EP1931875B1 - High pressure pump, in particular for a fuel injection device of an internal combustion engine - Google Patents

High pressure pump, in particular for a fuel injection device of an internal combustion engine Download PDF

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Publication number
EP1931875B1
EP1931875B1 EP20060793348 EP06793348A EP1931875B1 EP 1931875 B1 EP1931875 B1 EP 1931875B1 EP 20060793348 EP20060793348 EP 20060793348 EP 06793348 A EP06793348 A EP 06793348A EP 1931875 B1 EP1931875 B1 EP 1931875B1
Authority
EP
European Patent Office
Prior art keywords
tappet
pump
high
pressure pump
ball
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP20060793348
Other languages
German (de)
French (fr)
Other versions
EP1931875A1 (en
Inventor
Alfons Schoetz
Gerhard Meier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to DE200510046670 priority Critical patent/DE102005046670A1/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to PCT/EP2006/066162 priority patent/WO2007036423A1/en
Publication of EP1931875A1 publication Critical patent/EP1931875A1/en
Application granted granted Critical
Publication of EP1931875B1 publication Critical patent/EP1931875B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02Pumps 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
    • F02M59/10Pumps 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
    • F02M59/102Mechanical drive, e.g. tappets or cams

Description

    State of the art
  • The invention relates to a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is through the DE 199 07 311 A1 known. This high-pressure pump has a pump housing and at least one pump element arranged in the pump element. The pump element has a driven by a drive shaft of the high pressure pump in a stroke pump piston. The pump piston is tightly guided in a cylinder bore of a pump housing part of the high-pressure pump and delimits a pump working space in the cylinder bore. The pump piston is supported at least indirectly via a hollow-cylindrical ram on the drive shaft. The plunger is slidably guided in a bore of a pump housing in the direction of the longitudinal axis of the pump piston. Under certain circumstances, there may be a rotation of the plunger about its longitudinal axis in the bore, whereby an increased wear of the plunger and / or the pump housing and possibly other parts of the high-pressure pump is caused. Conventional anti-rotation for the ram are expensive to manufacture and assembly.
  • Advantages of the invention
  • The high pressure pump according to the invention with the features of claim 1 has the advantage that an anti-rotation of the plunger is ensured by simple means. The ball is a standard part that can be purchased inexpensively as a vendor.
  • In the dependent claims advantageous refinements and developments of the high pressure pump according to the invention are given. Due to the design according to claim 2, a low friction in the rotation of the plunger is achieved because there is at least on a support of the ball on the plunger rolling friction. Due to the design according to claim 3, a safe investment of the ball is achieved in the groove of the plunger. The embodiment according to claim 4, a particularly low friction is achieved because there is rolling friction between both the ball and the plunger and between the ball and the recording. The embodiment according to claim 8, a particularly simple mounting of the receptacle and the ball is possible.
  • drawing
  • Two embodiments of the invention are illustrated in the drawing and explained in more detail in the following description. Show it FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section, FIG. 2 one in FIG. 1 with II designated section of the high pressure pump in an enlarged view according to a first embodiment, FIG. 3 the high-pressure pump in a section along line III-III in FIG. 2, FIG. 4 one in FIG. 3 with IV designated section in again enlarged view and FIG. 5 the detail II of the high pressure pump according to a second embodiment.
  • Description of the embodiments
  • In the FIGS. 1 to 5 a high pressure pump for a fuel injector of an internal combustion engine is shown. The high-pressure pump has a multipart pump housing 10 in which a drive shaft 12 driven in rotation by the internal combustion engine is arranged. The drive shaft 12 is rotatably supported, for example, via two bearing points spaced apart from one another in the direction of the axis of rotation 13 of the drive shaft 12. The bearings can be arranged in different parts of the pump housing 10, for example, a first bearing point in a base body 14 of the pump housing 10 and a second bearing point can be arranged in a connected to the base body 14 flange 15.
  • In a lying between the two bearing areas, the drive shaft 12 at least one cam 16 or eccentrically to its axis of rotation 13 formed portion, wherein the cam 16 may be formed as a multiple cam. The high pressure pump has at least one or more arranged in the housing 10 pump elements 18, each with a pump piston 20 which is driven by the cam 16 of the drive shaft 12 in a lifting movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12. In the region of each pump element 18, a pump housing part 22 connected to the main body 14 is provided, which is designed as a cylinder head. The pump housing part 22 has a voltage applied to an outer side of the base body 14 and a flange 24 through an opening in the base body 14 to the drive shaft 12 through protruding, at least approximately cylindrical projection 26 with respect to the flange 24 of smaller diameter. The pump piston 20 is guided tightly displaceable in a shoulder 26 formed in the cylinder bore 28 in the pump housing part 22 and limited with its drive shaft 12 facing away from the end face in the cylinder bore 28 a pump working space 30. The cylinder bore 28 may extend into the flange 24, in the then the pump working space 30 is arranged. The pump working chamber 30 has a connection with a fuel feed, for example a feed pump, via a fuel feed channel 32 extending in the pump housing 10. At the mouth of the fuel inlet channel 32 into the pump working chamber 30, an inlet valve 34 opening into the pump working chamber 30 is arranged. The pump working chamber 30 also has a connection in the pump housing 10 extending fuel drain passage 36 to an outlet with an outlet, which is connected for example to a high-pressure accumulator 110. One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine. At the mouth of the fuel drainage channel 36 into the pump working chamber 30, an outlet valve 38 opening out of the pump working chamber 30 is arranged.
  • Between the pump piston 20 and the cam 16 of the drive shaft 12, a plunger 40 is arranged, via which the pump piston 20 at least indirectly on the cam 16 of the drive shaft 12 is supported. The plunger 40 is formed in a hollow cylindrical shape with a round outer cross section and is guided displaceably in a bore 42 of the main body 14 of the pump housing 10 in the direction of the longitudinal axis 21 of the pump piston 20. The longitudinal axis 41 of the plunger 40 is thus at least substantially identical to the longitudinal axis 21 of the pump piston 20. In the ram 40, a support element 44 is inserted in the drive shaft 12 facing end portion in which a roller 46 is rotatably mounted, which rolls on the cam 16 of the drive shaft 12. The axis of rotation 47 of the roller 46 is at least approximately parallel to the axis of rotation 13 of the drive shaft 12. The support member 44 has on its side facing the drive shaft 12 a recess 48 in which the roller 46 is mounted.
  • On the plunger 40 or on the pump piston 20 engages a prestressed return spring 52, which is supported on the pump housing part 22. By the return spring 52, the pump piston 20 and the plunger 40 are acted upon cam 16 of the drive shaft 12 out, so that the contact of the roller 44 on the cam 16 and the intake shaft 12 toward the suction stroke of the pump piston 20 and at high speed of the drive shaft 12th is ensured. The pump piston 20 may be coupled to the plunger 40, at least in the direction of its longitudinal axis 21. Alternatively, the pump piston 20 may not be connected to the plunger 40, then by the return spring 52, the system of the pump piston 20 is secured to the plunger 40. It can be provided that the restoring spring 52 engages, for example, via a spring plate 53 on an enlarged diameter piston base of the pump piston 20, which is thereby held in abutment against a flange projecting inwardly from the sleeve on the plunger 40, which in turn bears against the support element 44 is held, so that the entire composite of pump piston 20, plunger 40 and support member 44 is acted upon with roller 46 to the cam 16 of the drive shaft 12 out.
  • In the outer casing of the plunger 40, at least one extending in the direction of the longitudinal axis 41 groove 56 is arranged, which preferably at least in cross section is approximately circular section shaped. In the groove 56 engages at least approximately radially to the longitudinal axis 41 of the plunger 40, a ball 58 with a part of its circumference, which is fixed in the pump housing 10 in the tangential direction to the plunger 40. In the FIGS. 2 to 4 the high-pressure pump is shown according to a first embodiment, in which the ball 58 is movably guided in a receptacle 60 in the direction of the longitudinal axis 41 of the plunger 40. The receptacle 60 has as in FIGS. 2 and 4 1 illustrates a channel-shaped recess 62, which is at least substantially prismatic in cross-section perpendicular to the longitudinal axis 41 of the plunger 40 and has two mutually opposite oblique walls against which the ball 58 abuts. The ball 58 dives with part of its circumference in the recess 62 and is thereby fixed in the tangential direction of the plunger 40, so that the plunger 40 is secured by the ball 58 against rotation about its longitudinal axis 41. During the lifting movement of the plunger 40 together with the pump piston 20, the ball 58 rolls both in the groove 56 of the plunger 40 and in the recess 62 of the receptacle 60, so that only a small rolling friction occurs.
  • The recording 60 is like in the FIGS. 2 and 3 represented for example in a at least approximately radially with respect to the longitudinal axis 41 of the plunger 40 arranged bore 64 in the base body 14 of the pump housing 10 is inserted. The receptacle 60 is cylindrical in shape, on the tappet 40 facing the inside of the recess 62 is formed. The bore 64 is closed to the outside of the main body 14 of the pump housing 10 by means of a plug 66. Between the plug 66 and the receptacle 60 is preferably a prestressed spring 68, for example a helical compression spring, clamped by the displaceable in the bore 64 receptacle 60 and thus the ball 58th is pressed towards the plunger 40. In an annular groove of the plug 66 may be an elastic sealing ring 70, for example, an O-ring, be arranged to seal the interior of the pump housing 10 to the outside. It can be provided that the plug 66 is screwed or pressed into the bore 64. In addition, it can be provided that the flange part 15 at least partially covers the bore 64 in a state assembled with the base body 14 and thus secures the stopper 66 in the bore 64. The receptacle 60 with the ball 58, the plug 66 and the spring 68 are inserted before the assembly of the pump housing 10 in the bore 64 from the outside of the base body 14 forth. When mounting the receptacle 60, it must be ensured that its recess 62 is aligned exactly parallel to the groove 56 of the plunger 40 in order to allow the lifting movement of the plunger 40 with the least possible friction.
  • The depth of the groove 56 in the plunger 40 and thus the immersion depth of the ball 58 in the groove 56 and the bias of the spring 68 determine the magnitude of the torque against which the plunger 40 can be secured against rotation. The greater the depth of the groove 56 and thus the immersion depth of the ball 58 in this and the greater the bias of the spring 68, the greater the torque against which the plunger 40 can be secured against rotation.
  • In FIG. 5 is the high-pressure pump according to a second embodiment shown, in which the basic structure of the high-pressure pump is the same as in the first embodiment, but the receptacle 160 is modified for the ball 58. The receptacle 160 has on its side facing the plunger 40 on a kugelkalottenförmige recess 162 in which the ball 58 is rotatably mounted. The receptacle 160 is in a blind bore of the Hole 64 in the base body 14 of the pump housing 10 occluding stopper 166 slidably inserted. Between the plug 166 and the receptacle 160, the prestressed spring 68 is arranged. An advantage of the embodiment of the high pressure pump according to the second embodiment is that the receptacle 160 is formed simpler than in the first embodiment and that the receptacle 160 can be used in any rotational positions in the pump housing 10. However, in the second embodiment, only between the ball 58 and the plunger 40 rolling friction exists, while between the ball 58 and the receptacle 160 is sliding friction.
  • When the suction stroke of the pump piston 20, in which this moves radially inward, the pump chamber 30 is filled by the Kraftstoffzulaüfkanal 32 with open inlet valve 34 with fuel, the exhaust valve 38 is closed. During the delivery stroke of the pump piston 20, in which this moves radially outward, fuel is pumped under high pressure through the fuel discharge passage 36 with the exhaust valve 38 open to the high-pressure accumulator 110 by the pump piston 20, wherein the inlet valve 34 is closed.

Claims (10)

  1. High-pressure pump, in particular for a fuel injection device of an internal combustion engine, with a pump casing (10, 14, 22), with at least one pump element (18) which has a pump piston (20) which is driven in a lifting movement by a drive shaft (12) and which is guided displaceably in a cylinder bore (28) of part of the pump casing (22) and delimits a pump working space (30) in the said cylinder bore, the pump piston (20) being supported at least indirectly via a hollow-cylindrical tappet (40) on the drive shaft (12), the tappet (40) being guided displaceably in a bore (42) of part of the pump casing (14) in the direction of the longitudinal axis (21) of the pump piston (20), characterized in that the tappet (40) has in its outer casing a groove (56) which runs in the direction of its longitudinal axis (41) and into which a ball (58) fixed at least indirectly in part of the pump casing (14) in the tangential direction to the tappet (40) engages, at least approximately radially to the longitudinal axis (41) of the tappet (40), so as to protect the tappet (40) against twisting.
  2. High-pressure pump according to Claim 1, characterized in that rolling friction prevails at least between the ball (58) and the tappet (40).
  3. High-pressure pump according to Claim 1 or 2, characterized in that the ball (58) is pressed into the groove (56) of the tappet (40) at least indirectly by a prestressed spring (68).
  4. High-pressure pump according to Claim 2 or 3, characterized in that the ball (58) is guided movably in the direction of the longitudinal axis (41) of the tappet (40) in a receptacle (60) arranged in the pump-casing part (14).
  5. High-pressure pump according to Claim 4, characterized in that the guide (62) for the ball (58) in the receptacle (60) is of at least approximately prismatic design in cross section perpendicularly to the longitudinal axis (41) of the tappet (40).
  6. High-pressure pump according to Claim 2 or 3, characterized in that the ball (58) is mounted rotatably in a receptacle (160) arranged in the pump-casing part (14).
  7. High-pressure pump according to Claim 6, characterized in that the receptacle (160) has an at least approximately spherical-cap-shaped depression (162) in which the ball (58) is mounted.
  8. High-pressure pump according to one of Claims 4 to 7, characterized in that the receptacle (60; 160) is inserted in a bore (64) in the pump-casing part (14), preferably from an outer side of the pump-casing part (14) which faces away from the bore (42) in which the tappet (40) is guided.
  9. High-pressure pump according to Claim 3, and at least one of Claims 4 to 8, characterized in that the receptacle (60; 160) is movable in an at least approximately radial direction with respect to the longitudinal axis (41) of the tappet (40) and in that the spring (68) acts on that outer side of the receptacle (60; 160) which faces away from the tappet (40).
  10. High-pressure pump according to one of the preceding claims, characterized in that a roller (46), via which the tappet (40) is supported on the drive shaft (12), is at least indirectly mounted rotatably in the tappet (40).
EP20060793348 2005-09-29 2006-09-08 High pressure pump, in particular for a fuel injection device of an internal combustion engine Expired - Fee Related EP1931875B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE200510046670 DE102005046670A1 (en) 2005-09-29 2005-09-29 High pressure pump for fuel injection device of internal combustion engine, has ball indirectly fixed in part of base plate in tangential direction to tappet and engaged in groove approximately radial to longitudinal axis of tappet
PCT/EP2006/066162 WO2007036423A1 (en) 2005-09-29 2006-09-08 High pressure pump, in particular for a fuel injection device of an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1931875A1 EP1931875A1 (en) 2008-06-18
EP1931875B1 true EP1931875B1 (en) 2010-03-10

Family

ID=37398784

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060793348 Expired - Fee Related EP1931875B1 (en) 2005-09-29 2006-09-08 High pressure pump, in particular for a fuel injection device of an internal combustion engine

Country Status (4)

Country Link
EP (1) EP1931875B1 (en)
AT (1) AT460584T (en)
DE (2) DE102005046670A1 (en)
WO (1) WO2007036423A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009028392B4 (en) * 2009-08-10 2018-05-24 Robert Bosch Gmbh high pressure pump

Families Citing this family (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007049148A1 (en) 2007-10-12 2009-04-16 Robert Bosch Gmbh High-pressure fuel pump for fuel injection device of internal-combustion engine, has spring plate rotatably provided around predetermined limited angle range around longitudinal axis, and coupled unrotatably with supporting element
ITMI20080288A1 (en) * 2008-02-22 2009-08-23 Bosch Gmbh Robert High-pressure pump for supplying high pressure fuel to an internal combustion engine
DE102008000710A1 (en) 2008-03-17 2009-09-24 Robert Bosch Gmbh high pressure pump
DE102008015548A1 (en) 2008-03-25 2009-10-01 Robert Bosch Gmbh High-pressure pump i.e. radial or series piston pump, for fuel injection system of air-compressing self-ignition internal-combustion engine, has anti-twist protection pin indirectly connecting with roller support and housing parts
DE102008015547A1 (en) 2008-03-25 2009-10-01 Robert Bosch Gmbh High pressure pump, particularly radial piston pump or in-line piston pump for fuel injection systems of air compressors or self-igniting internal combustion engines, comprises drive shaft that has cam attached to pump assembly
DE102008001890A1 (en) 2008-05-21 2009-11-26 Robert Bosch Gmbh High-pressure pump i.e. radial or tandem piston pump, for fuel i.e. diesel, injection system of air compressed, self ignition internal combustion engine, has aligning element for aligning tappet body in orientation at area
DE102008002178A1 (en) 2008-06-03 2009-12-10 Robert Bosch Gmbh High-pressure pump i.e. radial or row piston pump, for fuel injection system of air-compressing, self-igniting internal-combustion engine, has anti-twist protection pin whose end is intervened in cylinder head
DE102008040081A1 (en) 2008-07-02 2010-01-07 Robert Bosch Gmbh high pressure pump
DE102008040083A1 (en) 2008-07-02 2010-01-07 Robert Bosch Gmbh high pressure pump
DE102008040075A1 (en) 2008-07-02 2010-01-07 Robert Bosch Gmbh High pressure pump, particularly fuel pump for fuel injection systems of air-compression, self-igniting internal combustion engines, has pump assembly provided in housing, and drive shaft which has cam assigned to pump assembly
DE102008040961A1 (en) 2008-08-04 2010-02-11 Robert Bosch Gmbh High pressure fuel pump for operating internal-combustion engine of motor vehicle, has pin positioned in pump housing and inclined to movement axis of pump piston, where pump piston engages with tip of pin in recess of tappet body
DE102008040959A1 (en) 2008-08-04 2010-02-11 Robert Bosch Gmbh High pressure fuel pump for operating internal-combustion engine of motor vehicle, has insertion part extended with nose-like projection into slotted hole-like recess of hollow-cylindrical tappet body
DE102008050661A1 (en) 2008-09-22 2010-03-25 Vladimir Volchkov Drive device i.e. high pressure pump, for fuel injection to reciprocating piston engine, has return spring component consisting of pairs of helical compression springs, and pistons provided on supporting element
DE102008050657A1 (en) 2008-09-22 2010-03-25 Vladimir Volchkov Driving gear for reciprocating piston engines, particularly for fuel injecting high-pressure pumps, has return spring component, where each pair has two springs with left- and right rotation points
DE102008050662A1 (en) 2008-09-22 2010-03-25 Vladimir Volchkov Driving gear for reciprocating piston engines, particularly for fuel injecting high-pressure pumps, has main body, where roller turns away from cam or extender wheel, and roller is provided in support element
DE102008043846A1 (en) 2008-11-19 2010-05-20 Robert Bosch Gmbh High pressure pump, particularly radial or in-line piston pump for fuel injection units of air compression, self igniting internal combustion engines, has pump assembly and piston with guide bush and pressure piece
DE102008043847A1 (en) 2008-11-19 2010-05-20 Robert Bosch Gmbh High-pressure pump e.g. radial piston pump, for fuel injection system of e.g. self-igniting internal-combustion engine, has pump assembly, and drive shaft with cam, where angles to axis of pump assembly are preset for respective gap areas
DE102008043839A1 (en) 2008-11-19 2010-05-20 Robert Bosch Gmbh High pressure pump, particularly fuel pump for fuel injection units of air compression, self igniting internal combustion engines, comprises pump assembly which has pump piston and pump working chamber that is limited by pump piston
DE102009002487A1 (en) 2009-04-20 2010-10-21 Robert Bosch Gmbh High-pressure pump for use as e.g. radial piston pump utilized for air-compressing auto-ignition internal combustion engine, has piston that is driven into pressure chamber by directly applying pressure on plunger during suction stroke
DE102009002518A1 (en) 2009-04-21 2010-10-28 Robert Bosch Gmbh high pressure pump
DE102009002520A1 (en) 2009-04-21 2010-10-28 Robert Bosch Gmbh High-pressure pump, particularly radial piston pump or in-line piston pump for fuel injection systems of air-compressing, self-ignited internal combustion engines, has pump assembly and drive shaft
DE102009003054A1 (en) 2009-05-13 2010-11-18 Robert Bosch Gmbh high pressure pump
DE102009003097B4 (en) 2009-05-14 2018-02-08 Robert Bosch Gmbh High-pressure pump, in particular radial piston pump, with at least one plunger body, a rotatable roller shoe, a roller and an axial contact point for the roller, which is arranged at a distance from the axis of rotation of the roller
DE102009027145A1 (en) 2009-06-24 2010-12-30 Robert Bosch Gmbh High pressure pump for e.g. radial piston pump of fuel injection system of self-igniting internal combustion engine, has mechanically actuatable locking device locking drive shaft in predetermined rotational position of drive shaft
DE102009028381A1 (en) 2009-08-10 2011-02-17 Robert Bosch Gmbh High pressure pump e.g. radial piston pump, for fuel injection system of air-compressing auto-ignition internal combustion engine, has drive shaft supported in housing part by slide bearing, and slide bearing injected into housing
DE102009028394A1 (en) * 2009-08-10 2011-02-17 Robert Bosch Gmbh high pressure pump
DE102009046284A1 (en) 2009-11-02 2011-05-12 Robert Bosch Gmbh Method for coating and/or post-processing a workpiece, comprises partially applying a layer by arc deposition on an outer side of the workpiece, and treating the workpiece coated with the layer in the area of the applied layer
DE102009047380A1 (en) 2009-12-02 2011-06-09 Robert Bosch Gmbh Pump i.e. fuel pump, for fuel injection system of air-compressing self-igniting internal-combustion engine, has volume-balancing device provided for squeezing area of pump assembly and partially balancing variation of volume of area
DE102010003886A1 (en) 2010-04-13 2011-10-13 Robert Bosch Gmbh high pressure pump
DE102010027749A1 (en) 2010-04-14 2011-10-20 Robert Bosch Gmbh High pressure pump e.g. radial piston pump, for fuel injection in air-compressing, self-igniting internal combustion engine, has plunger hole with elliptical cross section, where outer sides of plunger body are adapted to cross section
DE102010027792A1 (en) 2010-04-15 2011-10-20 Robert Bosch Gmbh high pressure pump
DE102010030792A1 (en) 2010-07-01 2012-01-05 Robert Bosch Gmbh High pressure pump for fuel injector of combustion engine, has plunger radially pre-tensioned under use of hydraulic force such that ball is pushed into longitudinal groove of plunger, where ball is subjected with force in radial direction
DE102010031616A1 (en) 2010-07-21 2012-01-26 Robert Bosch Gmbh High pressure pump i.e. radial/series piston pump, for air-compressing type diesel injection system of self-ignition type combustion engine, has driving part provided in roller such that driving part and gear are partly interlinked
DE102010038468A1 (en) 2010-07-27 2012-02-02 Robert Bosch Gmbh high pressure pump
DE102010063328A1 (en) 2010-12-17 2012-06-21 Robert Bosch Gmbh high pressure pump
DE102010063321A1 (en) 2010-12-17 2012-06-21 Robert Bosch Gmbh high pressure pump
DE102010063351A1 (en) 2010-12-17 2012-06-21 Robert Bosch Gmbh high pressure pump
JP5605380B2 (en) * 2012-02-03 2014-10-15 株式会社デンソー Supply pump
DE102012204264A1 (en) 2012-03-19 2013-09-19 Robert Bosch Gmbh high pressure pump
DE102017107100B3 (en) * 2017-04-03 2018-06-14 Schaeffler Technologies AG & Co. KG Lightweight roller tappet

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DE4041656A1 (en) * 1990-12-22 1992-07-02 Bosch Gmbh Robert Fuel injection pump for internal combustion engines
DE19907311A1 (en) 1999-02-22 2000-08-31 Bosch Gmbh Robert Hydraulic pump unit
DE10345089A1 (en) * 2003-09-26 2005-04-21 Bosch Gmbh Robert Plunger for a high pressure pump and high pressure pump with at least one plunger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009028392B4 (en) * 2009-08-10 2018-05-24 Robert Bosch Gmbh high pressure pump

Also Published As

Publication number Publication date
DE102005046670A1 (en) 2007-04-05
DE502006006407D1 (en) 2010-04-22
AT460584T (en) 2010-03-15
WO2007036423A1 (en) 2007-04-05
EP1931875A1 (en) 2008-06-18

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