EP2496822A1 - Buse d'injection pour un injecteur de carburant sans fuite - Google Patents

Buse d'injection pour un injecteur de carburant sans fuite

Info

Publication number
EP2496822A1
EP2496822A1 EP10763670A EP10763670A EP2496822A1 EP 2496822 A1 EP2496822 A1 EP 2496822A1 EP 10763670 A EP10763670 A EP 10763670A EP 10763670 A EP10763670 A EP 10763670A EP 2496822 A1 EP2496822 A1 EP 2496822A1
Authority
EP
European Patent Office
Prior art keywords
recess
valve needle
valve
fuel
fuel injector
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
EP10763670A
Other languages
German (de)
English (en)
Other versions
EP2496822B1 (fr
Inventor
Katja Grothe
Wilhelm Christ
Klaus-Peter Gansert
Thilo Kreher
Frank Ulrich Rueckert
Gerhard Suenderhauf
Fridolin Zeck
Marcus Schilling
Kerstin Kling
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 EP2496822A1 publication Critical patent/EP2496822A1/fr
Application granted granted Critical
Publication of EP2496822B1 publication Critical patent/EP2496822B1/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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting

Definitions

  • the invention relates to a fuel injector for an internal combustion engine having a valve body in which a valve needle is arranged longitudinally displaceable, which cooperates with a formed on the valve needle valve needle tip with a valve seat of the valve body, which limits a valve body formed between the valve body and valve fuel pressure chamber, said Cooperation of the valve needle with the valve seat, a fuel flow to at least one injection port allows or is interrupted, the fuel is supplied to the pressure chamber continuously or discontinuously and wherein in the pressure space between the valve needle and the valve body, a closing throttle is formed.
  • Such a fuel! Njektor is known from DE 10 2007 032 741 A1.
  • the fuel injector described in this document is leak-free designed for high injection pressures by dispensing with a low-pressure stage.
  • only small forces are available for closing the valve needle, which reduces the ability to inject small quantities of fuel.
  • This disadvantage is difficult to compensate, for example, by the use of correspondingly fast switching control valves, which is expensive and expensive. Therefore, in the subject of this document, a permanent and constant closing force is generated on the valve needle by a sharp-edged gap choke is formed between the valve needle and the valve body in the pressure chamber.
  • the gap throttle is formed by a separately incorporated into the valve needle collar having a sharp edge at its outer edge, so that between the edge of the collar and the Ven- Til ecology the sharp-edged circumferential and thus an annular gap forming gap choke is formed.
  • the federal government may also have lateral poles.
  • a relief bore in the form of a closing throttle may also be provided, such a bore being incorporated in a separate component in the form of a throttle plate.
  • a throttle plate is due to the separate component an increased construction cost.
  • the invention is based on the object to provide a fuel injector in which one of the closing operation of the valve needle is optimized by an improved over the prior art closing throttle.
  • the closing throttle is formed by at least one segment-shaped recess on a circumferential sealing collar and that the collar is part of the valve needle guide portion.
  • the recess has a longitudinal extent, which has at least the simple maximum recess depth based on the number of all recesses.
  • the longitudinal extension of the recess has twice the maximum recess depth based on the number of all recesses.
  • the longitudinal extent refers to the axial length of the recess along the valve needle, while the recess depth refers to the (changing) distance of the recess to the valve body.
  • The- The geometric design defines the pressure drop of the fuel along the closing throttle and thus influences the closing behavior of the valve needle. It has proven to be advantageous to arrange a total of three recesses distributed on the circumference of the valve needle.
  • the at least one recess is circular arc-shaped. This embodiment offers advantages in the case of recess grinding.
  • the recess is aligned at an angle to the longitudinal axis of the valve needle.
  • the recess is integrated in a flow recess.
  • a flow recess Such a configuration is provided in particular when the needle guide already contains consultancynanschliffe to direct the amount of fuel to the injection openings. In this case, the integration of the throttles in these bevels for cost reasons is advantageous.
  • an upper bevel, the recess and the flow recess in the flow direction of the fuel are arranged in alignment with each other in the valve needle guide region.
  • turbulence in the flow of the fuel can be avoided.
  • the rotationally symmetrical intermediate region is basically without a hydraulic or mechanical function, but possibly offers advantages in the machining of the nozzle needle.
  • This advantage can be achieved in a further embodiment of the invention without the rotationally symmetrical intermediate region when a transition region is arranged between the recess and the flow gap recess, wherein the transition region has the same contour as the recess.
  • This is advantageously achieved in that the recess and a gap area in front of the recess and the Strömungsspaltaus supraung are made in a grinding operation.
  • the transition region can then be produced in a second sanding pass by a simple transfer of the sanding tool. the.
  • a particular advantage is that the valve needle does not have to be re-clamped for this second sanding cycle.
  • valve body 1 shows a sectional view of a valve body longitudinally displaceably arranged valve needle with a segment-shaped recess on a circumferential sealing collar
  • FIG. 2 shows a view of the valve needle according to FIG. 1,
  • FIG. 3 shows a detailed view of a valve needle, in which the segment-shaped recess is arranged at an angle to the longitudinal axis of the valve needle,
  • FIG. 4 is a detailed view of a valve needle, in which the segment-shaped recess is integrated in a mecanicnanschliff,
  • FIG. 5 shows a view of a valve needle with a recess in the collar, which is arranged in alignment with a flow recess in the needle guide of the valve needle following the collar with the inclusion of a rotationally symmetrical region
  • FIG. 6 is a sectional view through the valve needle and the valve body according to Figure 5,
  • FIG. 7 is a detailed view of a valve needle with a recess in the collar, which is arranged in alignment with a subsequent flow recess in the needle guide of the valve needle
  • 8 is a sectional view through the valve needle and the valve body according to Figure 5
  • FIG. 10 shows a position of a grinding tool in a second grinding step for producing a valve needle according to FIG.
  • valve needles 1 and valve body 2 of a fuel injector shown in detail in the figures are designed in particular for use in self-igniting internal combustion engines with a common rail injection system.
  • the fuel injector is suitable for precisely controlling even small fuel injection quantities which have to be metered as part of a pilot injection in order to achieve low emission values.
  • the various embodiments all relate to a closing throttle, which is intended to ensure a stable closing of the valve needle 1 in fuel injectors without pressure stage. By closing the valve needle 1 is above the
  • Closing throttle a higher hydraulic pressure than below the closing throttle built, which supports the closing and accelerates.
  • valve needle 1 shows a first embodiment of such a valve needle 1, which is guided longitudinally displaceably in a valve body 2.
  • the valve body 2 has a needle seat cooperating with a valve needle tip 3 (FIG. 2), which cooperates with at least one injection opening, through which fuel can be introduced into a combustion chamber of an associated cylinder-piston unit of the internal combustion engine.
  • the fuel taken from the rail of the common rail injection system under high pressure (up to 3,000 bar) is supplied to the at least one injection opening controlled by a pressure space in the form of a gap formation between the nozzle needle 1 and the valve body 2.
  • the control normally takes an unillustrated and acting on a valve ball actuator module, wherein the valve ball with a in a Holding body of the actuator module incorporated valve seat cooperates.
  • the valve seat is connected via a connecting line to a control chamber, which in turn is flow-connected to the rail via an inlet throttle.
  • the control chamber is arranged opposite to the valve needle tip 3 at the end of the valve needle 1 in the valve body 2 cooperating with the holding body.
  • the valve ball lifts from the valve seat and acting on the control room side end face of the valve needle 1 hydraulic pressure in the control chamber is lowered by discharge of fuel through the connecting line and further via a subsequent to the valve seat discharge line in the holding body.
  • valve needle 1 In this switching state, the valve needle 1 is moved from the approximately approaching under rail pressure at a pressure shoulder 14 of the valve needle 1 fuel against the force of a valve needle spring 4 in the direction of the holding body and the valve needle tip 3 lifts from the needle seat. The fuel is then injected into the combustion chamber, the at least one injection port. If the actuator module is moved into its second switching position, the valve ball is moved onto the valve seat and fuel flowing into the control chamber through the inlet throttle from the rail increases the hydraulic pressure in the control chamber. The valve needle tip 3 is pressed back onto the needle seat. The injection process is thus terminated.
  • annular gap 5 is formed as part of the gap formation or of the pressure chamber in an upper valve spring area, into which - as explained - the fuel under rail pressure flows.
  • the valve body 2 is formed so that it forms a guide 6, in which the valve needle 1 with an upper valve needle guide portion 1 1 is performed exactly.
  • an upper bevel 7 is incorporated in the valve needle 1 and the upper valve needle guide portion 1 1, which extends to a circumferential sealing collar 8 of the valve needle 1.
  • the collar 8 is part of the upper (or below explained below) valve needle guide portion 1 1.
  • a segment-shaped recess 9 is incorporated in extension to the upper section 7, for example, ground.
  • upper sections 7 and recessed in the collar 8 recesses 9 may be arranged distributed.
  • a rotationally symmetrical region 10 incorporated in the valve needle 11 follows in the form of a recess.
  • this rotationally symmetrical region 10 includes another cooperating with the guide 6 lower Ventilnadel operationsbe- area 1 1, in which at least one flow recess 12 is incorporated.
  • the flow recess 12 is designed such that the fuel passes along the flow recess 12 without throttling losses in an annular space 13, which in turn is connected to the needle seat.
  • the annular space 13 is created by manufacturing the valve needle 1 with a reduced diameter in relation to the valve needle guide area 11. As a result, the pressure shoulder 14 is formed.
  • FIG. 2 shows the nozzle needle 1 embodied according to FIG. 1 in a perspective view, although the control-chamber-side end is not shown.
  • Figure 3 shows an embodiment of the valve needle 1, wherein the recess 9a is aligned at an angle to the longitudinal axis of the valve needle 1 in the valve guide portion 1 1.
  • the recess 9a extends up to the rotationally symmetrical region 10 and can be configured such that the recess 9a itself forms the closing throttle.
  • the closing throttle may be formed by a throttle point 17 in the collar 8a of the recess 9a.
  • the closing throttle in the form of a throttle point 17a similar to FIG. 3 is inserted or incorporated into the existing flow recess 12 in the valve guide region 11 of the valve needle 1.
  • the upper bevel 7, the recess 9 recessed in the collar 8 and the flow recess 12 are aligned in the flow direction of the fuel.
  • a rotationally symmetrical region 10 is incorporated into the valve needle 1.
  • This arrangement is advantageous in terms of a turbulence-free flow of the fuel.
  • a transition region 15 between the recess 9 and the flow recess 12 is arranged.
  • the particular advantage of this transition region 15 is that this as shown in Figures 9 and 10, can be easily made in two consecutive grinding operations, without re-tightening the valve needle 1.
  • a grinding tool 16 has the contour shown in FIGS. 9 and 10, and in a first grinding run according to FIG. 9 the upper bevel 7 is above or in the drawing to the left of the recess 9, the recess 9 itself and the flow recess 12 in the valve needle guide. rich 1 1 ground into the valve needle 1. Of particular importance here is that the upper section 7 is ground deeper than the flow recess 12 in the valve needle 1. Furthermore, the transition region 15 is shown in a raw state. However, it is also provided within the scope of the invention to loop the transition region 15 completely into the valve needle 1 during the second grinding cycle.
  • the displacement region 15 is ground into the valve needle 1 by displacing the grinding tool 16 to the right. In this case, only the part of the grinding tool 16 touches the valve needle 1, which grinds this transition region 15.

Landscapes

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

Abstract

L'invention concerne un injecteur de carburant pour un moteur à combustion interne, comprenant un corps de soupape (2) dans lequel une aiguille de soupape (1) est agencée mobile dans la direction longitudinale et coopère avec une pointe d'aiguille de soupape (3) formée sur l'aiguille de soupape (1) et dotée d'un siège de soupape du corps de soupape (2), ledit siège de soupape délimitant une chambre de compression remplie de carburant formée entre le corps de soupape (2) et l'aiguille de soupape (1). La coopération de l'aiguille de soupape (1) avec le siège de soupape (2) permettant un écoulement de carburant vers au moins une ouverture d'injection ou interrompant ce dernier, le carburant étant amené de manière continue ou discontinue à la chambre de compression et un dispositif d'étranglement de fermeture étant réalisé dans la chambre de compression entre l'aiguille de soupape (1) et le corps de soupape (2). L'invention vise à mettre au point un injecteur de carburant dont le processus de fermeture de l'aiguille de soupape (1) est optimisé par un dispositif d'étranglement de fermeture amélioré par rapport à l'état de la technique. A cet effet, le dispositif d'étranglement de fermeture est formé par au moins un évidement (9, 9a) en forme de segment sur un collet (8, 8a) d'étanchéité périphérique, le collet (8, 8a) faisant partie de la zone de guidage de l'aiguille de soupape (11).
EP10763670.6A 2009-11-06 2010-09-30 Buse d'injection pour un injecteur de carburant sans fuite Active EP2496822B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910046452 DE102009046452A1 (de) 2009-11-06 2009-11-06 Einspritzdüse für einen lecklosen Kraftstoffinjektor
PCT/EP2010/064560 WO2011054608A1 (fr) 2009-11-06 2010-09-30 Buse d'injection pour un injecteur de carburant sans fuite

Publications (2)

Publication Number Publication Date
EP2496822A1 true EP2496822A1 (fr) 2012-09-12
EP2496822B1 EP2496822B1 (fr) 2014-04-16

Family

ID=43087105

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10763670.6A Active EP2496822B1 (fr) 2009-11-06 2010-09-30 Buse d'injection pour un injecteur de carburant sans fuite

Country Status (3)

Country Link
EP (1) EP2496822B1 (fr)
DE (1) DE102009046452A1 (fr)
WO (1) WO2011054608A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011077464A1 (de) * 2011-06-14 2012-12-20 Robert Bosch Gmbh Kraftstoffinjektor für eine Brennkraftmaschine
DE102013219568A1 (de) * 2013-09-27 2015-04-02 Robert Bosch Gmbh Kraftstoffeinspritzventil und ein Verfahren zu dessen Herstellung

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10062959A1 (de) * 2000-12-16 2002-06-20 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10346075B4 (de) * 2003-10-04 2014-05-08 Robert Bosch Gmbh Verfahren zur Herstellung eines Kraftstoffeinspritzventils und nach diesem Verfahren hergestelltes Kraftstoffeinspritzventil
EP1851427B1 (fr) * 2005-02-22 2011-05-11 Continental Automotive Systems US, Inc. Injecteur a rampe commune avec dispositif actif de fermeture par pointeau
DE102005046665A1 (de) * 2005-09-29 2007-04-05 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102006036447A1 (de) * 2006-08-04 2008-02-07 Robert Bosch Gmbh Injektor für ein Kraftstoffeinspritzsystem
DE102007032741A1 (de) 2007-07-13 2009-01-15 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102008001425A1 (de) * 2008-04-28 2009-10-29 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2011054608A1 *

Also Published As

Publication number Publication date
EP2496822B1 (fr) 2014-04-16
WO2011054608A1 (fr) 2011-05-12
DE102009046452A1 (de) 2011-05-12

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