WO2018068925A1 - Injecteur à rampe commune piézoélectrique à compensation hydraulique du jeu par déplacement du siège de soupape - Google Patents

Injecteur à rampe commune piézoélectrique à compensation hydraulique du jeu par déplacement du siège de soupape Download PDF

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Publication number
WO2018068925A1
WO2018068925A1 PCT/EP2017/070363 EP2017070363W WO2018068925A1 WO 2018068925 A1 WO2018068925 A1 WO 2018068925A1 EP 2017070363 W EP2017070363 W EP 2017070363W WO 2018068925 A1 WO2018068925 A1 WO 2018068925A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
valve body
nozzle
chamber
injection
Prior art date
Application number
PCT/EP2017/070363
Other languages
German (de)
English (en)
Inventor
Willibald SCHÜRZ
Original Assignee
Continental Automotive 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 Continental Automotive Gmbh filed Critical Continental Automotive Gmbh
Publication of WO2018068925A1 publication Critical patent/WO2018068925A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M47/027—Electrically actuated valves draining the chamber to release the 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
    • 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
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion

Definitions

  • the present invention relates to an injection valve with servo valve control for the injection of fuel into the combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • Such injection valves are typically used in conjunction with a high-pressure so-called common rail systems.
  • a piezoelectric element is often used as the actuator, with the control of the injection quantity of such common rail injection valves being predominantly controlled indirectly via a servo valve.
  • the supply of fuel is typically carried out under very high pressure via a high pressure port and a high pressure line in the injector body through a valve plate on a throttle plate.
  • a control chamber is connected via an inlet throttle with the high pressure line.
  • the control chamber is connected via an outlet throttle with a valve chamber.
  • the injection nozzle In the front or lower area, which is the area which faces the combustion chamber, the injection nozzle has a nozzle body and a nozzle needle, wherein the nozzle needle is biased with a nozzle spring so that it exerts a closing force on the nozzle needle. Since the control chamber is connected to the rail system via the high-pressure connection, in the non-actuated state, a high pressure prevails in the control chamber, which corresponds to the pressure in the rail system (rail pressure). This results in an additional hydraulic force effect, which holds the nozzle needle in the closed position and thus the openings of the injection valve are closed.
  • the piezo actuator If the piezo actuator is actuated, it actuates the servo valve. As a result, fuel can leave the control chamber via the outlet throttle. As a result, the pressure in the control chamber is lowered and after falling below a certain pressure threshold, the nozzle needle is opened. After a subsequent discharge of the piezoelectric actuator closes the servo valve, the control chamber is refilled via a connection to the high pressure system, so that the pressure in the control room again builds up to rail pressure level and the nozzle needle closes.
  • the dynamics of the pressure drop or pressure build-up in the control chamber and the needle speed during the needle opening or needle closing movement are essentially determined by the dimensioning of the inlet and outlet throttles.
  • injectors in the engine provides thermally very complex boundary conditions with different heat sources and heat sinks.
  • the temperature increase is represent of relaxing the fuel from rail pressure on the other ⁇ ambient pressure a significant heat source in a row.
  • Object of the present invention is therefore to avoid the above-mentioned problems of injectors according to the prior art and to provide an injection valve with servo valve control available, which decoupled the actuator sufficiently from the nozzle needle, on the other hand, by temperature fluctuations and wear of components occurring length changes during operation of the injection valve compensated.
  • This object is solved by the characterizing part of claim 1 and further explained by the teaching of the dependent claims.
  • the invention provides an injection valve with Servoventil- control for the injection of fuel into a combustion chamber of an internal combustion engine, wherein the injection ⁇ valve has an injector body with an injection nozzle, which in turn contains a nozzle module with a nozzle body and a nozzle needle, wherein the nozzle module in the lower, the combustion chamber facing side of the injector body is arranged.
  • the nozzle needle corresponds with a nozzle spring such that it exerts a closing force on the nozzle needle.
  • the injection valve is also connected to a high-pressure line, via which it is connected to the high-pressure fuel system (common rail).
  • the high pressure line is connected via a supply line to a control chamber, wherein the control chamber is in turn connected via a fluid passage with the valve chamber.
  • a nozzle orifice is present, which can support the closing of the nozzle needle hydraulically.
  • valve body In the valve chamber itself, a valve body is arranged, which cooperates with a valve spring which pushes the valve body of a throttle plate.
  • the valve body itself is in the closed state of the injection valve with the actuator in contact, preferably with a piezoelectric actuator, which is biased by a wave spring.
  • more of the valve body is now formed as a stepped piston with a region of larger diameter and a smaller diameter region. The valve body is guided in the valve plate. In the transition region from the large diameter of the valve body to the small diameter of the .
  • Valve body is formed a hydraulic coupling space which is defined by the valve body and the valve plate. Between the smaller diameter of the valve body and the valve plate, a first guide is formed and formed between the large diameter of the valve body and the valve plate, a second guide, which are designed such that they in the closed state of the injector in the coupling space slightly compared to rail pressure lowered pressure prevails, whereby a permanent leakage in the region of the first guide of the small diameter of the valve body is small, which permanent leakage is supplied via the second guide in the region of the large diameter of the coupling space. Furthermore, an outlet throttle is formed in the valve body for connecting the valve chamber with a low-pressure region.
  • the system of staged pistons with the respective permanent leaks in the guides and the coupling volume acts as a hydraulic coupler.
  • the outlet throttle By forming the outlet throttle in the valve body, a very small volume between the valve seat and the outlet throttle can be realized. This has advantages with regard to the representation of small hydraulic spray intervals in the case of multiple injection.
  • the injection valve is designed such that it occurs in highly dynamic BEWE ⁇ conditions of the injector almost none leakage in the guides such that the guides are nearly dense.
  • the sealing gaps are nearly dense and consequently the coupler is very stiff.
  • the actuator has stacked piezoelectric elements (piezo stack) and is preferably designed as a fully active piezo stack, which generally tends less to cracking inside the piezo stacking sequence, as in contrast to a not fully active stack not only parts its respective piezoelectric layers are covered by electrode material, but the cover over the entire surface and the contacting takes place in the piezo stack sequence alternately edge side of the stack side.
  • the layers to be contacted in opposite directions are alternately insulated on the edge side on this contact side.
  • the high-pressure fuel line can be connected to the interior of the nozzle body via a nozzle diaphragm. In this way, a better hydraulic control of the injector is ensured.
  • the guides between the valve body and the valve plate are each formed with a sealing gap of about 1 to 3 ym.
  • the coupling volume it has proven to be advantageous if it has a defined chamber height.
  • the above criteria provide a particularly suitable operation of the injection valve. In harnessdyna ⁇ mix movements as this represents the piezo movement, the sealing gaps are almost sealed and thus the coupler very stiff.
  • the nozzle needle of the injection valve preferably opens inwards, in particular in diesel applications, because there the pressures of the fuel are very high and thus a high sealing force acts on the sealing seat of the injection valve.
  • an outwardly opening valve of the invention can also be realized, in particular ⁇ sondere at petrol injectors.
  • the actuator is biased by a spring and at the same time shaft seals by ⁇ it is finished.
  • the piezoelectric actuator is stabilized, on the other hand it is additionally protected.
  • Figure 1 shows a longitudinal section through the lower part of a
  • Figure 2 shows a detail section A of Figure 1
  • FIG. 3 is a detail drawing of the valve chamber in longitudinal section.
  • Figure 1 shows the essential part of an injection valve according to the invention, which is located substantially within an injector body 10. Is connected - It can be seen in the right panel of Figure 1 a high pressure line 20, which in the upper region of the injection valve - not shown - by means of a high ⁇ pressure port to a high-pressure fuel system -Common rail.
  • a high pressure line 20 which in the upper region of the injection valve - not shown - by means of a high ⁇ pressure port to a high-pressure fuel system -Common rail.
  • an actuator 40 surrounded by a wave spring 30 is shown, which is connected to the injector body 10 via an actuator head plate 50.
  • the actuator 40 preferably consists of a piezo stack. However, other materials, such as a magnetostrictive material may also be used.
  • a bottom plate 60 of the actuator 40 Via a bottom plate 60 of the actuator 40, this can be brought into contact with a valve body 80 arranged in a valve body 80 and acts directly on this.
  • the high-pressure fuel line 20 likewise runs through the valve plate 70 and opens there into a throttle plate 90 in the region of an inlet throttle 100 and a nozzle diaphragm 110.
  • a nozzle module 120 which is made a nozzle body 130, a nozzle needle 140 and a nozzle spring 150 composed.
  • FIG. 2 shows the detail section A, namely the area of the throttle plate 90 in more detail.
  • the fuel enters the system and passes through the choke 100 to ⁇ running in a control chamber 160.
  • fuel passes through the nozzle orifice 110 into the interior region of the nozzle module 120 at the control chamber 160 over.
  • the control chamber 160 is in turn connected to a fluid passage 170 which leads to the valve plate 70.
  • a valve space 180 Connected to the fluid passage 170, provided in the valve plate 70, is a valve space 180, which can be seen in more detail in FIG.
  • valve space 180 which is formed in the valve plate 70, adjoins.
  • valve body 80 which is acted upon in its lower part by a valve spring (not shown), which exerts an upward force on the valve body 80, so that the servo valve is securely closed even in the unpressurized state.
  • the spring force can be very small since, during operation of the injection valve, the essential closing force for the servo valve results from the pressure in the control chamber 160 and valve chamber 170.
  • the valve body 80 is formed as a stepped piston having a larger diameter portion 190 and a smaller diameter portion 200.
  • the valve body 80 is inserted into the valve plate 70 such that a first guide 210 is formed between the smaller diameter 200 of the valve body 80 and the valve plate 70 and a second guide 220 is formed between the larger diameter 190 of the valve body 80 and the valve plate 70.
  • a central bore 230 is formed, which connects the valve chamber 180 in the region of the smaller diameter 200 of the valve body 80 via an outlet throttle 240 with a low pressure region.
  • a coupling volume 250 is formed in a transition region from the large diameter 190 of the valve body 80 to the small diameter 200 of the valve body 80.
  • the coupling volume 250 is defined by the valve body 80 and the valve plate 90.
  • the coupling volume 250 has a de ⁇ finêt chamber height 280th
  • the first guide 210 and the second guide 220 between the valve body 80 and the valve plate 70 are designed such that under certain conditions defined below, leaks are realized.
  • the piezoactuator 40 which is preferably designed as a fully active piezostack, is integrated into the injector body 10 in such a way that it is supported upwards directly in the injector body 10.
  • the piezoelectric actuator 40 is furnished ⁇ seals by the wave spring 30 against the fuel-carrying areas in the injection valve, wherein the wave spring 30 simultaneously provides for the pre ⁇ voltage of the actuator 40.
  • Unlike the state of the art Technology is thus not sealed the entire actuator space to the fuel, but only the area of the actuator 40 itself. This is possible because it can be dispensed with the use of an Invar sleeve for temperature compensation.
  • the low-pressure volume in the region of the actuator 40 increases by at least an order of magnitude, which is why the pressure pulses which are generated when the servo valve is opened are reduced to a similar extent.
  • the stroke of the piezoelectric actuator 40 is transmitted to the valve body 80.
  • the valve body 80 is, as mentioned above, designed as a stepped piston. Both piston diameter 190, 200 are on a tight mating game of about 1 to 3 ym inserted into the Ven ⁇ tilplatte 70th
  • the hydraulic coupling space 250 results between the smaller diameter 190 of the valve body 80 and the larger diameter 200 of the valve body 80 via a defined chamber height 280, which is limited by the valve body 80 and the valve plate 70.
  • valve body 80 In the closed state, the valve body 80 is supported on the bottom plate 60 on the actuator 40, since the valve body 80 is acted upon by the pressure in the valve chamber 180 in the direction of the actuator 80. In the coupling space 250 there is a pressure which is slightly lowered in relation to the rail pressure, since the pairing clearance in the smaller diameter 200 of the valve body 80 results in a small first pressure
  • Permanent leakage 260 results. This first permanent leak 260 must be supplied via the mating clearance at the larger diameter 190 of the valve body 80. For this purpose, a certain pressure difference is required. Movements of the valve body 80 with very little dynamics, such as temperature expansion and wear, can be compensated by changing the chamber height 280. For highly dynamic movements, as illustrated by the piezo-motion, the guides 210, 220 are nearly dense and consequently the coupler is very stiff. In order to open the servo valve, the actuator is to be discharged from the loaded state in this concept, that is, the actuator 40 is operated inversely. By discharging the actuator 80 shortens, the bottom plate 60 lifts off from the valve body 80 and the servo valve is thus opened.
  • valve chamber 180 It flows from a defined volume flow from the valve chamber 180 via the valve body 80 formed in the outlet throttle 240.
  • the pressure in the valve chamber 180 decreases. Due to the pressure drop in the valve chamber 180, fuel flows from the control chamber 160 into the valve chamber 180 via the fluid connection 170. Since less fuel flows through the inlet throttle 100 than flows through the outlet throttle 170, the pressure in the control chamber 160 drops. This reduces the force acting on the nozzle needle 140 hydraulic closing force. After falling below a certain pressure threshold opens the nozzle needle 140 and the injection begins.
  • the movement of the nozzle needle 140 is determined essentially by the tuning of the flow rates of the inlet and outlet throttles 100, 240.
  • the piezoelectric actuator 40 is reloaded. After reaching the initial charging state of the contact between the actuator base plate 60 and valve body 80 is restored and thus the servo valve closed again.
  • the pressure builds up again to rail pressure level and the nozzle needle 140 closes again.
  • the coupling space 250 should change as little as possible during the opening period of the servo valve.
  • the coupling concept described above results in an advantageous behavior in that the mating games at the small diameter 200 and the large diameter 190 of the valve body 80 in the open state of the servo valve are smaller than in the closed state of the servo valve. This re ⁇ sultiert therefore that when the servo valve is closed in the valve chamber 180 rail pressure prevails, with open servo valve depending on the vote of the inlet and outlet throttle 100, 240 of the valve chamber pressure drops to about half the rail pressure.
  • the expansion of the mating games behaves approximately linearly to the pressure in the valve chamber 180, that is, in the open state of the servo valve, the sealing gaps on the valve body 80 are denser than in the closed state. This results in a fast regeneration behavior of the coupler function.
  • outlet throttle 240 is integrated in the valve body 80, a very small volume between the valve seat and the outlet throttle 240 can be realized. This brings advantages towards ⁇ clear the display of small hydraulic spray distances for multiple injection.

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

Abstract

La présente invention concerne un injecteur à commande d'injecteur asservie présentant un corps d'injecteur (10) pourvu d'une buse d'injection qui présente un module de buse (120) comprenant un corps de buse (130) et une aiguille de buse (140). L'aiguille de buse (140) est alignée avec un ressort de buse (150) qui est disposé de manière à appliquer une force de fermeture sur l'aiguille d'injecteur (140), l'injecteur comportant en outre un conduit haute pression (20) qui est raccordé au système de carburant haute pression et qui est relié à une chambre de commande (160) par l'intermédiaire d'une restriction d'entrée (100). La chambre de commande (160) est reliée à une chambre d'injection (180) par un passage de fluide (170). Un corps de soupape (80) est disposée dans la chambre d'injection (180) et coopère avec un ressort de soupape qui repousse le corps de soupape pour l'écarter d'une platine de restriction (90). Lorsque l'injecteur est à l'état fermé, le corps de soupape (80) se trouve en contact avec un actionneur piézoélectrique (40). L'invention est caractérisée en ce que le corps de soupape (80) se présente sous forme d'un piston étagé présentant un grand diamètre (190) et un petit diamètre (200), le corps de soupape (80) coulissant à l'intérieur d'une platine à soupape (70). L'invention est également caractérisée en ce qu'une chambre de couplage hydraulique (250) est formée dans la zone de transition du grand diamètre (190) au petit diamètre (200), ladite chambre de couplage (250) étant délimitée par le corps de soupape (80) et la platine à soupape (70), un premier passage (210) étant formé entre le petit diamètre (200) et la platine à soupape (70) et un second passage étant formé entre le grand diamètre (190) et la platine à soupape, de telle manière qu'à l'état fermé de l'injecteur, la pression dans la chambre de couplage (250) est légèrement réduite par rapport à la pression de la rampe, ce qui crée une faible fuite permanente (260) à travers le premier passage (210), ladite fuite permanente étant dirigée vers l'espace de couplage (250) à travers second passage (220) formé au niveau du grand diamètre (190). Une restriction de sortie (240) est en outre formée dans le corps de soupape (80) jusqu'au raccordement de la chambre à soupape (180) avec la zone basse pression.
PCT/EP2017/070363 2016-10-14 2017-08-10 Injecteur à rampe commune piézoélectrique à compensation hydraulique du jeu par déplacement du siège de soupape WO2018068925A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016220074.7A DE102016220074B4 (de) 2016-10-14 2016-10-14 Piezo-Common-Rail-Injektor mit hydraulischem Spielausgleich über Bewegung des Ventilsitzes
DE102016220074.7 2016-10-14

Publications (1)

Publication Number Publication Date
WO2018068925A1 true WO2018068925A1 (fr) 2018-04-19

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PCT/EP2017/070363 WO2018068925A1 (fr) 2016-10-14 2017-08-10 Injecteur à rampe commune piézoélectrique à compensation hydraulique du jeu par déplacement du siège de soupape

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DE (1) DE102016220074B4 (fr)
WO (1) WO2018068925A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112502879A (zh) * 2020-11-10 2021-03-16 一汽解放汽车有限公司 一种燃料喷射阀

Citations (3)

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Publication number Priority date Publication date Assignee Title
EP1389274A1 (fr) 2001-05-23 2004-02-18 Westport Research Inc. Soupape a injection actionnee directement
DE102014220890A1 (de) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Einspritzventil zum Einspritzen von Fluid in einen Brennraum einer Brennkraftmaschine
WO2016059069A1 (fr) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape

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Publication number Priority date Publication date Assignee Title
DE102004017303A1 (de) * 2004-04-08 2005-10-27 Robert Bosch Gmbh Einspritzdüse
DE102006026399A1 (de) * 2006-06-07 2007-12-13 Robert Bosch Gmbh Kraftstoffinjektor mit Servounterstützung
DE102007013249A1 (de) * 2007-03-20 2008-09-25 Robert Bosch Gmbh Kraftstoffinjektor mit verbessertem Einspritzverhalten
DE102007017729A1 (de) * 2007-04-16 2008-10-23 Robert Bosch Gmbh Druckausgeglichenes Stellelement
DE102013212330A1 (de) * 2013-06-26 2014-12-31 Continental Automotive Gmbh Verfahren zum Herstellen von Injektoren, insbesondere Kraftstoffinjektoren, sowie Injektor

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1389274A1 (fr) 2001-05-23 2004-02-18 Westport Research Inc. Soupape a injection actionnee directement
DE102014220890A1 (de) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Einspritzventil zum Einspritzen von Fluid in einen Brennraum einer Brennkraftmaschine
WO2016059069A1 (fr) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape

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DE102016220074B4 (de) 2023-02-02
DE102016220074A1 (de) 2018-04-19

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