EP2422072A1 - Pompe à haute pression - Google Patents

Pompe à haute pression

Info

Publication number
EP2422072A1
EP2422072A1 EP10706987A EP10706987A EP2422072A1 EP 2422072 A1 EP2422072 A1 EP 2422072A1 EP 10706987 A EP10706987 A EP 10706987A EP 10706987 A EP10706987 A EP 10706987A EP 2422072 A1 EP2422072 A1 EP 2422072A1
Authority
EP
European Patent Office
Prior art keywords
pump
pump piston
piston
pressure
cylinder bore
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
EP10706987A
Other languages
German (de)
English (en)
Other versions
EP2422072B1 (fr
Inventor
Andreas Dutt
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 EP2422072A1 publication Critical patent/EP2422072A1/fr
Application granted granted Critical
Publication of EP2422072B1 publication Critical patent/EP2422072B1/fr
Not-in-force 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
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0265—Pumps feeding common rails
    • 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
    • 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
    • F02M59/445—Selection of particular materials
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/02—Elasticity

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-compressing, self-igniting internal combustion engines.
  • a high-pressure pump for a fuel injection device of an internal combustion engine has a multipart pump housing, in which at least one pump element is arranged.
  • the pump element comprises a driven by a drive shaft in a pumping motion pump piston which is slidably guided in a cylinder bore of a portion of the pump housing and defines a pump working space therein.
  • 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.
  • the pump chamber is filled with fuel through a fuel inlet channel with the inlet valve open, with the outlet valve is closed.
  • fuel is conveyed by the pump piston under high pressure through a fuel discharge channel with the exhaust valve open to a high-pressure accumulator, wherein the inlet valve is closed.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that a high efficiency is possible. Specifically, the increase in leakage of fuel from the pump working space can be prevented or at least reduced.
  • Young's modulus has a transverse strain number which is not less than 0.3. As a result, a negative radial deformation, in which the pump piston is radially compressed due to the pressure load, can be avoided. This can prevent excessive leakage. A leakage between the pump piston and the cylinder bore, in which the pump piston is guided, has the
  • the material of the pump piston along the axis of the cylinder bore has a smaller modulus of elasticity than perpendicular to the axis of the cylinder bore.
  • the material of the pump piston is a metallic or partially metallic material which is processed anisotropically.
  • the material of the pump piston is processed by at least one anisotropic rolling process and / or at least one anisotropic solidification process.
  • the material of the pump piston is a glass and / or carbon fiber material which is anisotropically reinforced by glass and / or carbon fibers.
  • Elastic modulus in the axial direction and in a direction perpendicular to the axial direction can be specified.
  • the size of the modulus of elasticity can be specified in the axial direction and in the radial direction.
  • the pump piston has an end face, that the end face of the pump piston in the cylinder bore limits the pump working space, and that the pump piston is configured such that when the end face of the pump piston is subjected to a high pressure prevailing in the pump work chamber, the pressure is at least substantially zero Radial deformation of the pump piston at least in the portion of the material having the anisotropic elastic modulus occurs.
  • the material of the pump piston which has an anisotropic elastic modulus, has a transverse strain number from a range of about 0.3 to about 0.6.
  • the pump piston has an end face, that the end face of the pump piston in the cylinder bore limits the pump working space and that the pump piston is designed such that when the end face of the pump piston is acted upon with a high pumping force.
  • a positive radial deformation of the pump piston at least in the portion of the material having the anisotropic elastic modulus occurs.
  • the material of the pump piston, which has an anisotropic elastic modulus has a transverse strain number that is greater than 0.5.
  • a positive radial deformation can be achieved in an advantageous manner, so that the increase in leakage with increasing pressure is further reduced or completely prevented.
  • an expansion of the cylinder bore in the region of the pump piston can be compensated in whole or in part by a positive radial expansion.
  • FIG. 1 shows a high pressure pump in a schematic, axial sectional view according to an embodiment of the invention.
  • FIG. 2 is a schematic representation of the section of the high-pressure pump of the exemplary embodiment of the invention designated by II in FIG. 1, illustrating a longitudinal load;
  • FIG. 2 is a schematic representation of the section of the high-pressure pump of the exemplary embodiment of the invention designated by II in FIG. 1, illustrating a longitudinal load;
  • FIG. 3 is a schematic representation of the detail shown in FIG. 2, which illustrates a transverse load
  • Fig. 4 shows the detail shown in Fig. 2 in a schematic representation illustrating a sum of the illustrated in Fig. 2 longitudinal load and the illustrated in Fig. 3 lateral load.
  • Fig. 1 shows a high pressure pump 1 in a schematic, axial sectional view according to an embodiment.
  • the high-pressure pump 1 can serve in particular as a radial or series piston pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • the high pressure pump 1 is suitable for a fuel injection system having a fuel 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 multi-part housing 2.
  • the housing 2 consists of the housing parts 3, 4, 5, wherein the housing part 3 is a base body 3, the housing part 4 is a cylinder head 4 and the housing part 5 is a fixed to the base body 3 flange 5.
  • the high pressure pump 1 has a drive shaft 6, which is mounted on the one hand at a bearing point 7 in the housing part 2 and on the other hand at a bearing point 8 in the housing part 3. Between the bearings 7, 8, the drive shaft 6 has a cam 9.
  • the cam 9 may be configured as a single or multiple cam. Further, the term of the cam also includes a configuration of the cam 9 in which the drive shaft 6 has an eccentric portion or the like.
  • the housing part 3 of the high-pressure pump 1 has a guide bore 12, in which a pump assembly 13 is arranged.
  • the cam 9 is associated with the pump assembly 13.
  • Such pump assemblies may also be associated with the cam 9 and / or associated with one or more further cams corresponding to the cam 9.
  • a radial or reciprocating piston pump can thereby be realized.
  • the cylinder head 4 has a projection 14.
  • the projection 14 extends into the guide bore 12.
  • the projection 14 has a cylinder bore 15 in which a pump piston 16 along an axis 17 of the cylinder bore 15 is slidably guided.
  • the pump piston 16 can be moved back and forth along the axis 17 in the cylinder bore 15, as illustrated by the double arrow 18.
  • the piston 16 has an end face 19 which limits a pump working chamber 20 in the cylinder bore 15.
  • In the pump working chamber 20 performs a fuel passage 21, in which an inlet valve 22 is arranged.
  • fuel flows from the fuel channel 21 into the pump working chamber 20 via the inlet valve 22.
  • a fuel channel 23 is provided, in which an outlet valve 24 is arranged.
  • the pump assembly 13 has a roller 25 which is mounted in a roller shoe 26.
  • the roller shoe 26 is inserted into a substantially hollow cylindrical plunger body 27. Further, the plunger body 27 is connected to a disc-shaped driving element 28, which the pump piston 16 above a federal
  • a reciprocating motion of the pump piston 16 is achieved by a rotation of the drive shaft 6 with the cam 9 about a rotation axis 32 of the drive shaft 6, so that the promotion of fuel under high pressure to a fuel rail or the like on the Fuel channel 23 takes place.
  • the delivery stroke is thus located in the pump working chamber 20 under high pressure fuel.
  • the generation of the high pressure in the pump working chamber 20 is thus carried out during operation by means of the moving pump piston 16 which is guided very closely in the cylinder bore 15. Between the cylinder bore 15 and an outer side 35 of the pump piston 16 there is a certain guide gap.
  • the guide gap between the cylinder jacket-shaped outer side 35 of the pump piston 16 and the cylinder bore 15 is chosen so that on the one hand sufficient ease of the pump piston 16 is ensured and on the other hand leakage over the guide gap is as small as possible. By this given very narrow leadership low pressure leakage is specified.
  • a pressure-induced widening of the guide gap starting from the pump working space 20 along the cylinder bore 15 may occur.
  • the pump piston 16 of the high pressure pump 1 of the embodiment is formed of a material having an anisotropic elastic modulus.
  • leakage over the guide gap can be reduced.
  • an increase in the amount of leakage possible with increasing pressure in the pump working chamber 20 can be prevented or at least reduced.
  • an excessively large leakage can be prevented.
  • leakage creates a significant loss of energy, which can thus be reduced or prevented.
  • a high efficiency of the high-pressure pump 1 can be ensured even at high pressures to be generated.
  • FIG. 2 shows the detail of the pump piston 16 of the high-pressure pump 1 of the exemplary embodiment in FIG. 1 in a schematic representation, wherein a radial deformation URL is illustrated on the basis of a longitudinal load.
  • a pressure P which acts on the end face 19 of the pump piston 16.
  • the pump piston 16 thereby enters a
  • the pump piston 16 Shortening of the pump piston 16, that is, a change in length 36, on.
  • the pump piston 16 is cylindrical in this embodiment.
  • the pump piston 16 has in this case in the initial state, that is, without pressurization on the end face 19, a radius R.
  • the pump piston 16 is formed from a material which has an anisotropic modulus of elasticity.
  • a relatively small elasticity is predetermined along the axis 17, while in the radial direction, that is perpendicular to the axis 17, a relatively large elasticity is predetermined.
  • the modulus of elasticity is therefore relatively small along the axis 17 and relatively large in the radial direction.
  • the material of the pump piston 16 has a transverse strain number v, which is not smaller than 0.3. The ratio of a longitudinal strain to a transverse strain is thus greater than or equal to 0.3.
  • an anisotropically machined steel may have a transverse strain of 0.3.
  • This radial deformation URL due to the longitudinal load causes a certain expansion of the pump piston 16 along its axis 17, as illustrated in FIG. 2 by an interrupted line 37. It should be noted that in FIG. 2, only the radial deformation U RL is illustrated due to the longitudinal load, which does not occur in isolation in practice. For the radial deformation URL due to the longitudinal load, there is also a radial deformation URQ due to a transverse load, which is illustrated below with reference to FIG.
  • FIG. 3 shows the pump piston 16 shown in FIG. 2 in a partial, schematic representation, the radial deformation URQ being illustrated on the basis of the transverse load of the pump piston 16.
  • the application of the pump piston 16 is idealized on its outer side 35 without the action on its end face 19 shown.
  • On the outer side 35 of the pump piston 16 along the axis 17 is acted upon by the pressure in the guide gap between the pump piston 16 and the cylinder bore 15. In the area of the end face 19, this pressure is equal to the pressure P in the pump working chamber 20.
  • a direction 38 along the guide gap the pressure in the guide gap decreases continuously. This is shown in FIG.
  • FIG. 4 shows the detail of the pump piston 16 shown in Fig. 2 in a schematic representation for explaining the embodiment, the sum of the illustrated with reference to FIG. 2 Radialumformung U RL on the basis of longitudinal load and with reference to FIG. 3 illustrated radial deformation U R. Q is shown on the basis of lateral load. While FIGS. 2 and 3 thus show the isolated effects which serve to design the pump piston 16, the combined effect occurring in practice is illustrated in FIG.
  • the radial deformation U results from the sum of the radial deformation U RL due to longitudinal loading and the radial deformation U RQ due to transverse loading:
  • the radial deformation U is positive and large when the elasticity in the longitudinal direction E L becomes small, when the transverse strain number v becomes large and when the elasticity in the transverse direction E Q becomes large ,
  • the desired radial deformation U can be predetermined.
  • the high-pressure pump 1 of the exemplary embodiment is also suitable for generating very high pressures in the pump working chamber 20.
  • the pump piston 16 may be formed, for example, of a metallic material.
  • targeted rolling and solidification methods can be used to achieve an anisotropic modulus of elasticity in the pump piston 16.
  • a difference between the modulus of elasticity in the longitudinal direction E L , that is to say along the axis 17, and the modulus of elasticity in the transverse direction E Q , that is to say in the direction of travel, is specifically determined. tion of the radius R, given.
  • the deformation 36 under pressure along the axis 17 of the pump piston 16 becomes large, the material of the material of the pump piston 16 preferably deviating in the transverse direction, that is to say in the radial direction, due to the large transverse strain number v. while the pump piston 16 is constricted only very slightly due to the pressure load on its outer side 35 because of the high modulus of elasticity in the transverse direction E Q.
  • a deformation of the pump piston 16 can be specified under pressure load targeted.

Abstract

L'invention concerne une pompe à haute pression (1) utilisée, en particulier comme pompe à piston radial ou série, dans des installations d'injection de carburant de moteurs à combustion interne à suralimentation et autoallumage, et qui présente un module de pompe (13) et un arbre d'entraînement (6). Le module de pompe (13) comporte un piston de pompe (16) guidé dans un alésage de cylindre (15) le long d'un axe (17) de l'alésage de cylindre (15) et apte à être entraîné par l'arbre d'entraînement (6). En outre, une surface frontale (19) du piston de pompe (16) délimite dans l'alésage de cylindre (15) une chambre de travail (20) de la pompe. Le piston de pompe (16) est formé d'un matériau qui présente un module d'élasticité anisotrope. Lorsque la pression qui règne dans la chambre de travail (20) de la pompe est élevée et provoque une dilatation de l'alésage de cylindre (15), cela permet d'obtenir une déformation radiale du piston de pompe (16) qui compense la dilatation de l'alésage (15) du cylindre.
EP10706987A 2009-04-21 2010-02-25 Pompe à haute pression Not-in-force EP2422072B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910002518 DE102009002518A1 (de) 2009-04-21 2009-04-21 Hochdruckpumpe
PCT/EP2010/052373 WO2010121857A1 (fr) 2009-04-21 2010-02-25 Pompe à haute pression

Publications (2)

Publication Number Publication Date
EP2422072A1 true EP2422072A1 (fr) 2012-02-29
EP2422072B1 EP2422072B1 (fr) 2012-12-26

Family

ID=42236540

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10706987A Not-in-force EP2422072B1 (fr) 2009-04-21 2010-02-25 Pompe à haute pression

Country Status (4)

Country Link
EP (1) EP2422072B1 (fr)
CN (1) CN102414434B (fr)
DE (1) DE102009002518A1 (fr)
WO (1) WO2010121857A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201416109D0 (en) * 2014-09-12 2014-10-29 Delphi International Operations Luxembourg S.�.R.L. Fuel pump
GB2542349A (en) * 2015-09-15 2017-03-22 Gm Global Tech Operations Llc Fuel unit pump and internal combustion engine comprising it
DE102016215594B4 (de) 2016-08-19 2023-12-28 Vitesco Technologies GmbH Pumpenkolben für eine Kolben-Kraftstoffhochdruckpumpe sowie Kolben-Kraftstoffhochdruckpumpe

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2857139B1 (ja) * 1998-01-30 1999-02-10 三菱電機株式会社 高圧燃料供給ポンプ
SE515146C2 (sv) * 1999-10-18 2001-06-18 Ovako Steel Ab Högrent stål
DE10125943A1 (de) * 2001-05-29 2002-12-05 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102005046670A1 (de) 2005-09-29 2007-04-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
KR20070075908A (ko) * 2006-01-16 2007-07-24 엘지전자 주식회사 리니어 압축기의 오일 공급 장치
JP4625789B2 (ja) * 2006-07-20 2011-02-02 日立オートモティブシステムズ株式会社 高圧燃料ポンプ
DE102008040088A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
DE102008041176A1 (de) * 2008-08-12 2010-02-18 Robert Bosch Gmbh Hochdruckpumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2010121857A1 *

Also Published As

Publication number Publication date
CN102414434A (zh) 2012-04-11
DE102009002518A1 (de) 2010-10-28
WO2010121857A1 (fr) 2010-10-28
CN102414434B (zh) 2014-02-12
EP2422072B1 (fr) 2012-12-26

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