WO2018068926A1 - Injecteur asservi comportant une chambre d'injection à volume minimal - Google Patents

Injecteur asservi comportant une chambre d'injection à volume minimal Download PDF

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Publication number
WO2018068926A1
WO2018068926A1 PCT/EP2017/070368 EP2017070368W WO2018068926A1 WO 2018068926 A1 WO2018068926 A1 WO 2018068926A1 EP 2017070368 W EP2017070368 W EP 2017070368W WO 2018068926 A1 WO2018068926 A1 WO 2018068926A1
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WO
WIPO (PCT)
Prior art keywords
valve
chamber
nozzle
transmission pin
valve body
Prior art date
Application number
PCT/EP2017/070368
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 WO2018068926A1 publication Critical patent/WO2018068926A1/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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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 injecting fuel into the combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • injectors are typically used in conjunction with a so-called high pressure common rail system Commitment.
  • a piezo element is often used as an actuator, wherein the control of the injection quantity of such common rail injection valves takes place mainly indirectly via a servo valve. This means that 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 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 Dros ⁇ selplatte.
  • 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 injector In the lower part, that is the area which faces the combustion chamber, the injector has a nozzle body and a due ⁇ nozzle needle, the nozzle needle is biased by a nozzle spring so that it exerts a closing force on the nozzle needle. Since the control chamber is connected to the rail via the high-pressure connection, a high pressure prevails in the control chamber when it is not actuated, which corresponds to the pressure in the rail system (rail pressure).
  • the dynamics of the pressure drop or of the 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.
  • a common rail Inj ector with piezoelectric actuator play-free coupling between the piezoelectric actuator and the valve body of the servo valve is required.
  • a very precise temperature compensation of the thermal length changes in the area of the entire drive chain is required in order to change the idle stroke of the
  • the piezoelectric actuator is usually surrounded by an Invar sleeve, which has a similar thermal expansion behavior as the piezoelectric actuator.
  • Invar sleeve which has a similar thermal expansion behavior as the piezoelectric actuator.
  • too large a set idle stroke is disadvantageous, since thereby the required Piezoaktorhub is increased to the same extent and this in turn increases the necessary drive energy accordingly.
  • Thermally induced changes in length can be largely compensated by a suitable use of different materials.
  • An example is the already mentioned use of actuator housings from Invar, since Invar has a substantially same temperature expansion behavior as the piezoceramic. Ultimately, however, this represents only a basic compensation. Leerhubver shortened as a result of wear or change in the polarization state are not detected.
  • piezo common rail injectors comprising a hydraulic coupler consisting of use a cylinder with a drive piston on the actuator side and an output 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 is usually about 10 bar to ensure. In the prior art, this is achieved with a pressure-holding valve.
  • Object of the present invention is therefore to avoid the above-mentioned problems of injection valves according to the prior art and to provide an injection valve with Servovalve control available, which decoupled the actuator sufficiently from the nozzle needle on the one hand, 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. n
  • the invention provides an injection valve with Servoventil- control for injecting fuel into the combustion chamber of an internal combustion engine
  • the Einsprtizventil having an injector body with an injection nozzle, which in turn includes a nozzle module with a nozzle body and a nozzle needle, the nozzle module on 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.
  • Injection valve in the input is a aktornahe intermediate plate and is arranged in ⁇ nozzle direction immediately adjacent valve plate.
  • the injection valve is also connected to a
  • High-pressure line connected 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 connected via a fluid passage with a valve chamber, which is formed in the valve plate.
  • a nozzle orifice is present, which can support the closing of the nozzle needle hydraulically.
  • a valve body In the valve chamber, a valve body is arranged, which is in communication with a transmission pin, which in turn is connected to a biased by a wave spring actuator.
  • the transmission pin is now fitted with little play in the valve body, so that a sealing gap is formed between the transmission pin and the valve body.
  • the valve body has holes which connect the valve space with the sealing gap.
  • a coupling space is formed, which is connected via the sealing gap and the bore with the valve chamber.
  • the sealing gap is so small that, on the one hand, a flow idtim between the coupling space and the valve chamber, on the other hand, during the short time the valve actuation virtually no fluid exchange between the coupling space and the valve space can take place, so that the coupling space does not change in this time.
  • a valve seat between the valve body and the intermediate plate is provided and the transfer pin is formed a discharge throttle, which is in the connection with Boh ⁇ ments in the transfer pin, which connect the outlet throttle with the valve seat.
  • the system acts from the holes in the valve body with the sealing gap and the coupling volume as a hydraulic coupler.
  • the integrated in the transmission spinning outlet throttle is a very small volume of the valve seat of the servo valve reali ⁇ Sieren, which offers advantages in terms of representation of small hydraulic spray distances in multiple injections can.
  • 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, whereby the pressure in Ven ⁇ tilraum drops, is so short that in this time no appreciable amount of liquid (fuel) from the coupling volume over the sealing gap and the holes in the valve body can get into the valve chamber, so that even the high pressure is maintained in the hydraulic coupler.
  • pressure equalization across the existing fluid connection can occur across the sealing gap between the coupler volume and the valve space, so that length changes in the valve system can be permanently compensated.
  • the outlet throttle connects the valve chamber with a low pressure area in Area of the actuator when the valve body lifts off the valve seat.
  • valve seat between the valve body and the intermediate plate is formed as a flat seat. In this way, the seat can be inexpensively manufactured together with the production of the high-pressure sealing surface.
  • the transmission pin is guided in the intermediate plate with a small mating game.
  • the volume flow in the gap is very small in relation to the volume flow through the outlet throttle and thus the disturbing influence is negligibly small.
  • the transmission pin is made of hard metal. In this way, a very high rigidity of the transmission pin can be achieved.
  • a valve spring is arranged in the valve chamber, which acts on the valve body in the direction of the intermediate plate. This ensures that the servo valve is also under no pressure, safe ge ⁇ closed.
  • the spring force can be very small, since during operation of the injector, the essential closing force for the servo valve results from the pressure in the control chamber.
  • the actuator has stacked piezo elements (piezostacks) and is designed as a fully active piezo stack, which is generally less susceptible to cracking inside the piezo stack sequence, since, in contrast to a non-fully active stack, not only parts of its
  • the piezoelectric layers are covered by electrical material, but the cover is 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 differently in each case are alternately insulated on the edge side on this contact side.
  • the high pressure 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 ym.
  • a volume of about 0.5 mm 3 has proved to be advantageous. Both dimensions provide a particularly suitable operation of the injection valve.
  • the nozzle needle of the injection valve preferably opens inwards, especially 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 be re ⁇ al instrument as well, in particular in petrol injectors.
  • the actuator may be biased by a wave spring surrounding the actuator to stabilize and at the same time seal the piezoactuator to protect the piezoelectric stack.
  • Figure 1 is a sectional view of an inline piezo common rail injection valve
  • FIG. 2 shows a sectional view of an upper part of an injection valve
  • FIG. 3 shows a sectional view through the hydraulically relevant components of the injection valve according to the invention
  • FIG. 1 shows the essential part of an injection valve 10 and FIG. 2 shows a sectional view of the upper part of the injection valve 10.
  • the injection valve 10 has an injector body 20.
  • a high-pressure line 30 is formed in the upper region of the injection valve 10 by means of a high-pressure port 40 ( Figure 2) to a high-pressure fuel ⁇ material system - is connected - common rail.
  • Figure 2 On the
  • High-pressure port 40 a pressurized fuel is supplied to the high-pressure line 30.
  • the high-pressure line 30 extends essentially in the longitudinal direction through the injector body 20 through an intermediate plate 50 and a valve plate 60 as far as a high-pressure region 70, which can be seen in detail in FIG.
  • an actuator 90 surrounded by a wave spring 80 is arranged, which is connected to the injector body 20 via an actuator head plate 100.
  • the actuator 90 preferably consists of a piezo stack. However, other materials, especially magnetostrictive material, may also be used.
  • a transfer pin 120 brought into contact, which is guided in the intermediate plate 50, and acts directly on this.
  • the high pressure line 30 also extends through the interim ⁇ rule plate 50 and then flows into the valve plate 60 in the region of an inlet throttle 130 and a nozzle orifice 140.
  • the hydraulically relevant components of the intermediate plate 50 and the valve plate 60 described above are not shown in Figure 1, Figure 3 shows these in a detailed representation as section A of Figure 1.
  • a nozzle module 150 which is composed of a nozzle body 160, a nozzle needle 170 and a nozzle spring 180.
  • FIG. 3 shows the area of the intermediate plate 50 and the Ven ⁇ tilplatte 60 and the hydraulic-related components in greater detail.
  • the fuel enters the system and passes through the inlet throttle 130 in a control chamber 190. In parallel, fuel passes through the
  • the control chamber 190 is in turn connected to a fluid passage 200, which is formed in the valve plate 60.
  • the fluid passage 200 opens into a valve space 210 in the valve plate 60.
  • a valve body 220 of a servo valve which is acted upon in its lower portion by a valve spring (not shown), which exerts an upward force on the valve body 220 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 10, the essential closing force for the Servo valve from the pressure in the control chamber 190 and the valve chamber 210 results.
  • the valve body 220 has bores 230, which open into a central bore 240 in the valve body 220.
  • the transmission pin 120 is performed with very little game, which is in communication with the actuator 90 via the Aktorêtplatte 110.
  • leerhubbehaftete mechanical coupling between the Piezoaktorhub and the servo valve movement is replaced by a hydrau ⁇ lische coupling with a self-integrated in the servo valve body clearance compensation.
  • a central bore 270 is provided in the transmission pin 120, via which the central bore 270 establishes a hydraulic connection between a valve seat 290 of the valve body 220 and an outlet throttle 300.
  • the outlet throttle 300 is formed in the region of the transmission pin 120 facing the actuator 90 such that it forms a fluid connection between the central bore 270 in the transmission pin 120 and a low-pressure region 310.
  • a Zualufbohrung 330 is formed in the transmission pin 120, which is introduced radially into the transmission pin 120 and in the region of
  • Vetntilsitzes 290 is provided in the transfer pin 120. Via the inlet bore 330, the hydraulic connection between the valve seat 290 and the outlet throttle 300 via the central bore 270 in the transfer pin 120.
  • the valve body 220 forms with its end facing the actuator end of the valve seat 290 with the intermediate plate 50.
  • the transmission formed in the spin 120 outlet throttle 300 opens out in the region of the aktornahen Kochtra ⁇ supply 120 spins in the low pressure region 310th
  • the piezoactuator 90 which is preferably designed as a fully active piezostack, is integrated into the injector body 20 in such a way that it is supported upwards directly in the injector body 20.
  • the piezoelectric actuator 90 is furnished ⁇ seals by the wave spring 80 against the fuel-carrying areas in the injection valve 10, wherein the wave spring 80 simultaneously provides for the pre ⁇ voltage of the actuator 90.
  • the entire actuator space is sealed off from the fuel, but only the area of the actuator 90 itself. This is possible because it is possible to dispense with the use of an Invar sleeve for temperature compensation.
  • the low-pressure volume in the region of the actuator 90 increases by at least one 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 piezoactuator 90 is transmitted to the servo valve body 220 by means of the transmission pin 120, which is fitted with a very small clearance in the central bore 240 in the servo valve body.
  • the Servoventil stresses 220 are the two radial holes 230 which connect the valve space 210 and with this the control chamber 190 with the sealing gap 250 between the transmission pin 120 and the valve body 220.
  • In the closed state of the servo valve prevails in the valve chamber 210 and the control chamber 190 rail pressure, which is transmitted through the radial holes 230 in the sealing gap 250. This pressure is in the very small coupling space 260 transferred, which is located on the, the piezoelectric actuator 90 facing away from the end face of the transmission pin 120.
  • This pressure causes the transmission pin 120 is always pressed to the outside until it comes to rest on the Akorborêtplatte 110. This ensures a play-free contact between the piezoelectric actuator 90 and the servo valve. Movements with very low dynamics such as temperature expansion and wear can be compensated by changing the coupling space height 320.
  • the sealing gap 250 is almost dense and thus the coupler is very stiff.
  • valve body 220 When the piezoactuator 90 is actuated, the valve body 220 is pushed down via the transmission pin 120, so that the valve seat 290 opens between the valve body 220 and the intermediate plate. Via the inlet bore 330, the central bore 240 and the outlet throttle 300, the fuel escapes upward, so that the pressure in the valve chamber 210 drops. Thus, the servo valve must be kept open only against the valve spring force and a low hydraulic force.
  • Supply throttle 130 flows less fuel than flows through the outlet throttle 300, the pressure in the valve chamber 210 and in the control chamber 190 decreases. This reduces the force acting on the nozzle needle 170 hydraulic closing force in the control chamber 190. After falling below a certain threshold pressure opens the nozzle needle 150 and the injection begins.
  • the servo valve closes again, by the valve body 220 against the intermediate plate 50th is pressed and the valve seat 290 closes and seals.
  • the pressure in the valve chamber 210 increases again, as does the pressure in the control chamber 190, so that as a result the nozzle needle 150 is pressed down again into its seat.
  • the injection valve is closed.
  • the gap must the sealant 250 so small that even with a high rail pressure only a sufficiently small fuel leakage is possible and at the same time is also no jamming of Kochtra ⁇ supply spins 120 in the valve body 220th
  • the sealing gap 250 is chosen smaller than 1 ⁇ , wherein the volume in the Kopperlraum 260 with 0.5 mm 3 is sufficiently large to realize a very rigid drive.
  • Transfer pin 120 integrated drain throttle replaced.
  • the compensation of changes in length due to temperature effects, wear at contact points in the drive is improved, as well as the compensation of changes in length of the piezoelectric actuator itself, for example as a result of changes in Polari ⁇ sations tenues.
  • the reduction of the pressure pulses in the actuator chamber and thus the reduction of the parasitic effects on the sensor signal of the piezoelectric actuator are achieved inter alia by the enlargement of the low-pressure region.
  • Electrical contacts in the upper part of the injection valve vibrations can be reduced if the piezo head plate in the injector body stiff. Through this coupling, which also works for lighter boiling fuels, eliminates the costly adjustment process for the idle stroke in injector assembly.
  • the cavitation in the dive horrbe ⁇ congested area to be eliminated, thus improving the high pressure capability.
  • the volume downstream of the servo valve can be minimized and associated with it, the achievable minimum spray intervals can be reduced with multiple injection.
  • the manufacturing costs are reduced.
  • the drive energy for the piezoelectric actuator is reduced because the idle stroke is eliminated.
  • the increased Ge ⁇ accuracy the injection quantities variations depending on the Verpratzungskraft can be reduced in the cylinder head and the injection amount stability are ver ⁇ corrected in the dynamic engine operation.
  • the control chamber pressure can be fed back to the piezoelectric actuator to derive sensor signals, which are used to control the injection quantities. Due to the increased accuracy of the injection quantity variations can be reduced depending on the Verpratzungskraft in the cylinder head and the injection quantity stability can be improved in dynamic engine operation.

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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

Injecteur à mécanisme de commande asservi, comprenant un corps d'injecteur (20) pourvu d'une buse d'injection qui comporte un module de buse (150) comprenant un corps de buse (160) et une aiguille d'injection (150), l'aiguille d'injection (150) coïncidant avec un ressort de buse (180); une platine intermédiaire (50) et une platine à soupape (60), une conduite haute pression (30) et une chambre d'injection (190) à laquelle la conduite haute pression (30) est reliée par l'intermédiaire d'une restriction d'entrée (130). La chambre de commande (190) est reliée à une chambre d'injection (210) par un passage de fluide (200) dans lequel est agencé un corps de soupape (220) relié à une tige de transmission (120) laquelle est reliée à un actionneur (90) précontraint par une rondelle ondulée (80). La tige de transmission (120) est ajustée avec un faible jeu dans le corps de soupape (220) de manière qu'un espace interfacial d'étanchéité (250) est formé entre elle et le corps de soupape (220). Le corps de soupape présente des alésages (230) qui relient la chambre d'injection (210) à l'espace interfacial d'étanchéité (250). Une chambre de couplage (260) est formée entre la tige de transmission (120) et le corps de soupape (220), ladite chambre de couplage (260) étant reliée à la chambre d'injection (210) par l'espace interfacial d'étanchéité (250) et par les alésages (230). L'espace interfacial d'étanchéité (250) est dimensionné de telle manière qu'une communication fluidique subsiste entre la chambre de couplage (260) et la chambre d'injection (210), mais que pendant la durée d'actionnement de la soupape, aucun échange de fluide n'a lieu entre l'espace de couplage (260) et la chambre d'injection (210). Un siège de soupape (290) est disposé entre le corps de soupape (220) et la platine intermédiaire (50) et une restriction de sortie (300) est formée dans la tige de transmission (120), et est raccordée à des alésages (280) de la tige de transmission (120) qui relient le restricteur de sortie (300) au siège de soupape (290).
PCT/EP2017/070368 2016-10-14 2017-08-10 Injecteur asservi comportant une chambre d'injection à volume minimal WO2018068926A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016220071.2A DE102016220071A1 (de) 2016-10-14 2016-10-14 Servoinjektor mit minimalen Ventilraumvolumen
DE102016220071.2 2016-10-14

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Publication Number Publication Date
WO2018068926A1 true WO2018068926A1 (fr) 2018-04-19

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Citations (5)

* 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
EP2541035A1 (fr) * 2011-06-30 2013-01-02 Robert Bosch Gmbh Injecteur de carburant
EP2813698A1 (fr) * 2013-06-10 2014-12-17 Robert Bosch Gmbh Soupape d'injection de combustible
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

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007042466B3 (de) * 2007-09-06 2009-04-09 Continental Automotive Gmbh Einspritzsystem mit reduzierter Schaltleckage und Verfahren zum Herstellen eines Einspritzsystems

Patent Citations (5)

* 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
EP2541035A1 (fr) * 2011-06-30 2013-01-02 Robert Bosch Gmbh Injecteur de carburant
EP2813698A1 (fr) * 2013-06-10 2014-12-17 Robert Bosch Gmbh Soupape d'injection de combustible
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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