WO2011128151A1 - Pompe haute pression - Google Patents

Pompe haute pression Download PDF

Info

Publication number
WO2011128151A1
WO2011128151A1 PCT/EP2011/053108 EP2011053108W WO2011128151A1 WO 2011128151 A1 WO2011128151 A1 WO 2011128151A1 EP 2011053108 W EP2011053108 W EP 2011053108W WO 2011128151 A1 WO2011128151 A1 WO 2011128151A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller
cam
pressure pump
abschlappung
running surface
Prior art date
Application number
PCT/EP2011/053108
Other languages
German (de)
English (en)
Inventor
Friedrich Boecking
Arnold Gente
Matthias Greiner
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 CN201180029004.7A priority Critical patent/CN102939456B/zh
Priority to JP2013504183A priority patent/JP5395308B2/ja
Priority to EP11709037.3A priority patent/EP2558707B1/fr
Publication of WO2011128151A1 publication Critical patent/WO2011128151A1/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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams

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 has a pump housing, in which a pump element is arranged, which is driven by a drive shaft in a lifting movement
  • Pump piston includes.
  • 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 indirectly via a hollow cylindrical plunger on the drive shaft, wherein the plunger is slidably guided in a bore of a portion of the pump housing in the direction of the longitudinal axis of the pump piston.
  • the longitudinal axis of the plunger is substantially identical to the longitudinal axis of the pump piston.
  • the drive shaft facing end portion is a support member used 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 support member has on its side facing the drive shaft a recess in which the roller is mounted.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that a running behavior of the roller is improved on the tread of the cam. Specifically, the hydrodynamics between the roller and a roller shoe can be improved and at the same time an advantageous running behavior of the roller on the tread of the cam can be achieved.
  • the Abschlappung of the tread and the roller are designed so that in a centered position of the roll between an end portion of the roller and the tread a gap is formed.
  • the tread is designed to be convex in the region of the Abschlappung.
  • the Abschlappung of the tread is designed so that even in a decentered position of the roller between the end portion of the roller and the tread a gap is formed.
  • Cam run-up of the roller counteracted by the Abschlappung Specifically, thus a side start of the role can be prevented or at least avoided. Furthermore, it is advantageous in this case that the gap formed between the end section of the roller and the running surface in a decentered position of the roller, in which the roller is adjusted from the centered basic position in the direction of the Abschlappung the tread, at least approximately the same size as in FIG the centered basic position. In this way, at a given angle error between the roller shoe and the cam always a restoring force are exerted on the roller, which returns the role in the centered home position.
  • the Abschlappung the tread is formed up to a front side of the cam.
  • the tread has a central tread, which is designed at least approximately cylinder jacket-shaped and that the
  • a roller shoe is provided, in which the roller is mounted, and that the roller shoe allows a certain displaceability of the roller perpendicular to a running direction of the roller on the tread.
  • the role is preferably configured substantially as a cylindrical roller. This allows between the
  • roller shoe and the role of a constant small gap can be ensured even with a displacement of the roller perpendicular to the direction. This results in an improved hydrodynamics between the roller and the roller shoe. Thus, overall results in a favorable running behavior of the role.
  • the cam has a further Abschlappung on its tread and that the Abschlappung and further Abschlappung are configured symmetrically with respect to a centered basic position of the role.
  • the Abschlappung and further Abschlappung are designed so that the roller is guided in a centered basic position. Due to the Abschlappept on the cam thus the role is centered on its path. An oblique cam run-up of the roller is thus counteracted. As a result, a lateral start of the roller is prevented or at least avoided on both sides.
  • Fig. 1 is a high pressure pump in a schematic, axial sectional view
  • Fig. 2 denoted in Fig. 1 with II section of the high pressure pump of
  • Embodiment of the invention Embodiments of the invention.
  • Fig. 1 shows a high pressure pump 1 in a schematic, axial sectional view according to an 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
  • a preferred use of the high pressure pump 1 is for a fuel injection system with a
  • Fuel rail a so-called common rail that 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.
  • the pump housing 2 comprises a housing part 3 and one connected to the housing part 3
  • a cylinder head 5 is provided, which is connected to the housing part 3.
  • a drive shaft 6 is arranged.
  • the drive shaft 6 includes a cam 7.
  • the cam 7 can also be configured as a multiple cam.
  • the cam 7 can also be designed as an eccentric portion of the drive shaft 6.
  • a bearing 8 is formed in the housing part 3.
  • a further bearing 9 is provided on the flange 4.
  • the drive shaft 6 is mounted on the bearings 8, 9. During operation of the high pressure pump 1, the drive shaft 6 rotates about its axis of rotation 10.
  • the bearings 8, 9 are spaced from each other with respect to the axis of rotation 10 and arranged on different sides of the cam 7.
  • the high-pressure pump 1 has a pump assembly 15.
  • the high-pressure pump 1 may also have a plurality of pump assemblies.
  • the pump assembly 15 can be driven by means of the cam 7 of the drive shaft 6. If the high pressure pump 1 more
  • Pump assemblies these may be driven by the cam 7 together with the pump assembly 15. It is also possible that at least one further cam is provided on the drive shaft 6, which serves according to the cam 7 for driving at least one pump assembly. Depending on the configuration, a radial or series piston pump can thereby be realized.
  • the housing part 3 of the pump housing 2 has a bore 16.
  • a projection 17 is formed, which projects into the bore 16 of the housing part 3.
  • the pump assembly 15 is provided in the region of the projection 17 and the bore 16.
  • the approach 17 has a cylinder bore 18 in which a pump piston 19 is guided.
  • the pump piston 19 limits a pump working chamber 20 in the cylinder bore 18.
  • Fuel can enter the pump working chamber 20 via an inlet valve 21.
  • an outlet valve 22 is provided, via which fuel can be conveyed out of the pump working chamber 20 into a connecting line 23.
  • Connecting line 23 leads, for example, to a common rail.
  • the cylinder bore 18 has an axis 24 which is at least approximately pointing to the axis of rotation 10 and oriented perpendicular to the axis of rotation 10.
  • the pump piston 19 is slidable along the axis 24, as illustrated by the double arrow 25.
  • the pump assembly 15 also has a hollow cylindrical plunger body 26 which is guided in the bore 16. An inserted into the plunger body 26
  • Driving element 27 engages behind a collar 28 of the pump piston 19.
  • the driving element 27 is acted upon by a plunger spring 29 in the direction of the cam 7.
  • a plunger spring 29 in the direction of the cam 7.
  • a roller shoe 30 is also used.
  • the collar 28 of the pump piston 19 abuts against the roller shoe 30.
  • a roller 31 is mounted, which is designed as a roller 31.
  • the roller 31 is in this case at least substantially cylindrical. This results in an advantageous guidance of the roller 31 in the roller shoe 30. In particular, results in an advantageous
  • roller shoe 30 Accordingly, an advantageous storage of the roller 31 is ensured in the roller shoe 30.
  • the cam 7 has an end face 32, which faces the bearing point 9, and a further end face 33, which faces the bearing point 8.
  • the end faces 32, 33 are
  • the cam 7 has a running surface 34.
  • the roller 31 runs, for example, in a running direction 35 along the running surface 34.
  • the running surface 34 has a central tread 36 on which the running surface 34 is configured at least approximately in the form of a cylinder jacket.
  • a centered basic position of the roller 31 is given to the tread 34, which is shown in FIG.
  • the roller 31 rotates about its axis 37.
  • the roller 31 runs along the running surface 34, so that according to the cam lift of the cam 7, an actuation of the pump piston 19 of the pump assembly 15 takes place. This will take turns
  • Fig. 2 shows the designated in Fig. 1 with II section of the high-pressure pump 1 of the embodiment, wherein the roller shoe 30, the roller 31 and part of the cam 7 are shown.
  • the cam 7 has on its tread 34 a Abschlappung 40 and a further Abschlappung 41.
  • the Abschlappung 40 extends to the end face 32.
  • the further Abschlappung 41 extends to the other
  • the Abschlappened 40, 41 are configured as convex Abschlappungen 40, 41. With respect to the at least approximately cylindrical roller 31 are formed by the Abschlappept 40, 41 small gaps 42, 43 between the roller 31 and the tread 34. The gaps 42, 43 relate to an end section 44 and a further end section 45 of the roller 31. A central portion 46 of the roller 31, however, is applied to the middle tread 36.
  • an angle error can occur at an angle 47. If an angular error occurs, then results between the roller shoe 30 with the roller 31 and the cam 7 and the axis 24, a non-vanishing angle 47. For a reliable operation of the high-pressure pump 1, such a game may also be required. Due to the configuration of the cam 7 with the Abschlappept 40, 41 is a
  • the roller 31 is namely guided by the bending force of the roller 31 caused by the pressure force from the generation of pressure around the cam 7 by the Abschlappept 40, 41. It is thus at an oblique cam run-up of the roller 31 through the Abschlappept 40, 41 a restoring force on the roller 31 and thus also the roller shoe 30 is exercised. As a result, an oblique cam run-up of the roller 31 is counteracted. Depending on the configuration of the high-pressure pump 1, this also counteracts a possible lateral start-up of the roller 31.
  • the Abschlappitch 40, 41 are necessary to avoid edge beams.

Abstract

L'invention concerne une pompe haute pression servant notamment de pompe à pistons radiaux ou de pompe à pistons en ligne pour systèmes d'injection de carburant de moteurs à combustion interne à compression d'air à auto-allumage, comprenant un module de pompe (15) et un arbre d'entraînement (6) qui comprend une came (7) associée au module de pompe (15). Le module de pompe (15) présente un talon de galet (30) et un galet (31) monté dans le talon (30). Le galet (31) se déplace sur une surface de roulement (34) de la came (7). A cet effet, la came (7) présente sur sa surface de roulement (34), des bords fuyants (40, 41). Grâce à ces bords fuyants (40, 41), un guidage avantageux du galet (31) est assuré sur la surface de roulement (34). Les bords fuyants (40, 41) sont nécessaires pour éviter une surcharge aux arêtes. Du fait que les bords fuyants se trouvent sur l'arbre à came et non pas sur le galet (31), l'hydrodynamique entre le galet (31) et le talon de galet (30) peut être perfectionnée.
PCT/EP2011/053108 2010-04-15 2011-03-02 Pompe haute pression WO2011128151A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201180029004.7A CN102939456B (zh) 2010-04-15 2011-03-02 高压泵
JP2013504183A JP5395308B2 (ja) 2010-04-15 2011-03-02 高圧ポンプ
EP11709037.3A EP2558707B1 (fr) 2010-04-15 2011-03-02 Pompe haute pression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010027792A DE102010027792A1 (de) 2010-04-15 2010-04-15 Hochdruckpumpe
DE102010027792.4 2010-04-15

Publications (1)

Publication Number Publication Date
WO2011128151A1 true WO2011128151A1 (fr) 2011-10-20

Family

ID=44041758

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/053108 WO2011128151A1 (fr) 2010-04-15 2011-03-02 Pompe haute pression

Country Status (5)

Country Link
EP (1) EP2558707B1 (fr)
JP (1) JP5395308B2 (fr)
CN (1) CN102939456B (fr)
DE (1) DE102010027792A1 (fr)
WO (1) WO2011128151A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9835123B2 (en) 2015-01-13 2017-12-05 Roller Bearing Company Of America, Inc. Roller for a fuel pump actuator

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013212047A1 (de) * 2013-06-25 2015-01-08 Robert Bosch Gmbh Pumpvorrichtung, insbesondere Kraftstoffhochdruckpumpvorrichtung für eine Kraftstoffeinspritzeinrichtung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB536181A (en) * 1939-02-08 1941-05-06 Sulzer Ag Improvements in or relating to cam mechanisms
DE10257914A1 (de) * 2001-12-12 2003-07-24 Denso Corp Kraftstoffeinspritzpumpe
DE102005046670A1 (de) 2005-09-29 2007-04-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102006051332A1 (de) * 2006-10-31 2008-05-08 Robert Bosch Gmbh Förderpumpe, insbesondere zur Förderung von Dieselkraftstoff mit einer verbesserten Lagerung der Antriebswelle
DE102008040081A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05332222A (ja) * 1992-05-27 1993-12-14 Nippondenso Co Ltd 燃料噴射ポンプ
JPH0821329A (ja) * 1994-07-08 1996-01-23 Toyota Motor Corp 燃料噴射ポンプ
JP3867758B2 (ja) * 1999-06-22 2007-01-10 株式会社デンソー 高圧サプライポンプ
WO2002081920A1 (fr) * 2001-04-06 2002-10-17 Robert Bosch Gmbh Pompe d'injection a un piston pour systeme d'injection de carburant par accumulation de pression
GB0329585D0 (en) * 2003-12-20 2004-01-28 Itw Ltd Pumps
CN100357591C (zh) * 2005-03-28 2007-12-26 颜志江 高压清洗机泵体
DE102006045933A1 (de) * 2006-09-28 2008-04-03 Robert Bosch Gmbh Stößelbaugruppe für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einer Stößelbaugruppe
JP2009281289A (ja) * 2008-05-22 2009-12-03 Toyota Motor Corp 内燃機関の燃料ポンプ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB536181A (en) * 1939-02-08 1941-05-06 Sulzer Ag Improvements in or relating to cam mechanisms
DE10257914A1 (de) * 2001-12-12 2003-07-24 Denso Corp Kraftstoffeinspritzpumpe
DE102005046670A1 (de) 2005-09-29 2007-04-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102006051332A1 (de) * 2006-10-31 2008-05-08 Robert Bosch Gmbh Förderpumpe, insbesondere zur Förderung von Dieselkraftstoff mit einer verbesserten Lagerung der Antriebswelle
DE102008040081A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9835123B2 (en) 2015-01-13 2017-12-05 Roller Bearing Company Of America, Inc. Roller for a fuel pump actuator

Also Published As

Publication number Publication date
JP2013524095A (ja) 2013-06-17
CN102939456B (zh) 2015-04-08
DE102010027792A1 (de) 2011-10-20
EP2558707B1 (fr) 2018-05-16
EP2558707A1 (fr) 2013-02-20
CN102939456A (zh) 2013-02-20
JP5395308B2 (ja) 2014-01-22

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