EP2076669A1 - Stösselbaugruppe für eine hochdruckpumpe und hochdruckpumpe mit wenigstens einer stösselbaugruppe - Google Patents
Stösselbaugruppe für eine hochdruckpumpe und hochdruckpumpe mit wenigstens einer stösselbaugruppeInfo
- Publication number
- EP2076669A1 EP2076669A1 EP07788020A EP07788020A EP2076669A1 EP 2076669 A1 EP2076669 A1 EP 2076669A1 EP 07788020 A EP07788020 A EP 07788020A EP 07788020 A EP07788020 A EP 07788020A EP 2076669 A1 EP2076669 A1 EP 2076669A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- roller
- axis
- rotation
- plunger body
- plunger
- 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
Links
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
- F02M59/10—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
- F04B1/0439—Supporting or guiding means for the pistons
-
- 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
-
- 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
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2101—Cams
- Y10T74/2107—Follower
Definitions
- Plunger assembly for a high pressure pump and high pressure pump with at least one plunger assembly
- the invention relates to a plunger assembly for a high-pressure pump and a high-pressure pump with at least one plunger assembly according to the preamble of claim 1 or of claim 8 or of claim 9.
- Such a plunger assembly and high-pressure pump is known from DE 103 45 061 Al.
- This high-pressure pump has at least one plunger assembly, which in turn has a hollow cylindrical plunger body and a roller shoe inserted therein in the direction of the longitudinal axis of the plunger body, in which a roller is rotatably mounted.
- the high-pressure pump has at least one pump element, which in turn has a pump piston, by which a pump working space is limited.
- the plunger assembly is disposed between the pump piston and a rotationally driven drive shaft of the high pressure pump, wherein the drive shaft has at least one cam or eccentric on which the roller runs.
- the plunger body is guided displaceably in a bore of a housing part of the high-pressure pump.
- the ram assembly serves to the rotational movement of the drive shaft in a
- the ram assembly according to the invention with the features according to claim 1 has the advantage that the roller shoe can execute a tilting movement within the plunger body in a defined extent and align, such that the axis of rotation of the roller parallel to
- Rotary axis of the drive shaft extends and thus edge beams are avoided, while on the other hand in the vertical direction with respect to the axes of rotation of the roller and the drive shaft acting lateral forces are absorbed by the small game.
- a tilting movement of the plunger body in the bore of the pump housing part is made possible, such that the axis of rotation of the roller parallel to the axis of rotation of the Can align drive shaft and thus edge beams are avoided.
- FIG. 1 shows a high-pressure pump in a longitudinal section
- Figure 2 shows the high-pressure pump in a cross section along line II-II in Figure 1
- Figure 3 is a section III in Figure 1 with a plunger assembly of the high pressure pump in an enlarged view
- Figure 4 the plunger assembly in a cross-section along line IV-IV in Figure 3 according to a first embodiment
- Figure 5 the plunger assembly in cross-section according to a second embodiment
- Figure 6 shows the plunger assembly in a longitudinal section according to a third embodiment
- Figure 7 shows a roller shoe in a view in the direction of arrow VII in Figure 6
- Figure 8 shows the plunger assembly in a longitudinal section according to a fourth embodiment.
- FIGS. 1 to 8 show a high-pressure pump for a fuel injection device of an internal combustion engine.
- the high-pressure pump has a housing 10, which is designed in several parts and in which a rotationally driven drive shaft 12 is arranged.
- the drive shaft 12 is rotatably supported in the housing 10 via two spaced apart in the direction of the axis of rotation 13 of the drive shaft 12 bearings.
- Bearing points can be arranged in different parts 14,16 of the housing 10.
- the drive shaft 12 has at least one cam 26 or eccentric, wherein the cam 26 may also be formed as a multiple cam.
- the high-pressure pump has at least one or more in each case a housing detail 18 arranged pump elements 32, each with a pump piston 34 which through the cam 26 of
- Drive shaft 12 is driven indirectly in a lifting movement in at least approximately radial direction to the rotational axis 13 of the drive shaft 12.
- the pump piston 34 is guided in a cylinder bore 36 in the housing part 18 and slidably limited with its end facing away from the drive shaft 12 in the cylinder bore 36 a pump chamber 38.
- the pump chamber 38 has a running in the housing 10 fuel inlet channel 40 is connected to a fuel inlet, for example a delivery pump. At the mouth of the fuel inlet channel 40 into the pump working chamber 38 an opening into the pump working chamber 38 inlet valve 42 is arranged, which has a spring-loaded valve member 43.
- the pump chamber 38 also has a in
- Housing part 18 extending fuel drain passage 44 to a connection to an outlet, which is connected, for example, with a high-pressure accumulator 110.
- a high-pressure accumulator 110 one or more preferably arranged on the cylinders of the internal combustion engine injectors 120 are connected by the fuel in the cylinder Internal combustion engine is injected.
- an outlet valve 46 which opens out of the pump working chamber 38 is arranged, which likewise has a spring-loaded valve member 47.
- the pump element 32 is associated with a plunger assembly 50, via which the pump piston 34 is supported on the cam 26 of the drive shaft 12.
- the plunger assembly 50 includes a hollow cylindrical plunger body 52 which is slidably guided in a bore 54 of a portion 14 of the housing 10 of the high pressure pump.
- the pump piston 34 has a smaller diameter than the plunger body 52 and projects with its end remote from the pump working chamber 38 end of the cylinder bore 36 and into the plunger body 52 inside. At its end facing away from the pump working chamber 38, the pump piston 34 may have a piston foot 35 which is larger in diameter than its remaining area.
- a roller shoe 56 is inserted in the plunger body 52 of the drive shaft 12 side facing in the direction of the longitudinal axis 53 of the plunger body 52.
- a cylindrical roller 60 is rotatably mounted in a cylinder-section-shaped receptacle 58 on the cam 26 of the drive shaft 12 facing side of the roller shoe 56.
- the axis of rotation of the roller 60 is designated 61.
- the roller shoe 56 comes into abutment in the plunger body 52 in the direction of the longitudinal axis 53 against a stop 62 which, for example, is formed by an annular web projecting radially inwardly from the plunger body 52. As shown in FIGS.
- the roller shoe 56 has one or preferably a plurality of openings 57 which allow fuel to pass through during the lifting movement of the plunger assembly 50.
- the plunger assembly 50 and pump piston 34 are urged by a biased spring 64 toward the cam 26 of the drive shaft 12.
- the spring 64 is formed as the pump piston 34 surrounding and projecting into the plunger body 52 helical compression spring.
- the spring 64 is supported on the one hand on the pump housing part 18 and on the other hand on a spring plate 65 from.
- the spring plate 65 is connected to the pump piston 34 and rests on the roller shoe 56 facing away from the side of the annular web 62. The spring 64 thus acts on the spring plate 65 both on the pump piston 34 and on the plunger body 52nd
- the roller shoe 56 is arranged in the tappet body 52 such that the roller shoe 56 in the direction of the axis of rotation 61 of the roller 60 has a greater clearance in the tappet body 52 than in directions perpendicular to the axis of rotation 61 of the roller 60.
- the roller shoe 56 is in particular pressed into the plunger body 52, wherein the pressing takes place in directions perpendicular to the axis of rotation 61 of the roller 60, so that in these directions no play between roller shoe 56 and plunger body 52 is present.
- the roller shoe 56 is thus arranged without play in the plunger body 52 in the drawing plane of FIG.
- the roller shoe 56 In the direction of the axis of rotation 61 of the roller 60 is between the roller shoe 56 and the plunger body 52 game available.
- the roller shoe 56 is arranged in the drawing plane of Figure 1 with play in the tappet body 52.
- the roller shoe 56 can thus perform a limited tilting movement in the tappet body 52 about an imaginary tilting axis perpendicular to the axis of rotation 61 of the roller 60 and perpendicular to the longitudinal axis 53 of the tappet body 52 this intersecting, whereby an alignment of the axis of rotation 61 of the roller 60 at least approximately parallel to Rotary axis 13 of the drive shaft 12 is possible.
- the tilting movement of the roller shoe 56 is indicated by the arrows K in Figures 3,6 and 8.
- the plunger body 52 at least before the pressing of the roller shoe 56 has a constant inner diameter.
- the above-described tilting movement of the roller shoe 56 in the plunger body 52 can be achieved according to a first embodiment shown in Figure 4, that the roller shoe 56 in cross-section perpendicular to the longitudinal axis 53 of the plunger body 52 viewed in directions perpendicular to the axis of rotation 61 of the roller 60 has a larger diameter D. as in the direction of the axis of rotation 61 of the roller 60, where the diameter is denoted by d.
- the areas of the roller shoe 56 with the diameter D extend on both sides of a longitudinal axis 53 of the plunger body 52 intersecting center plane 55 of the roller shoe 56 and the areas with the diameter d on both sides of the axis of rotation 61 of the roller 60 containing center plane of the roller shoe 56.
- the transitions between the regions of large diameter D and small diameter d may be rounded, for example approximately sinusoidal.
- the areas of large diameter D and small diameter d are each formed cylindrical with constant diameter D or d.
- the difference of the diameter D and d is greatly exaggerated for reasons of clarity.
- the difference between the diameters D and d may be, for example, depending on the application about 10 to 100 microns.
- the roller shoe 56 is made of, for example, hardened steel, and the portions having the different diameters D and d can be formed thereon before or after the hardening treatment of the roller shoe 56, for example, by grinding the roller shoe 56.
- the roller shoe 56 is shown according to a second embodiment, in which this in Cross-section viewed perpendicular to the longitudinal axis 53 of the plunger body 52 is oval, for example, elliptical.
- this in Cross-section viewed perpendicular to the longitudinal axis 53 of the plunger body 52 is oval, for example, elliptical.
- the roller shoe 56 In directions perpendicular to the axis of rotation 61 of the roller 60, the roller shoe 56 has a large diameter D and in the direction of the axis of rotation 61 of the roller 60 has a small diameter d. Between the diameters D and d, the diameter of the roller shoe 56 changes continuously.
- the oval cross-sectional shape of the roller shoe 56 can be generated even before its hardening treatment or thereafter, for example, by grinding the roller shoe 56 having a circular cross-section in the initial state.
- the difference between the diameters D and d may be, for example, depending on the application about 10 to 100 microns.
- the plunger body 52 is formed relatively thin-walled, which then changes during pressing of the roller shoe 56 formed as described above in the plunger body 52 whose outer shape according to the shape of the roller shoe 56.
- the plunger body 52 then has after pressing the roller shoe 56 in directions perpendicular to the axis of rotation 61 of the roller 60 has a larger outer diameter D 'as in the direction of the axis of rotation 61 of the roller 60, where the outer diameter is denoted by d by /.
- This design of the plunger body 52 allows that the plunger body 52 in the bore 54 of the pump housing part 14 can perform a limited tilting movement to enable the alignment of the axis of rotation 61 of the roller 60 at least approximately parallel to the axis of rotation 13 of the drive shaft 12.
- the plunger body 52 is guided in the bore 54 in directions perpendicular to the axis of rotation 61 of the roller 60 with little play and arranged in the direction of the axis of rotation 61 of the roller 60 with a larger clearance.
- the difference of the games of the plunger body 52 in directions perpendicular to the axis of rotation 61 and in the direction of the axis of rotation 61 of the roller 60 in the bore 54 may each for example, be about 10 to 100 microns after use.
- Plunger body 52 containing and perpendicular to the axis of rotation 61 of the roller 60 extending center plane 55 of the roller shoe 56, while the arranged in the direction of the axis of rotation 61 of the roller 60 at a distance from the median plane 55 edge portions 70 of the top of the roller shoe 56 in the direction of the longitudinal axis 53 of the plunger body 52 lower.
- the required removal of material in the edge regions 70 of the roller shoe 56 can be done for example by milling or grinding.
- FIG 8 shows the roller shoe 56 according to a fourth exemplary embodiment, in which the roller shoe 56 has a convex curvature on its upper side facing the stop 62, by which an elevation 72 is formed on this upper side of the roller shoe 56, its highest line in the median plane 55 of the roller shoe 56 extends.
- the curvature of the top of the roller shoe 56 is only in sections parallel to the axis of rotation 61 of the roller 60 present, while in sections perpendicular to the axis of rotation 61 of the roller 60 through the roller shoe 56 at the top thereof produce straight cutting lines.
- the curvature of the upper side of the roller shoe 56 can be produced, for example, by grinding a contour having a relatively large radius R whose center M lies on the extension of the longitudinal axis 53 of the tappet body 52. Due to the curvature of the upper side of the roller shoe 56 results in a only linear contact of the roller shoe 56 with its top on stop 62, so that the roller shoe 56 in the plunger body 52 can perform the tilting movement already explained above without this being hindered by the stop 62. In addition, for the piston foot 35 of the pump piston 34 also results in a linear contact with the upper side of the roller shoe 56, whereby the tilting movement of the roller shoe 56 is facilitated with respect to the pump piston 34.
- the pump piston 34 is not shown in Figure 8 for reasons of clarity.
- the roller shoe 56 is rigidly arranged in the plunger body 52, for example, is pressed or that the roller shoe 56 is integral with the plunger body 52 and no tilting movement of the roller shoe 56 in the plunger body 52 is possible.
- the plunger body 52 is arranged in the bore 54 of the pump housing part 14 so that the plunger body 52 is guided in the bore 54 in directions perpendicular to the axis of rotation 61 of the roller 60 with less play than in
- the bore 54 in the pump housing part 14 in this case has a constant diameter.
- the plunger body 52 may be formed as described above for the roller shoe 56 and thus in directions perpendicular to the axis of rotation 61 of
- Roller 60 has a larger outer diameter D 'than in the direction of the axis of rotation 61 of the roller 60, where the outer diameter is d /.
- the plunger body 52 may have in cross-section areas with large outer diameter D 'and areas with smaller outer diameter d / analogous to the formation of the roller shoe 56 of Figure 4 or the plunger body 52 may be formed oval in cross-section analogous to the formation of the roller shoe 56 of FIG 5. Die Difference of the games of the plunger body 52 in directions perpendicular to the axis of rotation 61 and in the direction of the axis of rotation 61 of the roller 60 in the bore 54 may, depending on
- Use case for example, about 10 to 100 microns.
- the plunger assembly 50 is held on the roller 60 in contact with the cam 26 of the drive shaft 12.
- the plunger assembly 50 is driven in a lifting movement.
- the suction stroke of the pump piston 34 in which this moves radially inward, the pump chamber 38 is filled by the fuel inlet passage 40 with the inlet valve 42 open with fuel, the exhaust valve 46 is closed.
- the delivery stroke of the pump piston 34 in which this moves radially outward, fuel is pumped under high pressure through the fuel discharge passage 44 with the outlet valve 46 open to the high-pressure accumulator 110 by the pump piston 34, wherein the inlet valve 42 is closed.
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006045933A DE102006045933A1 (de) | 2006-09-28 | 2006-09-28 | Stößelbaugruppe für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einer Stößelbaugruppe |
PCT/EP2007/057811 WO2008037524A1 (de) | 2006-09-28 | 2007-07-30 | Stösselbaugruppe für eine hochdruckpumpe und hochdruckpumpe mit wenigstens einer stösselbaugruppe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2076669A1 true EP2076669A1 (de) | 2009-07-08 |
EP2076669B1 EP2076669B1 (de) | 2010-10-06 |
Family
ID=38577270
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07788020A Not-in-force EP2076669B1 (de) | 2006-09-28 | 2007-07-30 | Stösselbaugruppe für eine hochdruckpumpe und hochdruckpumpe mit wenigstens einer stösselbaugruppe |
Country Status (8)
Country | Link |
---|---|
US (1) | US20100037865A1 (de) |
EP (1) | EP2076669B1 (de) |
JP (1) | JP2010505058A (de) |
CN (1) | CN101523044A (de) |
AT (1) | ATE483907T1 (de) |
BR (1) | BRPI0716260A2 (de) |
DE (2) | DE102006045933A1 (de) |
WO (1) | WO2008037524A1 (de) |
Families Citing this family (77)
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DE102007034036A1 (de) * | 2007-07-20 | 2009-01-22 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe mit Rollenstößel |
DE102008001871A1 (de) * | 2008-05-20 | 2009-11-26 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe |
JP2010037997A (ja) * | 2008-08-01 | 2010-02-18 | Denso Corp | 燃料供給ポンプ |
DE102008042182A1 (de) | 2008-09-18 | 2010-03-25 | Robert Bosch Gmbh | Kolbenpumpe mit kugelkalottenförmigen Lagerflächen für eine Laufrolle |
DE102008042334A1 (de) | 2008-09-24 | 2010-03-25 | Robert Bosch Gmbh | Kolbenpumpe mit gegenüber einer Antriebswelle verkippten Laufrollen |
DE102008043436A1 (de) | 2008-11-04 | 2010-05-06 | Robert Bosch Gmbh | Kolbenpumpe mit einem Kolbenhalter |
DE102008043434A1 (de) | 2008-11-04 | 2010-05-06 | Robert Bosch Gmbh | Kolbenpumpe mit einer eine reduzierte Nockenbahnlänge aufweisenden Antriebswelle |
DE102008043429A1 (de) | 2008-11-04 | 2010-05-06 | Robert Bosch Gmbh | Nockenwellentrieb mit gegen axiales Rutschen optimierten Lagerbuchsen |
DE102008043432A1 (de) | 2008-11-04 | 2010-05-06 | Robert Bosch Gmbh | Kolbenpumpe mit einer Antriebswelle mit optimiertem Dreifachnocken |
DE102009000531A1 (de) | 2009-02-02 | 2010-08-05 | Robert Bosch Gmbh | Pumpenanordnung mit einer thermisch isolierten Kolbenpumpe |
DE102009001096A1 (de) | 2009-02-24 | 2010-08-26 | Robert Bosch Gmbh | Radialkolbenpumpe mit einer Nockenwelle mit partiell gehärteten Nockenflanken |
DE102009001116A1 (de) | 2009-02-24 | 2010-08-26 | Robert Bosch Gmbh | Kolbenpumpe nach dem Boxerprinzip |
DE102009001118A1 (de) | 2009-02-24 | 2010-08-26 | Robert Bosch Gmbh | Kolbenpumpe mit zwei um 60 Grad versetzten Pumpenkolben |
DE102009001108A1 (de) | 2009-02-24 | 2010-08-26 | Robert Bosch Gmbh | Kolbenpumpe mit innen geführtem Stößelkörper |
DE102009001268A1 (de) | 2009-03-02 | 2010-09-09 | Robert Bosch Gmbh | Pumpenanordnung für Kraftstoff mit axial gestuftem Flansch zwischen Hochdruckpumpe und Niederdruckpumpe |
DE102009002124A1 (de) | 2009-04-02 | 2010-10-14 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102009002434A1 (de) | 2009-04-16 | 2010-10-21 | Robert Bosch Gmbh | Kolbenpumpe, insbesondere Kraftstoffpumpe |
DE102009002679A1 (de) | 2009-04-28 | 2010-11-04 | Robert Bosch Gmbh | Kolbenpumpe mit außen liegender Stößelfeder |
DE102009026596A1 (de) | 2009-05-29 | 2010-12-02 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102009026603A1 (de) | 2009-05-29 | 2010-12-02 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102009026610A1 (de) | 2009-05-29 | 2010-12-02 | Robert Bosch Gmbh | Hochdruckpumpe |
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DE102009027156A1 (de) | 2009-06-24 | 2010-12-30 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102009028373A1 (de) * | 2009-08-10 | 2011-02-17 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102009028394A1 (de) * | 2009-08-10 | 2011-02-17 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102009029297A1 (de) | 2009-09-09 | 2011-03-10 | Robert Bosch Gmbh | Kolbenpumpe mit kavitationsfreiem Rollenschuh/Laufrollen-Verband |
DE102010001099A1 (de) * | 2010-01-21 | 2011-07-28 | Robert Bosch GmbH, 70469 | Hochdruckpumpe |
JP5496696B2 (ja) * | 2010-01-27 | 2014-05-21 | Ntn株式会社 | ポンプ用タペット |
DE102010027792A1 (de) * | 2010-04-15 | 2011-10-20 | Robert Bosch Gmbh | Hochdruckpumpe |
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DE102011076057A1 (de) | 2011-05-18 | 2012-11-22 | Robert Bosch Gmbh | Hochdruckeinspritzsystem |
DE102011076060A1 (de) | 2011-05-18 | 2012-11-22 | Robert Bosch Gmbh | System zum Fördern eines Fluides |
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DE102012201302A1 (de) | 2012-01-31 | 2013-08-01 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102012201308A1 (de) | 2012-01-31 | 2013-08-01 | Robert Bosch Gmbh | Hochdruckpumpe |
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EP2628942B1 (de) * | 2012-02-14 | 2014-10-01 | Continental Automotive GmbH | Pumpe und Common-Rail-Kraftstoffeinspritzsystem |
DE102012202717A1 (de) | 2012-02-22 | 2013-08-22 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102012202720A1 (de) | 2012-02-22 | 2013-08-22 | Robert Bosch Gmbh | Hochdruckpumpe |
EP2657505B1 (de) | 2012-04-25 | 2015-07-22 | Delphi International Operations Luxembourg S.à r.l. | Hochdruckkraftstoffpumpenanordnung |
DE102012208189A1 (de) | 2012-05-16 | 2013-11-21 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102012208187A1 (de) | 2012-05-16 | 2013-11-21 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102012211395A1 (de) | 2012-07-02 | 2014-01-02 | Robert Bosch Gmbh | Zumesseinheit |
DE102012211996A1 (de) | 2012-07-10 | 2014-01-16 | Robert Bosch Gmbh | Zumesseinheit |
DE102012212153A1 (de) | 2012-07-11 | 2014-01-16 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102012212154A1 (de) | 2012-07-11 | 2014-01-16 | Robert Bosch Gmbh | Hochdruckpumpe |
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-
2007
- 2007-07-30 JP JP2009529626A patent/JP2010505058A/ja not_active Withdrawn
- 2007-07-30 DE DE502007005293T patent/DE502007005293D1/de active Active
- 2007-07-30 CN CN200780036280.XA patent/CN101523044A/zh active Pending
- 2007-07-30 US US12/440,953 patent/US20100037865A1/en not_active Abandoned
- 2007-07-30 BR BRPI0716260-0A patent/BRPI0716260A2/pt not_active IP Right Cessation
- 2007-07-30 EP EP07788020A patent/EP2076669B1/de not_active Not-in-force
- 2007-07-30 WO PCT/EP2007/057811 patent/WO2008037524A1/de active Application Filing
- 2007-07-30 AT AT07788020T patent/ATE483907T1/de active
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Also Published As
Publication number | Publication date |
---|---|
WO2008037524A1 (de) | 2008-04-03 |
DE502007005293D1 (de) | 2010-11-18 |
US20100037865A1 (en) | 2010-02-18 |
CN101523044A (zh) | 2009-09-02 |
ATE483907T1 (de) | 2010-10-15 |
DE102006045933A1 (de) | 2008-04-03 |
BRPI0716260A2 (pt) | 2013-08-06 |
JP2010505058A (ja) | 2010-02-18 |
EP2076669B1 (de) | 2010-10-06 |
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