EP0195440B1 - Soupape d'injection de combustible - Google Patents

Soupape d'injection de combustible Download PDF

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Publication number
EP0195440B1
EP0195440B1 EP86103736A EP86103736A EP0195440B1 EP 0195440 B1 EP0195440 B1 EP 0195440B1 EP 86103736 A EP86103736 A EP 86103736A EP 86103736 A EP86103736 A EP 86103736A EP 0195440 B1 EP0195440 B1 EP 0195440B1
Authority
EP
European Patent Office
Prior art keywords
needle
chamber
valve
pressure
fuel injection
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.)
Expired
Application number
EP86103736A
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German (de)
English (en)
Other versions
EP0195440A2 (fr
EP0195440A3 (en
Inventor
Gerhard Dipl.-Ing. Finsterwalder
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz AG
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Filing date
Publication date
Application filed by Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Priority to AT86103736T priority Critical patent/ATE46744T1/de
Publication of EP0195440A2 publication Critical patent/EP0195440A2/fr
Publication of EP0195440A3 publication Critical patent/EP0195440A3/de
Application granted granted Critical
Publication of EP0195440B1 publication Critical patent/EP0195440B1/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
    • F02M61/04—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
    • F02M61/06—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 the valves being furnished at seated ends with pintle or plug shaped extensions
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • 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

Definitions

  • the invention relates to a fuel injector according to the preamble of claim 1.
  • the demands for low fuel consumption and low pollutant emissions from modern diesel engines require, among other things, a high injection pressure of the fuel.
  • the injection pressure depends on the delivery rate of the injection pump and the outflow cross section or the outflow resistance of the outlet openings of the injection valve.
  • the outflow resistance of the outlet openings is usually determined in such a way that the permissible injection pressure is not exceeded at nominal engine speed and at full load. Since the delivery rate of conventional injection pumps decreases with falling engine speed, the injection pressure usually decreases with engine speed. This drop in injection pressure is undesirable because of the decreasing mixture formation energy. It can be prevented by reducing the outlet openings accordingly or by increasing their flow resistance.
  • a known means of varying the outflow resistance of outlet openings is to use the appropriately shaped tip of the valve needle as a control element and to control the outflow resistance as a function of the valve lift.
  • the inflow cross-section of the outlet openings is influenced by a cylinder slide in the blind hole.
  • valve needle seat whose cone angles on the valve needle and on the valve insert are practically the same.
  • a more or less large annular gap is released at the outflow opening, through which the fuel reaches the outflow opening more or less throttled.
  • the injection pressure only acts on the pressure shoulder before the valve needle is opened. After lifting the valve needle from its seat, the entire valve needle tip is additionally pressurized. The result of this is a sudden increase in the force acting on the injection valve needle in the opening direction. which immediately opens it up to the stop. This makes continuous needle stroke control impossible. This effect is greater the larger the valve needle seat diameter and thus the additional force at the moment the valve needle is lifted.
  • an injection valve is known in which a force proportional to the injection pressure acts on the side of the injection valve needle remote from the seat.
  • the fuel reaches a spring chamber via a check valve, from where it presses on the valve needle via a piston.
  • the check valve ensures that the injection pressure remains effective in the spring chamber even after the injection is completed and the pressure line is relieved. As a result, an increased closing force is exerted on the valve needle, which leads to a quick and safe closing of the injection valve.
  • the invention is based on the object of avoiding the disadvantages mentioned above and compensating for the additional force on the valve needle which occurs when the injection valve is opened, in order thereby to continuously control the needle stroke as a prerequisite for continuously controlling the outflow cross section or the outflow resistance of the outlet openings of an injection valve as a function of to enable the delivery rate of the injection pump.
  • the arrangement according to claim 2 largely achieves pressure compensation between the forces on the two ends of the valve needle, so that only the force balance controlling the needle stroke between the force on the pressure shoulder and the spring force is decisive.
  • the force on the pressure shoulder and thus also the opposing force of the spring is relatively low even at high opening pressures of the injection valve. Since the diameter of the needle seat is particularly large due to the narrow pressure shoulder, its stress is low. Therefore, the use of high opening pressures and the arrangement of the outlet openings in the needle seat area is possible without risking its durability.
  • the arrangement according to the invention according to claim 4 has the effect that the injection pressure acting under the valve needle passes through the hollow bore of the valve needle to the second pressure chamber.
  • the side of the valve needle remote from the seat is subjected to the pressure which acts on the underside of the valve needle, which, due to the equality of the active surfaces, leads to compensation of the pressure level of the valve needle.
  • DE-PS 759 420 describes an injection valve opening against the flow direction of the fuel, the valve needle of which is also hollow-drilled. This creates a connection between the atomizer head and the space above the nozzle needle. However, this connection does not serve to apply the injection pressure prevailing in the atomizer head to the spring-side end of the valve needle, but rather to empty the space above the nozzle needle of leakage fuel.
  • the arrangement according to the invention according to claim 4 also ensures that the pressure increasing the closing force of the valve needle in the second pressure chamber is maintained long enough to reliably prevent re-opening of the injection valve by returning pressure waves in the injection line. On the other hand, however, it is ensured that the pressure in the second pressure chamber has dropped so far by the following injection that a reopening of the injection valve is ensured.
  • Claim 5 describes a particularly simple form of the combination of valve needle and transfer piece.
  • DE-PS-759 420 also shows a valve needle with a hollow-bore transmission piece which is attached to the spring-side end and has a reduced diameter.
  • this transmission piece is not used to transmit hydraulic pressure to the valve needle, nor is it used to seal a second pressure chamber against leakage oil discharge.
  • the arrangement according to claim 6 ensures that the force exerted by the injection pressure on the needle tip when the valve needle is lifted from its seat is compensated for by an equally large but oppositely acting force on the transfer piece and thus a continuous control of the needle stroke depending on the injection pressure.
  • the embodiment according to claim 7 ensures that the valve needle has a low weight and thus exhibits favorable dynamic behavior.
  • the valve needle of DE-PS-759 420 only has a small diameter capillary bore, which hardly brings any weight reduction.
  • Claim 8 describes an advantageous embodiment of a discharge from the second pressure chamber with the desired throttle characteristic.
  • Claims 9 and 10 describe advantageous designs of the check valve with low weight and low manufacturing costs.
  • the embodiment according to claim 12 offers the possibility of supplying fuel to a hotspot located in the combustion chamber in a metered manner and thus initiating combustion, particularly in the case of flame-resistant fuels.
  • the fuel injector shown in FIG. 1 essentially consists of a valve body 1, a valve insert 2 and a valve needle 3, an intermediate piece 4 being provided between the valve body 1 and the valve insert 2.
  • the valve needle 3 engages in a tubular configuration of the valve insert 2.
  • the tubular end is at the axial end Training of the valve needle seat 5 is provided in the form of two interlocking cones.
  • the three parts valve body 1, valve insert 2 and intermediate piece 4 are pressed together axially pressure-tight by a sleeve 6, the intermediate piece 4 being fixed by the valve insert 2, for example, by pins, not shown.
  • the sleeve 6 is designed as a union nut and is firmly screwed to the valve body 1.
  • the fuel is conducted via channels 7, 8 in the valve body 1 via a channel 9 in the intermediate piece 4 and via a channel 10 in the valve insert 2 from a connecting piece 29 to a first pressure chamber 11 on a pressure shoulder 12 of the valve needle 3.
  • the valve needle 3 forms the pressure shoulder 12 by changing its outer diameter. From the pressure shoulder 12 to the valve needle seat 5, the valve needle 3 has a radial gap in the valve insert 2, as a result of which an annular space 13 is formed.
  • the fuel passes from the pressure chamber 11 to the valve needle seat 5 through this intermediate space 13.
  • the valve needle 3 itself is guided axially and axially tightly by the valve insert 2 on an axial section which is arranged on the side of the pressure shoulder 12 facing away from the valve needle seat 5.
  • the valve needle 3 is acted upon in the closing direction by a force from an energy store.
  • the energy accumulator can in particular be a compression spring 14 which is inserted in a cavity 22 of the valve body 1.
  • a displaceable piston which stores the force in a compressible medium such as air, could also be provided for this purpose.
  • the compression spring 14 acts via a spring plate 16 on a transmission piece 17, which in turn rests on the valve needle 3.
  • the transfer piece 17 is axially movably guided in the intermediate piece 4 and has an outer diameter which corresponds to the largest diameter of the contact surface of the valve needle 3 on the valve needle seat 5.
  • the outer diameter of the transfer piece 17 is smaller than the guide diameter of the valve needle 3.
  • the transfer piece 17 engages slightly in the valve insert 2, so that the different diameters of the valve needle 3 and the transfer piece 17 form a radial shoulder 18 between the valve insert 2 and the intermediate piece 4 becomes. This radial shoulder 18 is the end stop for the stroke of the valve needle 3.
  • the two-part construction of the valve needle 3 and the transfer piece 17 advantageously means that the valve needle guide in the valve insert 2 does not need to be exactly aligned with the guide bore for the transfer piece 17.
  • valve needle 3, the transmission piece 17 and the spring plate 16 are hollow-drilled over the entire axial length, and the cavity 22 is designed as a second pressure chamber 15.
  • a sudschiagventit 19 is provided in the interior of the valve needle 3.
  • the check valve 19 consists of a ball 28 which rests on a conical seat in the hollow bore 20.
  • the ball 20 closes an axial opening 21 in the tip of the valve needle 3.
  • the opening 21 leads into a cavity 25 at the tip of the valve needle 3 in the valve insert 2, the cavity 25 being separated from the radial intermediate space 13 by the valve needle seat 5.
  • the outlet openings 23 are arranged in a star shape, which bring the fuel into the combustion chamber of the internal combustion engine.
  • the bore in the transmission piece 17 and a through bore in the spring plate 16 are connected, so that the hollow bore 20 is directly connected to the second pressure chamber 15.
  • the diameter of the hollow bore 20 corresponds to the smallest diameter of the contact surface of the valve needle 3 on the valve needle seat 5.
  • An outflow from the second pressure chamber 15 is provided between the transmission piece 17 and the intermediate piece 4 by appropriate radial play of these two parts.
  • the throttle characteristics of the drain can be influenced by the size of this game.
  • the fuel passes from the second pressure chamber 15 between the transfer piece 17 and the intermediate piece 4 to the radial shoulder 18, from where it is conducted via a radial channel to a leak oil line 26.
  • the leakage oil line 26 is connected without pressure to the injection pump or to the tank of the internal combustion engine.
  • the mode of operation of an injection valve according to the invention is based on the pressurization of the second pressure chamber 15 with fuel pressure.
  • the fuel is fed through the bores 7, 8, 9 and 10 into the pressure chamber 11 of the pressure shoulder 12. Furthermore, the fuel reaches the valve needle seat 5 via the radial intermediate space 13. If the fuel is now pressurized by the injection pump, the pressure shoulder 12 in the pressure chamber 11 is loaded with a force resulting therefrom. This force is in equilibrium with the force from the energy store, which presses the valve needle 3 onto the valve needle seat 5. If the fuel pressure is sufficiently high, the valve needle 3 is raised slightly. At this moment the fuel flows into the valve needle seat 5 and acts on the axial end of the valve needle 3 there. As a result of this additional pressure, the valve needle is suddenly subjected to a considerable force in the opening direction and moves in the direction of paragraph 18.
  • valve needle 3 is at this moment in balance of forces between the force from the energy accumulator and the pressure force of the fuel at the pressure shoulder 12.
  • a certain stroke of the valve needle 3 occurs, which in turn has an associated outflow cross section or outflow resistance via the geometry on the valve needle seats or on the valve needle seat 5 controls.
  • the outflow cross section or the outflow resistance is therefore pressure-dependent and is influenced in such a way that a spray pressure which is as constant and high as possible over the entire load and speed range is generated at the outlet openings 23.
  • Large outflow cross-sections are provided for large amounts of fuel at full load and correspondingly much smaller outflow cross-sections for smaller amounts of fuel in the part-load range, so that despite these different conditions, the mixture is formed in the combustion chamber of the internal combustion engine with optimal discharge pressure even at part-load.
  • the valve needle according to the invention is designed with a particularly small pressure shoulder. On the other hand, this allows a very large valve needle seat. Also, because of the small pressure shoulder, the forces that act on the pressure shoulder due to the fuel pressure are low. This in turn means that only a weak force from the energy store must act in the closing direction of the valve needle 3.
  • valve needle seat 5 since the area of the valve needle seat 5 has become larger, the valve needle seat stress is considerably reduced in two respects.
  • a valve needle designed in this way is therefore particularly suitable for very high fuel injection pressures. The high forces occurring in the opening direction of the valve needle due to the large valve seat surface are compensated for by the fuel pressure acting in the opposite direction in the second pressure chamber 15 after a very short period of time.
  • any desired injection characteristic or pressure curve over the valve needle stroke can be achieved by adapting the characteristic curve of the spring from the energy accumulator. If the spring has a low spring stiffness, ie if the spring force changes only slightly above the needle stroke, then the force on the pressure shoulder 12 and thus the injection pressure at the outlet openings 23 remain almost constant over the needle stroke. If, on the other hand, a steep spring characteristic curve is selected, targeted injection pressure profiles can be realized. By choosing the spring stiffness, the dependence of the injection pressure on the engine load and the speed can be changed. Greater spring stiffness results in increasing injection pressure with increasing load and speed.
  • the fuel pressure initially breaks down in the injection pump.
  • This vacuum wave travels into the fuel injector and thus acts after a time delay both in the pressure chamber 11 on the pressure shoulder and on the valve needle seat.
  • This begins to move in the closing direction because of the falling fuel pressure and thus the decreasing force on the pressure shoulder 12.
  • the closing process is considerably accelerated by the residual pressure in the further pressure chamber 15 in connection with the check valve 19, since the backflow of the fuel from the second pressure chamber 15 into the space on the valve needle seat surface is prevented. This high closing force reliably prevents the fuel from being re-injected.
  • the pressure chamber 15 is connected to the leak oil line 26 via a throttle.
  • the throttle has such a strong throttle characteristic that the pressure in the second pressure chamber 15 is only released after a considerable time interval. It only has to be ensured that the pressure in the second pressure chamber 15 has dropped to Leckol level before the next injection process.
  • this drain is provided by a defined gap in the axial guide between the transfer piece 17 and the intermediate piece 4. It may be expedient to provide a separate connecting bore in the intermediate piece 4 with a certain throttle characteristic.
  • FIG. 2 shows a second exemplary embodiment of the fuel injection valve according to the invention.
  • the transfer piece 17 is formed there in one piece with the valve needle 3.
  • the intermediate piece 4 is guided axially by the valve needle 3.
  • a spring-loaded check valve 19 is inserted in the hollow bore 20.
  • the hydraulically acting check valve 19 with a ball 28 in the front part of the hollow bore 20 according to FIG. 1 is omitted in this case.
  • valve 3 shows further configurations of the valve needle seat 5 and the outlet openings 23.
  • 3a describes a throttle pin nozzle with a throttle pin 24 and with radial, star-shaped main outlet openings 23.
  • an injection jet is emitted via the axially downward-pointing outlet opening 23, which either remains constant in quantity as the stroke of the valve needle 3 increases or continuously decreases becomes, while at the same time the ra dialen outlet openings 23 increases the amount of fuel escaping.
  • the stroke of the valve needle 3 determines the entire outlet cross section or outflow resistance of all outlet openings 23 as a function of the injection pressure.
  • Such an injector is particularly suitable for the use of a combustion process with an externally unheated glow ignition source.
  • a fuel jet which steadily decreases with the stroke, then emerges in a particularly advantageous manner, which heats an incandescent body, in particular a hollow body, such that the incandescent body can ignite the injection jets emerging from the star-shaped outlet openings 23.
  • FIG. 3b shows a radially star-shaped multi-hole nozzle with an outflow cross-section of the outlet openings 23 which is dependent on the stroke of the valve needle 3.
  • the control of the outflow cross-section takes place via a slide 31 at the axial end of the nozzle needle 3.
  • the slide 31 releases parts of the outlet openings 23.
  • the outlet openings 23 can be arranged at different heights with respect to the slide edge, so that not all but only some of the outlet openings 23 are released at the same time.
  • the openings 21 to the hollow bore 20 are at right angles to the valve axis directly on the valve needle seat 5.
  • a pin nozzle with a regulated discharge cross-section is shown depending on the stroke of the valve needle 3.
  • the valve needle 3 In the front end of the valve needle 3 there is a pin 32 which dips into a corresponding opening in the valve insert 2. If the valve needle 3 lifts off the valve needle seat 5, the fuel flows past the pin 32 through the annular outlet opening 23 into the combustion chamber.
  • the pin 32 is tapered at the front end. The outflow cross-section of the outlet opening 23 is thus controlled by the pin 32 via the stroke of the valve needle 3 and the pin 32.

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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 (13)

1. Soupape d'injection de combustible pour un moteur à combustion interne avec un corps de soupape (1 ) et une garniture de soupape (2) dans laquelle est guidé axialement un pointeau de soupape (3) qui s'applique par une extrémité axiale sur un siège de pointeau de soupape (5) de la garniture de soupape (2), et qui est sollicité en direction du siège de pointeau de soupape (5) par un effort en provenance d'un accumulateur d'effort, une section transversale d'écoulement d'au moins un orifice de sortie (23) étant susceptible d'être commandée par le pointeau de soupape (3), et du combustible en provenance d'une pompe d'injection séparée étant susceptible d'être amené par l'intermédiaire de canalisations et de canaux (7, 8, 9, 10, 13, 20) jusqu'à une première chambre de pression (11) sur un épaulement (12) du pointeau de soupape (3) ainsi que jusqu'à une seconde chambre de pression (15), tandis que dans le canal allant de la première chambre de pression (11) à la deuxième chambre de pression (15), et qui constitue l'unique arrivée à la seconde chambre de pression (15), une garniture jouant le rôle de soupape de retenue est prévue, cette soupape de retenue (28) s'ouvrant dans le sens d'écoulement vers la seconde chambre de pression et se fermant dans le sens opposé, cependant que, du fait de la pression du combustible dans la deuxième chambre de pression (15), le pointeau de soupape (3) est susceptible d'être sollicité par un effort en direction du siège de pointeau de soupape (5), soupape d'injection caractérisée en ce que le canal allant de la première chambre de pression (11) à la deuxième chambre de pression (15) comporte un premier tronçon allant de la première chambre de pression (11 ) au siège de pointeau de soupape (5), un second tronçon de commande se raccordant au siège de pointeau de soupape (5), et un troisième tronçon aboutissant à la seconde chambre de pression (15), le second et le troisième tronçons étant reliés par l'intermédiaire d'au moins un orifice de communication (21), et au moins un orifice de sortie (23) dans la garniture de soupape (2) étant disposé au voisinage du siège de soupape et/ou du second tronçon.
2. Soupape d'injection de combustible selon la revendication 1, caractérisée en ce que la surface déterminante pour l'action de l'effort du combustible dans la seconde chambre de pression (15) correpond à peu près à la surface de projection de la surface du siège de pointeau de soupape sur le plan perpendiculaire à l'axe du pointeau de soupape (3).
3. Soupape d'injection de combustible selon la revendication 1, caractérisée en ce que la surface de projection sur l'épaulement (12) du pointeau de soupape est beaucoup plus petite que la surface de projection de la pointe du pointeau de soupape.
4. Soupape d'injection de combustible selon la revendication 1, avec une pièce intermédiaire (4) disposée exialement entre la garniture de soupape (2) et le corps de soupape (1 ), caractérisée en ce que le canal allant de la première chambre de pression (11 ) à la seconde chambre de pression (15) revêt la forme d'un perçage creux (20) dans le pointeau de soupape (3), tandis qu'il est prévu, partant de la seconde chambre de pression (15) une évacuation reliée à une canalisation de fuite d'huile (26), et cette évacuation comportant un étranglement hydraulique prononcé.
5. Soupape d'injction de combustible selon la revendication 4, avec une pièce creuse perforée de transmission (17) disposée centralement dans la pièce intemédiaire (4), soupape d'injection caractérisée en ce que la pièce de transmission (17) est venue d'une seule pièce avec le pointeau de soupape (3) et centre la pièce intemédiaire (4) lors du montage par l'intermédiaire d'un perçage (27).
6. Soupape d'injection de combustible selon la revendication 5, caractérisée en ce que le diamètre du perçage cylindrique (27) dans la pièce intermédiaire (4) correspond à peu près au diamètre externe du siège de pointeau de soupape (5).
7. Soupape d'injection de combustible selon la revendication 6, caractérisée en ce que le diamètre du perçage (20) dans la pointeau de soupape (3) correspond à peu près au diamètre interne du siège de pointeau de soupape (5).
8. Soupape d'injection de combustible selon la revendication 5, caractérisée en ce que l'ajustement entre la pièce de transmission (17) et la pièce intermédiaire (4) ménage un interstice défini avec une caractéristique d'étranglement.
9. Soupape d'injection de combustible selon la revendication 1, caractérisée en ce que la garniture jouant le rôle de soupape de retenue est réalisée sous la forme d'une bille (28) s'appliquant, du fait de la pression du combustible, sur une surface conique à la pointe ou bien à l'extrémité (3) dans le perçage (20).
10. Soupape d'injection de combustible selon la revendication 1, caractérisée en ce que la garniture jouant le rôle de soupape de retenue est réalisée sous la forme d'une soupape à bille sollicitée par un ressort, qui est insérée à l'extrémité côté accumulateur d'effort ou bien à la pointe du pointeau de soupape (3) dans le perçage (20).
11. Soupape d'injection de combustible selon la revendication 1, caractérisée en ce que la garniture de soupape (2) comporte plusieurs orifices de sortie (23) s'étendant radialement à peu près en forme d'étoile, qui partent du siège de pointeau de soupape (5).
12. Soupape d'injection de combustible selon la revendication 11, caractérisée en ce que la garniture de soupape (2) conjointement avec le pointeau de soupape (3) constituent une buse à téton d'étranglement.
13. Soupape d'injection de combustible selon la revendication 1, caractérisée en ce que la soupape d'injection de combustible est conçue pour une étendue de pression de combustible allant d'environ 500 à 2000 bars.
EP86103736A 1985-03-20 1986-03-19 Soupape d'injection de combustible Expired EP0195440B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86103736T ATE46744T1 (de) 1985-03-20 1986-03-19 Brennstoffeinspritzventil.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3510075 1985-03-20
DE19853510075 DE3510075A1 (de) 1985-03-20 1985-03-20 Brennstoffeinspritzventil

Publications (3)

Publication Number Publication Date
EP0195440A2 EP0195440A2 (fr) 1986-09-24
EP0195440A3 EP0195440A3 (en) 1987-09-30
EP0195440B1 true EP0195440B1 (fr) 1989-09-27

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Family Applications (1)

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EP86103736A Expired EP0195440B1 (fr) 1985-03-20 1986-03-19 Soupape d'injection de combustible

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EP (1) EP0195440B1 (fr)
AT (1) ATE46744T1 (fr)
DE (2) DE3510075A1 (fr)

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GB2203795A (en) * 1987-04-24 1988-10-26 Lucas Ind Plc I.C. engine fuel injection nozzle
US5645224A (en) * 1995-03-27 1997-07-08 Caterpillar Inc. Modulating flow diverter for a fuel injector
DE102019103511A1 (de) * 2019-02-12 2020-08-13 Liebherr-Components Deggendorf Gmbh Düse für einen Kraftstoffinjektor
CN117627833A (zh) * 2023-10-19 2024-03-01 山东省机械设计研究院 一种复合多交叉喷孔下的高压共轨喷油嘴用阀体及喷油嘴

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US4186884A (en) * 1978-01-11 1980-02-05 Lucas Industries Limited Liquid fuel injection nozzles
DD153167A1 (de) * 1980-09-12 1981-12-23 Hans Gaertner Mehrstrahl-zapfenduese fuer direkteinspritzung bei verbrennungsmotoren
GB2129052B (en) * 1982-10-23 1986-01-29 Lucas Ind Plc Fuel injection nozzle for i c engines

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Publication number Publication date
DE3665903D1 (en) 1989-11-02
EP0195440A2 (fr) 1986-09-24
EP0195440A3 (en) 1987-09-30
DE3510075A1 (de) 1986-09-25
ATE46744T1 (de) 1989-10-15

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