EP2183476B1 - Kraftstoffeinspritzventil mit verbesserter dichtheit am dichtsitz eines druckausgeglichenen steuerventils - Google Patents

Kraftstoffeinspritzventil mit verbesserter dichtheit am dichtsitz eines druckausgeglichenen steuerventils Download PDF

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Publication number
EP2183476B1
EP2183476B1 EP08774899A EP08774899A EP2183476B1 EP 2183476 B1 EP2183476 B1 EP 2183476B1 EP 08774899 A EP08774899 A EP 08774899A EP 08774899 A EP08774899 A EP 08774899A EP 2183476 B1 EP2183476 B1 EP 2183476B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
seat
control valve
cone angle
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.)
Active
Application number
EP08774899A
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German (de)
English (en)
French (fr)
Other versions
EP2183476A1 (de
Inventor
Holger Rapp
Wolfgang Stoecklein
Nadja Eisenmenger
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 EP2183476A1 publication Critical patent/EP2183476A1/de
Application granted granted Critical
Publication of EP2183476B1 publication Critical patent/EP2183476B1/de
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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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
    • 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
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing

Definitions

  • the invention is based on a fuel injection valve according to the preamble of patent claim 1.
  • Such a fuel injection valve is for example by the EP 1 612 403 A1 and the WO 03/004861 A1 known.
  • one or more injection openings are opened and closed by the longitudinal movement of a nozzle needle. Due to the pressure in a control chamber, a closing force is exerted indirectly via a valve piston on the nozzle needle, so that this, if in the Control chamber a correspondingly high fuel pressure is present, is held in its closed position. If an injection takes place, the control chamber is connected to a leakage oil space by means of a solenoid valve designed as a control valve.
  • the control valve has as a control valve element on a valve sleeve which defines an annular space to the outside, which is connected to the control chamber via an outlet throttle.
  • the valve sleeve is operated force-free or pressure-balanced, ie, on the valve sleeve is not exerted by the fuel pressure in the annulus resulting force in the direction of movement.
  • a closing spring By a closing spring, the valve sleeve is pressed against a valve seat and thereby closes the annulus to the outside. If an injection takes place, then the valve sleeve is lifted off from the valve seat via the electromagnet, which can be done very quickly by overcoming the relatively small closing force of the closing spring due to the lack of hydraulic force component.
  • the control chamber is connected to the leakage oil space and thereby relieved of pressure.
  • the valve sleeve is pressure balanced, because the diameter of the guide in which the valve sleeve is slidably guided, and the seat diameter of the valve seat, which seals the valve sleeve in the idle state, are the same. As a result, no pressure forces in the opening or closing direction, but only those in the radial direction arise at rest. If the seat deviates from the guide diameter, hydraulic forces are generated in the axial direction. Are guide and valve seat - as in most cases - executed in a component, so a deviation of the seat from the guide diameter can only be present in each case such that hydraulic forces arise in the opening direction. In the other case, the valve sleeve would not be available in the valve body. This is associated in particular with the disadvantage that with a surface adjustment in the sealing seat in the course of operation always only hydraulic forces in the opening direction can arise, which can lead to an unwanted opening and thus to a leakage of the valve in the extreme case.
  • a fuel injection valve according to the invention with the fuel-supplying components is shown schematically in longitudinal section.
  • the fuel injection valve comprises a multipart, here the simplicity but only one piece shown holding body 1 and a nozzle body 2, which are pressed by a clamping nut 3 against each other.
  • a nozzle needle (valve needle) 4 is arranged longitudinally displaceable, which controls the opening of at least one injection opening 5 by their longitudinal movement.
  • the fuel is supplied to the injection openings 5 via a pressure chamber 6 , which surrounds the nozzle needle 4 and which can be filled with fuel at high pressure via an inlet channel 7 .
  • nozzle needle 4 moves away from the injection openings 5 and thus moves into its open position, fuel is injected from the pressure chamber 6 via the injection openings 5 into a combustion chamber, not shown in the drawing, of the internal combustion engine. If, however, the nozzle needle 4 is in its closed position, that is to say in contact with a valve seat, the injection openings 5 are closed by the nozzle needle 4.
  • a longitudinal bore 8 is formed, which is coaxial with the nozzle needle 4 and in which a control piston 9 is arranged longitudinally displaceable.
  • the control piston 9 rests against the nozzle needle 4 via a pressure piece 10 , so that it moves in the longitudinal direction synchronously with the nozzle needle 4.
  • a spring 11 which is supported on the one hand on a shoulder in the holding body 1 and on the other hand on the pressure piece 10, so that by the force of the spring 11, the pressure piece 10 in the direction of the nozzle body 2 and thus the nozzle needle 4 is pressed in its closed position.
  • a high-pressure pump 12 For supplying the fuel under high pressure, a high-pressure pump 12 is provided, which compresses the fuel from a fuel tank 13 and a high-pressure accumulator 14 , in which the fuel is kept under high pressure. Via a high-pressure line 15 and a high-pressure port 16 which is formed on the fuel injection valve, the high-pressure fuel is supplied to the fuel injection valve and injected in the manner described via the injection openings 5 in the combustion chamber of the internal combustion engine.
  • control piston 9 With its end facing away from the nozzle body 2, the control piston 9 defines a control chamber 17, which is connected to the inlet channel 7 via an inlet bore 18, in which an inlet throttle 19 is located.
  • the control chamber 17 is also connected via a longitudinal bore 20, which is formed in the holding body 1 and in a control valve body 21 , with a high-pressure side valve chamber 22 which is connected via a control valve 23 with a low-pressure side valve chamber (leakage oil chamber) 24 .
  • the control valve 23 serves to lower the fuel pressure in the control chamber 17 and has a control valve element in the form of a control or valve sleeve 25 , which is guided on a piston-shaped housing bolt 33 with guide diameter d F.
  • the valve sleeve 25 is in this case longitudinally movable and is in its closed position on a valve seat 26 with seat diameter ds, so that the valve sleeve 25 radially outwardly limited high-pressure side valve chamber 22 is sealed against the leakage oil chamber 24.
  • the valve sleeve 25 is force-balanced, because the guide diameter d F and the seat diameter d S are equal and therefore no pressure forces in the open or closed direction act on the valve sleeve 25 in the idle state.
  • the valve sleeve 25 is acted upon by a closing spring 27 which exerts a closing force on the valve sleeve 25 and thus presses against the valve seat 26.
  • a closing spring 27 which exerts a closing force on the valve sleeve 25 and thus presses against the valve seat 26.
  • Via an electromagnet 28 the valve sleeve 25 can be lifted from the valve seat 26, so that the high-pressure side Valve chamber 22 and thus over the longitudinal bore 20 and the control
  • the high-pressure side valve chamber 22 is tapered in the seat near area by an inner annular projection 29 of the valve sleeve 25.
  • the contact line of the valve sleeve 25 on the control valve body 21 does not migrate inwardly, but remains at d s ⁇ d F.
  • the control valve 23 remains practically pressure or force balanced in the new state, since the forces acting on the two shoulder surfaces 29a, 29b of the annular shoulder 29 cancel hydraulic forces. In other words, in spite of the annular shoulder 29, no appreciable hydraulic forces act on the valve sleeve 25 in the axial direction.
  • valve seat 26 is formed by a conical surface with a cone angle ⁇ k .
  • the valve sleeve 25 has a sealing edge 30 which by a low-pressure side conical surface 30a with cone angle ⁇ V1 ( ⁇ V1 > ⁇ K ) and by a high-pressure side conical surface 30b, so the heel surface 29b of the annular projection 29, with cone angle ⁇ V2 ( ⁇ V2 ⁇ K ) is formed.
  • the sealing edge 30 is formed at the diameter d s . Due to the conical contour on the valve seat 26 and the double cone contour on the valve sleeve 25, a surface adjustment now takes place starting from the sealing edge 30 in the same way radially inwards and outwards.
  • the limitation of the surface adjustment to the outside is done by the outer diameter d a of the control valve body 21 and inwardly by the inner diameter d i of the valve sleeve 25.
  • the limitation of the surface adjustment outward on the diameter d a by a Wegbegrenzungskante with diameter d a on the Valve sleeve 25 done.
  • the seat limitation between d i and d a has the task of keeping the seat forces occurring at low strokes and thus also their scattering from copy to copy small.
  • the valve seat 26 has a seat edge 31 , which is formed by a low-pressure-side conical surface 26a with a cone angle ⁇ K1 ( ⁇ K1 ⁇ V ) and a high-pressure side conical surface 26b with a cone angle ⁇ K2 ( ⁇ K2 > ⁇ V ).
  • the seat edge 31 is formed at the diameter d s .
  • the valve seat 26 is formed by a conical surface with a cone angle ⁇ K.
  • the sealing surface and thus also the shoulder surface 29b of the valve sleeve 25 is designed as an annular torus (radius R ) formed, whereby at the diameter d s , at which the tangent to the torus also has the cone angle ⁇ K , a seat line 32 is formed. Due to the conical contour of the valve seat 26 and the toroidal contour on the valve sleeve 25, a surface adjustment takes place now starting from the seat line 32 in the same way radially inwards and outwards.
  • valve sleeve 25 The limitation of the surface adjustment to the outside is effected by the outer diameter d a of the control valve body 21 and inwardly by the inner diameter d i of the valve sleeve 25.
  • the sealing surface of the valve sleeve can be formed by a conical surface and the valve seat as an annular torus in the reverse manner ,
  • Fig. 3 shows a non-inventive embodiment of the control valve 23, wherein the same or functionally identical parts with the same reference numerals as in Fig. 2 are designated.
  • This in Fig. 3 shown control valve 23 has a valve element designed as a valve needle valve element 25 and a two-part valve housing (guide member 34 and seat part 35 ).
  • the valve needle 25 is guided displaceably in an axial bore 36 of the guide part 34.
  • the seat part 35 has a valve seat 26 which is provided radially between the annular high-pressure-side valve chamber 22 and the low-pressure-side valve chamber 24.
  • the valve needle 25 terminates the high pressure side valve chamber 22 radially inwardly and has a radially projecting into the high pressure side valve chamber 22 annular projection 29, the valve seat 26 facing shoulder surface 29a cooperating with the valve seat 26 Forms sealing surface.
  • the seat diameter d s of the valve seat 26 and the guide diameter d F of the valve needle 25 are preferably the same.
  • the sealing surface of the valve needle 25 is formed by a conical surface and the valve seat 26 has a seat edge 31 which is characterized by a low-pressure side conical surface 26a whose cone angle is smaller than the cone angle of the valve needle 25, and a high-pressure side conical surface 26b whose cone angle is greater than the cone angle the valve needle 25 is formed.
  • control valve 23 are the valve seat 26 and the sealing surface of the valve needle 25 as in Fign.2a and 2c educated.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
EP08774899A 2007-07-30 2008-07-09 Kraftstoffeinspritzventil mit verbesserter dichtheit am dichtsitz eines druckausgeglichenen steuerventils Active EP2183476B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710035698 DE102007035698A1 (de) 2007-07-30 2007-07-30 Kraftstoffeinspritzventil mit verbesserter Dichtheit am Dichtsitz eines druckausgeglichenen Steuerventils
PCT/EP2008/058879 WO2009016003A1 (de) 2007-07-30 2008-07-09 Kraftstoffeinspritzventil mit verbesserter dichtheit am dichtsitz eines druckausgeglichenen steuerventils

Publications (2)

Publication Number Publication Date
EP2183476A1 EP2183476A1 (de) 2010-05-12
EP2183476B1 true EP2183476B1 (de) 2013-03-27

Family

ID=39745269

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08774899A Active EP2183476B1 (de) 2007-07-30 2008-07-09 Kraftstoffeinspritzventil mit verbesserter dichtheit am dichtsitz eines druckausgeglichenen steuerventils

Country Status (6)

Country Link
EP (1) EP2183476B1 (ru)
JP (2) JP5193299B2 (ru)
CN (1) CN101784785B (ru)
DE (1) DE102007035698A1 (ru)
RU (1) RU2485343C2 (ru)
WO (1) WO2009016003A1 (ru)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019211021A1 (de) * 2018-05-02 2019-11-07 Robert Bosch Gmbh Ventileinrichtung für eine hochdruckpumpe

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007044356A1 (de) * 2007-09-17 2009-03-19 Robert Bosch Gmbh Injektor
DE102008005532A1 (de) * 2008-01-22 2009-07-23 Robert Bosch Gmbh Kraftstoffinjektor, dessen Steuerventilelement einen Stützbereich aufweist
DE102008040956A1 (de) * 2008-08-04 2010-02-11 Robert Bosch Gmbh Kraftstoff-Injektor
DE102009029355A1 (de) * 2009-09-10 2011-03-24 Robert Bosch Gmbh Injektor
DE102009046563A1 (de) * 2009-11-10 2011-05-12 Robert Bosch Gmbh Kraftstoffinjektor
DE102010031670A1 (de) 2010-07-22 2012-01-26 Robert Bosch Gmbh Steuerventil
DE102011078400A1 (de) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Kraftstoffinjektor
JP2013174158A (ja) * 2012-02-24 2013-09-05 Nabtesco Corp 電磁弁
DE102013002232B4 (de) * 2013-02-11 2022-11-17 Man Energy Solutions Se Kolben einer Brennkraftmaschine
RU2543636C2 (ru) * 2013-03-11 2015-03-10 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Казанский государственный аграрный университет" (ФГБОУ ВПО Казанский ГАУ) Дизельная форсунка
CN104265532B (zh) * 2014-07-31 2016-08-24 中国第一汽车股份有限公司无锡油泵油嘴研究所 用于喷油器的控制阀
DE102015203515A1 (de) * 2015-02-27 2016-09-01 Robert Bosch Gmbh Teildruckausgeglichenes Druckregelventil für einen Hochdruckspeicher
CN111539077B (zh) * 2020-04-02 2023-04-18 苏州萨伯工业设计有限公司 阀套内锥面锥角偏差精度设计与磨削量检测方法
CN114522817A (zh) * 2022-04-21 2022-05-24 山西海普瑞科技有限公司 一种用于防止高压水射流破坏的喷嘴结构

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DE19709794A1 (de) * 1997-03-10 1998-09-17 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
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DE10001099A1 (de) * 2000-01-13 2001-08-02 Bosch Gmbh Robert Steuerventil für einen Injektor eines Kraftstoffeinspritzsystems für Brennkraftmaschinen mit Druckerhöhung im Steuerraum
JP2002332933A (ja) * 2001-05-10 2002-11-22 Toyota Motor Corp 燃料噴射装置
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019211021A1 (de) * 2018-05-02 2019-11-07 Robert Bosch Gmbh Ventileinrichtung für eine hochdruckpumpe

Also Published As

Publication number Publication date
JP2012211597A (ja) 2012-11-01
RU2010107374A (ru) 2011-09-10
JP5523518B2 (ja) 2014-06-18
JP5193299B2 (ja) 2013-05-08
WO2009016003A1 (de) 2009-02-05
CN101784785B (zh) 2013-08-21
CN101784785A (zh) 2010-07-21
JP2010534790A (ja) 2010-11-11
DE102007035698A1 (de) 2009-02-05
EP2183476A1 (de) 2010-05-12
RU2485343C2 (ru) 2013-06-20

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