EP3207243B1 - Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape - Google Patents

Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape Download PDF

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Publication number
EP3207243B1
EP3207243B1 EP15778973.6A EP15778973A EP3207243B1 EP 3207243 B1 EP3207243 B1 EP 3207243B1 EP 15778973 A EP15778973 A EP 15778973A EP 3207243 B1 EP3207243 B1 EP 3207243B1
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EP
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Prior art keywords
valve
nozzle
chamber
injection
actuator
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EP15778973.6A
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German (de)
English (en)
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EP3207243A1 (fr
Inventor
Willibald SCHÜRZ
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Continental Automotive GmbH
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Continental Automotive GmbH
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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
    • F02M2200/70—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 invention relates to an injection valve with servo valve control for the injection of fuel into the combustion chamber of an internal combustion engine, wherein the injection valve is typically used in conjunction with a high-pressure common-rail system.
  • a piezo element is often used as the actuator, wherein the control of the injection quantity of such common rail injection valves is controlled either directly, but predominantly indirectly via a servo valve.
  • the nozzle needle is not directly coupled to the movement of the piezoelectric actuator, but that the piezoelectric actuator in turn actuates a servo valve.
  • the supply of fuel typically occurs under very high pressure via a high pressure port and a high pressure line in the injector body through a valve plate to 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 From the front or lower area, which is the area facing 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. 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, which keeps the nozzle needle in the closed position and thus the openings of the injection valve are closed. If the piezo actuator is actuated, it actuates the servo valve.
  • the piezoelectric actuator is usually surrounded by an Invar sleeve, which has a similar thermal expansion behavior as the piezoelectric actuator.
  • injectors in the engine provides thermally very complex boundary conditions with different heat sources and heat sinks.
  • the piezoelectric actuator self-heating plays an important role as a result of electrical losses.
  • the temperature increase due to the relaxation of the fuel from rail pressure to ambient pressure is a significant source of heat.
  • the installation of the injector in the cylinder head of an engine results in various contact points, such as the combustion chamber seal and the contact of the nozzle tip to the combustion gases corresponding heat flows.
  • An influencing factor to be taken into account on the idle stroke also represents the verpratzenzungskraft in the cylinder head. This is also subject to great tolerance.
  • piezo common rail injectors which use a hydraulic coupler consisting of a cylinder with a drive piston on the actuator side and a driven piston on the valve side.
  • a disadvantage of this arrangement is that this hydraulic coupler is in the low pressure range.
  • a certain pressure level usually about 10 bar, to ensure. In the prior art, this is achieved with a pressure-holding valve.
  • EP 1 640 604 A1 discloses an injection valve, wherein the valve body communicates with a pin, which in turn is connected to an actuator, which is biased by an actuator spring.
  • 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 compensated by components occurring length changes during operation of the injection valve.
  • the invention provides an injection valve with servo valve control for injecting fuel into the 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, 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 an inlet throttle with a control chamber, wherein the control chamber is in turn connected via an outlet throttle 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 so that the valve spring so the valve body depressed from the throttle plate, that in the idle state, a gap between the valve body and throttle plate remains.
  • the valve body itself is also connected to a valve pin in connection, which in turn is connected to an actuator, preferably with a piezoelectric actuator.
  • an actuator preferably with a piezoelectric actuator.
  • this is usually biased by a spring, the actuator spring, so that the layered structure of the piezoceramic layer stack of the piezoelectric actuator is permanently mechanically stabilized.
  • the piezoceramic layer stack should not come into direct contact with the mostly chemically aggressive fuel, for example diesel. Therefore, a fluid seal is preferably provided towards the piezo stack, for example in the form of a sealing membrane between the piezo stack and fluid-carrying parts of the injector. Or the spring itself is sealingly formed with respect to the fuel, for example as a wave spring or corrugated tube spring.
  • the valve pin is now fitted with a very small clearance in the valve body, so that a sealing gap between the valve pin and the valve body is formed.
  • the valve body itself has holes that connect the valve chamber with the sealing gap.
  • the lower end of the valve pin is not completely connected to the valve body, so that between the valve pin and the valve body, a coupler volume is formed, which is connected via the sealing gap and the bore with the valve chamber.
  • the valve chamber is connected via the outlet throttle with the control chamber, the valve chamber is in the injection valve according to the invention under high pressure (rail pressure). This means that the coupling volume is filled with fuel via the holes in the valve body and the sealing gap between the valve pin and valve body, this fuel is also under rail pressure.
  • the sealing gap is dimensioned such that on the one hand there is a fluid connection between the coupling volume and the valve chamber, on the other hand during the short time of valve actuation virtually no fluid exchange between the coupling volume and the valve space can take place, so that the coupling volume practically does not change in this time.
  • the system acts from the holes in the valve body with the sealing gap and the coupling volume as a hydraulic coupler.
  • the coupler is in the idle state of the valve under high pressure, so that a lowered boiling point of the fuel, such as by admixture of low-boiling components, such as bioalcohol, has no negative impact.
  • the time in which the valve is actuated, ie in which the actuator deflects and opens the servo valve, the pressure in the valve chamber drops, is so short that in this time no significant amount of liquid (fuel) from the coupling volume on the sealing gap and the bore in the valve body can get into the valve chamber, so that the high pressure is maintained in the hydraulic coupler itself.
  • pressure equalization across the existing fluid interconnect may occur across the seal gap between the coupler volume and the valve space, allowing length changes in the valve system to be permanently compensated.
  • the actuator has stacked piezoelectric elements (piezo stack) and is preferably in the form of a fully active piezo stack, which is less prone to crack formation in the interior of the piezo stacking sequence since, in contrast to a not fully active stack not only parts of it
  • the covering is over the entire surface and the contacting takes place in the piezo stacking sequence alternately edge side of the stack side of respective piezoelectric layers of electrode material.
  • the layers to be contacted in opposite directions are alternately insulated on the edge side on this contact side.
  • the high-pressure fuel line is preferably connected via a nozzle orifice to the interior of the nozzle body, which serves for better hydraulic control of the injection valve.
  • valve pin and valve body are about 1 micron.
  • a volume of about 0.5 mm 3 has proven to be advantageous. Both dimensions provide a particularly suitable operation of the injection valve.
  • 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 can likewise be realized with the invention, in particular in the case of gasoline injectors.
  • the actuator itself is biased by a wave spring surrounding the actuator to stabilize the piezoelectric actuator and at the same time sealed to protect the piezoelectric stack.
  • Fig. 1 shows the essential part of an injection valve according to the invention, which is located substantially within an injector body 100.
  • a high-pressure fuel line 210 is shown, which is connected in the upper region of the injection valve-not shown here-by means of a high-pressure connection to a high-pressure fuel system-common rail.
  • the actuator 400 surrounded by a wave spring 450 is shown, which is connected to the injector body 100 via its actuator head plate 410.
  • the actuator 400 preferably consists of a piezo stack. However, other materials, such as a magnetostrictive material may also be used.
  • a bottom plate of the actuator 420 Via a bottom plate of the actuator 420, this is connected to a valve body 320 arranged in a valve body 310 and acts directly on this.
  • the high pressure fuel line is also guided through the valve plate 320 and flows there into the throttle plate 290 in the region of the inlet throttle 230 and the nozzle diaphragm 240th
  • the combustion chamber facing part is the actual nozzle module 110, consisting of the nozzle body 120, the nozzle needle 130 and the nozzle spring 140th
  • Fig. 2 shows the area around the throttle plate in more detail. From the top right, the fuel enters the system via the high-pressure fuel line 210 and is guided via the inlet throttle 230 into a control chamber 250. At the same time, fuel is guided past the nozzle orifice 240 into the inner region of the nozzle module 110 on the control chamber 250.
  • the control chamber 250 is in turn connected to an outlet throttle 270, which leads to the valve plate 320. There joins the valve chamber 300, which in Fig. 3 is shown in more detail.
  • valve chamber 300 which is formed in the valve plate 320, connects.
  • valve chamber 300 In the valve chamber 300 is a valve body 320 which is surrounded in its lower part by a valve spring 330 which exerts an upward force on the valve body 310, so that a gap 340 between the valve body 310 and throttle plate 290 is formed and the upper portion of the Valve body 310 seals with the valve plate 320 and thus closes the valve chamber 300 upwards.
  • the valve body 310 has holes 370, which open into a central bore. In this, the valve pin 350 is performed with very little game, which is in communication with the actuator, not shown here.
  • the piezoelectric actuator 400 which is preferably designed as a fully active piezo stack, is integrated into the injector body 100 so that it is supported directly upwards in the injector body 100.
  • the piezoelectric actuator 400 is sealed by a wave spring 450 against the fuel-carrying areas in the injection valve, wherein the wave spring 450 simultaneously provides for the bias of the actuator 400.
  • the wave spring 450 simultaneously provides for the bias of the actuator 400.
  • not the entire actuator space is sealed off from the fuel, but only the area of the actuator 400 itself. This is possible since the use of an Invar sleeve for temperature compensation can be dispensed with.
  • the low pressure volume in the region of the actuator 400 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 400 is transmitted to the servo valve body 310 via the valve pin 350, which is preferably made of hard metal.
  • the valve pin 350 moves with a very small clearance in the bore in the servo valve body 310.
  • the exemplary embodiment can be found at about half the height of the servo valve body 310 has two radial bores 370, which the Valve chamber 300 with the sealing gap 360 between valve pin 350 and servo valve body 310 connect.
  • rail pressure prevails in the valve chamber, which is transmitted through the radial holes 370 in the sealing gap 360.
  • This pressure is then also transferred to the very small coupler volume 380, which is located on the end face of the valve pin 350 facing away from the piezoactuator 400.
  • This pressure causes the pin to be pushed outwards until it comes to rest on the actuator bottom plate. This ensures a play-free contact between the piezoelectric actuator 400 and servo valve. Movements with very low dynamics, such as temperature expansion and wear, can be compensated by changing the Kopplerraum invented. For highly dynamic movements, however, as this is the piezobody movement, the sealing gap is almost dense and thus the coupler is very stiff.
  • the valve body 310 is pressed down, so that the valve opens upwards. This allows fuel to escape upwards, so that the pressure in the valve chamber 300 drops sharply.
  • the servo valve must be kept open only against the valve spring force and a low hydraulic force.
  • the servo valve closes again, by the valve body 310 against the valve plate 320th is pressed and sealed.
  • the pressure in the valve chamber 300 rises again, as well as in the control chamber 250, so that as a result the nozzle needle 130 is pressed down again into its seat.
  • the injection valve is closed.
  • the sealing gap 360 must be selected to be so small that even at high rail pressure only a sufficiently small fuel leakage is possible and at the same time no clamping of the valve pin 350 in the servo valve body 310 takes place.
  • the sealing gap 360 will be smaller than one micrometer, with the coupler volume 380 of 0.5 mm 3 being sufficiently large to realize a very rigid drive.

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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)

Claims (8)

  1. Soupape d'injection pourvue d'une commande de servo-soupape et destinée à injecter du carburant dans la chambre de combustion d'un moteur à combustion interne, la soupape d'injection comprenant un corps d'injecteur (100) muni d'une buse d'injection, laquelle comporte un module de buse (110) pourvu d'un corps de buse (120) et d'une aiguille de buse (130), le module de buse (110) étant disposé dans le côté inférieur, tourné vers la chambre de combustion, du corps d'injecteur (100) et l'aiguille de buse (130) correspondant à un ressort de buse (140) qui est disposé de façon à exercer une force de fermeture sur l'aiguille de buse (130), la soupape d'injection comprenant en outre une conduite à haute pression (210) qui comporte à un endroit un raccord destiné au système de carburant à haute pression et qui est reliée, à un autre endroit, à une chambre de commande (250) par le biais d'un étrangleur d'admission (230), la chambre de commande (250) étant reliée à une chambre de soupape (300) par le biais d'un étrangleur de sortie (270), un corps de soupape (310) étant disposé dans la chambre de soupape (300), le corps de soupape (310) coopérant avec un ressort de soupape (330) de telle sorte que le ressort de soupape (330) repousse le corps de soupape (310) pour l'écarter d'une plaque d'étrangleur (290) de façon à ménager une fente (340) entre le corps de soupape (310) et la plaque d'étrangleur (290), le corps de soupape (310) communiquant en outre avec une tige de soupape (350) qui est reliée quant à elle à un actionneur (400) précontraint par un ressort d'actionneur (450), caractérisée en ce que la tige de soupape (350) est enchâssée avec un très petit jeu dans le corps de soupape (310), et forme une fente d'étanchéité (360) entre la tige de soupape (350) et le corps de soupape (310) et le corps de soupape (310) comporte des trous (370) qui relient la chambre de soupape (300) à l'a fente d'étanchéité (360), et en outre l'extrémité inférieure de la tige de soupape (350) n'est pas complètement reliée au corps de soupape (310) de sorte qu'un volume d'accouplement (380) se forme entre la tige de soupape (350) et le corps de soupape (310), lequel volume d'accouplement est relié à la chambre de soupape (300) par le biais de la fente d'étanchéité (360) et des trous (370), et la fente d'étanchéité (360) permettant d'une part une liaison fluidique entre le volume d'accouplement (380) et la chambre de soupape (300), d'autre part empêchant, pendant le court laps de temps de l'actionnement de la soupape, pratiquement un échange de fluide entre le volume d'accouplement (380) et la chambre de soupape (300) et le volume d'accouplement (380) ne variant pas pendant ce temps.
  2. Soupape d'injection selon la revendication 1, caractérisée en ce que le ressort d'actionneur (450) est conçu comme un ressort ondulé (450) ou un ressort tubulaire ondulé (450).
  3. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce que l'actionneur comprend des éléments piézoélectriques, de préférence sous la forme d'un empilement piézoélectrique entièrement actif.
  4. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce que la conduite de carburant à haute pression (210) est reliée à l'intérieur du corps de buse par le biais d'un obturateur de buse (240) .
  5. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce que la fente d'étanchéité (360) est d'environ 1 µm.
  6. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce que le volume d'accouplement (380) est d'environ 0,5 mm3.
  7. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce que l'aiguille de buse s'ouvre vers l'intérieur.
  8. Soupape d'injection selon l'une des revendications précédentes, caractérisée en ce que l'actionneur (400) est précontraint et en même temps obturé par un ressort ondulé (450) .
EP15778973.6A 2014-10-15 2015-10-13 Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape Active EP3207243B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014220883.1A DE102014220883B4 (de) 2014-10-15 2014-10-15 Piezo-Common Rail Injektor mit ins Servoventil integriertem hydraulischem Spielausgleich
PCT/EP2015/073710 WO2016059069A1 (fr) 2014-10-15 2015-10-13 Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape

Publications (2)

Publication Number Publication Date
EP3207243A1 EP3207243A1 (fr) 2017-08-23
EP3207243B1 true EP3207243B1 (fr) 2018-09-26

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EP15778973.6A Active EP3207243B1 (fr) 2014-10-15 2015-10-13 Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape

Country Status (5)

Country Link
US (1) US10233885B2 (fr)
EP (1) EP3207243B1 (fr)
CN (1) CN106795851B (fr)
DE (1) DE102014220883B4 (fr)
WO (1) WO2016059069A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014220883B4 (de) 2014-10-15 2016-09-22 Continental Automotive Gmbh Piezo-Common Rail Injektor mit ins Servoventil integriertem hydraulischem Spielausgleich
DE102016220071A1 (de) * 2016-10-14 2018-04-19 Continental Automotive Gmbh Servoinjektor mit minimalen Ventilraumvolumen
DE102016220074B4 (de) * 2016-10-14 2023-02-02 Vitesco Technologies GmbH Piezo-Common-Rail-Injektor mit hydraulischem Spielausgleich über Bewegung des Ventilsitzes
JP6926718B2 (ja) * 2017-06-23 2021-08-25 株式会社Ｓｏｋｅｎ 燃料噴射装置
JP6988196B2 (ja) * 2017-06-27 2022-01-05 株式会社Soken 燃料噴射装置
JP7006161B2 (ja) * 2017-11-15 2022-01-24 株式会社Soken 燃料噴射装置
DE102018200288A1 (de) * 2018-01-10 2019-07-11 Continental Automotive Gmbh Piezo-Common-Rail-Injektor mit nach innen öffnendem Servoventil
JP7064363B2 (ja) * 2018-03-29 2022-05-10 株式会社Soken 燃料噴射装置
JP7024567B2 (ja) * 2018-04-06 2022-02-24 株式会社デンソー 燃料噴射弁
CN109184983B (zh) * 2018-07-26 2021-03-30 哈尔滨工程大学 喷油规律可变的蓄压式重油压电喷油器
CN109236531A (zh) * 2018-07-26 2019-01-18 哈尔滨工程大学 喷油规律可变的重油压电喷油器
DE102018126185A1 (de) 2018-10-22 2020-04-23 Schaeffler Technologies AG & Co. KG Werkzeug und Verfahren zur mechanischen Oberflächenbearbeitung

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19708304C2 (de) * 1997-02-28 1999-09-30 Siemens Ag Vorrichtung zur Übertragung einer Bewegung und Einspritzventil mit einer Vorrichtung zur Übertragung einer Bewegung
US6575138B2 (en) * 1999-10-15 2003-06-10 Westport Research Inc. Directly actuated injection valve
US6298829B1 (en) * 1999-10-15 2001-10-09 Westport Research Inc. Directly actuated injection valve
DE10112147A1 (de) * 2001-03-14 2002-09-19 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE102004046191B3 (de) 2004-09-23 2006-04-13 Siemens Ag Servoventil und Einspritzventil
DE102009000170B4 (de) 2009-01-13 2017-11-30 Robert Bosch Gmbh Kraftstoffinjektor
DE102009045556A1 (de) * 2009-10-12 2011-04-14 Robert Bosch Gmbh Injektor
DE102010027278B4 (de) * 2010-07-15 2020-07-02 Metismotion Gmbh Thermisch volumenneutraler Hubübertrager sowie Dosierventil mit einem solchen Hubübertrager und Verwendung des Dosierventils
DE102012212614A1 (de) * 2012-07-18 2014-01-23 Continental Automotive Gmbh Piezoinjektor mit hydraulisch gekoppelter Düsennadelbewegung
DE102013222650A1 (de) 2013-06-10 2014-12-11 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102014220883B4 (de) 2014-10-15 2016-09-22 Continental Automotive Gmbh Piezo-Common Rail Injektor mit ins Servoventil integriertem hydraulischem Spielausgleich

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3207243A1 (fr) 2017-08-23
CN106795851A (zh) 2017-05-31
DE102014220883B4 (de) 2016-09-22
CN106795851B (zh) 2019-06-18
US20170260950A1 (en) 2017-09-14
DE102014220883A1 (de) 2016-04-21
US10233885B2 (en) 2019-03-19
WO2016059069A1 (fr) 2016-04-21

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