EP1798415B1 - Pompe à haute pression - Google Patents

Pompe à haute pression Download PDF

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Publication number
EP1798415B1
EP1798415B1 EP20060123976 EP06123976A EP1798415B1 EP 1798415 B1 EP1798415 B1 EP 1798415B1 EP 20060123976 EP20060123976 EP 20060123976 EP 06123976 A EP06123976 A EP 06123976A EP 1798415 B1 EP1798415 B1 EP 1798415B1
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
pump
high pressure
space
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 - Fee Related
Application number
EP20060123976
Other languages
German (de)
English (en)
Other versions
EP1798415A1 (fr
Inventor
Ngoc-Tam Vu
Thomas Grossner
Christoph Klesse
Matthias Knüppe
Thomas Riedel
Christian Taudt
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.)
Continental Automotive GmbH
Original Assignee
Continental Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of EP1798415A1 publication Critical patent/EP1798415A1/fr
Application granted granted Critical
Publication of EP1798415B1 publication Critical patent/EP1798415B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04B1/0408—Pistons
    • 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
    • F04B1/0421—Cylinders
    • 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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • 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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/107—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring

Definitions

  • the invention relates to a high-pressure pump.
  • High-pressure pumps are subject to heavy loads when exposed to pressures of, for example, 2000 bar. Such comparatively high pressures make both high demands on the material of the high-pressure pump and on their construction. At the same time large forces must be absorbed by such high-pressure pumps.
  • GB 301,821 discloses a high-pressure compressor having the structural features as defined in the preamble of claim 1, and in which power is transmitted from a drive unit to the compressor piston via a piston unit interposed therebetween.
  • the EP 0 400 693 A2 discloses a high-pressure pump in which the pressure generated by a drive device and at least one piston in a hydraulic fluid via transfer membranes on a pressurized fluid is transferable, each piston having two separation membranes are assigned.
  • the US Pat. No. 1,516,032 discloses a pump having a cylinder in which a piston is disposed at each end of the cylinder, and another piston is disposed between the two pistons, and at least two of the pistons are movable in the same direction.
  • the object of the invention is to provide a high-pressure pump, which is low even at high pump pressures Wear is subject to and allows reliable and accurate operation.
  • the invention is characterized by a high pressure pump with a pump housing and at least one pump unit with a cylinder chamber having a longitudinal axis in which a high-pressure piston is arranged axially movable.
  • the drive of the high-pressure pump via a drive shaft, the drive shaft is in operative connection with a first piston of the at least one pump unit and a pressure chamber of the at least one pump unit is acted upon by the first piston with a first pressure.
  • the pressure chamber is in operative connection with a second piston of the at least one pump unit, which in turn is in operative connection with the high-pressure piston stands.
  • the second piston has a surface facing the pressure chamber and delimiting the same
  • the high-pressure piston has a surface facing the cylinder chamber and delimiting it which is smaller than the surface facing the pressure chamber and the limiting surface
  • the first piston is relative to the second piston arranged so that the first piston and the second piston are movable in the same direction when used as intended.
  • the first piston is designed as a push cup.
  • the plunger cup has an annular end surface which forms a boundary surface of the pressure chamber.
  • the arrangement of the first piston relative to the second piston such that the first and the second piston when intended Insert are movable in the same direction is a simple and compact design of the high-pressure pump, in particular the at least one pump unit, possible.
  • the first piston is a push cup, a better guidance of the first piston in the pump housing can be achieved, in particular if parts of the push cup can be guided in the pump housing. Due to the design of the annular end face of the tappet cup as a boundary surface of the pressure chamber, a particularly space-saving arrangement of the tappet cup in the pump housing is possible, whereby in particular the overall length of the at least one pump unit can be reduced.
  • the first piston is arranged coaxially with the high-pressure piston. This can in particular represent a simplification of the production of the high pressure pump, since the holes for the cylinder chamber, the pressure chamber and other arranged in the pump housing chambers and chambers can be realized in one operation.
  • the pressure chamber is filled with a pressurized fluid, which can be zuchellbar via a pressure chamber inlet line, and the pressure chamber inlet line has a pressure chamber inlet valve.
  • the pressure chamber inlet valve is a volume flow control valve. This allows a particularly precise metering of pressurized fluid, which is necessary to compensate for a leakage of pressurized fluid. By a precise metering of pressurized fluid, a particularly uniform transfer behavior from the first piston to the second piston and the high-pressure piston can be achieved.
  • the pressure chamber inlet valve is a check valve.
  • This is a particularly simple and inexpensive type of valve, in which a reliable metering of pressure fluid for pressure fluid leakage compensation is possible and the backflow of pressurized fluid can be prevented in the pressure chamber inlet line.
  • the high-pressure pump is a radial piston pump with at least two pump units. With such a pump, particularly high injection pressures can be realized.
  • the high-pressure pump is a series piston pump with at least two pump units.
  • FIG. 1 shows a high-pressure pump 10 with a pump housing 12 and three pump units 13, 13a, 13b, which is arranged at an angle of 120 degrees to each other.
  • the high-pressure pump 10 has centrally a drive shaft 14, which is in operative connection with an eccentric ring 16 and is rotatably mounted in a rotational direction D in the pump housing 12 in the counterclockwise direction.
  • a camshaft can be used as the drive shaft 14.
  • the number of delivery and compression strokes on the number of cams can be specified.
  • the number of conveying or compression strokes corresponds to the number of cams.
  • the pump units 13, 13a, 13b are constructed identically. In the following, the pump unit 13 will also be described as representative of the other two pump units 13a, 13b.
  • the pump unit 13 consists essentially of a first piston 18, a second piston 24 and a high pressure piston 30, which are arranged coaxially with each other.
  • the second piston 24 and the high pressure piston 30 may be integrally formed as individual components or with each other.
  • a pressure chamber 22 is arranged, between the pump housing 12 and the second piston 24 on the side remote from the pressure chamber 22 side of the second piston 24, an intermediate chamber 26 is arranged, which is hydraulically coupled to the pressure chamber 22 , and on the
  • the cylinder chamber 32 has a preferably central longitudinal axis L, which forms the central longitudinal axis of the entire pump unit 13 in the embodiment shown here, the intermediate chamber 26 side facing away from the high-pressure piston 30.
  • the first piston 18 is mounted axially movable in a bore in the pump housing 12 and is in operative connection with the eccentric ring 16.
  • the first piston 18 is held by means of a first spring 20 in constant contact with the eccentric ring 16.
  • a second spring 28 is disposed in the intermediate chamber 26, which counteracts a compression stroke of the high-pressure piston 30.
  • the second spring 28 is preferably supported on the pump housing 12 and on the second piston 24.
  • the second spring 28 exerts a force on the second piston 24 and the high-pressure piston 30 connected to it, through which they can reach their starting position without the action of further forces.
  • cylinder chamber 32 In order to be able to fill the cylinder chamber 32 with fluid, it has a cylinder chamber inlet line 33, in which a cylinder chamber inlet valve 34 is preferably arranged.
  • the cylinder space inlet valve 34 facilitates the filling of the cylinder space 32 and prevents the backflow of the fluid from the cylinder space supply line 33 during filling.
  • the cylinder space 32 further has a cylinder space drain line 35 and a cylinder chamber arranged in this Cylinder space outlet 36 on. This fluid can be ejected from the cylinder chamber 32.
  • the first piston 18 is in operative connection with the pressure chamber 22.
  • the first piston 18 pressurizes the pressure chamber 22 with a first pressure P1.
  • the pressure chamber 22 is also in operative connection with the second piston 24.
  • the second piston 24 is acted upon by the pressure prevailing in the pressure chamber 22 and impressed by the first piston 18 first pressure P1. Due to the pressurization, the second piston 24 is moved out of its rest position in the same direction as the first piston 18 and thereby performs a stroke. Since the second piston 24 is in operative connection with the high-pressure piston 30, the high-pressure piston 30 also carries a stroke in the same direction as the first piston 18 and the second piston 24 and acts on the cylinder chamber 32 with a second pressure P2.
  • the second piston 24 has a pressure chamber 22 facing and this limiting surface 52.
  • the high-pressure piston 30 has a cylinder space 32 facing and this limiting surface 54. The latter is smaller than the pressure chamber 22 facing and this limiting surface 52 of the second piston 24th
  • the pressure chamber 22 is filled with a substantially incompressible pressure fluid.
  • a pressurized fluid is particularly suitable a lubricating oil.
  • a lubricating oil By using a lubricating oil, the moving parts of the high-pressure pump are simultaneously lubricated. An additional lubricant supply is thus not required, which simplifies the construction of the high-pressure pump. By lubricating the moving components, the friction is reduced, thereby significantly increasing the life of the high-pressure pump.
  • the pressure chamber 22 has a pressure chamber supply line 37.
  • a pressure chamber inlet valve 38 is arranged, which is preferably a check valve.
  • the designed as a check valve pressure chamber inlet valve 38 facilitates the filling of the pressure chamber 22 and prevents when filling the backflow of the pressurized fluid from the pressure chamber inlet line 37th
  • the intermediate chamber 26, which is hydraulically coupled to the pressure chamber 22, has a pressure chamber outlet line 39 and a pressure chamber outlet valve 40, which is preferably a check valve. This pressure fluid can be drained from the intermediate chamber 26 and the pressure chamber 22 hydraulically coupled with this if necessary.
  • the first piston 18, the second piston 24 and the high-pressure piston 30 should be in a position in the pump unit 13 in which they each have a minimum distance from the drive shaft 14.
  • the first piston 18 By a rotational movement of the drive shaft 14 in the direction of rotation D counterclockwise, the first piston 18 is axially moved away from the drive shaft 14 by the eccentric ring 16 and compressed in the pressure chamber 22 pressurized fluid to a first pressure P1.
  • the pressure P1 acts on the pressure chamber 22 facing and this limiting surface 52 of the second piston 24.
  • the second piston 24 is in operative connection with the intermediate chamber 26.
  • the cylinder chamber inlet valve 34 and the cylinder chamber outlet valve 36 are closed. By the movement of the high-pressure piston 30, a compression of the fluid located in the cylinder chamber 32 can take place.
  • the compressed fluid may be expelled after the compression stroke via the now open cylinder chamber outlet valve 36 and the cylinder chamber drain line 35.
  • the high-pressure pump is, for example, a high-pressure fuel pump of an injection system of an internal combustion engine, the fluid subjected to high pressure can reach a high-pressure fuel reservoir, the so-called common rail.
  • the pressure chamber outlet valve 40 is opened during the compression stroke and the pressure fluid located in the intermediate chamber 26 is pushed out via the pressure chamber drain line 39.
  • the first piston 18 is moved by the counterclockwise movement D of the drive shaft 14 by means of the eccentric ring 16 radially to the drive shaft 14 back.
  • the pressure chamber 22 is filled via the formed as a check valve pressure chamber inlet valve 38 and the pressure chamber inlet line 37 with pressurized fluid.
  • the high pressure piston 30 is moved together with the second piston 24 by the spring force of the second spring 28 in the same direction with the first piston 18 to the drive shaft 14 back.
  • the pistons 18, 24, 30 have now reached their initial state with a minimum distance to the drive shaft 14. Subsequently, a new stroke for compression of the media can take place again.
  • FIG. 2 a pump unit 13 of a second embodiment of the high-pressure pump is shown.
  • the first piston 18 is mounted axially movable, wherein the first piston 18 is formed as a push cup.
  • the first piston 18 designed as a push cup has a bottom portion 42 and an adjoining annular side wall portion 44.
  • the side wall portion 44 has in its upper region an annular end face 46 and the bottom portion 42 in its lower region an end face 50.
  • About the end face 50 of the bottom portion 42 of the first piston 18 of the first piston 18 is connected to a camshaft, not shown, or an eccentric ring, not shown in operative connection.
  • the first piston 18 by means of the first spring 20, which is arranged in the pressure chamber 22, held in constant contact with the camshaft or the eccentric ring.
  • the side wall portion 44 is guided in an annular gap 56 of the pump housing 12. In the side wall portion 44 of the first piston 18 seals 48 are introduced.
  • the designed as a push cup first piston 18 is connected via the annular end face 46, which forms a boundary surface of the pressure chamber 22, with the pressure chamber 22 in operative connection.
  • the pressure chamber 22 With the first pressure P1.
  • the pressure chamber 22 is in operative connection with the second piston 24, whereby it is acted upon by the pressure prevailing in the first pressure chamber 22 first pressure P1.
  • the second piston 24 can be moved out of its rest position in the same direction with the first piston 18 and execute a stroke.
  • the second piston 24 in turn is in operative connection with the high-pressure piston 30, so that the high-pressure piston 30 in the same direction with the first piston 18 and the second piston 24 perform a compression stroke and thus the cylinder chamber 32 can act on the second pressure P2.
  • the ratio of second pressure P2 to first pressure P1 again arises, as shown in detail for the first embodiment, from the ratio of the surface dimensions A1 and A2.
  • first piston 18 As a push cup with a boundary surface of the pressure chamber 22 forming annular end surface 46 and the space in the pump housing 12 space-saving pressure chamber 22 is a particularly space-saving design of the pump unit 13 and thus the entire high-pressure pump 10 is possible.
  • the second spring 28 is arranged, which counteracts the compression stroke of the high-pressure piston 30.
  • the second spring 28 ensures that the second piston 24 and the high-pressure piston 30 coupled to it return to its initial position following the compression stroke, which is characterized by the minimum distance of the pistons 24, 30 from the drive shaft 14.
  • the second spring 28 is supported advantageously on the housing 12 and the second piston 24 from.
  • the pressure chamber inlet valve 38 is arranged, which is preferably designed as a flow control valve to allow a particularly precise metering of pressurized fluid.
  • the other structure of the pump unit 13 of the second embodiment of the high-pressure pump is identical to the first embodiment.
  • the pump unit 13 can be used both in a radial piston pump and in a high-pressure pump designed as a linear piston pump.
  • the pressure fluid in the pressure chamber 22 is compressed and subjected to the first pressure P1.
  • This first pressure P1 acts on the pressure chamber 22 to the pressure chamber 22 facing and this limiting surface 52.
  • the pressure on the space 22 facing and this limiting surface 52 applied pressure P1 causes the second piston 24 and the high-pressure piston 30 in the same direction with the first piston 18 are moved upward and perform a compression stroke. This is done, as already detailed in the first embodiment described, a compression of the fluid located in the cylinder chamber 32.
  • the compressed fluid may be expelled via the cylinder space drain line 35 subsequent to the compression stroke. If the high-pressure pump 10 is a high-pressure fuel pump, the cylinder space drain line 35 can be connected to the common rail.
  • the second spring 28 moves the second piston 24 and the high pressure piston 30 back to their original positions.
  • fluid is sucked into the cylinder space 32 via the cylinder space supply line 33.
  • the first piston 18 is moved back in the same direction as the second piston 24 and the high-pressure piston 30 and in the pressure chamber 22, the leakage can be compensated via the pressure chamber inlet valve 38.
  • pressure fluid 22 can be metered particularly precisely to the pressure chamber 22. This may be particularly important in the partial load range of the high-pressure pump, since in this case a reduction in the amount of pressurized fluid is possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (7)

  1. Pompe à haute pression (10), comprenant :
    - un boîtier de pompe (12), et
    - au moins une unité de pompe (13) avec une chambre formant cylindre (32) ayant un axe longitudinal (L), dans lequel un piston haute pression (30) est disposé de façon à pouvoir se déplacer axialement,
    dans laquelle :
    - la pompe à haute pression (10) est actionnée par un arbre d'entraînement (14),
    - l'arbre d'entraînement (14) est en liaison fonctionnelle avec un premier piston (18) de la au moins une unité de pompe (13),
    - une chambre de pression (22) de la au moins une unité de pompe (13) peut être alimentée, par le premier piston (18), avec une première pression (p1),
    - la chambre de pression (22) est en liaison fonctionnelle avec un second piston (24) de la au moins une unité de pompe (13) lequel est, à son tour, en liaison fonctionnelle avec le piston haute pression (30),
    - le second piston (24) présente une face (52) tournée vers la chambre de pression (22) et délimitant celle-ci et le piston haute pression (30) présente une face (54) tournée vers la chambre formant cylindre (32) et délimitant celle-ci, laquelle face est plus petite que la face (52) tournée vers la chambre de pression (22) et délimitant celle-ci, et
    - le premier piston (18) est disposé par rapport au second piston (24) de façon à ce que le premier piston (18) et le second piston (24) peuvent se déplacer dans le même sens lors d'une utilisation conforme aux prescriptions,
    caractérisée en ce que le premier piston (18) se présente sous la forme d' un godet poussoir et en ce que le godet poussoir présente une face frontale (46) annulaire formant une face de délimitation de la chambre de pression (22).
  2. Pompe à haute pression (10) selon la revendication 1, caractérisée en ce que le premier piston (18) est disposé coaxialement par rapport au piston haute pression (30).
  3. Pompe à haute pression (10) selon l'une quelconque des revendications précédentes, caractérisée en ce que la chambre de pression (22) est remplie d'un fluide de pression, qui peut être acheminé à travers un conduit d'admission (37) de la chambre de pression et
    en ce que le conduit d'admission (37) de la chambrede pression présente une soupape d'admission (38) au niveau de la chambre de pression.
  4. Pompe à haute pression (10) selon la revendication 3, caractérisée en ce que la soupape d'admission (38) au niveau de la chambre de pression est une soupape de régulation de courant volumique.
  5. Pompe à haute pression (10) selon la revendication 3, caractérisée en ce que la soupape d'admission (38) au niveau de la chambre de pression est une soupape de non-retour.
  6. Pompe à haute pression (10) selon l'une quelconque des revendications précédentes, caractérisée en ce que la pompe à haute pression est une pompe à pistons radiaux ayant au moins deux unités de pompe (13).
  7. Pompe à haute pression (10) selon l'une quelconque des revendications 1 à 5, caractérisée en ce que la pompe à haute pression est une pompe à pistons en ligne ayant au moins deux unités de pompe (13).
EP20060123976 2005-12-14 2006-11-14 Pompe à haute pression Expired - Fee Related EP1798415B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510059831 DE102005059831B3 (de) 2005-12-14 2005-12-14 Hochdruckpumpe

Publications (2)

Publication Number Publication Date
EP1798415A1 EP1798415A1 (fr) 2007-06-20
EP1798415B1 true EP1798415B1 (fr) 2011-04-13

Family

ID=37603824

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060123976 Expired - Fee Related EP1798415B1 (fr) 2005-12-14 2006-11-14 Pompe à haute pression

Country Status (2)

Country Link
EP (1) EP1798415B1 (fr)
DE (2) DE102005059831B3 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013215953A1 (de) * 2013-08-13 2015-02-19 Continental Automotive Gmbh Hochdruckpumpe

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1516032A (en) * 1923-08-02 1924-11-18 Charles E White Pump
GB301821A (en) * 1927-12-06 1929-05-09 Johann Fuelscher Improvements in or relating to high pressure reciprocating compressors
DE3012028A1 (de) * 1980-03-28 1981-10-08 Josef Emmerich Pumpenfabrik GmbH, 5481 Hönningen Vorrichtung zum foerdern von fliessfaehigen medien
DE3446107A1 (de) * 1984-12-18 1986-06-19 Karl 7180 Crailsheim Eickmann Anordnung, geeignet auch fuer pumpen und motoren mit sehr hohen drucken oder nicht schmierendem fluid
EP0285685A1 (fr) * 1987-04-07 1988-10-12 Karl Eickmann Ensemble d'écoulement de fluide avec des éléments flexibles en direction axiale et délimitant des chambres pour des pressions jusqu'à plusieurs milliers d'atmosphères
DE19507295B4 (de) * 1995-03-02 2004-09-02 Siemens Ag Radialkolbenpumpe, insbesondere Kraftstoffpumpe für einen Verbrennungsmotor
DE10243148A1 (de) * 2002-09-17 2004-03-25 Siemens Ag Radialkolbenpumpeneinheit
DE10260775A1 (de) * 2002-12-23 2004-07-01 Daimlerchrysler Ag Kraftstoffversorgungssystem für Verbrennungsmotoren mit Direkteinspritzung

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Publication number Publication date
DE502006009295D1 (de) 2011-05-26
DE102005059831B3 (de) 2007-06-21
EP1798415A1 (fr) 2007-06-20

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