to stable control points.
- the control of the electromagnet 10 is pulse width modulated.
- An optimized control frequency results in movement ripples of the armature 13 and thus of the valve piston 25. These measures lead to reduced friction hysteresis and good dynamics of the fuel metering unit.
- the control valve 11 Before the fuel metering unit 10, 11 is put into operation, the control valve 11 must be adjusted by means of a corresponding axial displacement of the spring plate 29 in the valve bore 24 and subsequent fixation of the same.
- the setting process is carried out as follows. First, a defined current is applied to the electromagnet 10. Then the spring plate 29 is pushed into the valve bore 24 until a defined volume flow results from the control opening (e.g. 32, FIG. 1). In this position, the spring plate 29 is fixed, for. B. by the spring plate 29 is formed as a press-in part or the valve housing 22 is plastically deformed from the outside.
- This valve setting point is expediently placed in the range of minimum fuel flow rates, since this enables the tolerance-sensitive idling range to be implemented exactly.
- the magnet coil 12 has been designed with a step 46.
- the inner space of the electromagnet 10 can be optimally used.
- the working air gap of the electromagnet 10 was placed in the center of the coil 12 for reasons of magnetic force optimization. Due to the contact-free guidance of the compression spring 37 inside the valve piston 25, the spring and magnetic hysteresis can be kept at a minimum level, so that an exact fuel metering is ensured.
- the entire control valve 11 and the electromagnet 10 are fuel-flooded.
- the control valve 11 is thus hydraulically balanced. Interferences do not affect metering.
- the flooded electromagnet 10 acts as a hydraulic cushion, which counteracts both interference and frictional wear.
- the fuel metering unit 10, 11 must therefore meet the high requirements placed on such a zero delivery situation of the internal combustion engine.
- the measures taken for this purpose which is a so-called “zero funding relief”, are shown in FIGS. 6, 7 and 8.
- the structural and functional components corresponding to the embodiment according to FIG. 1 have the same reference numerals as numbered in Fig. 1.
- valve piston 25 is opened via the valve piston 25.
- This open position of the valve piston 25 - caused by the anchor bolt 14 against the resistance of the compression spring 27 - can be seen in particular from FIG. 7. In this valve piston position
- Control opening 32 is hydraulically connected to the radial bore 47 via a recess 48 on the cylindrical circumference of the valve piston 25.
- the radial bore 47 can - through a channel 49 - z. B. connected to the suction side of the pre-feed pump. 6 and 7, the position of the valve piston 25 results in a hydraulic connection between the control opening 32 and a channel 50 leading from there to the high-pressure pump with the suction side of the pre-feed pump.
- valve-side edge of the spring plate 29 is designed as an axial sealing seat 51, which cooperates in a sealing manner with the end plate 52 of the valve piston 25 on the spring plate side.
- the annular sealing seat 51 can, for. B. be designed as an elastomer flat sealing seat or as a steel cone seat.
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)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19853103 | 1998-11-18 | ||
DE19853103A DE19853103A1 (de) | 1998-11-18 | 1998-11-18 | Kraftstoffeinspritzsystem für Brennkraftmaschinen |
PCT/DE1999/001848 WO2000029742A1 (de) | 1998-11-18 | 1999-06-25 | Kraftstoffeinspritzsystem für brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1047871A1 true EP1047871A1 (de) | 2000-11-02 |
EP1047871B1 EP1047871B1 (de) | 2004-01-28 |
Family
ID=7888157
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99939946A Expired - Lifetime EP1047871B1 (de) | 1998-11-18 | 1999-06-25 | Kraftstoffeinspritzsystem für brennkraftmaschinen |
Country Status (5)
Country | Link |
---|---|
US (1) | US6446606B1 (de) |
EP (1) | EP1047871B1 (de) |
JP (1) | JP4358445B2 (de) |
DE (2) | DE19853103A1 (de) |
WO (1) | WO2000029742A1 (de) |
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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 (de) | 2001-12-19 | 2003-07-02 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
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 |
AU2003273426A1 (en) | 2002-07-11 | 2004-02-02 | Siemens Automotive Hydraulics Sa | Device for controlling flow rate of a direct injection fuel pump |
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 |
AU2003227486A1 (en) * | 2003-04-11 | 2004-11-04 | Bosch Automotive Systems Corporation | Liquid fuel flow regulating valve, and fuel injection system of internal combustion engine with the liquid fuel flow regulating valve |
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 |
DE602005003427T2 (de) * | 2004-09-24 | 2008-09-18 | Denso Corporation, Kariya | Durchflussregelventil |
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 |
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CN103075285A (zh) * | 2013-02-05 | 2013-05-01 | 李正富 | 高压共轨燃油计量阀 |
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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 |
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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 WO PCT/DE1999/001848 patent/WO2000029742A1/de active IP Right Grant
- 1999-06-25 JP JP2000582707A patent/JP4358445B2/ja not_active Expired - Fee Related
- 1999-06-25 EP EP99939946A patent/EP1047871B1/de 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
Non-Patent Citations (1)
Title |
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See references of WO0029742A1 * |
Also Published As
Publication number | Publication date |
---|---|
US6446606B1 (en) | 2002-09-10 |
JP2002530568A (ja) | 2002-09-17 |
DE19853103A1 (de) | 2000-05-25 |
JP4358445B2 (ja) | 2009-11-04 |
DE59908419D1 (de) | 2004-03-04 |
EP1047871B1 (de) | 2004-01-28 |
WO2000029742A1 (de) | 2000-05-25 |
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