WO2000077389A1 - Pumpenanordnung zur förderung von kraftstoff - Google Patents
Pumpenanordnung zur förderung von kraftstoff Download PDFInfo
- Publication number
- WO2000077389A1 WO2000077389A1 PCT/DE2000/001672 DE0001672W WO0077389A1 WO 2000077389 A1 WO2000077389 A1 WO 2000077389A1 DE 0001672 W DE0001672 W DE 0001672W WO 0077389 A1 WO0077389 A1 WO 0077389A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pump
- fuel
- flow
- arrangement
- drive
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
-
- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
-
- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/007—Venting 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
- F02M63/0225—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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/24—Bypassing
- F04B49/243—Bypassing by keeping open the inlet valve
Definitions
- the present invention relates to a pump arrangement for fuel, having a main feed pump and an upstream feed pump, which promotes a fuel flow via a fuel line from a tank and the total fuel flow conveyed through a drive / crank chamber of the main feed pump, the flow of the total fuel flow after the drive / Crank chamber a return for the lubrication flow to the tank and a delivery run for the delivery flow to one
- the Pump arrangement for fuel which has a main delivery pump designed as a high-pressure pump and an upstream delivery pump.
- the pre-pump is designed as an electric fuel pump and promotes a fuel flow through a fuel line from a tank.
- the total fuel flow delivered is led through the drive / crank chamber of the main pump. After the drive / crank room, the total fuel flow is divided into a lubrication flow and a delivery flow.
- the lubrication flow returns to the tank via a return.
- the delivery flow first reaches a metering unit via a delivery run and then on to the Main pump.
- the main feed pump has at least one pump cylinder which delimits a pump chamber in which a piston is guided so that it can be moved back and forth.
- the delivery flow is sucked into the pump chamber in a so-called suction stroke and, in a subsequent delivery stroke, the fuel in the pump chamber is compressed and conveyed, for example, into a storage volume of a common rail injection system.
- the main pump of the known pump arrangement also has drive means which are designed, for example, as a drive shaft.
- the drive means rotate or move at high speeds in a so-called drive or crank chamber. With the rotation or movement of the drive means in the drive / crank chamber, a large thermal and / or mechanical load arises in this area. For this reason, the
- Preliminary pump conveyed total fuel flow completely through the drive / crank chamber of the pump arrangement.
- the high fuel throughput in the area of the drive / crank chamber enables particularly good lubrication and high heat dissipation.
- forced lubrication of the drive / crank chamber is also possible, since the total fuel flow is present in the drive / crank chamber with the full delivery pressure of the preliminary pump.
- the object of the present invention is to improve a pump arrangement of the type mentioned at the outset, in particular to create a pump arrangement which is of particularly simple and robust construction and works particularly reliably.
- the invention suggests from the pump arrangement of the type mentioned at the outset that the pre-feed pump is mechanically driven and that a zero-feed run branches off between the metering unit and the main feed pump, in which a zero-feed throttle is arranged and which opens into the fuel line on the suction side of the pre-feed pump.
- the pre-pump is designed as a particularly simple and robust, mechanically driven pump.
- the pump arrangement first had to be adapted to use a mechanically driven pre-pump.
- the pump arrangement according to the invention has a zero delivery run, which is between the metering unit and the main pump, ie. H. on the suction side of the main pump, branches and before the pre-pump, d. H. on the suction side of the pre-pump, into the fuel line.
- a zero-feed throttle is arranged in the zero-feed run in order to limit a zero-feed flow to a specific flow value. It is conceivable that the zero delivery run opens into the tank instead of the fuel line. If, however, a filter is arranged between the tank and the preliminary pump, the zero delivery run between the filter and the preliminary pump should open into the fuel line.
- the preliminary pump be designed as a gear pump.
- a gear pump has a particularly simple design, works reliably and is particularly efficient.
- Gear pumps are particularly well suited for use in the hydraulics of motor vehicles.
- piston pumps, vane pumps, roller cell pumps or other pumps can also be used as the preliminary pump.
- a check valve and a throttle are arranged in series in the return.
- Venting throttle is arranged.
- the further return is designed, for example, as a vent hole with a specific throttle cross section.
- the return line and the further return line can also be designed as a common return line, in which the vent throttle and the check valve and the throttle are arranged parallel to one another.
- an overflow run branches off from the delivery run, in which an overflow valve is arranged and which opens into the fuel line upstream of the delivery pump in the flow direction of the total fuel flow.
- the overflow quantity of the overflow valve carries the residual flow, i. H. the amount of fuel that is not supplied by the metering unit
- Main pump is forwarded back to the suction side of the pre-pump.
- the metering unit is advantageously designed as a proportional slide valve.
- the main feed pump is designed as a high-pressure pump, in particular as a multi-cylinder radial piston eccentric pump.
- a radial piston pump has a drive shaft which is rotatably mounted about its longitudinal axis in a pump housing of the pump.
- the drive shaft is eccentric or provided with cam-like elevations in the circumferential direction.
- the radial piston pump has a plurality of pump cylinders arranged radially with respect to the drive shaft.
- Pump cylinder delimits a pump chamber in which a piston is guided so that it can move back and forth.
- the pistons are moved back and forth in the pump chambers by turning the drive shaft.
- the pump arrangement according to the invention preferably delivers the fuel into a storage volume of a common rail injection system.
- a common rail injection system is used to supply fuel to internal combustion engines.
- the injection nozzles in common-rail injection systems are fed from a common storage volume, which is also referred to as a common distributor rail.
- common rail injection systems in particular, the advantages of the pump arrangement according to the invention are particularly evident since the production costs for common rail injection systems are reduced and the reliability of these injection systems can be decisively improved by using the pump arrangement according to the invention.
- the main pump and the pre-pump are combined to form an integral pump assembly.
- the Pump assembly is externally connected to the tank via the fuel line and a return for the lubrication flow and for ventilation and to the storage volume of the common rail injection system via a high pressure line.
- the connections required for the connections to the tank and the storage volume of the common rail injection system can all be routed to a common flange to the outside, where they can then be connected particularly easily to the corresponding connecting lines.
- the integral pump assembly can be made particularly small.
- Figure 1 is a schematic representation of a pump arrangement according to the invention according to a preferred embodiment.
- FIG. 2 shows a pump assembly according to the invention, partly in section.
- the pump arrangement shown in FIG. 1 is a pump arrangement for a common rail injection system for supplying fuel to gasoline and diesel engines.
- the fuel is supplied to the individual combustion chambers via separate lines
- common rail injection systems
- common manifold common manifold
- the pump arrangement shown schematically in FIG. 1 is marked in their entirety with the reference number 1.
- the pump arrangement 1 has a main feed pump 2 and an upstream feed pump 3.
- the preliminary pump 3 delivers fuel from a tank 5 via a fuel line 4.
- a fuel filter 6 is arranged in the fuel line 4, via which the fuel delivered by the feed pump 3 is guided.
- the total fuel flow delivered by the pre-delivery pump 3 is delivered by a drive / crank chamber 2a of the main delivery pump 2. In the flow direction 7 of the
- a return 9 is provided after the drive / crank chamber 2a, via which a lubricating flow to the tank 5, and a further return 8 is provided, via which a ventilation flow can flow back to the tank 5.
- a return 8 is one
- Venting throttle 10 and a throttle 11 and a check valve 12 are arranged in the return 9. Also after the drive / crank chamber 2a, a delivery run 13 is provided for a delivery flow to a metering unit 14 and further to the main pump 2.
- the metering unit 14 is designed as a proportional slide valve.
- the preliminary pump 3 is designed as a mechanically driven gear pump.
- the main pump 2 is designed as a high-pressure pump, in particular as a multi-cylinder radial piston eccentric pump.
- the radial piston pump shown only symbolically in FIG. 1 comprises a drive shaft 2b, which is eccentric or has cam-like elevations in the circumferential direction (cf. FIG. 2).
- the radial piston pump comprises a plurality of pump cylinders 2c arranged radially with respect to the drive shaft 2b, each of which delimits a pump chamber 2e and only one of which is shown in FIG.
- a piston 2d is guided in a reciprocating manner in the pump cylinder 2c.
- the pistons 2d of the radial piston pump are turned by rotating the drive shaft 2b in the respective Pump cylinder 2c reciprocated.
- the delivery flow is sucked into the pump chamber 2 ⁇ in a so-called suction stroke via a check valve 17, and in a subsequent delivery stroke the fuel located in the pump chamber 2e is compressed and via a high-pressure line 15 in the A check valve 16 is arranged, conveyed to a high-pressure storage volume, not shown, of a common rail injection system.
- a zero delivery run 18 branches off between the metering unit 14 and the main delivery pump 2, in which a zero delivery throttle 19 is arranged.
- the zero conveyor trolley 18 opens in the flow direction 7 of the Alterkraf material stream before Vorforderpumpe 3, ie, on the suction side of the Vorforderpumpe 3, the 'fuel line. 4
- An overflow run 20 branches off from the conveying run 13 in front of the metering unit 14, in which an overflow valve 21 is arranged.
- the overflow run 20 opens in the flow direction 7 of the total fuel flow upstream of the preliminary pump 3, i.e. on the suction side of the preliminary pump 3, into the fuel line 4.
- the pressure of the overflow valve 21 in the drive / crank chamber 2a is approximately 6 bar.
- the pressure of the overflow valve 21 is chosen so high that the lubricating flow through the drive / crank chamber 2a of the main pump 2 is constant and large enough to ensure good lubrication of the drive shaft 2b and good heat dissipation from the drive shaft 2b.
- the pressure of the overflow valve 21 must be chosen so large that the lubrication of the Slider bearing in the drive / crank chamber 2a.
- the overflow valve 21 in the pump arrangement 1 according to the invention replaces the one used in the pump arrangements known from the prior art, much more complex and correspondingly more expensive cascade overflow valve.
- FIG. 2 shows the pump arrangement 1 according to the invention partially in section.
- the pump arrangement 1 has a pump housing 22 in which the main feed pump 2 and the feed pump 3 are combined to form an integral pump assembly.
- the drive shaft 2b of the main pump 2 is guided into the pump housing 22 from the outside.
- the drive shaft 2b rotates about its longitudinal axis 23 in the drive / crank chamber 2a, which is formed in the pump housing 22.
- the drive / crank chamber 2a is sealed off from the outside by a shaft sealing ring 24 to the pump housing 22.
- the total fuel flow, seen in the longitudinal direction of the drive shaft 2b flows approximately centrally into the drive / crank chamber 2a, so that in the
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP00940210A EP1190174B1 (de) | 1999-06-09 | 2000-05-24 | Pumpenanordnung zur förderung von kraftstoff |
US10/009,188 US6722857B1 (en) | 1999-06-09 | 2000-05-24 | Pump assembly for fuel |
DE50008130T DE50008130D1 (de) | 1999-06-09 | 2000-05-24 | Pumpenanordnung zur förderung von kraftstoff |
JP2001503420A JP4662668B2 (ja) | 1999-06-09 | 2000-05-24 | 燃料のためのポンプ装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19926308.6 | 1999-06-09 | ||
DE19926308A DE19926308A1 (de) | 1999-06-09 | 1999-06-09 | Pumpenanordnung für Kraftstoff |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000077389A1 true WO2000077389A1 (de) | 2000-12-21 |
Family
ID=7910682
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2000/001672 WO2000077389A1 (de) | 1999-06-09 | 2000-05-24 | Pumpenanordnung zur förderung von kraftstoff |
Country Status (5)
Country | Link |
---|---|
US (1) | US6722857B1 (de) |
EP (1) | EP1190174B1 (de) |
JP (1) | JP4662668B2 (de) |
DE (2) | DE19926308A1 (de) |
WO (1) | WO2000077389A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006134002A1 (de) * | 2005-06-16 | 2006-12-21 | Robert Bosch Gmbh | Kraftstoffeinspritzsystem für eine brennkraftmaschine |
Families Citing this family (29)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10139054C1 (de) | 2001-08-08 | 2003-01-30 | Bosch Gmbh Robert | Verfahren, Computerprogramm, Steuer- und/oder Regelgerät sowie Kraftstoffsystem für eine Brennkraftmaschine, insbesondere mit Direkteinspritzung |
DE10139052B4 (de) | 2001-08-08 | 2004-09-02 | Robert Bosch Gmbh | Verfahren zum Betreiben einer Brennkraftmaschine, insbesondere mit Direkteinspritzung, Computerprogramm, Steuer- und/oder Regelgerät, sowie Kraftstoffsystem für eine Brennkraftmaschine |
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 |
DE10237592A1 (de) | 2002-08-16 | 2004-03-11 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
DE10307877A1 (de) * | 2003-02-25 | 2004-09-02 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
JP3915718B2 (ja) * | 2003-03-11 | 2007-05-16 | 株式会社デンソー | 燃料供給ポンプ |
JP3851287B2 (ja) * | 2003-03-19 | 2006-11-29 | ボッシュ株式会社 | 内燃機関用の燃料噴射装置 |
DE102005033638A1 (de) * | 2005-07-19 | 2007-01-25 | Robert Bosch Gmbh | Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine |
DE102009001563A1 (de) * | 2009-03-16 | 2010-09-23 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102009003051A1 (de) * | 2009-05-13 | 2010-11-18 | Robert Bosch Gmbh | Verfahren zum Befüllen eines Kraftstoffsystems für Kraftfahrzeuge |
DE102009027335A1 (de) | 2009-06-30 | 2011-01-05 | Robert Bosch Gmbh | Kraftstoffsystem für eine Brennkraftmaschine |
DE102009028440A1 (de) | 2009-08-11 | 2011-02-17 | Robert Bosch Gmbh | Kraftstoff-Fördereinrichtung für eine Brennkraftmaschine |
DE102010042587A1 (de) * | 2010-10-18 | 2012-04-19 | Robert Bosch Gmbh | Kraftstoffpumpe für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine |
DE102010043283A1 (de) | 2010-11-03 | 2012-05-03 | Robert Bosch Gmbh | Niederdruckkreislauf für ein Kraftstoffeinspritzsystem sowie Kraftstoffeinspritzsystem |
WO2012069046A1 (de) * | 2010-11-24 | 2012-05-31 | Ixetic Bad Homburg Gmbh | Radialkolbenpumpe |
DE102010064374B3 (de) * | 2010-12-30 | 2012-07-12 | Continental Automotive Gmbh | Kraftstoffeinspritzsystem einer Brennkraftmaschine sowie dazugehöriges Druckregelverfahren, Steuergerät und Kraftfahrzeug |
DE102012207431A1 (de) * | 2012-05-04 | 2013-11-07 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe |
DE102012212062A1 (de) * | 2012-07-11 | 2014-01-16 | Robert Bosch Gmbh | Niederdruckkreislauf für ein Kraftstoffeinspritzsystem, Kraftstoffeinspritzsystem sowie Verfahren zum Betreiben eines Kraftstoffeinspritzsystems |
AT513154B1 (de) * | 2012-09-17 | 2014-02-15 | Bosch Gmbh Robert | Niederdruckkreislauf für ein Kraftstoffeinspritzsystem |
DE102012224408A1 (de) * | 2012-12-27 | 2014-07-17 | Robert Bosch Gmbh | Kraftstoffeinspritzsystem |
DE102013210036A1 (de) * | 2013-05-29 | 2014-12-04 | Robert Bosch Gmbh | Hochdruckpumpe für ein Kraftstoffeinspritzsystem |
GB201508464D0 (en) * | 2015-05-18 | 2015-07-01 | Delphi Int Operations Lux Srl | Pump assembly for a fuel injection system |
CN106246424B (zh) * | 2016-08-29 | 2019-07-30 | 潍柴动力股份有限公司 | 高压油泵、发动机燃油系统及发动机 |
JP2018155221A (ja) * | 2017-03-21 | 2018-10-04 | いすゞ自動車株式会社 | 内燃機関の燃料噴射装置 |
DE102018108406A1 (de) | 2017-06-22 | 2018-12-27 | Denso Corporation | Hochdruckkraftstoffpumpe und Kraftstoffversorgungssystem |
JP6988352B2 (ja) | 2017-10-11 | 2022-01-05 | 株式会社デンソー | 燃料ポンプ |
DE102018103252B4 (de) * | 2018-02-14 | 2022-01-20 | Danfoss Power Solutions Gmbh & Co. Ohg | Verfahren und Vorrichtung zur Entlüftung der Ansaugseite einer künstlich kommutierten Hydraulikpumpe |
US11846246B2 (en) * | 2021-05-27 | 2023-12-19 | Thermo King Llc | Methods and systems for controlling engine inlet pressure via a fuel delivery system of a transport climate control system |
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DE2551826A1 (de) * | 1975-11-19 | 1977-05-26 | Teves Gmbh Alfred | Kolbenpumpe |
DE3504265A1 (de) * | 1985-02-08 | 1986-08-14 | M.A.N.-B & W Diesel GmbH, 8900 Augsburg | Kraftstoffhochdruck-einspritzvorrichtung an brennkraftmaschinen |
US5626114A (en) * | 1994-12-07 | 1997-05-06 | Zexel Corporation | Fuel pump for high-pressure fuel injection system |
DE19827926A1 (de) * | 1997-06-24 | 1999-01-07 | Unisia Jecs Corp | Kraftstoffpumpe |
DE19742180A1 (de) * | 1997-09-24 | 1999-03-25 | Siemens Ag | Einspritzsystem für eine Brennkraftmaschine und Verfahren zum Regeln eines Einspritzsystems |
DE19801355A1 (de) * | 1998-01-16 | 1999-07-29 | Bosch Gmbh Robert | Hochdruckpumpe zur Kraftstoffversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen |
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DE2648043C2 (de) * | 1976-10-23 | 1984-05-24 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe für Brennkraftmaschinen |
CH674243A5 (de) * | 1987-07-08 | 1990-05-15 | Dereco Dieselmotoren Forschung | |
US5325837A (en) * | 1992-11-19 | 1994-07-05 | Robert Bosch Gmbh | Fuel injection apparatus for internal combustion engines |
JPH06257529A (ja) * | 1993-02-18 | 1994-09-13 | Robert Bosch Gmbh | 内燃機関用の燃料噴射装置 |
JP3435770B2 (ja) * | 1993-12-03 | 2003-08-11 | 株式会社デンソー | 高圧燃料噴射装置 |
JP3939779B2 (ja) * | 1995-05-26 | 2007-07-04 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | 内燃機関の燃料供給のための燃料供給装置 |
DE19630938C5 (de) * | 1996-07-31 | 2008-02-14 | Siemens Ag | Kraftstoffzuleitung mit einem Volumenstromregelventil und Volumenstromregelventil |
DE19648690A1 (de) * | 1996-11-25 | 1998-05-28 | Bosch Gmbh Robert | Kraftstoffeinspritzsystem |
IT1289796B1 (it) * | 1996-12-23 | 1998-10-16 | Elasis Sistema Ricerca Fiat | Perfezionamenti ad un dispositivo a pompa per l'alimentazione del carburante da un serbatoio ad un motore a combustione interna. |
DE19736160A1 (de) * | 1997-08-20 | 1999-02-25 | Bosch Gmbh Robert | Pumpenanordnung zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen |
DE19746563A1 (de) * | 1997-10-22 | 1999-04-29 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen |
JPH11200990A (ja) * | 1998-01-07 | 1999-07-27 | Unisia Jecs Corp | 燃料噴射制御装置 |
-
1999
- 1999-06-09 DE DE19926308A patent/DE19926308A1/de not_active Ceased
-
2000
- 2000-05-24 DE DE50008130T patent/DE50008130D1/de not_active Expired - Lifetime
- 2000-05-24 US US10/009,188 patent/US6722857B1/en not_active Expired - Fee Related
- 2000-05-24 JP JP2001503420A patent/JP4662668B2/ja not_active Expired - Fee Related
- 2000-05-24 EP EP00940210A patent/EP1190174B1/de not_active Expired - Lifetime
- 2000-05-24 WO PCT/DE2000/001672 patent/WO2000077389A1/de active IP Right Grant
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE2551826A1 (de) * | 1975-11-19 | 1977-05-26 | Teves Gmbh Alfred | Kolbenpumpe |
DE3504265A1 (de) * | 1985-02-08 | 1986-08-14 | M.A.N.-B & W Diesel GmbH, 8900 Augsburg | Kraftstoffhochdruck-einspritzvorrichtung an brennkraftmaschinen |
US5626114A (en) * | 1994-12-07 | 1997-05-06 | Zexel Corporation | Fuel pump for high-pressure fuel injection system |
DE19827926A1 (de) * | 1997-06-24 | 1999-01-07 | Unisia Jecs Corp | Kraftstoffpumpe |
DE19742180A1 (de) * | 1997-09-24 | 1999-03-25 | Siemens Ag | Einspritzsystem für eine Brennkraftmaschine und Verfahren zum Regeln eines Einspritzsystems |
DE19801355A1 (de) * | 1998-01-16 | 1999-07-29 | Bosch Gmbh Robert | Hochdruckpumpe zur Kraftstoffversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006134002A1 (de) * | 2005-06-16 | 2006-12-21 | Robert Bosch Gmbh | Kraftstoffeinspritzsystem für eine brennkraftmaschine |
KR101046851B1 (ko) * | 2005-06-16 | 2011-07-06 | 로베르트 보쉬 게엠베하 | 엔진용 연료 분사 시스템 |
US8371267B2 (en) | 2005-06-16 | 2013-02-12 | Robert Bosch Gmbh | Fuel injection system for an internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
DE19926308A1 (de) | 2000-12-21 |
JP2003502542A (ja) | 2003-01-21 |
JP4662668B2 (ja) | 2011-03-30 |
EP1190174A1 (de) | 2002-03-27 |
DE50008130D1 (de) | 2004-11-11 |
US6722857B1 (en) | 2004-04-20 |
EP1190174B1 (de) | 2004-10-06 |
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