EP1818539A2 - Pompe a pistons radiaux destinée a un système d'injection de carburant présentant une meilleure résistance aux pressions élevées - Google Patents

Pompe a pistons radiaux destinée a un système d'injection de carburant présentant une meilleure résistance aux pressions élevées Download PDF

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Publication number
EP1818539A2
EP1818539A2 EP20070109457 EP07109457A EP1818539A2 EP 1818539 A2 EP1818539 A2 EP 1818539A2 EP 20070109457 EP20070109457 EP 20070109457 EP 07109457 A EP07109457 A EP 07109457A EP 1818539 A2 EP1818539 A2 EP 1818539A2
Authority
EP
European Patent Office
Prior art keywords
radial piston
piston pump
pump according
high pressure
check valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20070109457
Other languages
German (de)
English (en)
Other versions
EP1818539A3 (fr
EP1818539B1 (fr
Inventor
Josef Guentert
Karl-Heinz Linek
Florian Kleer
Peter Grabert
Gerd Loesch
Paul Wuetherich
Nicola Cimaglia
Antonio Diaferia
Rosanna Iorizzo
Sandra Ranaldo
Giuseppe Palma
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 EP1818539A2 publication Critical patent/EP1818539A2/fr
Publication of EP1818539A3 publication Critical patent/EP1818539A3/fr
Application granted granted Critical
Publication of EP1818539B1 publication Critical patent/EP1818539B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/10—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
    • 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
    • F02M59/462—Delivery 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
    • F02M59/44—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
    • F02M59/48—Assembling; Disassembling; Replacing
    • F02M59/485—Means for fixing delivery valve casing and barrel to each other or to pump casing
    • 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
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/22—Reinforcements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7922—Spring biased
    • Y10T137/7927—Ball valves

Definitions

  • the invention relates to a radial piston pump for high-pressure fuel supply in fuel systems of internal combustion engines, in particular in a common rail injection system, preferably with a plurality of respect to a mounted in a pump housing drive shaft radially arranged pump elements, wherein the pump elements are actuated by the drive shaft and one suction side and one high pressure side and with high pressure passages in the pump housing, each connecting the high pressure side of a pump element to a high pressure port in the pump housing.
  • Such a radial piston pump is for example from the DE 197 29 788.9 A1 known. This series-produced radial piston pump reaches operating pressures of up to 1300 bar on the high pressure side. This results in considerable mechanical stresses in the pump housing.
  • the invention has for its object to develop a radial piston pump so that it can be used for pressures up to 2000 bar.
  • a radial piston pump for high-pressure fuel supply in fuel injection systems of internal combustion engines with preferably several with respect to a stored in a pump housing drive shaft radially arranged pump elements, the pump elements are actuated by the drive shaft and each have a suction side and a high pressure side and with high pressure channels in the pump housing, which each connect the high pressure side of a pump element with a high pressure port in the pump housing, achieved in that each high pressure channel connects the high pressure side of a pump element directly to the high pressure port.
  • the radial piston pump according to the invention can be operated at higher pressures, at the same time reducing the material stress.
  • the surfaces of the high-pressure channels are compressed and provided with compressive residual stresses, in particular by the fact that a ball is pulled or pressed through the high-pressure channels, the diameter of which is slightly larger than the diameter of the high pressure channels is. This measure further increases the pressure resistance of the pump housing in the area of the high-pressure channels.
  • the high-pressure channels are hardened, in particular induction-hardened.
  • the high-pressure channels are rounded in the region of cross-sectional changes and / or junctions of other high-pressure channels, in particular rounded in a hydroerosive manner.
  • a particularly advantageous embodiment of the radial piston pump according to the invention provides that the high-pressure channels are each reinforced by a tubular insert, in particular an insert made of a high-strength material, with high-strength steel being found to be particularly suitable.
  • the tubular inserts according to the invention are inserted into the casting mold like a core before casting. When casting pump housing and tubular inserts combine very well with each other. The fact that because of the tubular inserts, the high-pressure channels of a different, more preferably a firmer material than the rest of the pump housing, there is an adaptation of the component strength to the local stresses and strains.
  • the rest of the pump housing can be made of a relatively inexpensive material, in addition to good machinability and has good sliding properties.
  • the tubular inserts according to the invention is that, in contrast to conventional bores, the high-pressure ducts can be curved or partially curved. It is also possible that the high pressure side of a pump element is connected directly to the high pressure port in the pump housing by one use, so that no Branching of the high-pressure channels are required. This has a favorable effect on the maximum stresses occurring in the pump housing, on the manufacturing costs and in particular the manufacturing reliability.
  • each pump element has a cylinder bore and a cylinder head, that the piston oscillates in the cylinder bore and delimits a delivery space, that a first check valve is arranged on the intake side, and that a second check valve is arranged on the high pressure side is arranged. It has proven to be advantageous if the cylinder bore is formed as a blind hole and the first check valve is arranged at the bottom of the blind hole. By forming the cylinder bore as a blind hole a sealing point is saved.
  • the second check valve has a sleeve with a stepped central bore, that the stepped central bore has a sealing seat for a valve member, in particular a ball particularly preferably a ceramic ball, and that the sleeve of a closure screw sealing against the cylinder head pressed.
  • This second check valve has the advantage that it is very simple and can be tested outside the radial piston pump. In the radial piston pump or the pump element, only a sealing surface is provided, which seals the screwed second check valve on the front side. Such a sealing surface is easy to control in terms of production, so that the sealing of the high-pressure side of the pump element to the environment at this point is simplified by the use of the second check valve according to the invention.
  • the sealing of the high pressure side relative to the environment is particularly effective when the sleeve has a biting edge on its end face applied to the screw plug, so that the surface pressure increases and Also, a plastic deformation of the sealing surfaces is possible, which further improves the sealing function.
  • the assembly of the check valve facilitates further, since the cohesion of a mounted and tested check valve is always guaranteed.
  • the sleeve has a transverse bore and an annular groove and that produce the transverse bore and groove a hydraulic connection of the central bore to the delivery chamber.
  • a sealing seat on the pump housing facing side of the cylinder head is incorporated in this, wherein the check valve has a cage in which a on the valve member, in particular a ball, acting closing spring is arranged.
  • the closing spring By the closing spring, the return flow of fuel is reduced, which has an advantageous effect on the pump efficiency.
  • the assembly of the check valve according to the invention in the pump element is simplified if the cage is pressed into a stepped bore comprising the sealing seat.
  • a manufacturing technology advantageous embodiment provides that the cylinder bore is formed as a blind hole, that the first check valve according to one of claims 17 and 18 is arranged at the bottom of the blind hole, so that the sealing seat of first and second check valve can be made in one setting and the assembly of the first and second check valve in the same direction.
  • FIG. 1 shows an exemplary embodiment of a radial piston pump according to the invention in a front view (FIG. 1A), in a longitudinal section (FIG. 1B) and in a cross section along the section line A-A.
  • the radial piston pump consists of a pump housing 1, in which a drive shaft 3 is rotatably mounted.
  • the pump housing 1 may advantageously be made of cast iron with globular graphite (GGG).
  • the drive shaft 3 has an eccentric portion 5.
  • the eccentric portion 5 drives via a polygon ring 7 three circumferentially distributed pump elements 9 at.
  • Each pump element 9 has a piston 11 which is guided in a cylinder bore 13 and limits a delivery chamber 15.
  • the individual components are not provided with reference numerals on all pump elements 9 in order not to worsen the clarity unnecessarily. However, the three pump elements 9 are all constructed the same.
  • a suction side 19 and a high pressure side 21 there is a suction side 19 and a high pressure side 21.
  • the suction side 19 of the cylinder head 17 is supplied with fuel via a low-pressure bore 23 in the pump housing.
  • a first check valve 25 is arranged, which prevents the return flow of fuel (not shown) from the delivery chamber 15 into the low-pressure bore 23.
  • the high pressure side 21 of the pump element 9 opens into a high pressure passage 27 in the pump housing 1.
  • a second check valve 29 is provided, which prevents the backflow of fuel under high pressure from the high pressure passage 27 into the delivery chamber 15.
  • the pump elements 9 are screwed by means not shown screws to the pump housing 1 and pressed by the screwing on a Zylinderfuß constitutional 31 of the pump housing 1.
  • a high pressure passage 27 in the pump housing 1 goes off and flows into a high pressure port which is not visible in FIGS. 1a to 1c.
  • the course of the high pressure channels is explained below with reference to FIG 2.
  • a second high-pressure channel 27 is shown in the lower half. Since this high-pressure channel is substantially perpendicular to the plane of the drawing, it is shown in Figure 1b as a circular surface.
  • a pump housing 1 is shown dreidmeinsional. From this representation, the course of the high-pressure channels 27 according to a first embodiment of the invention can be clearly seen.
  • the voltages occurring in the pump housing could be drastically reduced at the same pressures, so that the permissible operating pressures at the same Component strength could be raised to over 1800 bar.
  • the mechanical stress of the pump housing is lower than in the radial piston pumps according to the prior art.
  • the number of high-pressure channels is minimized.
  • three high-pressure channels 27a, 27b, 27c suffice to establish a hydraulic connection from the three cylinder base surfaces 31 to a high-pressure connection 33.
  • the high pressure channels 27a, 27b, and 27c are curved, and are formed directly, i. without branches, lead from a Zylinderfuß constitutional 31 to the high pressure port 33.
  • the resulting from the operating pressures of the pump housing 1 are further reduced because there are no branches.
  • this embodiment can be realized by curved tubular inserts 39a, 39b and 39c. Through these tubular inserts 39a to 39c, the strength of the pump housing 1 can be further increased.
  • tubular inserts 39a to 39c are inserted into the mold prior to casting of the pump housing 1. During the subsequent casting of the pump housing 1, the tubular inserts 39 intimately connect to the pump housing 1, so that the power transmission between tubular insert 31 and pump housing 1 is optimal.
  • FIG. 3 shows an embodiment of a radial piston pump according to the invention is shown, in which the cylinder bore 13 is listed in the pump element 9 as a blind hole. At the bottom of the blind hole a sealing seat 41 for the first check valve 25 is provided.
  • the first check valve 25 may be identical in construction to the second check valve 29 described with reference to FIGS. 5 and 6.
  • the piston 11 also driven by a polygon ring and a Kolbenfußplatte 43.
  • the invention is not limited to radial piston pumps with such drives of the pump elements 9. Rather, alternative drives, for example by cams or the like can be used.
  • the piston feet may also include bucket tappets which are guided in the pump housing 1 (not shown).
  • FIG. 4 a shows a cylinder head 17 of a further exemplary embodiment of a radial piston pump according to the invention in cross section.
  • the first check valve 25 corresponds to the first check valve 25 shown in FIG. 1.
  • the second check valve 29 shown in FIG. 1b is illustrated and explained below with reference to FIG. 4a and FIG. 4b, which shows an enlarged section of FIG. 4a.
  • the second check valve 29 consists of a sleeve 45.
  • a sealing seat 49 for a ball 51 in particular a ceramic ball, worked out.
  • the ball 51 is pressed by a closing spring 53, which is supported against a locking screw 55, on the sealing seat 49.
  • a closing spring 53 By using a closing spring 53, the efficiency of the radial piston pump according to the invention can be increased by several percentage points, since the return flow of fuel from the high-pressure passage 27, not shown in FIG. 4b, into the delivery space 15, which is likewise not shown, is suppressed.
  • the sleeve 45 is pressed onto a shoulder 57 of the closure screw 55, so that the second check valve 29 according to the invention can be preassembled and tested together with the closure screw 55.
  • the sleeve 45 On its side facing away from the screw plug 55 face 59, the sleeve 45 has a circumferential biting edge 61, which serves to seal the second check valve 29 against the cylinder head 17.
  • a transverse bore 63 and an annular groove 64 in the sleeve 45 allow the outflow of fuel when the second check valve is open in a bore 65 in the cylinder head 17th
  • FIG. 5 shows a further exemplary embodiment of a radial piston pump according to the invention.
  • the second check valve 29 is arranged on the side 67 of the cylinder head 17 which faces in the housing 1.
  • the sealing seat 49 is incorporated in the cylinder head 17.
  • a cage 69 is pressed, which receives a closing spring 53 which presses the ball 51 against the sealing seat 49.
  • This second check valve 29 according to the invention is very easy to manufacture and assemble. It can also be used as the first check valve 25, for example in an embodiment according to FIG. In this case, it is particularly advantageous in the production that the sealing seat 41 of the first check valve 25 and the sealing seat 49 of the second check valve are arranged parallel to one another, which facilitates their machining in one clamping of the cylinder head.
  • the cage 69 is shown with inserted closing spring 53 in a longitudinal section and a view from above without closing spring 53.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)
EP20070109457 2002-05-14 2003-05-13 Pompe a pistons radiaux destinée a un système d'injection de carburant présentant une meilleure résistance aux pressions élevées Expired - Lifetime EP1818539B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2002121305 DE10221305A1 (de) 2002-05-14 2002-05-14 Radialkolbenpumpe für Kraftstoffeinspritzsystem mit verbesserter Hochdruckfestigkeit
EP03749849A EP1506349B1 (fr) 2002-05-14 2003-05-13 Pompe a pistons radiaux destinee a un systeme d'injection de carburant presentant une meilleure resistance aux pressions elevees

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP03749849.0 Division 2003-05-13
EP03749849A Division EP1506349B1 (fr) 2002-05-14 2003-05-13 Pompe a pistons radiaux destinee a un systeme d'injection de carburant presentant une meilleure resistance aux pressions elevees

Publications (3)

Publication Number Publication Date
EP1818539A2 true EP1818539A2 (fr) 2007-08-15
EP1818539A3 EP1818539A3 (fr) 2008-03-19
EP1818539B1 EP1818539B1 (fr) 2010-07-21

Family

ID=29285362

Family Applications (2)

Application Number Title Priority Date Filing Date
EP03749849A Expired - Lifetime EP1506349B1 (fr) 2002-05-14 2003-05-13 Pompe a pistons radiaux destinee a un systeme d'injection de carburant presentant une meilleure resistance aux pressions elevees
EP20070109457 Expired - Lifetime EP1818539B1 (fr) 2002-05-14 2003-05-13 Pompe a pistons radiaux destinée a un système d'injection de carburant présentant une meilleure résistance aux pressions élevées

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP03749849A Expired - Lifetime EP1506349B1 (fr) 2002-05-14 2003-05-13 Pompe a pistons radiaux destinee a un systeme d'injection de carburant presentant une meilleure resistance aux pressions elevees

Country Status (6)

Country Link
US (1) US7775192B2 (fr)
EP (2) EP1506349B1 (fr)
JP (1) JP4589104B2 (fr)
CN (1) CN100476209C (fr)
DE (3) DE10221305A1 (fr)
WO (1) WO2003095839A1 (fr)

Cited By (4)

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Publication number Priority date Publication date Assignee Title
WO2009058279A1 (fr) * 2007-10-31 2009-05-07 Caterpillar Inc. Pompe haute pression
WO2009115356A1 (fr) * 2008-03-17 2009-09-24 Robert Bosch Gmbh Pompe haute pression
WO2010060838A1 (fr) * 2008-11-28 2010-06-03 Continental Automotive Gmbh Ensemble pompe
WO2011020635A1 (fr) * 2009-08-21 2011-02-24 Robert Bosch Gmbh Pompe de carburant haute pression

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DE102004013244A1 (de) 2004-03-18 2005-10-06 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102007052748A1 (de) 2007-11-06 2009-05-07 Robert Bosch Gmbh Radialkolbenpumpe mit einem prismatischem Grundkörper für ein Kraftstoffeinspritzsystem
DE102007057503A1 (de) 2007-11-29 2009-06-04 Robert Bosch Gmbh Radialkolbenpumpe für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine
DE102009000488A1 (de) 2009-01-29 2010-08-05 Robert Bosch Gmbh Radialkolbenpumpe
WO2010115401A1 (fr) * 2009-04-09 2010-10-14 Robert Bosch Gmbh Machine hydraulique à pistons axiaux munie d'une plaque de raccordement
DE102010001099A1 (de) 2010-01-21 2011-07-28 Robert Bosch GmbH, 70469 Hochdruckpumpe
DE102010038953A1 (de) 2010-08-05 2012-02-09 Robert Bosch Gmbh Hochdruckpumpe
DE102011002688A1 (de) 2011-01-14 2012-07-19 Robert Bosch Gmbh Hochdruckpumpe
US20130192564A1 (en) * 2012-01-26 2013-08-01 Cummins Inc. Laser shock peening applied to fuel system pump head
EP2770203B1 (fr) * 2013-02-22 2016-10-12 Mitsubishi Heavy Industries, Ltd. Machine hydraulique à pistons radiaux et appareil de génération d'énergie de type renouvelable
DE102016201600B4 (de) * 2016-02-03 2017-10-12 Continental Automotive Gmbh Kraftstoffhochdruckpumpe und Kraftstoffeinspritzsystem
DE102016203261A1 (de) * 2016-02-29 2017-08-31 Robert Bosch Gmbh Verfahren zum Herstellen einer Bohrung, Bauteil und Kraftstoffinjektor

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EP0337439A2 (fr) 1988-04-13 1989-10-18 Nissan Motor Co., Ltd. Pompe à pistons radiaux à cylindres immobiles avec dispositif pour commande de refoulement

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WO2009058279A1 (fr) * 2007-10-31 2009-05-07 Caterpillar Inc. Pompe haute pression
WO2009115356A1 (fr) * 2008-03-17 2009-09-24 Robert Bosch Gmbh Pompe haute pression
WO2010060838A1 (fr) * 2008-11-28 2010-06-03 Continental Automotive Gmbh Ensemble pompe
WO2011020635A1 (fr) * 2009-08-21 2011-02-24 Robert Bosch Gmbh Pompe de carburant haute pression
CN102483017A (zh) * 2009-08-21 2012-05-30 罗伯特·博世有限公司 燃料高压泵

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JP2005525502A (ja) 2005-08-25
EP1506349B1 (fr) 2009-08-05
EP1818539A3 (fr) 2008-03-19
CN1653268A (zh) 2005-08-10
DE50311781D1 (de) 2009-09-17
DE10221305A1 (de) 2003-11-27
US20050207908A1 (en) 2005-09-22
DE50312918D1 (de) 2010-09-02
US7775192B2 (en) 2010-08-17
CN100476209C (zh) 2009-04-08
JP4589104B2 (ja) 2010-12-01
EP1818539B1 (fr) 2010-07-21
WO2003095839A1 (fr) 2003-11-20
EP1506349A1 (fr) 2005-02-16

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