EP2823177A1 - Pompe à piston - Google Patents

Pompe à piston

Info

Publication number
EP2823177A1
EP2823177A1 EP13700489.1A EP13700489A EP2823177A1 EP 2823177 A1 EP2823177 A1 EP 2823177A1 EP 13700489 A EP13700489 A EP 13700489A EP 2823177 A1 EP2823177 A1 EP 2823177A1
Authority
EP
European Patent Office
Prior art keywords
roller
board
face
piston
piston pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13700489.1A
Other languages
German (de)
English (en)
Other versions
EP2823177B1 (fr
Inventor
Gerhard Meier
Dominik Meinzer
Markus Schetter
Jochen Aleker
Arnold Gente
Andreas Dutt
Frank Maurer
Matthias Greiner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2823177A1 publication Critical patent/EP2823177A1/fr
Application granted granted Critical
Publication of EP2823177B1 publication Critical patent/EP2823177B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • 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
    • F04B1/0435—Arrangements for disconnecting the pistons from the actuated cam
    • 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

Definitions

  • the present invention relates to a piston pump, in particular a
  • High-pressure fuel pump comprising a housing, a piston and a drive shaft with a cam portion on which the piston is supported at least indirectly via a roller rotatably mounted in a roller tappet, wherein the side of the cam portion is provided on both sides in each case a board in the radial Direction extends beyond the cam portion.
  • the field of application of the present invention extends to piston pumps, in particular high-pressure fuel pumps, which are used for internal combustion engines in motor vehicles.
  • the drive shaft has a cam portion, on which the piston is indirectly supported via a rotatably mounted in a roller tappet roller.
  • a board is provided on both sides of the drive shaft, which extends in the radial direction over the cam portion.
  • Run-on surfaces for the roller where it comes with axial displacement and / or rotation of the ideal position to the plant.
  • EP 2 079 923 B1 discloses a piston pump of a
  • the piston pump has a piston that can be moved axially back and forth in a cylinder.
  • the piston is displaced by the cam of a camshaft against the force of a spring, wherein the spring as
  • a roller tappet usually consists of a tappet body on which a roller is rotatably mounted and held. This roller runs on the cam portion of the cam, whereby the friction between the camshaft and the piston is minimized.
  • On both sides of the cam portion is a shelf in the radial direction over the
  • Cam portion protruding arranged so that an axial movement and / or rotation of the ideal position of the roller is limited by the shelves to a defined extent.
  • a suitable, tribological mating of the roller and the edges of the wear on the roller and on the board kept so low that it does not lead to malfunction or a shortening of the life of the piston pump.
  • the roller is rotated by the friction occurring at the start of one of the ribs in rotation, if they do not already rotate by the rolling friction between the cam portion and roller.
  • the board tapers at an end face directed towards the roller towards an outer periphery of the rim and is in particular conically shaped such that an opening inclination results, wherein the roller on a face directed towards the board has a convex curvature, preferably with one Radius has.
  • This design of the board reliably prevents corner contact of the roller with the board. Corner contacts are characterized by high surface pressures and can lead to edge breakage. Edge breakages entail great risks for the operational safety of the piston pump and can lead to undesired operating failures of the piston pump.
  • the invention includes the technical teaching that an angle between a perpendicular to a longitudinal axis of the roller and the one to a
  • Outer circumference of the board tapered face is 0.1 ° to 10 ° and the radius of a directed to the board end face of the roller between 1 mm and 40 mm in size.
  • the board has a convex curvature, preferably with a radius, on a face directed towards the roller and the roller tapers on an end face directed toward the board towards the end face of the roller, the end face being in particular conically shaped, so that gives an opening inclination.
  • This design of the board reliably prevents corner contact of the roller with the board. Corner contacts are characterized by high surface pressures and can lead to edge breakage. Edge breakages entail great risks for the operational safety of the piston pump and can lead to operational failures of the piston pump.
  • Axial longitudinal axis of the roller and the tapered to an outer periphery of the rim face 0.1 ° to 10 ° and the radius of a directed to the board end face of the roller between 1 mm and 40 mm in size.
  • Such a design of the contact surfaces promotes a line contact and thus prevents the punctual contact on a sharp edge.
  • the board and the cam section are integrally formed.
  • the board and / or the roller made of a hardenable iron material. Manufacturing technology and from the point of view of assembly, the one-piece design allows a safe and easy way of on-board training on the camshaft. Furthermore, the
  • Wear resistance at the contact surfaces of the board and the roller can be increased by a surface hardening.
  • the board and / or the roller have a surface treatment to minimize friction.
  • a surface treatment is a
  • Surface texture can be realized in particular by grinding, polishing or etching.
  • the board has a lower height than half the diameter of the roller.
  • a small height of the board is associated with a greater restoring force of the roller and thus also reduces the wear of the contact surfaces of the board and the roller.
  • FIG. 2 is an enlarged schematic sectional view of the marked in Figure 1 area, comprising a cam portion including board and roller, 3 is a schematic sectional view of that shown in FIG.
  • FIG. 1 shows a piston pump which comprises a housing 1 in which a drive shaft 2 is mounted via two bearings 7a and 7b. Further, the drive shaft 2 between the two bearings 7a and 7b comprises a cross-sectionally oval Nockenabschitt 3.
  • the piston pump serves as a high-pressure fuel pump for an internal combustion engine in a motor vehicle. With it, the fuel is compressed to a very high pressure and conveyed to a fuel manifold, not shown here.
  • Piston pump is driven directly by the internal combustion engine. Therefore, the drive shaft 2 has a corresponding coupling portion 8, which is arranged outside of the housing 1.
  • the piston of the piston pump, not shown here is of the
  • Cam section 3 of the drive shaft 2 driven indirectly.
  • a roller tappet 4 is arranged. This comprises a plunger body 9 and a roller 5.
  • a piston spring not shown in the drawing, the roller tappet 4 is pressed together with the piston against the cam portion 3, to ensure that the
  • Roller 5 does not lift off from the cam portion 3 of the drive shaft 2.
  • a respective board 6 a and 6 b is provided on the drive shaft 2.
  • the rims 6a and 6b protrude in the radial direction beyond the cam portion 3, so that the roller 5 starts on migration during operation in the axial direction and / or rotation of the ideal position against one of the two shelves 6a or 6b. This will be the
  • Axial movement and / or rotation of the ideal position of the roller 5 during operation limited to a defined level.
  • care can be taken that by a suitable tribological pairing the roller 5 and the rims 6a and 6b of the wear on both the roller 5 and the shelves 6a and 6b is so low that it does not
  • the board 6a has a directed to the roller 5 at least approximately conical shaped end face. This end face is tilted such that the width of the board
  • the roller 5 has a convex curvature, in particular with a radius r, on a face directed towards the rim 6a.
  • the board 6a is formed such that its height is less than half the diameter of the roller 5.
  • Such a design of the board 6a and the roller 5 allows for angular deviations of the direction of the roller 5, high pressure due to edge support or corner contacts between roller. 5 and board 6a to avoid.
  • it is advantageous if the point of contact of the roller with the board 6a is between the Bordoberrent and the underborder.
  • FIG. 3 shows a further embodiment of the cam section 3 together with the rim 6a and the roller 5.
  • the board 6a has a convex curvature, in particular with a radius r, on a face directed towards the roller 5.
  • the roller 5 is formed at least approximately conical on an end face directed towards the rim 6a. This end face is tilted in such a way that its diameter decreases towards an end face of the roller 5 and the end face leads away from the rim 6a towards the outer circumference of the roller 5, so that a closing inclination results.
  • the board 6a is formed such that its height is less than half the diameter of the roller 5.
  • Such Training the board 6a and the roller 5 allows for angular deviations of the direction of the roller 5 to avoid high pressure due to edge beams or corner contacts between the roller 5 and board 6a. Moreover, it is advantageous if the point of contact of the roller 5 is located with the board 6a between the Bordobermine and the underborder. This is inventively fulfilled when the angle w between a
  • Perpendicular to an axis longitudinal axis of the roller 5 and the tapered to an outer periphery of the roller 5 end face is 0.1 ° to 10 ° and the radius r is directed to the roller 5 end face of the rim 6a between 1 mm and 40 mm in size.
  • Figure 4 shows a misalignment of the roller 5 on the cam portion 3. It comes in a contact point B for contact of the roller 5 with the board 6a.
  • the distance a indicates the distance of the contact point B from the center M of the caster width. This distance a coincides with the distance between the contact point B and the roller longitudinal axis in a non-twisted state.
  • the distance b is the distance between the contact point B and the center M of the caster width.
  • the angle c represents the angle of rotation of the roller 5 and can be up to 30 °.
  • the roller 5 undergoes a force, which from the normal force Fn and the
  • Return torque is greater than the friction torque. This can be achieved, for example, when the force Fr is particularly small, a reduction in Fr being accomplished by providing the rim 6a and the roller 5 with a friction reducing coating at least at possible contact surfaces between the roller 5 and the rim 6a.
  • Another way to promote the provision of the roller 5 is an enlargement of the lever arm a and / or a reduction of the lever arm b.
  • the permissible angular deviation can be specified. This can be realized by changing the dimensions of the roller 5, wherein the
  • Roller diameter should be increased and the roller width should be reduced. Further, the distance a is also increased, the smaller the board 6a is. Thus, the height of the rim 6a should have a lower height than half the diameter of the roller 5.

Landscapes

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

Abstract

L'invention concerne une pompe à piston, en particulier une pompe de carburant à haute pression, comprenant un carter (1), un piston et un arbre d'entraînement (2) pourvu d'une partie came (3) sur laquelle le piston s'appuie au moins indirectement par l'intermédiaire d'un galet de roulement (5) monté à rotation dans un poussoir à galet (4). Un bord (6), qui fait saillie dans la direction radiale au-delà de la partie came (3), est prévu latéralement à la partie came (3) sur les deux côtés. Le bord (6) s'effile sur une surface frontale orientée vers le galet de roulement (5) jusqu'à un pourtour extérieur du bord (6), le bord (6) étant en particulier de forme conique de sorte qu'il en résulte une inclinaison d'ouverture. Le galet de roulement (5) présente sur une surface frontale orientée vers le bord (6) une courbure convexe, de préférence dotée d'un rayon (r). En variante, le bord peut également présenter une courbure convexe et le galet peut s'effiler coniquement.
EP13700489.1A 2012-03-05 2013-01-07 Pompe à piston Active EP2823177B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012203428A DE102012203428A1 (de) 2012-03-05 2012-03-05 Kolbenpumpe
PCT/EP2013/050145 WO2013131662A1 (fr) 2012-03-05 2013-01-07 Pompe à piston

Publications (2)

Publication Number Publication Date
EP2823177A1 true EP2823177A1 (fr) 2015-01-14
EP2823177B1 EP2823177B1 (fr) 2016-04-06

Family

ID=47563435

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13700489.1A Active EP2823177B1 (fr) 2012-03-05 2013-01-07 Pompe à piston

Country Status (5)

Country Link
EP (1) EP2823177B1 (fr)
CN (1) CN104145114B (fr)
DE (1) DE102012203428A1 (fr)
IN (1) IN2014DN06231A (fr)
WO (1) WO2013131662A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023174892A1 (fr) * 2022-03-15 2023-09-21 Thyssenkrupp Dynamic Components Gmbh Ensemble piston-cylindre pour un compresseur à piston radial et compresseur à piston radial

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115434839A (zh) * 2022-09-29 2022-12-06 钧风电控科技(泰州)有限责任公司 一种用于柴油机用燃油喷射系统的供油泵的挺柱体部件

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0243339B1 (fr) * 1986-04-21 1992-06-03 Robert Bosch Ag Arbre à cames
US6345597B1 (en) * 2000-10-24 2002-02-12 John D. Keeler Non-rotatable valve lifter mechanism
GB0309699D0 (en) 2003-04-28 2003-06-04 Delphi Tech Inc Improvements in cams and cam followers
DE102006025924B4 (de) * 2006-06-02 2008-04-03 Siemens Ag Fluidpumpe mit Rollenstößel
DE102006048722A1 (de) 2006-10-16 2008-04-17 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoffhochdruckpumpe, mit Rollenstößel
DE102008040081A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
DE102009002520A1 (de) * 2009-04-21 2010-10-28 Robert Bosch Gmbh Hochdruckpumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2013131662A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023174892A1 (fr) * 2022-03-15 2023-09-21 Thyssenkrupp Dynamic Components Gmbh Ensemble piston-cylindre pour un compresseur à piston radial et compresseur à piston radial

Also Published As

Publication number Publication date
DE102012203428A1 (de) 2013-09-05
WO2013131662A1 (fr) 2013-09-12
CN104145114A (zh) 2014-11-12
CN104145114B (zh) 2017-07-28
IN2014DN06231A (fr) 2015-10-23
EP2823177B1 (fr) 2016-04-06

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