EP1714030B1 - Pompe haute pression, notamment pour systeme d'injection de carburant de moteur a combustion interne - Google Patents

Pompe haute pression, notamment pour systeme d'injection de carburant de moteur a combustion interne Download PDF

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Publication number
EP1714030B1
EP1714030B1 EP04802795A EP04802795A EP1714030B1 EP 1714030 B1 EP1714030 B1 EP 1714030B1 EP 04802795 A EP04802795 A EP 04802795A EP 04802795 A EP04802795 A EP 04802795A EP 1714030 B1 EP1714030 B1 EP 1714030B1
Authority
EP
European Patent Office
Prior art keywords
pressure pump
housing part
pump
pump piston
driveshaft
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
EP04802795A
Other languages
German (de)
English (en)
Other versions
EP1714030A1 (fr
Inventor
Armin Merz
Gerhard Meier
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1714030A1 publication Critical patent/EP1714030A1/fr
Application granted granted Critical
Publication of EP1714030B1 publication Critical patent/EP1714030B1/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
    • F04B1/053—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
    • 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
    • F02M59/10—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 the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F04B1/0413—Cams
    • 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
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the invention relates to a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is through the DE 199 07 311 A1 known.
  • This high-pressure pump has a housing and a plurality of pump elements arranged in the housing.
  • the pump elements each have a driven by a drive shaft of the high pressure pump in a stroke pump piston.
  • the pump piston is tightly guided in a cylinder bore of a housing part of the high pressure pump and limited in the cylinder bore a pump working space.
  • the pump piston is supported via a support element in the form of a plunger on the drive shaft.
  • the pump piston is acted upon by a prestressed return spring towards the plunger and the plunger is acted upon by the return spring to the drive shaft.
  • a roller is rotatably mounted, via which the plunger rests against a cam of the drive shaft.
  • the plunger is slidably guided in a bore of another housing part of the high-pressure pump, as the housing part, in which the cylinder bore is formed, wherein the bore and the plunger have a substantially larger diameter than the cylinder bore.
  • a disadvantage of this known High-pressure pump is that the cylinder bore, in which the pump piston is guided, and the bore in which the plunger is guided, are arranged in different housing parts, so that to ensure exact alignment of the cylinder bore and the bore for the plunger complex centering of the two Housing parts are required to each other.
  • the plunger has a high weight because of the large diameter, which in turn requires a return spring with high rigidity and correspondingly high weight to prevent the plunger from jumping off the drive shaft at high speeds, whereby the high-pressure pump has a high overall weight.
  • the high-pressure pump according to the invention with the features of claim 1 has the advantage that the cylinder bore for the pump piston and the receptacle for the support member are arranged on the same housing part and therefore no costly centering during assembly of the high pressure pump are required.
  • the support member can be made compact, whereby its weight is low and the return spring can be formed with correspondingly low rigidity, whereby the weight of the high-pressure pump can be kept low.
  • FIG. 1 a high pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section
  • FIG. 2 one in FIG. 1 with II designated section of the high pressure pump in an enlarged view according to a first embodiment
  • FIG. 3 the section II, in a view in the direction of arrow III in FIG. 2
  • FIG. 4 the detail II of the high pressure pump according to a second embodiment
  • FIG. 5 the detail in a view in the direction of arrow V in FIG. 4 ,
  • the high-pressure pump has a multi-part housing 10, in which a drive shaft 12 which can be driven in rotation by the internal combustion engine is arranged.
  • the drive shaft 12 is rotatably supported in a base body 14 of the housing 10 via two spaced apart in the direction of the axis of rotation 13 of the drive shaft 12 bearings.
  • the main body 14 of the housing 10 may in turn be designed in several parts and the bearings may be arranged in different parts of the main body 14.
  • the drive shaft 12 has at least one cam 16, wherein the cam 16 can also be designed as a multiple cam.
  • the high pressure pump has at least one or more arranged in the housing 10 pump elements 18, each with a pump piston 20 which is driven by the cam 16 of the drive shaft 12 in a lifting movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
  • a housing part 22 connected to the main body 14 is provided, which is designed as a cylinder head.
  • the housing part 22 has a voltage applied to an outer side of the base body 14 and a flange 24 through a Opening 15 in the main body 14 to the drive shaft 12 projecting through, at least approximately cylindrical projection 26 with respect to the flange 24 of smaller diameter.
  • the pump piston 20 is guided in a tightly displaceable manner in a cylinder bore 28 formed in the neck 26 in the housing part 22 and limited with its end face remote from the drive shaft 12 in the cylinder bore 28 a pump working space 30.
  • the cylinder bore 28 may extend into the flange 24, in which then the pump working space 30 is arranged.
  • the pump working chamber 30 has a connection extending in the housing 10 with a fuel inlet channel 32 with a fuel inlet, for example, a feed pump.
  • the pump working chamber 30 also has, via a fuel discharge channel 36 running in the housing 10, a connection to an outlet, which is connected, for example, to a high-pressure accumulator 110.
  • One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine.
  • an outlet valve 38 opening out of the pump working chamber 30 is arranged.
  • a support member 40 is arranged between the pump piston 20 and the cam 16 of the drive shaft 12.
  • the support member 40 has on its side facing the cam 16 a concave recess 42 in which a cylindrical roller 44 is rotatably mounted.
  • the axis of rotation 45 of the roller 44 is at least approximately parallel to the axis of rotation 13 of the drive shaft 12 and the roller 44 rolls on the cam 16 of the drive shaft 12 from.
  • the support member 40 is in a receptacle 46 of the housing part 22 in the direction of Lifting movement of the pump piston 20, which is guided along the longitudinal axis 21, slidably.
  • the receptacle 46 for the support member 40 is formed as a 26 formed in the neck of the housing part 22, adjoining the cylinder bore 28 slot, which extends to the drive shaft 12 facing the front end of the projection 26.
  • the slot 46 is bounded by two at least approximately mutually parallel walls 48 of the projection 26.
  • the support member 40 is formed at least approximately rectangular in cross section and is disposed between the two walls 48 with a small clearance.
  • the surfaces of the walls 46 facing the support element 40 and / or the surfaces 41 of the support element 40 facing the walls 46 are preferably machined so that they are flat and have a low surface roughness, for example, these surfaces are ground. Between the parallel walls 48, the support member 40 in the direction of the longitudinal axis 21 of the pump piston 20 is displaceable, but guided around the longitudinal axis 21 non-rotatable.
  • the pump piston 20 is coupled to the support member 40 in the direction of its longitudinal axis 21.
  • the support element 40 may have, for example, on its side facing the pump piston 20, a bore 50, into which the end of the pump piston 20 projects.
  • the bore 50 has at its periphery an annular groove 52 into which a radially elastic spring ring 54 is inserted.
  • the pump piston 20 also has, in its end region, an annular groove 56 into which the spring ring 54 engages when the pump piston 20 is inserted into the bore 50, whereby the coupling of the pump piston 20 to the support element 40 is achieved.
  • the support member 40 projects laterally through the slot 46 out of the projection 26 and on the protruding from the slot 46 ends of the support member 40 is a spring plate 58 on.
  • the spring plate 58 may be connected to the support member 40, for example by means of a latching connection.
  • a prestressed return spring 60 is arranged, which is designed as a helical compression spring which surrounds the projection 26.
  • the pump chamber 30 When the suction stroke of the pump piston 20, in which this moves radially inward, the pump chamber 30 is filled by the fuel inlet channel 32 with the inlet valve 34 open with fuel, the exhaust valve 38 is closed.
  • fuel is pumped under high pressure through the fuel discharge passage 36 with the exhaust valve 38 open to the high-pressure accumulator 110 by the pump piston 20, wherein the inlet valve 34 is closed.
  • the support member 40 is non-rotatably guided in the receptacle 46 about the longitudinal axis 21 of the pump piston 20 and takes on any transverse forces, so that they do not act on the pump piston 20.
  • the receptacle 46 can be aligned very accurately to the cylinder bore 28, since this is formed on the same housing part 22 as the cylinder bore 28.
  • the support member 40 can be made compact, since this only needs to have the recess 42 for receiving the roller 44 and his lateral, flat surfaces 41 is guided. The production the slot 46 as a receptacle for the support member 40 and the rectangular support member 40 is easily possible.
  • the high-pressure pump is shown in sections according to a second embodiment, in which the basic structure of the high pressure pump with respect to the first embodiment is unchanged and only the housing part 22 is modified.
  • the housing part 122 has the flange 124 and the protruding from this cylindrical extension 126.
  • annular groove 170 is introduced through which an inner, at least approximately cylindrical projection 172 is formed within the neck 126, in which the cylinder bore 28 is arranged, in which the pump piston 20 is guided.
  • the annular groove 170 extends in depth to close to the flange 124 of the housing part 122.
  • the inner projection 172 terminates at a greater distance from the drive shaft 12 than the outer shoulder 126 and the outer shoulder 126 has in its projecting beyond the inner projection 172 end region two diametrically opposed slots 146.
  • the support member 140 is at least approximately rectangular in cross-section, arranged in the projecting beyond the inner projection 172 end portion of the outer projection 126 and protrudes with its lateral ends in the slots 146 inside.
  • the support member 140 is slidably guided in the one receiving for this forming slots 146 of the outer shoulder 126 in the direction of the lifting movement of the pump piston 20 via its projecting into the slots 146 flat side surfaces 141.
  • the pump piston 20 may be coupled to the support member 140 as in the first embodiment.
  • a spring plate 158 On the support member 140 is a spring plate 158, against which the biased return spring 160 is supported, on the other hand is supported on the bottom of the annular groove 170.
  • the spring plate 158 may be connected to the support member 140, for example by means of a locking connection.
  • the return spring 160 is disposed in the annular groove 170 and surrounds the inner projection 172.
  • the spring plate 158 can also be supported on the pump piston 20, for example via a locking ring or on an enlarged diameter piston foot of the pump piston 20. In this case, the pump piston 20 through the Return spring 160 held in contact with the support member 140 and does not need to be additionally coupled to the support member 140.

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)

Claims (8)

  1. Pompe haute pression notamment pour une installation d'injection de carburant d'un moteur à combustion interne comportant un boîtier (10, 14, 22 ; 122), au moins un élément de pompe (18) comportant un piston de pompe (20) entraîné selon un mouvement de translation par un arbre d'entraînement (12), le piston de pompe (20) étant guidé en coulissement dans un alésage de cylindre (28) d'une partie de boîtier (22 ; 122) en délimitant dans cet alésage une chambre de travail de pompe (30),
    le piston de pompe (20) s'appuyant sur l'arbre d'entraînement (12) par un élément d'appui (40 ; 140) et
    le piston de pompe (20) et l'élément d'appui (40 ; 140) sont sollicités vers l'arbre d'entraînement (12) par un ressort de rappel précontraint (60 ; 160),
    caractérisée en ce que
    l'élément d'appui (40 ; 140) est coulissant dans la direction de l'axe longitudinal (21) du piston de pompe (20) dans un logement (46 ; 146) réalisé dans la partie de boîtier (22 ; 122) munie de l'alésage de cylindre (28), et en étant guidé de manière bloquée en rotation autour de l'axe longitudinal (21).
  2. Pompe haute pression selon la revendication 1,
    caractérisée en ce que
    le logement (46 ; 146) de la partie de boîtier (22 ; 122) est adjacent à l'alésage de cylindre (28) par rapport à l'arbre d'entraînement (12).
  3. Pompe haute pression selon la revendication 1 ou 2,
    caractérisée en ce que
    le logement (46 ; 146) est réalisé comme fente dans une partie de boîtier (22 ; 122).
  4. Pompe haute pression selon l'une des revendications 1 à 3,
    caractérisée en ce que
    l'élément d'appui (40 ; 140) est réalisé en section avec une forme au moins sensiblement rectangulaire.
  5. Pompe haute pression selon l'une des revendications précédentes,
    caractérisée en ce que
    la partie de boîtier (22 ; 122) comporte un prolongement (26 ; 126, 172) tourné vers l'arbre d'entraînement (12) et ayant de préférence une forme sensiblement cylindrique, dans lequel est réalisé l'alésage de cylindre (28) et le logement (46 ; 146).
  6. Pompe haute pression selon la revendication 5,
    caractérisée en ce que
    le ressort de rappel (60) est un ressort hélicoïdal de compression entourant le prolongement (26) de la partie de boîtier.
  7. Pompe haute pression selon la revendication 5,
    caractérisée en ce que
    le prolongement (126, 172) de la partie de boîtier (122) présente une rainure annulaire (170) ouverte vers l'arbre d'entraînement (12) qui subdivise le prolongement en un prolongement intérieur (172) et un prolongement extérieur (126) entourant ce dernier et en ce que le ressort de rappel (160) en forme de ressort hélicoïdal de compression est logé dans la rainure annulaire (170).
  8. Pompe à haute pression selon l'une des revendications précédentes,
    caractérisée en ce que
    le ressort de rappel (60 ; 160) s'appuie au moins indirectement contre l'élément d'appui (40 ; 140) et
    le piston de pompe (20) est couplé à l'élément d'appui (40 ; 140) dans la direction de son axe longitudinal (21).
EP04802795A 2004-01-30 2004-11-23 Pompe haute pression, notamment pour systeme d'injection de carburant de moteur a combustion interne Expired - Fee Related EP1714030B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004004705A DE102004004705A1 (de) 2004-01-30 2004-01-30 Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
PCT/DE2004/002584 WO2005073554A1 (fr) 2004-01-30 2004-11-23 Pompe haute pression, notamment pour systeme d'injection de carburant de moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1714030A1 EP1714030A1 (fr) 2006-10-25
EP1714030B1 true EP1714030B1 (fr) 2008-02-27

Family

ID=34801270

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04802795A Expired - Fee Related EP1714030B1 (fr) 2004-01-30 2004-11-23 Pompe haute pression, notamment pour systeme d'injection de carburant de moteur a combustion interne

Country Status (7)

Country Link
US (1) US7775193B2 (fr)
EP (1) EP1714030B1 (fr)
JP (1) JP4340289B2 (fr)
CN (1) CN100458150C (fr)
DE (2) DE102004004705A1 (fr)
ES (1) ES2298845T3 (fr)
WO (1) WO2005073554A1 (fr)

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007034036A1 (de) * 2007-07-20 2009-01-22 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit Rollenstößel
DE102008008438A1 (de) * 2008-02-11 2009-08-13 Continental Automotive Gmbh Hochdruckpumpe
DE102008001019A1 (de) 2008-04-07 2009-10-08 Robert Bosch Gmbh Hochdruckpumpenanordnung mit einstempliger Hochdruckpumpe
DE102008001718A1 (de) 2008-05-13 2009-11-19 Robert Bosch Gmbh Hochdruckkraftstoffpumpe
DE102008043436A1 (de) * 2008-11-04 2010-05-06 Robert Bosch Gmbh Kolbenpumpe mit einem Kolbenhalter
DE102008044298A1 (de) 2008-12-03 2010-06-10 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe
DE102009028394A1 (de) * 2009-08-10 2011-02-17 Robert Bosch Gmbh Hochdruckpumpe
DE102010011456A1 (de) * 2010-03-15 2011-09-15 Schaeffler Technologies Gmbh & Co. Kg Pumpe, insbesondere Kolbenpumpe für Hoch- oder Niederdruck
DE102010038468A1 (de) * 2010-07-27 2012-02-02 Robert Bosch Gmbh Hochdruckpumpe
DE102010041178A1 (de) 2010-09-22 2012-03-22 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe
DE102010043510A1 (de) 2010-11-05 2012-05-10 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe
DE102010062678A1 (de) 2010-12-09 2012-06-14 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe
DE102011003396A1 (de) 2011-01-31 2012-08-02 Continental Automotive Gmbh Pumpeneinheit für eine Hochdruckpumpe
JP2012172537A (ja) * 2011-02-18 2012-09-10 Denso Corp 燃料供給ポンプ、および燃料供給ポンプの製造方法
DE102011077535A1 (de) 2011-06-15 2012-12-20 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe
DE102011083571A1 (de) * 2011-09-28 2013-03-28 Robert Bosch Gmbh Stößelbaugruppe für eine Kraftstoffhochdruckpumpe sowie Kraftstoffhochdruckpumpe
JP5472340B2 (ja) 2012-02-10 2014-04-16 株式会社デンソー 燃料供給ポンプ
DE102013210036A1 (de) * 2013-05-29 2014-12-04 Robert Bosch Gmbh Hochdruckpumpe für ein Kraftstoffeinspritzsystem
DE102016203768B4 (de) * 2015-11-12 2017-10-26 Robert Bosch Gmbh Pumpe, insbesondere Hochdruckpumpe eines Kraftstoffeinspritzsystems, mit einem Montageverbund von Stößel-Baugruppe und Pumpenzylinderkopf, insbesondere durch eine Rastverbindung zwischen Federteller und Stößelkörper
JP7120081B2 (ja) * 2019-03-01 2022-08-17 株式会社デンソー 燃料噴射ポンプ

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US2301407A (en) * 1940-06-22 1942-11-10 Dayton Liquid Meter Company Fuel injection pump
US2351908A (en) * 1942-09-18 1944-06-20 Beeh Louis High-pressure pump
US4008009A (en) * 1975-09-30 1977-02-15 Endre Kovacs Fuel injection pump
EP0083579A1 (fr) * 1981-03-16 1983-07-20 ANDREW FRASER & COMPANY LIMITED Pompes a pistons radiaux
AU1106783A (en) * 1982-01-19 1983-07-28 Christian Helmut Thoma Hydraulic radial piston machines
JP3990732B2 (ja) * 1996-06-07 2007-10-17 イドロ レデュク 任意の流体用に使用できる高圧ポンプ
US5980214A (en) * 1997-09-12 1999-11-09 Stanadyne Automotive Corp. Fluid pump with split plungers
DE19907311A1 (de) * 1999-02-22 2000-08-31 Bosch Gmbh Robert Hydraulikpumpeneinheit
IL128934A (en) * 1999-03-11 2002-11-10 Mapple Technology Ltd Power unit

Also Published As

Publication number Publication date
US20070154326A1 (en) 2007-07-05
ES2298845T3 (es) 2008-05-16
JP2007500303A (ja) 2007-01-11
DE502004006367D1 (de) 2008-04-10
CN100458150C (zh) 2009-02-04
EP1714030A1 (fr) 2006-10-25
DE102004004705A1 (de) 2005-08-18
US7775193B2 (en) 2010-08-17
WO2005073554A1 (fr) 2005-08-11
JP4340289B2 (ja) 2009-10-07
CN1906411A (zh) 2007-01-31

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DE102008042334A1 (de) Kolbenpumpe mit gegenüber einer Antriebswelle verkippten Laufrollen

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