EP2715103A1 - Ensemble buse pour un injecteur de carburant et injecteur de carburant - Google Patents

Ensemble buse pour un injecteur de carburant et injecteur de carburant

Info

Publication number
EP2715103A1
EP2715103A1 EP12723468.0A EP12723468A EP2715103A1 EP 2715103 A1 EP2715103 A1 EP 2715103A1 EP 12723468 A EP12723468 A EP 12723468A EP 2715103 A1 EP2715103 A1 EP 2715103A1
Authority
EP
European Patent Office
Prior art keywords
nozzle
nozzle needle
throttle
assembly according
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
EP12723468.0A
Other languages
German (de)
English (en)
Other versions
EP2715103B1 (fr
Inventor
Andreas Koeninger
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 EP2715103A1 publication Critical patent/EP2715103A1/fr
Application granted granted Critical
Publication of EP2715103B1 publication Critical patent/EP2715103B1/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the invention relates to a nozzle assembly for a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine having the features of the preamble of claim 1. Furthermore, the invention relates to a fuel injector with such a nozzle assembly. State of the art
  • German Offenlegungsschrift DE 10 2009 001 704 A1 discloses a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine with a generic nozzle assembly.
  • the nozzle assembly comprises an axially adjustable injection valve element with a combustion chamber near
  • the nozzle assembly further comprises a spring-loaded in the axial direction sleeve or disc, which is penetrated by the injection valve element and at least one throttle opening forming the closing throttle.
  • the proposed nozzle assembly comprises a nozzle needle, which is guided in a high-pressure bore of a nozzle body for releasing and closing at least one injection opening via at least one guide portion and at least indirectly acted upon by the spring force of a closing spring, and a spring-loaded in the axial direction throttle bore body.
  • the throttle bore body bears against the nozzle needle and is acted upon in the axial direction by the spring force of the closing spring.
  • the throttle body is thus biased axially corresponding to the nozzle needle in the closing direction, so that it requires only a closing spring for biasing the nozzle needle and throttle body.
  • the spring force of the closing spring is transmitted via the throttle bore body to the nozzle needle.
  • the closing spring is preferably received in a first pressure chamber, which is in communication with a high pressure source.
  • the throttle bore body separates the first pressure chamber from a second pressure chamber, which communicates with the at least one injection port. Both pressure chambers are in turn connected via at least one throttle bore in the throttle bore body.
  • the at least one throttle bore has the effect that in the first pressure chamber, a hydraulic pressure pi and in the second
  • Pressure chamber act a hydraulic pressure p 2 , where pi> p 2 .
  • the hydraulic pressure i thus causes an additional hydraulic closing force, which supports the function of the closing spring.
  • the throttle bore body is formed like a piston and has an outer diameter D 1; which is larger than the outer diameter D 2 of the nozzle needle in the contact area with the throttle bore body. Due to the larger outer diameter, hydraulic active surfaces Ai and A 2 are preferably formed on both end faces of the piston-like throttle bore body, which delimit the two pressure chambers, via the latter
  • Size ratio can be effected in the axial direction of an effective hydraulic force, which additionally acts on the throttle bore body including the nozzle needle.
  • the ratio is preferably chosen such that the hydraulic effective area Ai delimiting the first pressure chamber is greater than the hydraulic effective area A 2 delimiting the second pressure chamber.
  • the throttle bore body further has at least one throttle bore, which is preferably designed as an axial bore.
  • An axial bore has the advantage over other throttle designs, such as inclined bores, that it has a lower temperature sensitivity.
  • the formation of at least one throttle bore as an axial bore is possible because the outer diameter Di of the piston-like throttle body is greater than the outer diameter D 2 of the nozzle needle.
  • the throttle bore body cooperate to guide the nozzle needle with a guide portion of the nozzle body.
  • the throttle bore body can cooperate with an axially spaced from the first guide portion formed second guide portion.
  • the leadership of the nozzle needle can be optimized so that the axial distance between the two guide sections is selected as large as possible.
  • the throttle bore body is located not only on the nozzle needle, but is integrally connected to the nozzle needle. The connection can be made for example by means of laser welding. In addition, alternatively or additionally, a non-positive or positive connection can be provided.
  • the one-piece connection of the throttle bore body with the nozzle needle, the assembly of the nozzle assembly can be simplified because fewer components are to be inserted into the nozzle body.
  • the centering of the nozzle needle is preferably carried out via the guide sections.
  • the throttle bore body is penetrated by the nozzle needle, wherein the throttle bore body penetrating portion of the nozzle needle has an outer diameter D 3 , which is smaller than the outer diameter D 2 of the nozzle needle.
  • the ratio of the outer diameter D 3 ⁇ D 2 ensures a hydraulic effective area ratio Ai> A 2 and thus an additional hydraulic force acting in the axial direction.
  • the nozzle needle By the nozzle needle through the throttle bore body through sets, the nozzle needle can be connected directly or indirectly via a plunger body with an actuator for actuating the nozzle needle.
  • the actuator may have an actuator ram, which is supported directly or indirectly on the nozzle needle.
  • the portion of the nozzle needle passing through the throttle body is a plunger body integrally connected to the nozzle needle.
  • the connection can be made for example by means of laser welding. Alternatively or additionally, a non-positive and / or positive connection can be selected.
  • plunger body may be the Aktorst Congressel or operatively connected to the Aktorst Congressel further plunger body. Since usually the outer diameter of the Aktorstsammlungels is smaller than the outer diameter D 2 of the nozzle needle is selected to effect a gain of the actuator force, it is further ensured that the hydraulic effective area ratio at the throttle body A- ⁇ A 2 is greater.
  • actuator plunger and nozzle needle are usually designed as two components, which must be assembled consuming during assembly. The proposed one-piece design therefore makes assembly easier.
  • the portion of the nozzle needle passing through the throttle bore body or the plunger body integrally connected to the nozzle needle is mounted radially floating in the throttle bore body.
  • the radially floating bearing bending loads on the nozzle needle or the plunger body can be prevented, which can be initiated for example due to lack of coaxiality of the components during assembly of the nozzle assembly in the nozzle needle or the plunger body.
  • the radially floating mounting can take place, for example, by providing an annular gap between the throttle bore body and the section of the nozzle needle or the plunger body passing through the throttle bore body.
  • the annular gap has a maximum outer diameter which is smaller than the outer diameter D 2 of the nozzle needle.
  • the annular gap is thus covered by an end face or a radially extending shoulder of the nozzle needle.
  • Drosseibohrungsisson is possibly no longer sufficient guidance of the nozzle needle guaranteed.
  • the section of the nozzle needle or the tappet body passing through the nozzle bore body is centered via an intermediate disk axially attached to the nozzle body.
  • the washer has an annular centering portion received in the nozzle body to facilitate assembly of the nozzle assembly.
  • a holding body is preferably attached axially and clamped axially with the nozzle body via a nozzle retaining nut.
  • the holding body may also be provided with an annular centering section, so that the assembly of nozzle assembly and holding body is simplified when the intermediate disk is omitted.
  • the fuel injector for injecting fuel into the combustion chamber of an internal combustion engine which has been proposed for solving the problem posed in the introduction comprises a nozzle assembly according to the invention and an actuator assembly for actuating the nozzle needle.
  • the nozzle needle via the Aktorbaueria is directly operable.
  • Direct actuation of the nozzle needle is understood here to mean an actuation in which the actuator force, for example via a hydraulic coupler, is possibly amplified.
  • the proposed nozzle assembly allows a fuel injector which is particularly compact in the axial direction and is also easy to assemble.
  • the functions guide / centering of the nozzle needle, closing throttle, sealing of the pressure chambers before / after the closing throttle and / or support of the spring force can be realized by a simple and therefore cost-effective component.
  • the component may have a throttle stepping for different application areas and be maintained according to the principle of a modular system.
  • the nozzle needle is connected to the plunger body and the closing spring and the Drosseibohrungsêt pushed onto the plunger body. Thereafter, the plunger body is inserted into the washer or a holding body. Finally, the nozzle body is connected to the intermediate disc and / or the holding body via a nozzle retaining nut.
  • FIG. 1 shows a longitudinal section through a first nozzle assembly according to the invention
  • FIG. 2 is a partial longitudinal section through a second nozzle assembly according to the invention. Detailed description of the drawings
  • the nozzle assembly shown in Figure 1 comprises a nozzle needle 1, which is guided in a high-pressure bore 2 of a nozzle body 3 in a liftable manner.
  • a nozzle needle 1 By way of the lifting movement of the nozzle needle 1, at least one injection opening 4 can be opened and closed, above which it is at high pressure
  • Fuel in the combustion chamber of an internal combustion engine can be injected.
  • the nozzle needle 1 is actuated via an actuator assembly, not shown.
  • the actuation of the nozzle needle 1 is carried out directly, possibly with the interposition of a hydraulic coupler.
  • the actuator assembly may include, for example, a magnetic actuator or a piezoelectric actuator.
  • two guide sections 5, 6 are formed in the nozzle body 3, which cooperate leading with corresponding portions of the nozzle needle 1.
  • the nozzle needle 1 In the region of the guide section 5, which is formed in the vicinity of a nozzle seat 13, the nozzle needle 1 has a section with an enlarged diameter, via which the nozzle needle 1 is guided in the guide section 5.
  • the enlarged diameter portion of the nozzle needle 1 has outer peripheral side polished portions to form flow passages for the fuel.
  • the polished sections are preferably uniformly distributed over the circumference of the nozzle needle 1.
  • Another guide section 6 is arranged at an axial distance from the guide section 5.
  • the guide section 6 cooperates with a throttle bore body 7, which is supported on a radially extending shoulder of the nozzle needle 1.
  • the throttle bore body 7 has an outer diameter Di, which is greater than the outer diameter D 2 of the nozzle needle 1 in the contact region with the throttle body 7 is.
  • the throttle bore body 7 may also be formed integrally with the nozzle needle 1.
  • the throttle body 7 is then formed by an enlarged diameter portion of the nozzle needle 1 or a throttle body 7 integrally connected to the nozzle needle 1.
  • the compound can be chosen such that a force, shape and / or material bond is effected.
  • At least one throttle bore 9 designed as an axial bore is formed in the throttle bore body 7, at least one throttle bore 9 designed as an axial bore is formed.
  • a first pressure chamber which is in communication with an inlet bore 16, and a second pressure chamber, which is in communication with the at least one injection aperture 4, are hydraulically connected in such a manner that the hydraulic fluid flows
  • Pressure pi in the first pressure chamber is greater than the hydraulic pressure p 2 in the second pressure chamber.
  • the hydraulic pressure pi in the first pressure chamber thus causes a force acting in the closing direction of the nozzle needle 1 on the throttle body 7 force, which acts to assist the needle closure.
  • the effect can be further enhanced by the hydraulic active surfaces formed on the throttle body 7.
  • the active hydraulic surfaces are designed in such a way that the hydraulic effective area delimiting the first pressure chamber is greater than the hydraulic effective area A 2 delimiting the second pressure chamber.
  • the closing direction of the throttle bore body 7 is further acted upon by the spring force of a closing spring 8, on the one hand on the throttle bore body
  • intermediate disc 1 1 is supported in the intermediate disc 1 1 or in the holding body 15 and the inlet bore 16 , which connects the first pressure chamber with a high-pressure source.
  • the intermediate plate 1 1 and the holding body 15 is axially attached to the nozzle body 3 and with this via a nozzle retaining nut (not shown) axially braced.
  • the second guide portion 6 extends substantially to the sealing surfaces 14 in order to ensure the largest possible axial distance between the two guide sections 5, 6, whereby the guide of the nozzle needle. 1 is optimized.
  • the guide portion 6 is limited only by the fact that the recorded in the first pressure chamber closing spring 8 limits the stroke of the throttle body 7.
  • the throttle body 7 is penetrated by a plunger body 10 which is integrally connected to the nozzle needle 1.
  • the connection 18 may in turn be a positive, positive and / or cohesive connection 18.
  • the plunger body 10 has an outer diameter D 3 , which is smaller than the outer diameter D 2 of the nozzle needle 1 is selected. This ensures a hydraulic effective area ratio Ai> A 2 .
  • the plunger body 10 serves the
  • Active connection of the nozzle needle 1 with the actuator assembly, not shown, wherein the active compound can also be produced via a coupler body and / or a coupler volume.
  • the assembly of the nozzle assembly is simplified. Over the two axially spaced guide portions 5, 6 an optimal guidance of the nozzle needle 1 in the nozzle body 3 is ensured.
  • the hydraulic active surfaces Ai and A 2 formed on the throttle body 7 cause due to their size ratio an additional hydraulic force acting in the axial direction.
  • FIG. 2 shows a modification of the embodiment of FIG. 1.
  • the nozzle needle 1 and the throttle bore body 7 are designed as separate components. This allows a radially floating mounting of the nozzle needle 1 in the region of the guide section 6. Due to the radially floating mounting of the nozzle needle 1, a bending stress of the nozzle needle 1 is avoided in the absence of coaxiality of the components zueinan-.
  • the nozzle needle 1 is integrally connected to a plunger body 10, wherein the plunger body 10 further is received in the washer 1 1 and the holding body 15.
  • the nozzle needle 1 thus experiences on the integrally connected plunger body 10, a further guide or centering, which can lead to a bending stress of the nozzle needle 1 in the absence of coaxiality of the components plunger body 10, nozzle needle 1 and throttle bore body 7. This can be counteracted by the nozzle needle 1 or the plunger body 10 integrally connected to the nozzle needle 1 being mounted radially floating in the throttle bore body 7.
  • an annular gap 17 is formed in the throttle body 7 in the present case.
  • the annular gap 17 is covered to the side of the second pressure chamber by an annular end face of the nozzle needle 1, so that no additional flow channel is provided, via which fuel can flow from the first pressure chamber into the second pressure chamber.
  • an annular centering 12 is formed on the washer 1 1 and on the holding body 15, with which the washer 1 1 and the holding body 15 is inserted into the high-pressure bore 2 of the nozzle body 3 can be.
  • a guide or centering of the nozzle needle 1 is further ensured in a seat remote area on the washer 1 1 and the holding body 15.

Landscapes

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

Abstract

L'invention concerne un ensemble buse pour un injecteur de carburant, comprenant une aiguille (1) guidée de façon à effectuer un mouvement alternatif sur au moins une section de guidage (5, 6) dans un alésage haute pression (2) d'un corps de buse (3) pour libérer et fermer au moins un orifice d'injection (4), et soumise au moins indirectement à la force de ressort d'un ressort de fermeture (8). L'ensemble buse comprend également un corps à orifice d'étranglement (7) soumis à la force du ressort dans la direction axiale. Selon l'invention, le corps à orifice d'étranglement (7) repose sur l'aiguille (1) et est soumis à la force du ressort de fermeture (8) dans la direction axiale. L'invention concerne en outre un injecteur de carburant équipé d'un tel ensemble buse.
EP12723468.0A 2011-05-30 2012-05-23 Ensemble buse pour un injecteur de carburant et injecteur de carburant Active EP2715103B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110076665 DE102011076665A1 (de) 2011-05-30 2011-05-30 Düsenbaugruppe für einen Kraftstoffinjektor sowie Kraftstoffinjektor
PCT/EP2012/059601 WO2012163759A1 (fr) 2011-05-30 2012-05-23 Ensemble buse pour un injecteur de carburant et injecteur de carburant

Publications (2)

Publication Number Publication Date
EP2715103A1 true EP2715103A1 (fr) 2014-04-09
EP2715103B1 EP2715103B1 (fr) 2016-08-10

Family

ID=46149458

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12723468.0A Active EP2715103B1 (fr) 2011-05-30 2012-05-23 Ensemble buse pour un injecteur de carburant et injecteur de carburant

Country Status (4)

Country Link
EP (1) EP2715103B1 (fr)
CN (1) CN103582751A (fr)
DE (1) DE102011076665A1 (fr)
WO (1) WO2012163759A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020260666A1 (fr) * 2019-06-27 2020-12-30 Delphi Technologies Ip Limited Injecteur de combustible à détection en circuit fermé

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013212142A1 (de) * 2013-06-25 2015-01-08 Robert Bosch Gmbh Düsenbaugruppe für einen Kraftstoffinjektor sowie Kraftstoffinjektor
DE102014209961A1 (de) * 2014-05-26 2015-11-26 Robert Bosch Gmbh Düsenbaugruppe für einen Kraftstoffinjektor sowie Kraftstoffinjektor
GB201421885D0 (en) * 2014-12-09 2015-01-21 Delphi International Operations Luxembourg S.�.R.L. Fuel injector
DE102015219646A1 (de) * 2015-10-09 2017-04-13 Continental Automotive Gmbh Fluid-Einspritzvorrichtung für Brennkraftmaschinen
CN105673280B (zh) * 2016-03-15 2018-07-03 任一虎 一种燃料喷嘴
CN112065627A (zh) * 2020-09-04 2020-12-11 温州弘腾科技有限公司 一种压力平衡喷油嘴的面积补偿制造方法以及由该方法制得的压力平衡喷油

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JP3796986B2 (ja) * 1998-11-24 2006-07-12 いすゞ自動車株式会社 燃料噴射ノズル特性の測定方法とその装置
DE10213441A1 (de) * 2002-03-26 2003-10-23 Hatz Motoren Kraftstoffeinspritzvorrichtung mit hydraulischer Düsennadelsteuerung
DE102007021330A1 (de) * 2007-05-07 2008-11-13 Robert Bosch Gmbh Kraftstoffinjektor für eine Brennkraftmaschine mit Common-Rail-Einspritzsystem
DE102009001704B4 (de) 2009-03-20 2018-06-28 Robert Bosch Gmbh Kraftstoff-Injektor
DE102010008467A1 (de) * 2010-02-18 2011-08-18 Continental Automotive GmbH, 30165 Hochdruck-Kraftstoff-Einspritzventil für einen Verbrennungsmotor

Non-Patent Citations (1)

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Title
See references of WO2012163759A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020260666A1 (fr) * 2019-06-27 2020-12-30 Delphi Technologies Ip Limited Injecteur de combustible à détection en circuit fermé

Also Published As

Publication number Publication date
WO2012163759A1 (fr) 2012-12-06
EP2715103B1 (fr) 2016-08-10
CN103582751A (zh) 2014-02-12
DE102011076665A1 (de) 2012-12-06

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