WO2012080330A1 - Pompe haute pression - Google Patents

Pompe haute pression Download PDF

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Publication number
WO2012080330A1
WO2012080330A1 PCT/EP2011/072751 EP2011072751W WO2012080330A1 WO 2012080330 A1 WO2012080330 A1 WO 2012080330A1 EP 2011072751 W EP2011072751 W EP 2011072751W WO 2012080330 A1 WO2012080330 A1 WO 2012080330A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller
lubricant
pressure pump
plunger body
pump
Prior art date
Application number
PCT/EP2011/072751
Other languages
German (de)
English (en)
Inventor
Francesco Lucarelli
Frank Scholz
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
Priority to CN201180060238.8A priority Critical patent/CN103261661B/zh
Priority to EP11794767.1A priority patent/EP2652309B1/fr
Publication of WO2012080330A1 publication Critical patent/WO2012080330A1/fr

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
    • F04B1/0408—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
    • F04B1/0413—Cams
    • F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil

Definitions

  • the invention relates to a high-pressure pump, in particular a radial or
  • the invention relates to the field of fuel pumps for fuel injection systems of air-compression, self-igniting internal combustion engines.
  • Fuel injection device of an internal combustion engine known.
  • High-pressure pump comprises a pump housing, in which a pump element is arranged, which comprises a driven by a drive shaft in a stroke pump piston.
  • the pump piston is slidably guided in a cylinder bore of a part of the pump housing and limited in this one pump working space.
  • the pump piston is supported on the drive shaft via a hollow-cylindrical ram, wherein the ram is displaceably guided in a bore of a part of the pump housing in the direction of the longitudinal axis of the pump piston.
  • a support element in which a roller is rotatably mounted, which rolls on the cam of the drive shaft.
  • the axis of rotation of the roller is at least approximately parallel to the axis of rotation of the drive shaft.
  • the high-pressure pump known from DE 10 2005 046 670 A1 has the disadvantage that frictional forces and thus wear occur as a result of the axial bearing of the roller in the tappet.
  • forces which force the roller into an axial contact surface of the plunger, which results in the frictional forces and the wear between the roller and the plunger in the respective contact and contact areas are caused by the dynamics of the pump drive. This can also cause particles by abrasion, which can lead to further pump damage.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that a performance of the pump assembly is improved. Specifically, the bearing of the roller can be improved, so that a friction-related wear is avoided or at least reduced. In addition, possibly occurring cavitation damage can be avoided.
  • the depression on the side surface of the roller to a rolling surface of the roller out is designed with a course that lies between a radial direction and a rotational direction of the roller.
  • the recess can be introduced at a certain angle in the side surface of the roller. This can
  • Lubricant recess can be achieved to the contact area. As a result, the lubrication is further improved.
  • blind hole configured lubricant recess is provided. During the rotation of the roller lubricant, in particular diesel fuel, from the
  • an axis of the blind hole is outwardly oriented at least partially in the direction of rotation of the roller. This results in a certain dynamic pressure of the lubricant in the blind hole, whereby the
  • the blind hole is at least approximately parallel to a rotational axis of the roller configured. This allows the
  • the roller can be facilitated with one or more blind holes.
  • the blind hole can be made comparatively long. It is also advantageous that on the side surface of the roller four or more than
  • Blind hole holes configured lubricant recesses are provided which are evenly distributed around a rotation axis to the side surface of the roller and that the side surface is axially mounted at least in the region of the axis of rotation of the contact surface of the plunger body.
  • Lubricant channel opens to the contact surface of the plunger body. Furthermore, it is advantageous that the lubricant channel is configured inclined from the inner abutment surface of the plunger body to an outer side of the plunger body in a conveying direction of the pump assembly. As a result, especially during the delivery stroke, lubricant, in particular diesel fuel, is guided to the contact region between the roller and the tappet body for axial bearing. Since during the delivery stroke, the forces occurring are particularly high and thus also by the dynamics of the pump drive forces that push the roller into the axial contact surface of the plunger body, are high, just then the hydrodynamic lubrication between the components significantly improved. It is also advantageous in this case that at least three lubricant passages configured as a lubricant channel are attached to the plunger body
  • Fig. 1 is a high pressure pump in a schematic, axial sectional view
  • FIG. 2 shows a roller of a pump assembly of the high-pressure pump shown in FIG. 1 from the viewing direction designated II according to a second exemplary embodiment of the invention
  • 3 shows the roller shown in Figure 2 a pump assembly of the high-pressure pump according to a third embodiment of the invention.
  • FIG. 4 shows a tappet body and a roller of a pump assembly of a
  • FIG. 5 shows the section of a high-pressure pump labeled V in FIG. 1 in an excerptional, schematic sectional view corresponding to a fifth
  • Fig. 1 shows a high pressure pump 1 in a schematic, axial sectional view according to a first embodiment of the invention.
  • the high pressure pump 1 can be configured in particular as a radial or inline piston pump.
  • the high-pressure pump 1 is suitable as a fuel pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the high pressure pump 1 is for a fuel injection system with a
  • Fuel rail that stores diesel fuel under high pressure.
  • high pressure pump 1 according to the invention is also suitable for others
  • the high pressure pump 1 has a multi-part pump housing 2 and one in the
  • the pump housing 2 arranged drive shaft 3.
  • the pump housing 2 consists in this embodiment of a base body 4, a connected to the base 4 flange 5 and a cylinder head 6.
  • the drive shaft 3 is mounted on a bearing 7 on the one hand to the flange 5 and on a bearing 8 on the other hand to the main body 4. In operation, the drive shaft 3 rotates about an axis 9.
  • the drive shaft 3 has at least one cam 10. On the cam 10, a tread 1 1 is formed.
  • the term of the cam 10 is to be understood in this case in general.
  • the cam 10 may for example also be configured as a multiple cam. Further
  • the cam 10 may also be formed by an eccentric portion of the drive shaft 3.
  • the high-pressure pump 1 has a pump assembly 15.
  • the pump assembly 15 is associated with the cam 10.
  • the cam 10 more
  • cams may be provided adjacent to the cam 10, which in turn may be associated with pump assemblies.
  • a radial or series piston pump can be realized depending on the design of the high-pressure pump 1, a radial or series piston pump can be realized.
  • the pump assembly 15 is arranged substantially in a bore 16 of the pump housing 2. In this case, a projection 17 of the cylinder head 6 protrudes into the bore 16. Die
  • Pump assembly 15 has a hollow cylindrical plunger body 18 which is guided in the bore 16 along an axis 19.
  • the plunger body 18 is a
  • Driving element 20 is arranged, which rests against a shoulder 21 of the plunger body 18 and against the shoulder 21 by a plunger spring 22, which surrounds the approach 17 rudimentary, is applied.
  • the pump assembly 15 has a pump piston 23.
  • the cylinder head 6 has a cylinder bore 24 extending along the axis 19 through the lug 17 of the
  • Cylinder head 6 extends.
  • the pump piston 23 is along the axis 19 in the
  • the pump piston 23 is guided by the driving element 20.
  • the pump piston 23 has a piston foot 25. Furthermore, in the
  • the piston foot 25 is of the
  • a roller 27 of the pump assembly 15 is mounted in the roller shoe 26.
  • the roller 27 rolls on a running surface 28 of the cam 10, wherein the roller 27 rotates about its axis of rotation 29.
  • this causes an alternating actuation of the pump piston 23 in and counter to a conveying direction 30 of the pump assembly 15.
  • the pump piston 23 of the pump assembly 15 defines a pump chamber 31 in the cylinder bore 24. In this case, via an inlet valve 32, a filling of the
  • Conveying direction 30 allows. In the subsequent actuation of the pump piston 23 in the conveying direction 30, the pressure of the fuel in the pump working chamber 31 increases sharply, via an outlet valve 33 of the high-pressure fuel via a Fuel line 34 can be promoted to a fuel rail or the like.
  • the plunger body has contact surfaces 35, 36.
  • the roller 27 has side surfaces 37, 38.
  • diesel fuel diesel oil
  • This diesel fuel can serve for example for lubricating the bearings 7, 8 here.
  • a suitable lubrication circuit can be provided, so that is located in the interior 39, for example, under low pressure diesel fuel.
  • diesel fuel can also escape from the pump working chamber 31 into the interior 39 by leakage between the pump piston 23 and the cylinder bore 24.
  • This diesel fuel can be used advantageously for lubricating the bearing of the roller 27 both in the roller shoe 26 and on the stop surfaces 35, 36 of the plunger body 18.
  • diesel fuel must be brought into the contact areas between the side surfaces 37, 38 of the roller 27 and the contact surfaces 35, 36 of the tappet body 18 for this purpose.
  • the roller 27 both in the region of the side surface 37 and in the region of the side surface 38 each have a plurality of lubricant recesses 40, 41, 42, 43, of which in the sectional view shown in Fig. 1, the lubricant recesses 40 to 43 are shown and marked.
  • four lubricant recesses 40, 41 may be provided on the side surface 37.
  • four lubricant recesses 42, 43 may be provided on the side surface 38.
  • Lubricant recesses 40 to 43 are preferably arranged in each case uniformly about the rotation axis 29 of the roller 27. In the position of the roller 27 shown in FIG. 1, the
  • the lubricant recesses 41, 43 are in the illustrated position of the roller 27 within the receptacle of the plunger body 18 for the roller 27.
  • Lubricating diesel oil leak out.
  • a lubrication is ensured on the one hand between the side surface 37 of the roller 27 and the stop surface 35 of the plunger body 18 and on the other hand between the side surface 38 of the roller 27 and the stop surface 36 of the plunger body 18.
  • blind holes 40 to 43 configured.
  • the blind holes 40 to 43 each extend parallel to the axis of rotation 29 of the roller 27.
  • Lubricant recesses 40 to 43 of the roller 27 ensured.
  • the lubrication for supporting the roller 27 is improved.
  • possible cavitation can be avoided.
  • the hydrodynamic lubrication between the components is improved.
  • the roller 27 on its side surface 38 lubricant recesses 42, 43, 44, 45, 46, 47, 48, 49.
  • a center 29 'of the side surface 38 of the roller 27 is defined.
  • a radial half-line 51 is shown which extends from the center point 29 'in a radial direction 52.
  • the radial half-line 51 or the radial direction 52 is in this case oriented perpendicular to the axis of rotation 29.
  • the radial half-line 51 and the radial direction 52 are perpendicular to the rolling surface 50.
  • the lubricant recesses 42 to 49 are in this embodiment as
  • Recesses 42 to 49 designed.
  • the recesses 42 to 49 are here in the
  • the recesses 42 to 49 thus do not extend into the region 53, but end at an edge 54 of the region 53.
  • the edge 54 is at least approximately circular in shape.
  • the region 53 may, for example, be designed in the shape of a dome.
  • the lubricant recesses 42 to 49 are not designed exclusively in the radial direction 52 in this embodiment.
  • a direction of rotation 55 is predetermined for the roller 27.
  • the roller 27 is arranged for this purpose in relation to the direction of rotation of the drive shaft 3 in a suitable manner between the roller shoe 26 and the cam 10.
  • the Schmierstoffaus traditions 42 to 49 are designed rectilinear in this embodiment.
  • an axis 56 is illustrated, along which the recess 42 designed as a lubricant recess 42 extends.
  • the axis 56 is in this case inclined relative to the radial half-line 51 by a positive angle 57 in the direction of rotation 55.
  • the lubricant recess 42 is configured with a profile 56 which lies between the radial direction 52 and the direction of rotation 55.
  • a theoretically conceivable course of the depression 42 in the direction of rotation 55 would in this case lead to an annular depression, for example along the edge 54. Since the course 56 of the depression 42 lies between the radial direction 52 and the direction of rotation 55, in this embodiment the depression 42 extends from the edge 54 of the region 53 to the rolling surface 50 of the roller 27.
  • the depression 42 can operate fill in the area of the interior 39 of the rolling surface 50 ago with the diesel oil.
  • the diesel oil guided through the depression then enters the region 53 at the edge 54. In this way, in particular the area 53 of the side surface 38 of the roller 27 is wetted with the diesel oil serving as a lubricant.
  • the other lubricant recesses 43 to 49 are corresponding to the
  • Lubricant recess 42 configured and also contribute to the improvement of lubrication. Since the lubricant recesses 42 to 49 evenly around the
  • Rotary axis 29 distributed on the side surface 38 are arranged, results in operation a uniform lubrication in the contact area.
  • the lubricant recesses 42 to 49 configured as recesses 42 to 49 can be configured, in particular, by grooves 42 to 49 in the side surface 38.
  • Rotary axis 29 are promoted and thereby improve the lubrication on both sides.
  • Fig. 3 shows the roller 27 shown in FIG. 2 corresponding to a third
  • the lubricant recesses 42 to 45 are configured by blind holes 42 to 45.
  • the blind holes 42 to 45 are here in contrast to the first described with reference to FIG. 1
  • Embodiment not parallel to the rotation axis 29 of the roller 27 configured.
  • namely with respect to the direction of rotation 55 of the roller 27 is a directed embodiment of the blind holes 42 to 45 provided on the side surface 38.
  • an axis 56 of the blind hole 42 is shown.
  • the axis 56 of the blind hole 42 is oriented outwardly in the direction of rotation 55 of the roller 27.
  • the axis 56 is namely inclined in the direction of rotation 55 by a positive angle 57. If the axis 56 is projected into the plane of the drawing, then the half-line 51 with the axis 56 closes in this plane
  • Embodiment an angle 57 of at least approximately 90 °. However, other angles 57 are conceivable.
  • the axis 56 of the blind hole 42 also has a component of the rotation axis 29. In operation, the
  • Blind hole 42 then filled in the region of the interior 39 of the high-pressure pump 1 with diesel oil. Since the axis 56 is directed component by component against the flow direction, a fuel pressure of the diesel oil builds up in the blind bore 42. By the dammed diesel oil lubrication between the side surface 38 of the roller 27 and the thrust surface 36 of the plunger body 18 can be further improved.
  • the further blind holes 43, 44, 45 are configured according to the blind hole 42.
  • the direction of rotation 55 and the center 29 ', which defines the radial direction 52 for the respective blind bore 43, 44, 45 serve as reference variables for the alignment of the blind bores 43, 44, 45.
  • FIG. 4 shows a plunger body 18 and a roller 27 of a pump assembly 15 of the high-pressure pump 1 shown in FIG. 1 in accordance with a fourth exemplary embodiment from the viewing direction denoted by II.
  • the fourth exemplary embodiment from the viewing direction denoted by II.
  • 18 lubricant lubricant recesses 60, 61, 62 are provided on the plunger body, which are formed as lubricant channels 60 to 62.
  • the lubricant recesses 60 to 62 may be configured as lubricant bores 60 to 62.
  • the lubricant recesses 60 to 62 extend from the abutment surface 36 of the plunger body 18 to an outer side 63 of the plunger body 18.
  • diesel oil to lubricate the contact area are performed.
  • comparable lubricant recesses for the side surface 37 of the roller 28 may be provided, extending from the outer side 63 of the plunger body 18 to the
  • FIG. 5 shows the detail, designated V in FIG. 1, of the pump assembly 15 of the high-pressure pump 1 in a schematic, partial sectional view
  • the lubricant recess 61 is not configured parallel to the axis of rotation 29 of the roller 27, but from the inner run-on surface 36 of the plunger body 18 to the outside 63 of the plunger body 18 in the conveying direction 30 of the pump assembly 15 is inclined. As a result, especially during a delivery stroke of
  • Rotation axis 29 are configured, as is possible, for example, in the embodiment shown in FIG. 4. Furthermore, further lubricant recesses 60, 62 can also be provided in the exemplary embodiment illustrated with reference to FIG. 5. As illustrated in FIG. 4, the lubricant recesses 60 to 62 are preferably distributed around the rotation axis 29 on the plunger body 18.
  • the two other Schmierstoffaus traditions 60, 61 may at least approximately at the height of the axis of rotation 29 open into the thrust surface 36.
  • the plunger body 18 is designed such that the center 29 'of the side surface 38 of the roller 27 is still within the contact surface 36 of the plunger body 18. The invention is not limited to the described embodiments.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une pompe haute pression (1) servant en particulier de pompe à pistons radiaux ou en ligne pour des installations d'injection de carburant de moteurs à combustion interne comprimant l'air et à allumage par compression. Ladite pompe comprend un module de pompe (15) et un arbre d'entraînement (3) comportant une came (10) associée au module de pompe (15). Le module de pompe (15) comprend un galet de roulement (27) circulant sur une surface de roulement (11) de la came (10) et un corps de poussoir (18) sur lequel le galet de roulement (27) est monté axialement. Sur au moins une surface latérale (37, 38) du galet de roulement (27) et/ou sur au moins une surface d'appui (35, 36) du corps de poussoir (18) sur laquelle le galet de roulement est monté axialement avec sa surface latérale (37, 38) sont formés des évidements pour lubrifiant (40 à 49, 60 à 62). Cela permet une lubrification avantageuse destinée à réduire l'usure.
PCT/EP2011/072751 2010-12-17 2011-12-14 Pompe haute pression WO2012080330A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201180060238.8A CN103261661B (zh) 2010-12-17 2011-12-14 高压泵
EP11794767.1A EP2652309B1 (fr) 2010-12-17 2011-12-14 Pompe haute pression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010063351A DE102010063351A1 (de) 2010-12-17 2010-12-17 Hochdruckpumpe
DE102010063351.8 2010-12-17

Publications (1)

Publication Number Publication Date
WO2012080330A1 true WO2012080330A1 (fr) 2012-06-21

Family

ID=45346496

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/072751 WO2012080330A1 (fr) 2010-12-17 2011-12-14 Pompe haute pression

Country Status (4)

Country Link
EP (1) EP2652309B1 (fr)
CN (1) CN103261661B (fr)
DE (1) DE102010063351A1 (fr)
WO (1) WO2012080330A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013075949A1 (fr) * 2011-11-21 2013-05-30 Robert Bosch Gmbh Pompe haute pression
WO2014056975A1 (fr) * 2012-10-11 2014-04-17 Continental Automotive Gmbh Porte-galet multifonctionnel pour un ensemble poussoir à galet
US20150300476A1 (en) * 2014-04-22 2015-10-22 Aktiebolaget Skf Cam follower roller device, notably for a fuel injection pump
EP2673495B1 (fr) * 2011-02-07 2016-09-14 Robert Bosch GmbH Pompe haute pression et methode de fonctionnement de celle-ci
EP4055267A4 (fr) * 2019-12-19 2023-08-02 Cummins, Inc. Ensemble rouleau poussoir

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106438145B (zh) * 2016-11-30 2019-05-31 无锡威孚高科技集团股份有限公司 共轨高压泵的无销挺柱部件
GB2557630A (en) * 2016-12-13 2018-06-27 Delphi Int Operations Luxembourg Sarl Cam actuated fuel pump
CN107091183B (zh) * 2017-07-04 2024-05-31 辽阳新风科技有限公司 一种滚轮结构和高压油泵

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Publication number Priority date Publication date Assignee Title
US4708102A (en) * 1986-09-08 1987-11-24 Navistar International Transportation Corp. Roller cam follower with positive lubrication
DE10115168C1 (de) * 2001-03-27 2002-08-22 Orange Gmbh Kraftstoff-Hochdruckpumpe, insbesondere für Einspritzsysteme von Brennkraftmaschinen
EP1544462A2 (fr) * 2003-12-15 2005-06-22 Denso Corporation Pompe à carburant avec rainure de lubrification
DE102005046670A1 (de) 2005-09-29 2007-04-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
US20070277763A1 (en) * 2006-06-06 2007-12-06 Brinks Barry T Cam Roller Pin With Transverse Grooves
DE102006031032A1 (de) * 2006-07-05 2008-01-10 Schaeffler Kg Pumpenstößel

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Publication number Priority date Publication date Assignee Title
DE10256528A1 (de) * 2002-12-04 2004-06-24 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102008040081A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
DE102009002487A1 (de) * 2009-04-20 2010-10-21 Robert Bosch Gmbh Hochdruckpumpe
DE102009002520A1 (de) * 2009-04-21 2010-10-28 Robert Bosch Gmbh Hochdruckpumpe

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Publication number Priority date Publication date Assignee Title
US4708102A (en) * 1986-09-08 1987-11-24 Navistar International Transportation Corp. Roller cam follower with positive lubrication
DE10115168C1 (de) * 2001-03-27 2002-08-22 Orange Gmbh Kraftstoff-Hochdruckpumpe, insbesondere für Einspritzsysteme von Brennkraftmaschinen
EP1544462A2 (fr) * 2003-12-15 2005-06-22 Denso Corporation Pompe à carburant avec rainure de lubrification
DE102005046670A1 (de) 2005-09-29 2007-04-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
US20070277763A1 (en) * 2006-06-06 2007-12-06 Brinks Barry T Cam Roller Pin With Transverse Grooves
DE102006031032A1 (de) * 2006-07-05 2008-01-10 Schaeffler Kg Pumpenstößel

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2673495B1 (fr) * 2011-02-07 2016-09-14 Robert Bosch GmbH Pompe haute pression et methode de fonctionnement de celle-ci
WO2013075949A1 (fr) * 2011-11-21 2013-05-30 Robert Bosch Gmbh Pompe haute pression
WO2014056975A1 (fr) * 2012-10-11 2014-04-17 Continental Automotive Gmbh Porte-galet multifonctionnel pour un ensemble poussoir à galet
KR20150027239A (ko) * 2012-10-11 2015-03-11 콘티넨탈 오토모티브 게엠베하 롤러 태핏 조립체를 위한 다기능 롤러 클립
CN104641102A (zh) * 2012-10-11 2015-05-20 大陆汽车有限公司 用于滚子梃杆组件的多功能滚子夹具
KR101656089B1 (ko) 2012-10-11 2016-09-08 콘티넨탈 오토모티브 게엠베하 롤러 태핏 조립체를 위한 다기능 롤러 클립
US20150300476A1 (en) * 2014-04-22 2015-10-22 Aktiebolaget Skf Cam follower roller device, notably for a fuel injection pump
US9726270B2 (en) * 2014-04-22 2017-08-08 Aktiebolaget Skf Cam follower roller device, notably for a fuel injection pump
EP4055267A4 (fr) * 2019-12-19 2023-08-02 Cummins, Inc. Ensemble rouleau poussoir

Also Published As

Publication number Publication date
CN103261661A (zh) 2013-08-21
EP2652309B1 (fr) 2014-11-05
EP2652309A1 (fr) 2013-10-23
DE102010063351A1 (de) 2012-06-21
CN103261661B (zh) 2016-04-27

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