EP1561028B1 - Pompe haute pression d'alimentation en carburant comprenant un clapet a bille dans l'admission basse pression - Google Patents

Pompe haute pression d'alimentation en carburant comprenant un clapet a bille dans l'admission basse pression Download PDF

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Publication number
EP1561028B1
EP1561028B1 EP03779679A EP03779679A EP1561028B1 EP 1561028 B1 EP1561028 B1 EP 1561028B1 EP 03779679 A EP03779679 A EP 03779679A EP 03779679 A EP03779679 A EP 03779679A EP 1561028 B1 EP1561028 B1 EP 1561028B1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel pump
ball
pressure fuel
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
Application number
EP03779679A
Other languages
German (de)
English (en)
Other versions
EP1561028A1 (fr
Inventor
Burkhard Boos
Stefan Kieferle
Matthias Distel
Achim Koehler
Sascha Ambrock
Karsten Ruth
Jaroslav Zivny
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
Priority claimed from DE10302043A external-priority patent/DE10302043A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1561028A1 publication Critical patent/EP1561028A1/fr
Application granted granted Critical
Publication of EP1561028B1 publication Critical patent/EP1561028B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1002—Ball 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/08—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by two or more pumping elements with conjoint outlet or several pumping elements feeding one engine cylinder
    • 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
    • F02M59/464—Inlet valves of the check valve type
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves

Definitions

  • the invention is based on one of the German patent DE 101 17 600 known high-pressure fuel pump for a fuel injection system having a housing, with a low-pressure inlet, with a delivery chamber in which the fuel is compressed, with a suction valve between the delivery chamber and low-pressure inlet, wherein a valve member of the suction valve is supported against a pressure spring arranged in the delivery chamber.
  • valve member of the suction valve is designed as a valve cone.
  • a high-pressure fuel pump according to the invention with the features of claim 1 has a small number of acted upon by high pressure sealing surfaces, so that inter alia, the number of components compared to the known from the prior art high-pressure fuel pump is reduced. This increases the reliability of the high-pressure fuel pump according to the invention and reduces the manufacturing and assembly costs of the same.
  • the production of the high-pressure fuel pump is simplified because a ball is cheaper to manufacture than a valve member with a sealing cone and a shaft, as is known in the prior art.
  • the efficiency of the high-pressure fuel pump according to the invention is improved because a ball forms a well-defined circular sealing line together with the sealing seat, which seals very well despite the unavoidable manufacturing tolerances in the manufacture of the valve seat with respect to the valve seat.
  • the suction valve according to the invention seals well, even if the angle or the position of the valve seat were not manufactured with the highest precision.
  • a spring plate is arranged between the compression spring and ball, so that the fixation of the ball is improved relative to the sealing seat and also a buckling of the compression spring is avoided.
  • the use of a spring plate allows that the diameter of compression spring and ball can be different. It has become especially as proven advantageous when the diameter of the ball is smaller than the diameter of the compression spring, since in this case the buckling of the compression spring is effectively avoided and the diameter of the ball corresponds to the hydraulic requirements of the high-pressure fuel pump in an optimal manner.
  • valve seat has a seat angle between 30 ° and 150 °, in particular between 80 ° and 100 °.
  • FIG. 1 shows an embodiment of a high-pressure fuel pump 10 according to the invention in cross section.
  • the high-pressure fuel pump 10 is designed as a radial piston pump with three pump elements 11.
  • the pump elements 11 comprise a piston 13, which is guided in a cylinder bore 15.
  • the cylinder bore 15 is executed in a housing 17 of the high-pressure fuel pump 10 as a blind hole.
  • the cylinder bore 15 can be made. After assembly of the high-pressure fuel pump according to the invention, the mounting holes 19 are closed by plugs 21.
  • the pistons 13 are driven by a drive shaft with an eccentric portion 22 via a polygon ring 23 with flats 25.
  • a Kolbenfußplatte 27 On the flats 25 is a Kolbenfußplatte 27, which puts the piston 13 in an oscillating motion when the drive shaft is driven and the polygon ring 23rd as a result performs a circular motion.
  • the oscillating movement of the pistons 13 is indicated in one of the pump element 11 by a double arrow 29.
  • the cylinder bore 15 and the piston 13 define a delivery chamber 31 per pump element 11, wherein the volume of the delivery chamber 31 depends on the position of the drive shaft.
  • the piston 13 is near its top dead center (TDC), the volume of the delivery chamber 31 is minimal, while it is at the other pump elements 11th has almost a maximum.
  • TDC top dead center
  • the Kolbenfußplatten 27 and with her the piston 13 are always held in contact with the flats 25 of the polygon ring 23.
  • the cylinder bore 15 is, as already mentioned, designed as a blind hole.
  • a suction valve 35 with a sealing seat 37 and a cooperating with the sealing seat 37 ball 39 is provided at the end of the cylinder bore 15.
  • the ball 39 is pressed against the valve seat 37 via a spring plate 41 by a compression spring 43 which is supported on the piston 13 at the other end.
  • the compression spring 43 is dimensioned so that fuel is not sucked in the lower dead center automatically. If a not shown, arranged on the suction side of the high-pressure fuel pump 10 metering unit is closed, the high-pressure fuel pump 10 promotes no fuel. When the metering unit is fully or partially opened, a positive pressure generated by a prefeed pump (not shown) builds up in front of the suction valve 35 and is pressed by the fuel against the compression spring 43 into the delivery chamber 31. The metering unit has the task to adjust the pressure in front of the suction chamber so that the desired flow rate is promoted by the high-pressure fuel pump 10.
  • the compression spring 43 can also be dimensioned so that the ball 39 is still slightly pressed against the sealing seat 37 in the bottom dead center (UT) of the piston 13. Only if on the in Fig. 1 not shown low pressure side of the high-pressure fuel pump 10, a sufficient pressure over the pressure prevails in the delivery chamber 31, fuel flows into the delivery chamber 31 a.
  • the pressure on the low pressure side of the high-pressure fuel pump 10, or the suction side of the delivery chamber 31 and thus the delivery rate of the high-pressure fuel pump 10 is characterized by a in Fig. 1 Not shown metering unit of a control unit (not shown) set depending on the operating condition of the internal combustion engine.
  • each of the pump element 11 draws approximately the same amount of fuel and thus a uniform torque and power consumption of the high-pressure fuel pump 10th results. This improves the smoothness of the internal combustion engine, especially at idle.
  • a high-pressure outlet and the associated pressure valve are in FIG. 1 not shown, since the high-pressure outlet and the associated pressure valve are arranged perpendicular to the plane of the drawing behind the pump elements 11.
  • the arrangement of these components can from the DE-PS 101 17 600 , which is incorporated herein by reference.
  • the leadership of the ball 39 is improved.
  • the diameter of the ball 39 can be selected independently of the diameter of the compression spring 43, which may be advantageous in the optimization of the high-pressure fuel pump 10.
  • Fig. 1 illustrated embodiment of a high-pressure fuel pump 10 according to the invention
  • This small number of high pressure sealing points justifies in many cases the slightly higher production cost in the production of the cylinder bore 15, if this is designed as a blind hole.
  • FIG. 2 is one of the post-published EP 1 357 283 A2 known high-pressure pump 10 also shown in section.
  • the same components are provided with the same reference numerals and it is the respect FIG. 1 Said accordingly.
  • the essential difference from the first embodiment is that the cylinder bore 15 is not designed as a blind hole, but as a through hole.
  • the cylinder bore 15 is closed by a screw 47.
  • the sealing seat 37 of the suction valve 35 is incorporated.
  • FIG. 3 which shows an enlarged detail A of the FIG. 2 shows the function of the suction valve 35 explained in detail.
  • the piston 13 is at top dead center. Accordingly, the delivery chamber 31 has its minimum volume and the ball 39 seals the delivery chamber 31 against the low-pressure inlet 45 of the high-pressure fuel pump 10 from. This sealing takes place along a circular sealing line (not shown), which results from the contact line between the ball 39 and the sealing seat 37.
  • the tightness of this trained as a ball valve suction valve 35 is very high, since there is only a linear contact between the ball 39 and sealing seat 37, resulting in a correspondingly high surface pressure on the sealing line.
  • the accuracy requirements in the production of a tightly closing ball valve are lower than with cone valves.
  • the diameter of the sealing line between the ball 39 and the sealing seat 37 can be varied with a constant ball diameter. It has been found that sealing angle ⁇ between 30 ° and 150 ° are possible and usually a sealing angle ⁇ of 90 ° leads to very good results.
  • the sealing seat 37 is adjoined by an axial bore 48 and a transverse bore 49.
  • a plurality of transverse bores 49 may be provided.
  • the transverse bore 49 opens into an annular space 50, which is bounded by the housing 17 and a reduced diameter portion 50 of the screw 47.
  • a biting edge 53 is formed, which seals the annular space 51 from the delivery chamber 31.
  • the annular space 51 communicates hydraulically with the low-pressure inlet 45, which is not visible in this illustration, of the high-pressure fuel pump 10. Because the annular space surrounds the screw 47 on all sides, fuel can be drawn into the delivery chamber 31 via the transverse bore 49 and the axial bore 48, regardless of how deep the screw 47 was screwed into the housing 17.
  • the efficiency of the high-pressure fuel pump is increased because the ball 39 releases a large flow area as soon as it lifts off the sealing seat 37, so that the fuel can be sucked in quickly and without large flow losses.
  • the annular cross-sectional area between the sealing seat 37 and the ball 39 is approximately up to 20 times greater than the cross-section of the transverse bore 49.
  • an internal combustion engine 54 is shown schematically. It comprises a fuel injection system 56. This in turn has a fuel tank 58, from which a low-pressure electric fuel pump 60 delivers fuel.
  • the low-pressure electric fuel pump 60 delivers fuel to the high-pressure fuel pump 10, which is formed as in the FIGS. 1 and 2 shown.
  • the high pressure outlet 18 of the high pressure fuel pump 10 is connected to a fuel rail 62. This is generally referred to as "common rail”.
  • a total of four injectors 64 are connected to the fuel manifold 62 . These each inject the fuel directly into combustion chambers 66 of the internal combustion engine 54.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Check Valves (AREA)

Abstract

L'invention concerne une pompe haute pression d'alimentation en carburant (10), notamment une pompe à pistons radiaux, dans laquelle les soupapes d'aspiration (35) sont réalisées sous forme de clapets à bille, ce qui a un effet avantageux sur le rendement de la pompe haute pression d'alimentation en carburant (10). L'utilisation de clapets à bille facilite en outre la production et le montage de la pompe haute pression d'alimentation en carburant (10) selon l'invention.

Claims (6)

  1. Pompe haute pression de carburant (10) d'une installation d'alimentation en carburant (56) comportant un boitier (17), une entrée basse pression (45), une chambre de refoulement (31) dans laquelle le carburant est comprimé par un piston oscillant (13), une soupape d'aspiration (35) entre la chambre de refoulement (31) et l'entrée basse pression (45), un organe de soupape de la soupape d'aspiration (35) s'appuyant par un ressort de compression (43) installé dans la chambre de refoulement (31) contre le piston (13) ainsi qu'une sortie haute pression,
    l'organe de la soupape d'aspiration (35) étant réalisé sous la forme d'une bille (39),
    caractérisée en ce que
    le boîtier (17) comporte un siège d'étanchéité (37), usiné, coopérant avec la bille (39).
  2. Pompe à haute pression de carburant selon la revendication 1,
    caractérisée par
    une coupelle à ressort (41) installée entre le ressort de compression (43) et la bille (39).
  3. Pompe à haute pression de carburant selon la revendication 1 ou 2,
    caractérisée en ce que
    le diamètre de la bille (39) est inférieur au diamètre du ressort de compression (43).
  4. Pompe à haute pression de carburant selon l'une des revendications précédentes,
    caractérisée en ce que
    le siège d'étanchéité (37) présente un angle de siège (α) compris entre 30° et 150° et notamment égal à 90°.
  5. Installation d'injection de carburant (56) comportant un réservoir à carburant (58), au moins un injecteur de carburant (64) qui injecte le carburant directement dans la chambre de combustion (66) d'un moteur à combustion interne (54), au moins une pompe à carburant haute pression (10) et une conduite collectrice de carburant (62) à laquelle est raccordé au moins un injecteur de carburant (64),
    caractérisée en ce que
    la pompe haute pression de carburant (10) est réalisée selon l'une des revendications précédentes.
  6. Moteur à combustion interne (54) comportant au moins une chambre de combustion (66) dans laquelle on injecte directement le carburant,
    caractérisé en ce qu'
    il comporte une installation d'injection de carburant (56) selon la revendication 5.
EP03779679A 2002-10-31 2003-10-31 Pompe haute pression d'alimentation en carburant comprenant un clapet a bille dans l'admission basse pression Expired - Lifetime EP1561028B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10250661 2002-10-31
DE10250661 2002-10-31
DE10302043A DE10302043A1 (de) 2002-10-31 2003-01-21 Kraftstoffhochdruckpumpe mit Kugelventil im Niederdruck-Einlass
DE10302043 2003-01-21
PCT/DE2003/003627 WO2004040128A1 (fr) 2002-10-31 2003-10-31 Pompe haute pression d'alimentation en carburant comprenant un clapet a bille dans l'admission basse pression

Publications (2)

Publication Number Publication Date
EP1561028A1 EP1561028A1 (fr) 2005-08-10
EP1561028B1 true EP1561028B1 (fr) 2008-07-23

Family

ID=32231867

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03779679A Expired - Lifetime EP1561028B1 (fr) 2002-10-31 2003-10-31 Pompe haute pression d'alimentation en carburant comprenant un clapet a bille dans l'admission basse pression

Country Status (4)

Country Link
US (1) US7273036B2 (fr)
EP (1) EP1561028B1 (fr)
JP (1) JP2006504904A (fr)
WO (1) WO2004040128A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT501668B1 (de) * 2004-08-24 2007-03-15 Bosch Gmbh Robert Steuerventil für eine einspritzdüse
JP4650629B2 (ja) * 2004-11-16 2011-03-16 株式会社アドヴィックス ラジアルプランジャポンプ
JP2006242019A (ja) * 2005-03-01 2006-09-14 Jtekt Corp 燃料ポンプ用チェック弁
DE102007016134A1 (de) * 2006-04-25 2007-11-08 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
AT503697B1 (de) * 2006-06-02 2008-06-15 Bosch Gmbh Robert Pumpenelement für eine hochdruckpumpe
EP1878918B1 (fr) * 2006-07-14 2009-06-24 Robert Bosch Gmbh Pompe à piston pour haute pression pour injecter du carburant dans un moteur à combustion interne
DE102007004605B4 (de) * 2007-01-30 2009-08-13 Continental Automotive Gmbh Hochdruckpumpe und Einspritzanlage für eine Brennkraftmaschine mit einer Hochdruckpumpe
DE102008043993B3 (de) * 2008-11-21 2010-04-29 Thielert Aircraft Engines Gmbh Common-Rail-Hochdruckpumpe
DE102010041310A1 (de) * 2010-09-24 2012-03-29 Robert Bosch Gmbh Pumpe und Verfahren zu deren Herstellung
EP2543812B1 (fr) * 2011-07-08 2014-11-05 Welltec A/S Pompe hydraulique de fond de trou
ITMI20130023A1 (it) * 2013-01-09 2014-07-10 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
US9470320B1 (en) 2013-06-03 2016-10-18 Kelso Technologies Inc. Ball valve assembly
GB201503556D0 (en) * 2015-03-03 2015-04-15 Delphi International Operations Luxembourg S.�.R.L. High temperature fuel deflector for a fuel pump drive assembly
ITUA20161817A1 (it) * 2016-03-18 2017-09-18 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
WO2019161259A1 (fr) * 2018-02-15 2019-08-22 Jacobsen Innovations, Inc. Système hydraulique numérique

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3682572A (en) * 1970-07-27 1972-08-08 Donald L Yarger Piston type pump
DE4027794C2 (de) * 1990-09-01 2002-06-20 Continental Teves Ag & Co Ohg Hydraulische Radialkolbenpumpe
DE4307651C2 (de) 1993-03-11 1996-05-09 Hatz Motoren Verbrennungsmotor mit Kraftstoffeinspritzung, insbesondere Einzylinder-Dieselmotor
DE19523283B4 (de) * 1995-06-27 2006-01-19 Robert Bosch Gmbh Pumpe, insbesondere Hochdruckpumpe für eine Kraftstoffeinspritzvorrichtung eines Verbrennungsmotors
EP0979353B1 (fr) 1998-02-27 2004-09-29 Stanadyne Corporation Pompe d'alimentation pour rampe d'alimentation en essence
US6694950B2 (en) * 1999-02-17 2004-02-24 Stanadyne Corporation Hybrid control method for fuel pump using intermittent recirculation at low and high engine speeds
DE19924774A1 (de) * 1999-05-29 2000-11-30 Bosch Gmbh Robert Kolbenpumpe
JP3924999B2 (ja) 1999-08-12 2007-06-06 株式会社日立製作所 燃料ポンプ及びそれを用いた筒内噴射エンジン
DE10015295A1 (de) * 2000-03-28 2001-10-04 Bosch Gmbh Robert Kolbenpumpe
DE10057244A1 (de) * 2000-11-18 2002-06-06 Bosch Gmbh Robert Kraftstoffeinspritzanlage für Brennkraftmaschinen mit verbessertem Startverhalten
DE10117600C1 (de) 2001-04-07 2002-08-22 Bosch Gmbh Robert Hochdruck-Kraftstoffpumpe für ein Kraftstoffsystem einer direkteinspritzenden Brennkraftmaschine, Kraftstoffsystem sowie Brennkraftmaschine
US6764286B2 (en) * 2001-10-29 2004-07-20 Kelsey-Hayes Company Piston pump with pump inlet check valve
WO2003048564A1 (fr) 2001-12-01 2003-06-12 Robert Bosch Gmbh Pompe a piston radiaux a graissage force
DE10218022A1 (de) 2002-04-23 2003-11-06 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Also Published As

Publication number Publication date
US7273036B2 (en) 2007-09-25
EP1561028A1 (fr) 2005-08-10
WO2004040128A1 (fr) 2004-05-13
US20060013701A1 (en) 2006-01-19
JP2006504904A (ja) 2006-02-09

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