EP0135872A2 - Injecteur de combustible pour moteurs à combustion interne - Google Patents

Injecteur de combustible pour moteurs à combustion interne Download PDF

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Publication number
EP0135872A2
EP0135872A2 EP84110659A EP84110659A EP0135872A2 EP 0135872 A2 EP0135872 A2 EP 0135872A2 EP 84110659 A EP84110659 A EP 84110659A EP 84110659 A EP84110659 A EP 84110659A EP 0135872 A2 EP0135872 A2 EP 0135872A2
Authority
EP
European Patent Office
Prior art keywords
valve needle
fuel
throttle
pressure
shoulder
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
EP84110659A
Other languages
German (de)
English (en)
Other versions
EP0135872A3 (en
EP0135872B1 (fr
Inventor
Karl Hofmann
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 EP0135872A2 publication Critical patent/EP0135872A2/fr
Publication of EP0135872A3 publication Critical patent/EP0135872A3/de
Application granted granted Critical
Publication of EP0135872B1 publication Critical patent/EP0135872B1/fr
Expired legal-status Critical Current

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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
    • 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
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • the invention relates to a fuel injector according to the preamble of the main claim.
  • the opening movement of the valve needle is damped in order to optimize the spraying time in order to improve the engine values, in particular to reduce the engine noise.
  • an additional mass is assigned to the valve needle, which is coupled to the valve needle after an undamped forward stroke of the valve needle and then dampens the movement of the valve needle as a function of speed and acceleration.
  • the time course of the opening movement of the valve needle can advantageously be varied within wide limits, but an increase in the outside diameter of the injection nozzle must be accepted, which can result in installation problems.
  • the arrangement according to the invention with the characterizing features of the main claim has the advantage that the means for damping the valve needle movement only slightly increase the outer dimensions of the injection nozzle.
  • the spraying time can still be matched to the engine requirements, which results in favorable engine values.
  • the arrangement according to the invention is particularly advantageous in the case of injection nozzles with valve needles whose diameter is less than 6 mm and in which experience has shown that, as a rule, they open too quickly without additional measures.
  • a simple and compact design results if the throttle body is mounted displaceably on the valve needle and is pressed by a return spring against a stop shoulder fixed to the housing on the valve needle, and if at least one valveless throttle gap leads to the pressure shoulder.
  • valve needle has a second pressure shoulder, on which the fuel pressure in the pressure chamber acts unthrottled.
  • the return spring of the throttle body and the throttle gaps are dimensioned or matched to one another such that at least in the higher one Speed range of the machine, a subsequent opening stroke of the valve needle begins before the throttle body comes into contact with the stop shoulder fixed to the housing during its return movement.
  • a subsequent opening stroke of the valve needle begins before the throttle body comes into contact with the stop shoulder fixed to the housing during its return movement.
  • FIG. 1 shows a longitudinal section through the nozzle body of the injection nozzle according to the exemplary embodiment
  • FIGS. 2 to 4 show functional diagrams of the damping means of the injection nozzle according to FIG. 1.
  • the injection nozzle has a nozzle body 10 in which a valve needle 12 is slidably mounted and a conical valve seat 14 is formed, from which a cylindrical spray opening 16 leads to the end wall 18 of the nozzle body 10 on the combustion chamber side.
  • the valve needle 12 has a guide cut 20, which merges with a pressure shoulder 22 into a smaller section 24. At a second pressure shoulder 26, this merges into a further offset section 28, to which a valve cone 30, a throttle pin 32 passing through the spray opening 16 with play and an injection molding pin 34 are connected.
  • a closing spring exerts a closing force in the direction of arrow P on the valve needle 12.
  • a pressure chamber 36 is formed in the nozzle body 10 and is connected via a channel 38 to an annular groove 40 on the upper end face of the nozzle body 10.
  • a fuel inlet channel opens into the annular groove 40 and runs within a nozzle holder.
  • the pressure chamber 36 is connected via bores 42, 44 with different diameters to a pressure chamber 46 in the guide bore of the nozzle body 10, which is delimited by the pressure shoulder 22 of the valve needle 12.
  • the two pressure chambers 36 and 46 are separated from one another by a throttle body 50 which is displaceably mounted on the stepped portion 24 of the valve needle 12 with a certain radial clearance 52 and is pressed by a return spring 54 against a stop shoulder 56 formed between the bores 42 and 44.
  • the outside diameter of the throttle body 50 is dimensioned such that there is also a certain radial clearance 58 between it and the wall of the bore 42.
  • a throttle bore 60 is contained in the throttle body 50, which connects the pressure chambers 36 and 46 to one another.
  • the fuel pressure in the pressure chamber 36 rises, from where it propagates through the radial clearance 52 and the throttle bore 60 into the pressure chamber 46.
  • the fuel pressure thus acts directly on the second pressure shoulder 26 and, via the throttle gaps 52, 60, on the first pressure shoulder 22 of the valve needle 12.
  • the valve needle 12 thereby lifts off the valve seat 14, after which a throttled fuel quantity reaches the combustion chamber within a pre-injection phase due to the radial play between the throttle pin 32 and the spray opening 16. Because the fuel can only flow into the pressure chamber 46 in a throttled manner, the opening movement of the valve needle 12 takes place correspondingly slowly, as a result of which the pre-injection phase is extended in the desired manner.
  • the throttle pin 32 has emerged from the injection opening 16 the main injection phase begins, in which the fuel reaches the combustion chamber unthrottled.
  • the closing spring returns the valve needle 12 to the illustrated closed position, the throttle body 50 being displaced downward into a position referred to as the second end position, against the force of the return spring 54, via the fuel volume enclosed between it and the pressure shoulder 22.
  • the return spring 54 only provides a relatively low resistance to the much stronger closing spring, so that the closing stroke is largely undamped. From the beginning of the closing stroke, the return spring 54 presses the throttle body 50 back against the stop shoulder 56, the amount of fuel previously flowing into the pressure chamber 46 being displaced from the pressure chamber 46 by the radial clearances 52, 58 and the throttle valve 60 into the pressure chamber 36.
  • the distance between the illustrated first and second end positions of the throttle body 50 corresponds to the valve needle stroke, reduced by a small return stroke, which the throttle body 50 executes during the closing time of the valve needle 12 under the constant influence of the return spring 54.
  • the throttle body 50 forms with the radial clearances 52, 58, the throttle bore 60 and the return spring 54 a time-displacement member, the function of which is illustrated in the diagrams according to FIGS. 2 to 4.
  • These graphs each show the course of the valve needle stroke with fully drawn lines h and the course of the deflection of the throttle body 50 with dashed lines a over time t.
  • the closed position of the valve needle 12 shown in FIG. 1 and the first end position of the throttle body 50 lie in the time axis t.
  • the closing stroke of the valve needle 12 is to begin, in which the throttle body 50 is pushed from the first end position E 1 to the second end position E2.
  • the throttle body 50 travels a distance a 5 which, as already mentioned, is somewhat smaller than the total stroke h g of the valve needle 12.
  • the closing stroke is ended at time t 2 .
  • the throttle body 50 begins with one under the influence of the return spring 54 move back given speed, which is shown in the diagram as angle ⁇ .
  • valve needle 12 At time t 3 , a new opening stroke of valve needle 12 should begin. If, as shown in FIG. 2, the throttle body 50 has not yet reached its first end position again at time t 3 ', it is returned to this end position at approximately the same speed as the valve needle 12. It then reaches the first end position E shown in FIG. 1 at time t 4 . From then on, the throttle body 50 is prevented by the stop shoulder 56 from moving further in the opening direction of the valve needle 12, as a result of which the described damping becomes effective again. This can be seen in the diagram by the fact that the stroke curve has a break point K at time t 4 . From time t 4 , the valve needle 12 is transferred to the stroke end position at a damped, ie at a reduced speed, whereupon the game described is repeated.
  • FIGS. 3 and 4 illustrate that the damping effect of the means described adapts automatically to the various operating states of the internal combustion engine.
  • the internal combustion engine runs at low speed and low load, so that the throttle body 50 reaches its first end position before the start of the next opening stroke. In this case, the damping is effective over the entire next opening stroke of the valve needle 12.
  • FIG. 4 shows an operating state in which the internal combustion engine is running at high speed and under high load, in which a large valve needle stroke is also established. In this case, the next opening stroke begins before the Throttle body 50 has returned to its first end position.
  • the kink K of the stroke curve h of the valve needle 12 has moved further toward the end of the stroke than in the operating state according to FIG. 2, so that a smaller part of the opening movement of the valve needle 12 is damped.
  • FIG. 4 also makes it clear that the break point K moves towards the end of the opening stroke of the valve needle 12, the faster the injection processes follow one another and the greater the valve needle stroke.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP84110659A 1983-09-12 1984-09-07 Injecteur de combustible pour moteurs à combustion interne Expired EP0135872B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3332808 1983-09-12
DE3332808A DE3332808A1 (de) 1983-09-12 1983-09-12 Kraftstoff-einspritzduese fuer brennkraftmaschinen

Publications (3)

Publication Number Publication Date
EP0135872A2 true EP0135872A2 (fr) 1985-04-03
EP0135872A3 EP0135872A3 (en) 1987-04-29
EP0135872B1 EP0135872B1 (fr) 1988-08-24

Family

ID=6208819

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84110659A Expired EP0135872B1 (fr) 1983-09-12 1984-09-07 Injecteur de combustible pour moteurs à combustion interne

Country Status (3)

Country Link
EP (1) EP0135872B1 (fr)
JP (1) JPS6065270A (fr)
DE (2) DE3332808A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2307275A (en) * 1995-11-17 1997-05-21 Caterpillar Inc Fuel injector nozzle with a damped check valve
FR2742190A1 (fr) * 1995-12-09 1997-06-13 Bosch Gmbh Robert Injecteur de carburant pour moteurs a combustion interne
WO1999067529A1 (fr) * 1998-06-25 1999-12-29 Caterpillar Inc. Injecteur de carburant avec ajutage interne a double debit
WO2002090753A1 (fr) * 2001-05-05 2002-11-14 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion, comprenant une chambre d'amortissement reduisant les oscillations de pression
WO2004003377A1 (fr) * 2002-06-29 2004-01-08 Robert Bosch Gmbh Dispositif permettant d'amortir la course de l'aiguille sur des injecteurs de carburant commandes par pression
EP1382838A3 (fr) * 2002-07-16 2004-04-21 Robert Bosch Gmbh Injecteur de carburant
US7971802B2 (en) 2007-05-01 2011-07-05 Delphi Technologies Holding S.Arl Fuel injector

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103321808B (zh) * 2013-07-08 2015-09-16 中国第一汽车股份有限公司无锡油泵油嘴研究所 一种新型喷油嘴针阀偶件

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1014131A (en) * 1962-05-09 1965-12-22 Ricardo & Co Engineers Fuel injection apparatus for internal combustion engines

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1014131A (en) * 1962-05-09 1965-12-22 Ricardo & Co Engineers Fuel injection apparatus for internal combustion engines

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2307275A (en) * 1995-11-17 1997-05-21 Caterpillar Inc Fuel injector nozzle with a damped check valve
US5826802A (en) * 1995-11-17 1998-10-27 Caterpillar Inc. Damped check valve for fluid injector system
GB2307275B (en) * 1995-11-17 1999-02-17 Caterpillar Inc Fuel injector nozzle
FR2742190A1 (fr) * 1995-12-09 1997-06-13 Bosch Gmbh Robert Injecteur de carburant pour moteurs a combustion interne
WO1999067529A1 (fr) * 1998-06-25 1999-12-29 Caterpillar Inc. Injecteur de carburant avec ajutage interne a double debit
US6113012A (en) * 1998-06-25 2000-09-05 Caterpillar Inc. Rate shaped fuel injector with internal dual flow rate office
WO2002090753A1 (fr) * 2001-05-05 2002-11-14 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion, comprenant une chambre d'amortissement reduisant les oscillations de pression
US7172140B2 (en) 2001-05-05 2007-02-06 Robert Bosch Gmbh Fuel injection valve for internal combustion engines with damping chamber reducing pressure oscillations
WO2004003377A1 (fr) * 2002-06-29 2004-01-08 Robert Bosch Gmbh Dispositif permettant d'amortir la course de l'aiguille sur des injecteurs de carburant commandes par pression
EP1382838A3 (fr) * 2002-07-16 2004-04-21 Robert Bosch Gmbh Injecteur de carburant
US7971802B2 (en) 2007-05-01 2011-07-05 Delphi Technologies Holding S.Arl Fuel injector

Also Published As

Publication number Publication date
EP0135872A3 (en) 1987-04-29
EP0135872B1 (fr) 1988-08-24
DE3332808A1 (de) 1985-03-28
JPS6065270A (ja) 1985-04-15
DE3473625D1 (en) 1988-09-29

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