EP2715103B1 - Ensemble buse pour un injecteur de carburant et injecteur de carburant - Google Patents

Ensemble buse pour un injecteur de carburant et injecteur de carburant Download PDF

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Publication number
EP2715103B1
EP2715103B1 EP12723468.0A EP12723468A EP2715103B1 EP 2715103 B1 EP2715103 B1 EP 2715103B1 EP 12723468 A EP12723468 A EP 12723468A EP 2715103 B1 EP2715103 B1 EP 2715103B1
Authority
EP
European Patent Office
Prior art keywords
nozzle
nozzle needle
throttle bore
throttle
needle
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
EP12723468.0A
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German (de)
English (en)
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EP2715103A1 (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
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Robert Bosch GmbH
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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
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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
    • 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.
  • a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine with eienr generic nozzle assembly comprises an axially adjustable injection valve member having a combustion chamber near portion which projects into a nozzle chamber, can flow into the fuel through a closing throttle.
  • 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.
  • a fuel injector which has a longitudinally movable nozzle needle, which is surrounded by a throttle bore body.
  • the throttle body is located on the nozzle needle and is acted upon by a closing spring.
  • 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 p 1 and in the second pressure chamber, a hydraulic pressure p 2 act, where p 1 > p 2 .
  • the hydraulic pressure p 1 thus causes an additional hydraulic closing force, which supports the function of the closing spring.
  • the section of the nozzle needle passing through the throttle body 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 A 1 > A 2 and thus an additional acting in the axial direction hydraulic force.
  • the nozzle needle passes through the throttle bore body, 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 throttle bore body is formed like a piston and has an outer diameter D 1 , which is greater than the outer diameter D 2 of the nozzle needle in the contact region with the throttle bore body. Due to the larger outer diameter are preferably formed on both end faces of the piston-like throttle bore body, which limit the two pressure chambers, hydraulic active surfaces A 1 and A 2 , on the size ratio of an effective axial force can be effected, which additionally acts on the throttle bore body including the nozzle needle. The ratio is preferably chosen such that the hydraulic effective area A 1 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 D 1 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.
  • a first guide portion which is preferably formed as a stepped bore in the nozzle body high pressure bore and cooperates with a portion of the nozzle needle having an enlarged diameter
  • 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.
  • a non-positive or positive connection can be provided. Due to the integral 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 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 Schemeel 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 1 is greater than A 2 .
  • actuator plunger and nozzle needle are usually designed as two components, which must be assembled consuming during assembly. Due to the proposed one-piece design, therefore, the assembly can be simplified.
  • 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 throttle bore body penetrating portion of the nozzle needle or the plunger 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.
  • the section of the nozzle needle or the tappet body passing through the throttle 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 further proposed for solving the input task asked fuel injector for injecting fuel into the combustion chamber of an internal combustion engine 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 throttle bore body are 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.
  • the in the FIG. 1 illustrated nozzle assembly 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 is guided in a high-pressure bore 2 of a nozzle body 3 in a liftable manner.
  • at least one injection port 4 can be opened and closed, via which high-pressure fuel in the combustion chamber of an internal combustion engine (not shown) 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 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 D 1 , which is greater than the outer diameter D 2 of the nozzle needle 1 in the contact area 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.
  • a first, in connection with an inlet bore 16 standing pressure chamber and a second, in connection with the at least one injection port 4 stationary pressure chamber are hydraulically connected in such a way that the hydraulic pressure p 1 in the first pressure chamber greater than that hydraulic pressure p 2 in the second pressure chamber is.
  • the hydraulic pressure p 1 in the first pressure chamber consequently causes a force acting in the closing direction of the nozzle needle 1 on the throttle bore body 7, 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 A 1 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 body 7 on the other hand to a holding body 15 and a support body 15 and the nozzle body 3 arranged intermediate disc 11 is supported.
  • the intermediate disc 11 or in the holding body 15 and the inlet bore 16 is formed, which connects the first pressure chamber with a high-pressure source.
  • the intermediate plate 11 and the holding body 15 is axially attached to the nozzle body 3 and axially clamped with this via a nozzle lock nut (not shown).
  • the second guide portion 6 extends substantially to the sealing surfaces 14 in order to ensure the greatest 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 A 1 > A 2 .
  • the plunger body 10 serves for the operative 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.
  • This component is also easy and inexpensive to produce.
  • 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 A 1 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 the 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. By 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 to each other.
  • the nozzle needle 1 is integrally connected to a plunger body 10, wherein the plunger body 10 further is received in the washer 11 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 out by an annular end face of the nozzle needle 1, so that no additional flow channel is provided, via which fuel from the first
  • Pressure chamber can flow into the second pressure chamber.
  • annular centering portion 12 is formed on the washer 11 and on the holding body 15, with which the washer 11 and the holding body 15 can be inserted into the high-pressure bore 2 of the nozzle body 3 , In this respect, a guide or centering of the nozzle needle 1 in an area remote from the seat is still ensured via the intermediate disk 11 or the holding body 15.

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

Claims (9)

  1. Module de buse pour un injecteur de carburant comprenant un pointeau de buse (1) qui est guidé suivant un mouvement alternatif dans un alésage haute pression (2) d'un corps de buse (3) pour libérer et fermer au moins une ouverture d'injection (4) par le biais d'au moins une portion de guidage (5, 6) et qui est sollicité au moins indirectement par la force de ressort d'un ressort de fermeture (8), et comprenant un corps d'alésage d'étranglement (7) sollicité dans la direction axiale par une force de ressort, le corps d'alésage d'étranglement (7) s'appliquant contre le pointeau de buse (1) et étant sollicité dans la direction axiale par la force de ressort du ressort de fermeture (8), caractérisé en ce que le corps d'alésage d'étranglement (7) est traversé par le pointeau de buse (1), la portion du pointeau de buse (1) traversant le corps d'alésage d'étranglement (7) présentant un diamètre extérieur D3 qui est inférieur au diamètre extérieur D2 du pointeau de buse (1).
  2. Module de buse selon la revendication 1, caractérisé en ce que le corps d'alésage d'étranglement (7) est réalisé sous forme de piston et possède un diamètre extérieur D1 qui est supérieur au diamètre extérieur D2 du pointeau de buse (1) dans la région de contact avec le corps d'alésage d'étranglement (7).
  3. Module de buse selon la revendication 1 ou 2, caractérisé en ce que le corps d'alésage d'étranglement (7) possède au moins un alésage d'étranglement (9) qui est réalisé sous forme d'alésage axial.
  4. Module de buse selon l'une quelconque des revendications précédentes,
    caractérisé en ce que le corps d'alésage d'étranglement (7) coopère, pour le guidage du pointeau de buse (1), avec une portion de guidage (6) du corps de buse (3).
  5. Module de buse selon l'une quelconque des revendications précédentes,
    caractérisé en ce que le corps d'alésage d'étranglement (7) est connecté d'une seule pièce avec le pointeau de buse (1).
  6. Module de buse selon l'une quelconque des revendications précédentes, caractérisé en ce que la portion du pointeau de buse (1) traversant le corps d'alésage d'étranglement (7) est un corps de poussoir (10) qui est connecté d'une seule pièce avec le pointeau de buse (1).
  7. Module de buse selon la revendication 1 ou 6,
    caractérisé en ce que la portion du pointeau de buse (1) traversant le corps d'alésage d'étranglement (7) ou le corps de poussoir (10) est supporté(e) radialement de manière flottante dans le corps d'alésage d'étranglement (7).
  8. Module de buse selon la revendication 1, 6 ou 7,
    caractérisé en ce que la portion du pointeau de buse (1) traversant le corps d'alésage d'étranglement (7) ou le corps de poussoir (10) est centré(e) par le biais d'une rondelle intermédiaire (11) appliquée axialement contre le corps de buse (3), laquelle possède de préférence une portion de centrage (12) de forme annulaire reçue dans le corps de buse (3).
  9. Injecteur de carburant pour l'injection de carburant dans la chambre de combustion d'un moteur à combustion interne comprenant un module de buse selon l'une quelconque des revendications précédentes ainsi qu'un module d'actionneur pour actionner le pointeau de buse (1), le pointeau de buse (1) pouvant être actionné de préférence directement par le biais du module d'actionneur.
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 EP2715103A1 (fr) 2014-04-09
EP2715103B1 true 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)

Families Citing this family (7)

* 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
GB2585064B (en) * 2019-06-27 2021-11-10 Delphi Tech Ip Ltd Fuel injector with closed loop detection
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

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Also Published As

Publication number Publication date
CN103582751A (zh) 2014-02-12
EP2715103A1 (fr) 2014-04-09
WO2012163759A1 (fr) 2012-12-06
DE102011076665A1 (de) 2012-12-06

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