EP2137402B1 - Hochdruckpumpe zur förderung von kraftstoff mit einem torsionsentkoppelten druckfederelement in der stösseleinrichtung - Google Patents

Hochdruckpumpe zur förderung von kraftstoff mit einem torsionsentkoppelten druckfederelement in der stösseleinrichtung Download PDF

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Publication number
EP2137402B1
EP2137402B1 EP08708238A EP08708238A EP2137402B1 EP 2137402 B1 EP2137402 B1 EP 2137402B1 EP 08708238 A EP08708238 A EP 08708238A EP 08708238 A EP08708238 A EP 08708238A EP 2137402 B1 EP2137402 B1 EP 2137402B1
Authority
EP
European Patent Office
Prior art keywords
spring element
pressure pump
compression spring
contact face
surface coating
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08708238A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2137402A1 (de
Inventor
Gerhard Meier
Bernd Haeusser
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2137402A1 publication Critical patent/EP2137402A1/de
Application granted granted Critical
Publication of EP2137402B1 publication Critical patent/EP2137402B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—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
    • 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
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • 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

Definitions

  • the present invention relates to a high-pressure pump, in particular for conveying fuel for a common-rail fuel injection system according to the type defined in more detail in the preamble of claim 1 (US Pat. DE-A-4 227 853 ).
  • High pressure pumps for the promotion of fuel which are used for common rail fuel injection systems, are generally known.
  • the high-pressure pumps are used to provide a high-pressure fuel within the common rail, which are acted upon by service bridges up to 2 Kbar and more. Therefore, special requirements are placed on the high-pressure pumps in order to promote the fuel in an efficient manner to the said pressures.
  • the high-pressure pumps are usually driven via a coupling with the crankshaft of the internal combustion engine, wherein the high-pressure pump can be designed according to the principle of a cam drive. These include a camshaft having a cam geometry which displaces a picking element into a lifting movement in the direction of a lifting axis, and thus a pump piston connected to the picking element is set in a lifting movement.
  • the pump piston can cooperate with this to promote the fuel.
  • the pump piston is guided in a liftable manner in the pump body or in the cylinder head, and communicates with the tapping element at least via a roller shoe.
  • the tapping element is usually designed as a roller, which rolls over the cam geometry.
  • the arrangement of the roller in operative connection with the cam geometry is advantageous, since forms a line contact between the roller and the cam geometry, which has a high load capacity. In addition, only rolling movements take place, which are wear-minimized compared to sliding movements.
  • the tapping element in the form of the roller is pressed to guide it on the cam geometry by means of a compression spring element against this, whereby at the same time the return stroke of the pump piston is ensured.
  • Such compression spring elements are designed as coil springs and extend between a collar within the cylinder head and the so-called roller shoe in which the roller is received.
  • linear guides have minimal play, which is comparatively large, and the line contact between the pick-off element and the cam geometry also remains unaffected. This circumstance leads to premature wear of the high pressure pump, which is undesirable in view of the required operating time and reliability of the high pressure pump.
  • the invention provides the technical teaching that the at least one contact surface between the compression spring element and the plunger device and / or the adjoining surface of the compression spring element comprises a frictional force minimized surface coating to create a Torsionsentkopplung the compression spring element.
  • the advantage of the solution according to the invention lies in a decoupling of the torsional movement of the compression spring element from the plunger device.
  • the rotation accompanying the compression of the compression spring element can not be transferred further to the plunger device in the case of a contact surface with a friction-minimized surface coating, so that rotation of the plunger device, and thus rotation of the pick-off element on the cam geometry, are no longer caused by the torsion of the compression spring element can.
  • the compression spring element is received between the cylinder head and the plunger guide, so that one end of the compression spring element is supported against a receiving contour in the plunger guide.
  • This AufwcDesign within the ram guide forms the contact surface, which includes the frictional force minimized surface coating.
  • this may also be formed on the part of the compression spring element, so that the surface of the compression spring element, which is adjacent to the tappet guide, having the friction-minimized surface coating.
  • the plunger device comprises a Andruekusionnelement, against which the compression spring element is brought into abutment, wherein at least one flat surface of the An réelleusionn institutes forms the contact surface with the frictional force minimized surface coating.
  • the An réelleusionnelement is annular and has two opposing planar surfaces, so that a planar surface of the contact surface in the tappet guide and the other planar surface to the end of the compression spring elements, adjacent.
  • the opposite plane surface or both planar surfaces of Andruekusionn be provided with a frictional force minimized surface coating.
  • the Anhuiludenelement can also be connected on one side rotationally fixed to the compression spring element, so that a defined sliding movement of the opposite plane surface of the Antikinnides can take place relative to the plunger guide. If the compression spring element is compressed, then a torsion in the compression spring element can be caused, which is compensated between the Antikinnelement and the tappet guide.
  • the tapping element is designed as a roller element and the tappet device further comprises a tappet guide with a roller shoe inserted into it, on which the contact surface is formed with the friction-minimized surface coating itself.
  • the contact surface with the friction-minimized surface coating can be formed both on the pressure disk element and on the tappet guide itself, whereby a combination of the respective contact surfaces with a respective friction-minimized surface coating is possible.
  • the advantage can be used to select different surface coatings, which slide on each other, so that a tribologically optimized friction pairing is formed.
  • a spring disk element is arranged rotationally fixed thereto, which is flush with the contact surface of the tappet guide.
  • the spring disk element can be cohesively, positively or by means of connecting elements attached to the compression spring element, so that the spring disk element is likewise designed as a planar ring contour, and forms an annular contact surface.
  • the adjacent to the contact surface of the tappet guide contact surface of the spring disk element comprises the frictional force minimized surface coating.
  • An even more advantageous embodiment of the present invention comprises both a spring disk element arranged on the end side of the compression spring element and a pressure disk element, so that the pressure disk element is arranged between the spring disk element and the tappet guide, and the contact surface of the compression spring element adjoins the contact surface of the spring disk element.
  • four contact surfaces with a respective friction-minimized surface coating in a stack arrangement can adjoin one another, wherein the pressure-disk element is located between the spring-disk element and the tappet guide.
  • the friction-minimized surface coating is applied to the at least one contact surface by means of a PVD process, a CVD process, a galvanic process or a chemical process. Furthermore, there is the possibility that the friction-minimized surface coating comprises a bonded coating and / or a dry lubricant applied to the contact surface.
  • the friction-minimized Surface coating may also be a hard coating, such as a titanium oxide coating, a zirconium oxide coating, a silicon oxide coating, a titanium carbide coating or a titanium nitride coating. Furthermore, it is possible to provide innovative PVD hard coatings such as TiMgN coatings.
  • a combination of friction-minimized surface coatings and a surface-layer treatment of the respective contact surface should also be provided as an advantageous possibility within the scope of the present invention.
  • Particularly advantageous are titanium carbide coatings, which are characterized by a very high hardness, coupled with a low coefficient of friction and highest adhesion.
  • Titanium nitrite coatings are characterized by high hardness, high toughness and a very low tendency to weld on, so that seizing and deposit formation can be avoided. Furthermore, good corrosion and oxidation properties are advantageous.
  • the plunger device which comprises the compression spring element, is located inside the pump body, which is filled with fuel. Therefore, the fuel may act as a lubricant, so that the surface coating cooperates with the lubricating effect of the fuel. Therefore, the surface coating should have a corresponding resistance to the fuel, which is particularly a diesel fuel.
  • a further surface coating may be mentioned a titanium-aluminum nitride coating, wherein a chromium nitride coating is also a possible hard material coating.
  • These coatings are characterized in particular by a very high chemical and thermal stability, in which case the chromium nitrite coating has a low tendency to adhesion, since the arrangement of the compression spring element can have locally high surface pressures in operative connection with the pressure disk element or the spring disk element Adhesion tendency is advantageous.
  • a frictional force-minimized surface coating in the form of a monolayer, wherein also binary layers (Ti (C, N)), multilayer coatings (TiC / TiN) or graded coatings (TiC / Ti (C, N) / TiN) represent a possible variant.
  • the friction-minimized surface coating according to the invention is not limited to a specific layer system, but comprises several different layer systems.
  • the sliding movement comprises an oscillating rotational movement in small angular ranges, since at each stroke of the roller shoe 15 there is a torsion of the compression spring element 7 relative to the tipping guide 10.
  • This rotation of the compression spring element 7 is thus compensated between the contact surfaces 8a, 8b, 8c and 8d, since the contact surfaces are minimized friction and allow a sliding movement to each other, the sliding causes minimal or even in connection with the lubricating effect of the fuel no significant frictional force.
  • the Verwarne Trent of the compression spring element 7 is not transmitted to the tappet guide 10 so that it does not transmit the rotational movement further to the tapping element 2, and the line contact between the tapping element 2 and the cam geometry 4 is maintained on the camshaft 3.
  • the invention is not limited in its execution to the above-mentioned preferred Au Unitsbeispiel. Rather, a number of variants is conceivable, which makes use of the solution shown in the scope of claim 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP08708238A 2007-03-16 2008-01-28 Hochdruckpumpe zur förderung von kraftstoff mit einem torsionsentkoppelten druckfederelement in der stösseleinrichtung Not-in-force EP2137402B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007012705A DE102007012705A1 (de) 2007-03-16 2007-03-16 Hochdruckpumpe zur Förderung von Kraftstoff mit einem torsionsentkoppelten Druckfederelement in der Stößeleinrichtung
PCT/EP2008/050915 WO2008113626A1 (de) 2007-03-16 2008-01-28 Hochdruckpumpe zur förderung von kraftstoff mit einem torsionsentkoppelten druckfederelement in der stösseleinrichtung

Publications (2)

Publication Number Publication Date
EP2137402A1 EP2137402A1 (de) 2009-12-30
EP2137402B1 true EP2137402B1 (de) 2010-11-24

Family

ID=39434276

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08708238A Not-in-force EP2137402B1 (de) 2007-03-16 2008-01-28 Hochdruckpumpe zur förderung von kraftstoff mit einem torsionsentkoppelten druckfederelement in der stösseleinrichtung

Country Status (8)

Country Link
US (1) US20100101539A1 (ja)
EP (1) EP2137402B1 (ja)
JP (1) JP2010521620A (ja)
KR (1) KR20090119977A (ja)
CN (1) CN101636579B (ja)
AT (1) ATE489554T1 (ja)
DE (2) DE102007012705A1 (ja)
WO (1) WO2008113626A1 (ja)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010001882A1 (de) * 2010-02-12 2011-08-18 Robert Bosch GmbH, 70469 Kraftstoffhochdruckpumpe
DE102010003886A1 (de) * 2010-04-13 2011-10-13 Robert Bosch Gmbh Hochdruckpumpe
DE102010020578A1 (de) * 2010-05-14 2011-11-17 Bayerische Motoren Werke Aktiengesellschaft Vorrichtung zum Antrieb eines Nebenaggregates
DE102010038468A1 (de) * 2010-07-27 2012-02-02 Robert Bosch Gmbh Hochdruckpumpe
DE102011077766A1 (de) * 2011-06-17 2012-12-20 Elringklinger Ag Betätigungseinrichtung für ein Abgasstrom-Steuerelement eines Abgasturboladers
DE102011086703A1 (de) * 2011-11-21 2013-05-23 Robert Bosch Gmbh Hochdruckpumpe
CN102539056A (zh) * 2011-12-31 2012-07-04 北京理工大学 一种滑动轴承油膜压力测量装置
NL2010455C2 (en) * 2013-03-14 2014-09-16 Glind Metrology B V Hydraulic pressure calibrator and calibration method.
JP2018031333A (ja) * 2016-08-26 2018-03-01 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
JP7058505B2 (ja) * 2018-01-09 2022-04-22 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング 燃料供給ポンプ
KR102228818B1 (ko) 2019-09-17 2021-03-18 (주)모토닉 고압연료펌프 및 그가 적용된 직접분사식 엘피아이 시스템
IT201900018122A1 (it) * 2019-10-07 2021-04-07 Bosch Gmbh Robert Gruppo di pompaggio per alimentare un fluido, in particolare combustibile, preferibilmente gasolio, ad una utenza, in particolare un motore a combustione interna

Family Cites Families (12)

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Publication number Priority date Publication date Assignee Title
DE3143073A1 (de) * 1981-10-30 1983-05-11 Robert Bosch Gmbh, 7000 Stuttgart Einspritzpumpe mit einstellbarem spritzzeitpunkt
DE3624134A1 (de) * 1986-07-17 1988-01-21 Bosch Gmbh Robert Einspritzpumpe
DE4227853C2 (de) * 1992-08-22 1996-05-30 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE4227854B4 (de) * 1992-08-22 2005-12-15 Robert Bosch Gmbh Kraftstoffeinspritzpumpe für Brennkraftmaschinen
US5239951A (en) * 1992-11-12 1993-08-31 Ford Motor Company Valve lifter
DE19829547C2 (de) * 1998-07-02 2002-03-28 Bosch Gmbh Robert Radialkolbenpumpe
DE10106983A1 (de) * 2001-02-15 2002-08-29 Ina Schaeffler Kg Stößel
CN2627233Y (zh) * 2003-05-21 2004-07-21 上海东维燃油喷射有限公司 带定位槽无套圈挺柱体部件
DE10345089A1 (de) * 2003-09-26 2005-04-21 Bosch Gmbh Robert Stößel für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einem Stößel
DE10355029A1 (de) * 2003-11-25 2005-06-23 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinsprizeinrichtung einer Brennkraftmaschine
DE102004048711B4 (de) * 2004-10-06 2006-09-14 Siemens Ag Radialkolbenpumpe mit Rollenstößel
US7311087B2 (en) * 2004-11-23 2007-12-25 Cummins Inc. Fuel pump with a guided tappet assembly and methods for guiding and assembly

Also Published As

Publication number Publication date
JP2010521620A (ja) 2010-06-24
DE102007012705A1 (de) 2008-09-18
KR20090119977A (ko) 2009-11-23
CN101636579B (zh) 2011-10-05
DE502008001897D1 (de) 2011-01-05
CN101636579A (zh) 2010-01-27
WO2008113626A1 (de) 2008-09-25
EP2137402A1 (de) 2009-12-30
US20100101539A1 (en) 2010-04-29
ATE489554T1 (de) 2010-12-15

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