WO2014183902A1 - Soupape d'injection de carburant pour moteurs à combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs à combustion interne Download PDF

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Publication number
WO2014183902A1
WO2014183902A1 PCT/EP2014/054928 EP2014054928W WO2014183902A1 WO 2014183902 A1 WO2014183902 A1 WO 2014183902A1 EP 2014054928 W EP2014054928 W EP 2014054928W WO 2014183902 A1 WO2014183902 A1 WO 2014183902A1
Authority
WO
WIPO (PCT)
Prior art keywords
nozzle needle
fuel injection
injection valve
pressure
feed 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.)
Ceased
Application number
PCT/EP2014/054928
Other languages
German (de)
English (en)
Inventor
Katja Grothe
Christian Berg
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 WO2014183902A1 publication Critical patent/WO2014183902A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • 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
    • 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
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines, as it is used for fuel injection into the combustion chamber of an internal combustion engine.
  • a fuel injection valve which comprises a holding body in which a pressure chamber is formed with a longitudinally displaceably arranged nozzle needle, which with a nozzle needle seat of the holding body
  • the nozzle needle seat limits the pressure chamber, wherein a fuel flow to at least one injection port is made possible or interrupted by the interaction of the nozzle needle with the nozzle needle seat.
  • Between holding body and nozzle needle hub-independent gap reactor is formed.
  • the gap throttle accelerates the closing operation of the nozzle needle in such a way that during the closing operation in the pressure chamber upstream of the
  • Gap throttle is a higher pressure than downstream of the gap choke; the resulting hydraulic forces on the nozzle needle in the direction of its longitudinal axis are then greater than without gap choke.
  • a fuel injection valve which comprises a holding body in which a pressure chamber is formed with a longitudinally displaceably arranged nozzle needle, which with a nozzle needle seat of the holding body
  • the nozzle needle seat limits the pressure chamber, whereby a fuel flow through the interaction of the nozzle needle with the nozzle needle seat at least one injection opening is enabled or interrupted.
  • the fuel flow to the injection openings flows between the nozzle needle and the wall of the pressure chamber, wherein between the nozzle needle and the wall of the pressure chamber in the vicinity of the nozzle needle seat a throttle point is formed to pressure fluctuations in the pressure chamber, due to the opening and
  • the fuel injection valve according to the invention has more constant injection rates and achieves a better multiple injection capability.
  • a better Kleinstmengenrich the fuel injection valve is achieved by a slower opening of the nozzle needle.
  • the life of the nozzle body is increased and the throttling effect more robust
  • the fuel injection valve to a pressure chamber, in which a
  • Nozzle needle is arranged longitudinally displaceable, wherein the nozzle needle by their
  • the fuel injection valve has a feed bore, via which the pressure chamber can be supplied with fuel under high pressure and at its pressure-chamber-side end
  • Throttling achieved since the throttle body is no longer designed radially circumferentially between the nozzle needle and the wall of the pressure chamber, but it results from the (partial) opening and closing a
  • the nozzle needle geometry is designed so that at the end of the opening process results in a small throttle effect, which is preferably defined only by the diameter of the feed bore.
  • a smaller throttle effect which is preferably defined only by the diameter of the feed bore.
  • a stronger throttle effect which is defined by the shared flow cross-section of the feed bore.
  • Pressure chamber nachströmenden and high pressure fuel to pressure oscillations The resulting maximum pressures are also referred to as high pressure overshoot.
  • the stronger throttling action at the end of the closing operation reduces the amount or momentum of the fuel flowing into the pressure chamber and thereby leads to maximum damping, to reduced high-pressure overshoots and to more constant injection rates.
  • Nozzle needle below its guide section at the level of the feed bore on a conical section Due to the conical geometry is changed by the Düsennadelhub the shared flow cross-section of the feed bore and with him the throttle effect.
  • the angle of the cone can be used to define the extent to which the released flow cross-section of the feed bore changes with the nozzle needle stroke.
  • the nozzle needle has a shoulder below its guide section instead of the conical section.
  • the guide section of the nozzle needle has at least one bevel on the shoulder.
  • the gradient of the throttling effect changing with the nozzle needle stroke can be increased.
  • the nozzle needle is guided at its end facing away from the nozzle needle seat in a valve piece.
  • Feed bore, inlet bore and control chamber are also formed here in the valve piece.
  • a compact design with as few individual parts can be realized.
  • the fuel volume between the throttle point and nozzle needle seat is increased, since the throttle point is so at the nozzle needle seat facing away from the end of the pressure chamber; the increased fuel volume can better dampen pressure surge occurring in the pressure chamber.
  • the feed bore opens into the pressure chamber side in a circumferential annular groove, which is formed in the valve piece. The filling of the pressure chamber with high-pressure fuel is thus uniform and any cuts on the shoulder of the nozzle needle must not be fixed against rotation to the feed bore.
  • valve piece is surrounded in an annular space on the outside by high pressure.
  • the pressure chamber facing away from the end of the feed hole opens into this annulus.
  • the inlet bore for the control chamber can be designed so that it also opens into the annulus.
  • FIG.l shows a longitudinal section through a fuel injection valve according to the invention in a schematic representation, wherein only the essential areas are shown.
  • Fig.2 shows the designated II section of Fig.l another
  • FIG. 3 shows a longitudinal section of a further embodiment in the same representation as in Figure 2.
  • Fig.l schematically shows an inventive fuel injection valve 1 in longitudinal section.
  • the fuel injection valve 1 has a holding body 6 and a nozzle body 2 which are mutually opposed by a not shown
  • Holding body 6 and nozzle body 2 form in their interior a pressure chamber 10, in which a piston-shaped nozzle needle 5 is arranged longitudinally displaceable.
  • a shoulder 50 is arranged, which together with the holding body 6, a feed gap 51st
  • the nozzle needle 5 acts at its the combustion chamber
  • a control chamber 12 is arranged, via the pressure of the opening and closing movement of the nozzle needle 5 is controlled in such a way that at pressure reduction in the control chamber 12, the nozzle needle 5 lifts from the nozzle needle seat 3 and so the at least one Injection opening 4 releases and upon pressure increase in the control chamber 12 the
  • Nozzle needle 5 is pressed against the nozzle needle seat 3 and thus closes the at least one injection opening 4.
  • the control chamber 12 is arranged in a valve member 7 which limits the pressure chamber 10 facing away from the combustion chamber.
  • a closing spring 8, which biases the nozzle needle 5 against the nozzle needle seat 3, is arranged in the control chamber 12 and acts on the end face of the nozzle needle 5 opposite the combustion chamber.
  • a guide section 17 of the nozzle needle 5, which is formed on the end of the nozzle needle 5 opposite the combustion chamber is guided radially in the valve piece 7. This guide portion 17 limits at its upper end the control chamber 12 and at its lower end the pressure chamber 10th
  • the control chamber 12 is connected through an inlet bore 20, which with a
  • High-pressure passage 15 is connected and is also formed in the valve piece 7, supplied with fuel under high pressure, which is provided for example by a common rail, not shown.
  • a Abiaufbohrung 21 which passes through a valve disc 13, leads into a low-pressure space 11.
  • the opening of the Abiaufbohrung 21 in the low-pressure space 11 can from a control valve 9, the e. is electromagnetically controlled, opened or closed.
  • a feed bore 22 connects the pressure chamber 10 with the high pressure passage 15.
  • the pressure chamber 10 facing opening of the feed bore 22 is in the closed position of the nozzle needle 5 partially and in the
  • Fig.l an at least partially dependent on the stroke of the nozzle needle 5 throttling of the fuel flowing into the pressure chamber 10 fuel at the opening of the feed bore 22 through a conical section 18 of the nozzle needle 5. Furthermore Fig.l shows an annular space 28, which surrounds the valve member 7 at high pressure and both feed bore 22 and inlet bore 20 with the high-pressure passage 15 and thus with a high-pressure fuel source, eg a common rail, connects.
  • a high-pressure fuel source eg a common rail
  • Control valve 9 the Abiaufbohrung 21 free and thus connects the control chamber 12 with the low-pressure chamber 11.
  • the pressure in the control chamber 12 drops off and with him the acting on the nozzle needle 5 closing force, whereupon the nozzle needle 5 opens and the injection port 4 is free.
  • the nozzle needle 5 opens relatively slowly due to the hydraulic power ratios and thus achieves a better Kleinstmengenmix.
  • the nozzle needle 5 releases the entire flow cross section of the feed bore 22.
  • the inflow of high-pressure fuel into the pressure chamber 10 is determined only by the geometry of the feed bore 22 and can flow freely. During the injection process, the pressure in the pressure chamber 10 decreases.
  • control valve 9 closes the
  • Closing reduces the nozzle needle 5 by their lifting movement the shared flow cross-section of the feed bore 22, so that with the progress of the closing movement of the nozzle needle 5, the throttling effect of the gap between the conical portion 18 and the mouth of the
  • Feeding bore 22 is increased. This leads to a faster closing of the nozzle needle 5. With the closing of the nozzle needle 5, the pressure rises in the
  • Fig.2 shows the designated II section of Fig.l another
  • Embodiment of the fuel injection valve 1 according to the invention in which the guide portion 17 of the nozzle needle 5 is guided in the valve piece 7 and the nozzle needle 5 below its guide portion 17 in the region of
  • Feeding bore 22 has a shoulder 30 which during the stroke of
  • Nozzle needle 5 along the cross section of the pressure chamber 10 facing Opening the feed bore 22 is moved and so the released
  • Flow cross section of the feed bore 22 changed.
  • the opening of the feed bore 22 partially and in the open position of the nozzle needle 5, the opening of the
  • This embodiment has a comparatively simple geometry.
  • FIG. 3 shows, in the same representation as FIG. 2, a further embodiment of the fuel injection valve 1 according to the invention in the closed position of the nozzle needle 5, in which the guide section 17 of the nozzle needle 5 is provided with at least one bevel 31 on the shoulder 30.
  • the feed bore 22 opens pressure chamber side in a circumferential annular groove 35 which is formed in the valve member 7, so that in the closed position of the nozzle needle 5 shown always a connection of the feed bore 22 is ensured with the pressure chamber 10 via the bevels 31; a filling of the pressure chamber 10 is always ensured by the bevels 31 and the annular groove 35 in the closed state of the nozzle needle 5.
  • This embodiment is comparatively robust with respect to manufacturing tolerances.
  • Throttle action correspondingly in reverse order: first constant minimum throttle effect, defined by the cross section of the feed bore 22, then linearly increasing throttling effect as long as the shoulder 30 along the cross section of the pressure chamber 10 facing opening of the Feeding bore 22 is moved and in the final phase of the closing operation of the nozzle needle 5 is a constant throttling action, defined by the bevels 31st

Landscapes

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

Abstract

L'invention concerne une soupape d'injection de carburant (1) destinée à des moteurs à combustion interne pour l'injection de carburant à haute pression, comprenant une chambre de pression (10) dans laquelle est agencée une aiguille d'injecteur (5) mobile longitudinalement par coulissement. Par son mouvement longitudinal, l'aiguille d'injecteur (5) coopère avec au moins un siège (3) d'aiguille d'injecteur et ouvre et ferme ainsi au moins un orifice d'injection (4), et l'aiguille d'injection (5) est soumise par la pression présente dans une chambre de commande (12) à une force de fermeture orientée dans la direction du siège (3) d'aiguille d'injecteur. La soupape comprend un alésage d'alimentation (22) par lequel la chambre de pression (10) peut être alimentée en carburant sous haute pression et qui forme à son extrémité côté chambre de pression une section transversale d'écoulement. Le déplacement de l'aiguille d'injecteur (5) vers le haut modifie la section transversale d'écoulement dégagée de l'alésage d'alimentation (22).
PCT/EP2014/054928 2013-05-17 2014-03-13 Soupape d'injection de carburant pour moteurs à combustion interne Ceased WO2014183902A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013209251.2 2013-05-17
DE201310209251 DE102013209251A1 (de) 2013-05-17 2013-05-17 Kraftstoffeinspritzventil für Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
WO2014183902A1 true WO2014183902A1 (fr) 2014-11-20

Family

ID=50272634

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/054928 Ceased WO2014183902A1 (fr) 2013-05-17 2014-03-13 Soupape d'injection de carburant pour moteurs à combustion interne

Country Status (2)

Country Link
DE (1) DE102013209251A1 (fr)
WO (1) WO2014183902A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60132065A (ja) * 1983-12-20 1985-07-13 Nissan Motor Co Ltd 燃料噴射ノズル
GB2335000A (en) * 1998-03-05 1999-09-08 Lucas Ind Plc Fuel injector having a restricted fuel flow path provided by a needle valve
DE19818200A1 (de) * 1998-04-23 1999-10-28 Bosch Gmbh Robert Kraftstoffeinspritzventil
WO2005116441A1 (fr) * 2004-05-26 2005-12-08 Robert Bosch Gmbh Soupape d'injection de carburant pour un moteur a combustion interne
DE102007032741A1 (de) * 2007-07-13 2009-01-15 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009028089A1 (de) 2009-07-29 2011-02-10 Robert Bosch Gmbh Kraftstoffeinspritzventil mit erhöhter Kleinmengenfähigkeit

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60132065A (ja) * 1983-12-20 1985-07-13 Nissan Motor Co Ltd 燃料噴射ノズル
GB2335000A (en) * 1998-03-05 1999-09-08 Lucas Ind Plc Fuel injector having a restricted fuel flow path provided by a needle valve
DE19818200A1 (de) * 1998-04-23 1999-10-28 Bosch Gmbh Robert Kraftstoffeinspritzventil
WO2005116441A1 (fr) * 2004-05-26 2005-12-08 Robert Bosch Gmbh Soupape d'injection de carburant pour un moteur a combustion interne
DE102007032741A1 (de) * 2007-07-13 2009-01-15 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen

Also Published As

Publication number Publication date
DE102013209251A1 (de) 2014-11-20

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