EP0195440A2 - Soupape d'injection de combustible - Google Patents

Soupape d'injection de combustible Download PDF

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Publication number
EP0195440A2
EP0195440A2 EP86103736A EP86103736A EP0195440A2 EP 0195440 A2 EP0195440 A2 EP 0195440A2 EP 86103736 A EP86103736 A EP 86103736A EP 86103736 A EP86103736 A EP 86103736A EP 0195440 A2 EP0195440 A2 EP 0195440A2
Authority
EP
European Patent Office
Prior art keywords
nozzle needle
fuel
pressure
nozzle
pressure chamber
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
EP86103736A
Other languages
German (de)
English (en)
Other versions
EP0195440A3 (en
EP0195440B1 (fr
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
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 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 present invention relates to a fuel injection valve for an internal combustion engine with a valve body and a nozzle insert, in which a nozzle needle is axially guided, which is arranged with an axial end resting on a nozzle needle seat of the nozzle insert and acted upon by a force from a force accumulator in the direction of the nozzle needle seat is, from the nozzle needle on the nozzle needle seat through its stroke, an outflow cross section of at least one outlet opening can be controlled and fuel can be supplied from a separate injection pump via lines and channels to a first pressure chamber on a pressure shoulder of the nozzle needle and up to a second pressure chamber.
  • injection pumps of internal combustion engines generate an injection pressure that is dependent on the speed and the load on the internal combustion engine.
  • the fuel delivered by the injection pump which is injected into the combustion chamber of the internal combustion engine via an injection nozzle with a constant outflow cross-section, can thus be used on the basis of the speed-dependent or load-dependent characteristic of B uel injection pump only at a very specific injection pressure and a certain Brennstof routinemenge an optimum spray pattern in terms of a good atomization of the fuel and thus a good mixture preparation can be achieved. It is known, in particular with regard to the optimization of the combustion process and low noise and pollutant emissions of the internal combustion engine, to adapt the injection process to the various load conditions of the internal combustion engine by controlling the outflow cross section of the injection nozzle.
  • DE-OS 33 38 120 describes a fuel injection valve in which the fuel is introduced into the combustion chamber of the internal combustion engine with a spray pressure that is as constant as possible at the outlet openings of the injection nozzle.
  • the cross section of the outlet openings is controlled as a function of the injection pressure in such a way that a high fuel atomization quality can be achieved over the entire load range of the internal combustion engine.
  • the DE-OS provides for the fuel to act on a pressure shoulder of a nozzle needle on the one hand and, on the other hand, via hollow bores in the nozzle needle to a pressure piston which, like the pressure shoulder, generates a force in the opening direction of the nozzle needle.
  • the invention has for its object to provide a fuel injector in which the fuel can be introduced into the combustion chamber with a high, largely uniform spray pressure over the entire speed and load range of the internal combustion engine and in which a controlled opening and closing process of the nozzle needle can be achieved in order to minimize etc. at low B uel consumption emit encouraging the pollutants such as NO, carbon black, and also to reduce the noise Missione.
  • the stroke of the nozzle needle after its opening is controlled as a function of the current pressure in the fuel.
  • the stroke defines a certain outflow cross-section via the geometry at the fuel outlet of the injection nozzle.
  • the force of the fuel pressure on the nozzle needle shoulder forms a balance with the force of the nozzle needle spring or another force accumulator.
  • the additional force in the opening direction of the nozzle needle on the nozzle needle seat surface due to the fuel pressure, which is exerted on the nozzle needle seat surface after the opening of the nozzle needle is compensated for by precisely this fuel pressure, which generates a force in the closing direction in a second pressure chamber.
  • the fuel injector according to the invention also has an excellent closing characteristic, since an insert acting as a check valve after the drop in the injection pressure prevents immediate relief of the second pressure chamber by flowing back into the supply line of the fuel. Sitting the valve needle due to the pressure drop in the fuel back to the nozzle needle seat, the force from the second pressure chamber which urges the nozzle needle is no longer balanced by the force of the fuel pressure at the D üsennadelsitz.
  • the force of the fuel pressure in the second pressure chamber thus acts as an additional closing force, which reliably prevents the fuel injector from being re-injected.
  • the invention is particularly expediently applicable to direct-injection diesel engines.
  • the projection surface of the pressure shoulder which is decisive for the force of the fuel on the pressure shoulder, be made considerably smaller in the plane perpendicular to the nozzle needle axis than the projection surface of the nozzle needle tip in the same plane.
  • Such a nozzle needle has a particularly small pressure shoulder.
  • a small pressure shoulder leads due to the small D üsennadelöff- voltage power at low nozzle needle spring forces, thereby achieving a low nozzle needle seat stress.
  • the nozzle seat area can be enlarged. to further reduce nozzle needle seat stress.
  • the entire length of the nozzle needle is drilled so that the hollow bore forms a feed opening on the nozzle needle seat at the tip of the nozzle needle.
  • the feed opening lies behind the nozzle needle seat in the direction of flow of the fuel during injection.
  • the check valve is inserted into the hollow bore of the nozzle needle.
  • the proposed fuel injector is particularly suitable for a pressure-resistant design for use at a fuel pressure of 500 to 2,000 bar.
  • the hydraulic mixture formation energy is increased considerably and the injection time is shortened, so that optimum atomization and combustion are achieved in the entire operating range of the internal combustion engine. This also results in low pollutant and noise emissions.
  • the fuel injector shown in FIG. 1 essentially consists of a valve body 1, a nozzle insert 2 and a nozzle needle 3, an intermediate piece 4 also being provided between the valve body 1 and the nozzle insert 2.
  • the nozzle needle 3 engages in a tubular configuration of the nozzle insert 2.
  • the nozzle needle seat 5 is provided in the form of two interlocking cones.
  • the three parts of valve body 1, nozzle insert 2 and intermediate piece 4 are pressed together axially pressure-tight by a sleeve 6, the intermediate piece 4 being fixed by the nozzle insert 2, for example, by means of pins, not shown.
  • the sleeve 6 can be designed as a union nut and fixed to the valve body 1 be screwed. There can also be other types of fastening such as screwed flanges, soldering, gluing or. Welds may be appropriate; it only has to be connected to one another in a fluid-tight manner.
  • the fuel is guided 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 nozzle insert 2 from a connecting piece 29 to a first pressure chamber 11 on a pressure shoulder 12 of the nozzle needle 3.
  • the nozzle needle 3 forms the pressure shoulder 12 by changing its outer diameter. From the pressure shoulder 12 to the nozzle needle seat 5, the nozzle needle 3 has a radial gap in the nozzle insert 2, as a result of which an annular space 13 is formed.
  • the fuel passes from the pressure chamber 11 to the nozzle needle seat 5 through this intermediate space 13.
  • the nozzle needle 3 itself is guided axially and axially tightly by the nozzle insert 2 on an axial section which is arranged on the side of the pressure shoulder 12 facing away from the nozzle needle seat 5.
  • the nozzle needle 3 is in closing. direction acted upon 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 nozzle needle 3.
  • the transmission piece 17 is axially movably guided in the intermediate piece 4 and has one outer diameter, which corresponds to the largest diameter of the contact surface of the nozzle needle 3 on the nozzle needle seat 5 .
  • the outer diameter of Ubertragungs Swisses 17 is smaller than the guide diameter of the nozzle needle 3.
  • the Ubertragungs Fantasy 17 engages slightly into the D Ü seneinslegi 2 so that the different diameters of the nozzle needle 3 and the Ubertragungsconces 17, a radial shoulder 18 between the nozzle insert 2 and Intermediate piece 4 is formed.
  • This radial shoulder 18 is the end stop for the stroke of the nozzle needle 3. Due to the two-part construction of the nozzle needle 3 and the transfer piece 17, the nozzle needle guide in the nozzle insert 2 advantageously does not need to be exactly aligned with the guide bore for the transfer piece 17.
  • the nozzle 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 check valve 19 is provided in the interior of the nozzle needle 3 at the axial end of the nozzle needle 3 on the nozzle needle seat side.
  • 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 nozzle needle 3.
  • the opening 21 leads into a cavity 22 at the tip of the nozzle needle 3 in the nozzle insert 2, the cavity 22 being separated from the radial intermediate space 13 by the nozzle 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 transfer piece 17 and a through bore in the spring plate 16 follow, so that the hollow bore 20 is connected directly to the second pressure chamber 15.
  • the diameter of the hollow bore 20 corresponds to the smallest diameter of the contact surface of the nozzle needle 3 on the nozzle needle seat 5.
  • a drain from the second pressure chamber 15 is provided between the transmission piece 17 and the intermediate piece 4 by radial play in the fit of these two parts. Due to the size of this game, the throttle characteristics of the drain can be influenced.
  • 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 passes through the radial intermediate space 13 to the nozzle needle seat 5. If the fuel is now pressurized by the injection pump, the pressure shoulder 12 in the pressure space 11 is loaded with a resultant force. This force is in equilibrium with the force from the energy store, which presses the nozzle needle onto the nozzle needle seat 5.
  • the nozzle needle 3 is at a sufficiently high pressure uel B slightly raised. At that moment, the fuel flows into the D üsennadelsitz 5 and acts on the local axial end of the nozzle needle 3. This additional pressure, the injector needle is suddenly subjected to a considerable force in the opening direction and starts to open.
  • the fuel then flows through the opening 21 past the check valve 19 into the hollow bore 20 of the nozzle needle 3.
  • the connection from the pressure chamber 11 to the second pressure chamber 15 is now established. Since the diameter of the bore 27 in the intermediate piece 4 corresponds to the maximum nozzle needle seat diameter, the compressive forces acting on the surfaces formed by this diameter are just completely compensated for. If the fuel pressure has also built up in the second pressure chamber 15 as a function of the displacement effect of the spring plate 16 entering the second pressure chamber 15 and the size of the volume of the second pressure chamber 15, the opening force initially acting on the nozzle needle 3 at the nozzle needle tip is just compensated. At this moment, the nozzle needle 3 is in the equilibrium of forces between the force from the energy store and the pressure force of the fuel at the pressure shoulder 12.
  • the outflow cross section 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 fuel pressures and quantities at full load, and correspondingly much smaller outflow cross sections are available for small fuel pressures in the part-load range, so that despite these different conditions, the mixture is formed in the combustion chamber of the internal combustion engine even at part load with optimal discharge pressure.
  • the nozzle needle according to the invention is designed with a particularly small pressure shoulder. On the other hand, this allows a very large nozzle 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 nozzle needle 3.
  • a nozzle 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 nozzle needle due to the large nozzle needle seat area are compensated by the fuel pressure acting in the opposite direction after a very short period of time in the second pressure chamber 15.
  • any desired injection characteristic or pressure curve can be achieved via the nozzle needle stroke. If the spring has a low spring stiffness, ie if the spring force changes only slightly over the needle stroke, then the force on the pressure shoulder 12 and thus the injection pressure at the outlet openings also remain 23 largely constant over the needle stroke. If, on the other hand, a stiff spring characteristic curve is selected, targeted injection pressure profiles can be implemented. By choosing the spring stiffness, the dependence of the injection pressure on the engine load and the speed can be changed. Larger party stiffnesses result in increasing injection pressure with increasing load and speed.
  • the fuel pressure initially breaks down in the injection pump.
  • This negative pressure wave travels up in the fuel injection valve and thus acts after a time delay, both in the pressure chamber 11 on the pressure shoulder 12 and the Ü D nozzle needle seat.
  • the compression spring 14 in the second pressure chamber 15 expands, as a result of which the spring force acting counter to the fuel pressure drops, and in addition the displacement effect of the nozzle needle 3 or the spring plate 16 reduces the pressure in the second pressure chamber 15, which is why the force applied to the nozzle needle 3 in Closing direction drops.
  • the closing process itself is still considerably increased by the pressure in the further pressure chamber 15 in connection with the check valve 15, since the backflow of the fuel from the second pressure chamber 15 into the space on the nozzle needle seat surface is prevented.
  • the fuel pressure thus largely prevailing in the second pressure chamber 15 since the delivery stroke accelerates the closing movement.
  • the nozzle needle 3 is basically still in a force balance control.
  • the nozzle needle 3 finally arrives at the nozzle needle seat 5 to rest, the fuel pressure acting from below on the nozzle needle tip in the opening direction is missing.
  • the nozzle needle 3 is thus suddenly due to the lack of pressure at the nozzle needle tip of a considerable closing force by the fuel pressure in the second pressure chamber 15, so that there is a very large closing force.
  • This high closing force reliably prevents the fuel injector from being re-injected.
  • the pressure chamber 15 is connected to a 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 is largely reduced 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. For this purpose, it may be expedient to provide a separate connecting bore in the intermediate piece 4 with a specific 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 nozzle needle 3.
  • the intermediate piece 4 is guided axially by the nozzle needle 3.
  • a spring-loaded check valve 19 is inserted in the hollow bore 20.
  • the hydraulic check valve 19 with a ball 28 in the front part of the hollow bore 20 moderate overall ß F ig. 1 does not apply in this case.
  • the hollow bore 20 has a additional throttle, which achieves a time delay in the pressure build-up of the fuel pressure in the second pressure chamber 15.
  • 3 shows further configurations of the nozzle needle seat 5 and the outlet openings 23.
  • 3a describes a throttle pin nozzle 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 nozzle needle 3 increases, or is continuously reduced, while at the same time the amount of fuel escaping increases in the radial outlet openings 23 arranged in a star shape.
  • the stroke of the nozzle needle 3 determines the entire outlet cross section of all outlet openings 23 and thus ensures an outlet cross section which is adapted to the 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 decreases steadily with the stroke and which heats up an incandescent body, in particular a hollow body, in such a way that the incandescent body can ignite the injection jets emerging from the star-shaped outlet openings 23.
  • Fig. 3b has a radially in a star shape ausspritzende M is ehrlochdüse with a dependent on the stroke of the nozzle needle 3 outflow cross-section of the outlet openings 23 shown.
  • 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 located at right angles to the nozzle needle axis directly on the nozzle needle seat 5.
  • a pin nozzle with a regulated discharge cross-section is shown depending on the stroke of the nozzle needle 3.
  • a pin 32 which engages in a corresponding opening in the nozzle insert 2. If the nozzle needle 3 lifts off the nozzle needle seat 5, the fuel flows to 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 nozzle needle 3 and the pin 32.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
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
DE19853510075 DE3510075A1 (de) 1985-03-20 1985-03-20 Brennstoffeinspritzventil
DE3510075 1985-03-20

Publications (3)

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

Family

ID=6265811

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86103736A Expired EP0195440B1 (fr) 1985-03-20 1986-03-19 Soupape d'injection de combustible

Country Status (3)

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2203795A (en) * 1987-04-24 1988-10-26 Lucas Ind Plc I.C. engine fuel injection nozzle
GB2299374A (en) * 1995-03-27 1996-10-02 Caterpillar Inc Valved injection nozzle
CN113423945A (zh) * 2019-02-12 2021-09-21 利勃海尔零部件德根多夫有限公司 用于燃料喷射器的喷嘴
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

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE759420C (de) * 1940-08-16 1953-11-16 Daimler Benz Ag Geschlossene Einspritzduese fuer Brennkraftmaschinen
DE875279C (de) * 1941-12-31 1953-04-30 Cav Ltd Brennstoff-Einspritzduese fuer Verbrennungskraftmaschinen
DE967936C (de) * 1953-10-23 1957-12-27 Maschf Augsburg Nuernberg Ag Brennstoffeinspritzventil
US2959360A (en) * 1957-09-20 1960-11-08 Alco Products Inc Fuel injectors
GB1412413A (en) * 1971-10-28 1975-11-05 Cav Ltd Liquid fuel injection systems
GB2012359B (en) * 1978-01-11 1982-05-06 Lucas Industries Ltd Fuel injection nozzle
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

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2203795A (en) * 1987-04-24 1988-10-26 Lucas Ind Plc I.C. engine fuel injection nozzle
GB2299374A (en) * 1995-03-27 1996-10-02 Caterpillar Inc Valved injection nozzle
US5645224A (en) * 1995-03-27 1997-07-08 Caterpillar Inc. Modulating flow diverter for a fuel injector
GB2299374B (en) * 1995-03-27 1999-02-24 Caterpillar Inc Modulating flow diverter for a fuel injector
CN113423945A (zh) * 2019-02-12 2021-09-21 利勃海尔零部件德根多夫有限公司 用于燃料喷射器的喷嘴
CN113423945B (zh) * 2019-02-12 2024-02-06 利勃海尔零部件德根多夫有限公司 用于燃料喷射器的喷嘴
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

Also Published As

Publication number Publication date
DE3665903D1 (en) 1989-11-02
EP0195440A3 (en) 1987-09-30
ATE46744T1 (de) 1989-10-15
EP0195440B1 (fr) 1989-09-27
DE3510075A1 (de) 1986-09-25

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