EP2652309B1 - Pompe haute pression - Google Patents

Pompe haute pression Download PDF

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Publication number
EP2652309B1
EP2652309B1 EP11794767.1A EP11794767A EP2652309B1 EP 2652309 B1 EP2652309 B1 EP 2652309B1 EP 11794767 A EP11794767 A EP 11794767A EP 2652309 B1 EP2652309 B1 EP 2652309B1
Authority
EP
European Patent Office
Prior art keywords
roller
lubricant
pressure pump
rotation
axis
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.)
Not-in-force
Application number
EP11794767.1A
Other languages
German (de)
English (en)
Other versions
EP2652309A1 (fr
Inventor
Francesco Lucarelli
Frank Scholz
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2652309A1 publication Critical patent/EP2652309A1/fr
Application granted granted Critical
Publication of EP2652309B1 publication Critical patent/EP2652309B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M59/10—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 linear piston pump. Specifically, the invention relates to the field of fuel pumps for fuel injection systems of air-compression, self-igniting internal combustion engines.
  • a high-pressure pump for a fuel injection device of an internal combustion engine 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.
  • a pump tappet with a plunger housing which has a longitudinally movably mounted in a guide tappet shirt and a roller space, and with a roll arranged in the roller space whose outer surface can be driven by a pump cam and whose inner circumferential surface together with a bolt attached to the plunger housing forms a bearing point in the form of a sliding or needle bearing.
  • To supply lubricant to the outer circumferential surface of the roller and / or to the bearing running transverse bores are provided by the plunger shirt, via which the roller space is connected to a lubricant feed channel opening into the guide.
  • the tappet shirt should have an outer annular groove connecting the transverse bores with the lubricant supply channel.
  • 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 side surface of the roller at least one designed as a recess lubricant recess is provided.
  • the side surface of the roller cooperates with the abutment surface of the tappet body to permit axial bearing.
  • Lubricants in particular diesel fuel
  • 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. In this way, as it were, a conveying effect for conveying the lubricant through the lubricant recess to the contact region can be achieved. As a result, the lubrication is further improved.
  • At least one lubricant recess designed as a blind hole is provided on the side surface of the roller.
  • lubricant in particular diesel fuel
  • 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 back pressure of the lubricant in the blind hole, whereby the hydrodynamic lubrication is improved.
  • the blind hole is at least approximately parallel to a rotational axis of the roller configured. In this way, the production of the roller can be facilitated with one or more blind holes. In addition, the blind hole can be made comparatively long.
  • At least one lubricant recess designed as a lubricant channel is provided on the plunger body and that one end of the lubricant channel opens onto the contact surface of the plunger body.
  • 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.
  • 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 having a fuel rail which stores diesel fuel under high pressure.
  • the high-pressure pump 1 according to the invention is also suitable for other applications.
  • the high-pressure pump 1 has a multipart pump housing 2 and a drive shaft 3 arranged in the pump housing 2.
  • 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 11 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 may be associated with other pump assemblies.
  • further cams may be provided adjacent to the cam 10, which in turn may be associated with pump assemblies.
  • 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.
  • the pump assembly 15 has a hollow cylindrical plunger body 18, which is guided in the bore 16 along an axis 19.
  • 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 which extends along the axis 19 through the projection 17 of the cylinder head 6.
  • the pump piston 23 is guided along the axis 19 in the cylinder bore 24.
  • the pump piston 23 is guided by the driving element 20.
  • the pump piston 23 has a piston foot 25.
  • a roller shoe 26 is inserted in the plunger body 18.
  • the piston foot 25 is held by the driving element 20 against the roller shoe 26.
  • a roller 27 of the pump assembly 15 is mounted. In operation, the roller 27 rolls on a running surface 28 of the cam 10, wherein the roller 27 rotates about its axis of rotation 29. As a result of the lifting movement of the cam 10, 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 delimits a pump working space 31 in the cylinder bore 24.
  • filling of the pump working space 31 is made possible by means of an inlet valve 32 in a stroke of the pump piston 23 against 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.
  • the side surface 37 of the roller 27 of the contact surface 35 of the plunger body 18 faces.
  • the side surface 38 of the roller 27 of the contact surface 36 of the plunger body 18 faces.
  • 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.
  • the roller 27 has 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 in Fig. 1 shown sectional view of 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.
  • the lubricant recesses 40 to 43 are preferably arranged uniformly around the rotation axis 29 of the roller 27.
  • the lubricant recesses 40, 42 of the roller 27 can be filled from the interior 39 with diesel fuel.
  • the lubricant recesses 41, 43 are located in the illustrated position of the roller 27 within the receptacle of the plunger body 18 for the roller 27.
  • from the Schmierstoffaus traditions 41, 43 serve as a lubricant serving diesel oil.
  • 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.
  • the occurrence of frictional forces that lead to wear or particle formation avoided.
  • damage to the high-pressure pump 1 over the lifetime can be avoided.
  • the lubricant recesses 40 to 43 are designed as blind holes 40 to 43.
  • the blind bores 40 to 43 in this case each extend parallel to the axis of rotation 29 of the roller 27.
  • Fig. 2 shows a roller 27 of a pump assembly 15 of in Fig. 1 illustrated high-pressure pump 1 from the designated II viewing direction according to a second embodiment.
  • the roller 27 on its side surface 38 lubricant recesses 42, 43, 44, 45, 46, 47, 48, 49.
  • the lubricant recesses 42 to 49 extend as far as a rolling surface 50 of the roller 27 with which the roller 27 rolls on the running surface 11 of the cam 10.
  • 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 configured in this embodiment as recesses 42 to 49.
  • the recesses 42 to 49 are in this case introduced into the side surface 38 of the roller 27.
  • a region 53 of the side surface 38 about the rotation axis 29 or the center 29 ', in which the roller 27 for axial bearing at least substantially together with the contact surface 36 of the plunger body 18 cooperates, is hereby released.
  • 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 configured according to the lubricant recess 42 and also contribute to the improvement of lubrication. Since the lubricant recesses 42 to 49 are distributed uniformly around the rotation axis 29 on the side surface 38, uniform lubrication in the contact region results during operation.
  • 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.
  • a corresponding design provided with lubricant recesses.
  • Fig. 3 shows the in Fig. 2 illustrated roller 27 according to a third embodiment.
  • 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 basis of the Fig. 1 described first 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.
  • the half-line 51 with the axis 56 in this embodiment includes an angle 57 of at least approximately 90 °.
  • the axis 56 of the blind hole 42 also has a component of the rotation axis 29.
  • the blind hole 42 is 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.
  • 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 in Fig. 1 illustrated high-pressure pump 1 according to a fourth embodiment of the designated II viewing direction.
  • the embodiment is independent of the predetermined direction of rotation 55 for the roller 27th
  • 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, which extend from the outer side 63 of the plunger body 18 to the inner abutment surface 35 of the plunger body 18.
  • Fig. 5 shows the in Fig. 1 V section of the pump assembly 15 of the high-pressure pump 1 in a schematic, excerpted sectional view according to a fifth embodiment.
  • 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.
  • diesel oil is guided through the lubricant channel 61 into the region between the side face 38 of the roller 27 and the stop face 36 of the tappet body 18, in particular during a delivery stroke of the pump assembly 15. This results in a reinforced lubrication just in a delivery stroke, in which the forces acting are large.
  • lubricant recesses 60 to 62 are configured parallel to the axis of rotation 29, as for example in the case of the Fig. 4 illustrated embodiment is possible. Furthermore, in the case of the Fig. 5 illustrated embodiment further lubricant recesses 60, 62 may be provided.
  • the lubricant recesses 60 to 62 are preferably distributed around the rotation axis 29 provided on the plunger body 18. As a result, for example, opens an end 64 of the lubricant recess 16 in the conveying direction 30 above the axis of rotation 29 in the thrust surface 36.
  • the two other Schmierstoffaus traditions 60, 61 may open at least approximately at the height of the axis of rotation 29 in 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.

Claims (9)

  1. Pompe à haute pression (1), notamment pompe à pistons radiaux ou en ligne pour systèmes d'injection de combustible de machines à combustion interne à autoallumage de compression d'air, comprenant au moins un sous-ensemble pompe (15) et un arbre d'entraînement (3) qui présente au moins une came (10) associée au sous-ensemble pompe (15), le sous-ensemble pompe (15) présentant un galet de roulement (27) qui tourne sur une surface de roulement (11) de la came (10) et un corps de coulisseau (18) sur lequel le galet de roulement (27) est monté au moins dans le sens axial, au moins un évidement à lubrifiant (40 - 49, 60 - 62) étant configuré sur au moins une surface latérale (37, 38) du galet de roulement (27) et/ou sur au moins une surface d'arrêt (35, 36) du corps de coulisseau (18) sur laquelle le galet de roulement (27) est monté dans le sens axial avec sa surface latérale (37, 38), caractérisée en ce qu'au moins un évidement à lubrifiant (42 - 49) réalisé sous la forme d'un enfoncement (42 - 49) est prévu sur la surface latérale (37, 38) du galet de roulement (27).
  2. Pompe à haute pression selon la revendication 1, caractérisée en ce que l'enfoncement (42 - 49) sur la surface latérale (37, 38) du galet de roulement (27) est configuré en direction d'une surface roulante (50) du galet de roulement (27) avec un tracé (56) qui se situe entre une direction radiale (52) et un sens de rotation (55) du galet de roulement (27).
  3. Pompe à haute pression selon l'une des revendications précédentes, caractérisée en ce qu'au moins un évidement à lubrifiant (40 - 45) réalisé sous la forme d'un alésage borgne (40 - 45) est prévu sur la surface latérale (37, 38) du galet de roulement (27).
  4. Pompe à haute pression selon la revendication 3, caractérisée en ce qu'un axe (56) de l'alésage borgne (42) est orienté vers l'extérieur au moins partiellement dans un sens de rotation (55) du galet de roulement (27).
  5. Pompe à haute pression selon la revendication 3, caractérisée en ce que l'alésage borgne (40 - 43) est configuré au moins approximativement parallèlement à un axe de rotation (29) du galet de roulement (27).
  6. Pompe à haute pression selon l'une des revendications 3 à 5, caractérisée en ce qu'au moins quatre évidements à lubrifiant (40 - 45) réalisés sous la forme d'alésages borgnes (40 - 45) sont prévus sur la surface latérale (37, 38) du galet de roulement (27), lesquels débouchent sur la surface latérale (37, 38) du galet de roulement (27) en étant distribués régulièrement autour d'un axe de rotation (29), et en ce que le galet de roulement (27) avec la surface latérale (37, 38) est monté dans le sens axial sur la surface d'arrêt (35, 36) du corps de coulisseau (18) au moins dans la zone (53) de l'axe de rotation (29).
  7. Pompe à haute pression selon l'une des revendications précédentes, caractérisée en ce qu'au moins un évidement à lubrifiant (60 - 62) réalisé sous la forme d'un canal à lubrifiant (60 - 62) est prévu sur le corps de coulisseau (18) et en ce qu'une extrémité (64) du canal à lubrifiant (61) débouche sur la surface d'arrêt (36) du corps de coulisseau (18).
  8. Pompe à haute pression selon la revendication 7, caractérisée en ce que le canal à lubrifiant (60 - 62) à partir de la surface d'arrêt (36) intérieure du corps de coulisseau (18) vers un côté extérieur (63) du corps de coulisseau (18) est configuré au moins partiellement incliné dans un sens de refoulement (30) du sous-ensemble pompe (15).
  9. Pompe à haute pression selon la revendication 7 ou 8, caractérisée en ce qu'au moins trois évidements à lubrifiant (60 - 62) réalisés sous la forme de canaux à lubrifiant (60 - 62) sont prévus sur le corps de coulisseau (18) et en ce que les extrémités (64) des canaux à lubrifiant (60 - 62) débouchent sur la surface d'arrêt (36) du corps de coulisseau (18) en étant distribuées autour d'un axe de rotation (29) du galet de roulement (27).
EP11794767.1A 2010-12-17 2011-12-14 Pompe haute pression Not-in-force EP2652309B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010063351A DE102010063351A1 (de) 2010-12-17 2010-12-17 Hochdruckpumpe
PCT/EP2011/072751 WO2012080330A1 (fr) 2010-12-17 2011-12-14 Pompe haute pression

Publications (2)

Publication Number Publication Date
EP2652309A1 EP2652309A1 (fr) 2013-10-23
EP2652309B1 true EP2652309B1 (fr) 2014-11-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11794767.1A Not-in-force EP2652309B1 (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)

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KR101656089B1 (ko) * 2012-10-11 2016-09-08 콘티넨탈 오토모티브 게엠베하 롤러 태핏 조립체를 위한 다기능 롤러 클립
EP2937566B1 (fr) * 2014-04-22 2016-10-19 Aktiebolaget SKF Dispositif de galet suiveur de came, notamment pour un pompe à injection de carburant
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
CN107091183A (zh) * 2017-07-04 2017-08-25 辽阳新风科技有限公司 一种滚轮结构和高压油泵
US20230003183A1 (en) * 2019-12-19 2023-01-05 Mustafa Utku Unal Tappet roller assembly

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DE102005046670A1 (de) 2005-09-29 2007-04-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
US7878169B2 (en) * 2006-06-06 2011-02-01 Woodward Governor Company Cam roller pin with transverse grooves
DE102006031032A1 (de) * 2006-07-05 2008-01-10 Schaeffler Kg Pumpenstößel
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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CN103261661B (zh) 2016-04-27
CN103261661A (zh) 2013-08-21
DE102010063351A1 (de) 2012-06-21
WO2012080330A1 (fr) 2012-06-21
EP2652309A1 (fr) 2013-10-23

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