EP2961977B1 - Dispositif pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion - Google Patents

Dispositif pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion Download PDF

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Publication number
EP2961977B1
EP2961977B1 EP14708195.4A EP14708195A EP2961977B1 EP 2961977 B1 EP2961977 B1 EP 2961977B1 EP 14708195 A EP14708195 A EP 14708195A EP 2961977 B1 EP2961977 B1 EP 2961977B1
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EP
European Patent Office
Prior art keywords
valve
housing
fuel
pressure
sealing surface
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Active
Application number
EP14708195.4A
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German (de)
English (en)
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EP2961977A1 (fr
Inventor
Marco Ganser
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Ganser Hydromag AG
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Ganser Hydromag AG
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Publication of EP2961977A1 publication Critical patent/EP2961977A1/fr
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    • 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
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/004—Joints; Sealings
    • F02M55/005—Joints; Sealings for high pressure conduits, e.g. connected to pump outlet or to injector inlet
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/008—Arrangement of fuel passages inside of injectors
    • 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
    • F02M61/165—Filtering elements specially adapted in fuel inlets to injector
    • 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
    • F02M67/00—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type
    • F02M67/10—Injectors peculiar thereto, e.g. valve less type
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the present invention relates to a device for the intermittent injection of high-pressure fuel into the combustion chamber of an internal combustion engine according to claim 1.
  • a device with injectors for injecting fuel into the combustion chamber of an internal combustion engine is in the earlier international application WO 2013/117311 A disclosed.
  • the injection valves of the device have a valve housing with a connection body, a memory body adjoining this with a discrete storage chamber, an intermediate body adjoining this, in which an electrically actuated actuator arrangement is accommodated, and a valve body adjoining the intermediate body.
  • the valve body carries at its free end a nozzle body with an injection valve seat and nozzle openings for injecting the fuel into the combustion chamber of the internal combustion engine.
  • With the injection valve seat a needle-shaped injection valve member cooperates, which is formed on the side facing away from the injector seat piston-shaped.
  • a closing spring is supported, which acts on the injection valve member with a directed in the direction of the injection valve seat closing force.
  • the closing spring is supported on a guide sleeve of a hydraulic control device.
  • the piston and the guide sleeve limit a control space which is connected to a pilot valve operated by means of the actuator.
  • the pilot valve is opened, so that fuel can flow out of the control chamber and thereby the injection valve member is lifted against the force of the closing spring from the injector seat.
  • the pilot valve is closed by means of the actuator assembly, after which the control chamber is refilled with fuel, and the injection valve member comes to rest on the injection valve seat.
  • connection body On the connection body there are two identically formed high-pressure connections connected to one another in terms of flow, one of which serves to be connected to a supply line for supplying the injection valve with fuel.
  • a connecting line can be connected to the other high-pressure connection in order to supply fuel to another injection valve.
  • the storage body has a larger diameter bore to form the discrete storage chamber.
  • the blind bore has a larger diameter to form a shoulder for supporting a valve carrier of a check valve.
  • the check valve seat is formed on the connection body, and with it a platelet-shaped check valve body cooperates, which has a continuous throttle bore in the center.
  • the non-return valve body is acted upon by means of a closing spring designed as a compression spring, which is supported on the other end of the valve carrier, with a directed in the closed position of the check valve closing force.
  • valve carrier Centrally through the valve carrier passes through a passage, and the valve carrier closes the storage chamber in the axial direction from the connection body out.
  • the check valve forming a throttle device allows the flow of fuel from the high pressure ports into the storage chamber at least approximately unhindered and throttles the flow in the opposite direction.
  • the valve carrier carries a cup-shaped hole filter, which protrudes from the valve carrier into the interior of the storage chamber and in which the passage opens through the valve carrier.
  • Another device for the intermittent injection of high-pressure fuel into the combustion chamber of an internal combustion engine is from the document WO 2007/009279 A known.
  • Each injection valve of this device is associated with a discrete storage chamber, wherein between the feed line and the storage chamber, a check valve with parallel throttle acts. If a plurality of such fuel injection valves or a plurality of injection valves, as disclosed in the above-mentioned CH and WO patent application, connected to each other and to a high-pressure fuel pump, the throttling action of the check valve is designed such that each fuel injection valve during an injection process high-pressure fuel from the discrete storage chambers other fuel injectors, from the high-pressure fuel lines and from the high-pressure fuel pump feeds.
  • This functionality is in the document WO 2007/009279 A in detail and also in the document WO 2009/033304 A described.
  • devices for injecting fuel into the combustion chamber of internal combustion engines are known from the documents EP 2 188 516 B1 and CH 702 496 B1 known.
  • the apparatus comprises a fuel injector, preferably a plurality of identically formed fuel injectors, having a housing with a high pressure inlet, a recess, and a high pressure chamber connected to the high pressure inlet.
  • the recess forms at least a part of the high-pressure chamber.
  • the fuel injection valve is associated with a valve carrier having a fuel passage and a check valve. Vorzugseise the check valve is arranged in the valve carrier.
  • a feed line for supplying fuel to the fuel injection valve is tensioned by means of a fastening element in the direction of the high-pressure inlet and fluidly connected thereto.
  • the high-pressure inlet has a conical sealing surface that widens from the interior of the housing in the direction toward the outside. This forms, in other words, an inner cone.
  • the valve carrier has, on an outer circumferential surface, a conical outer sealing surface, which bears sealingly against the conical sealing surface of the high-pressure inlet. The fastener presses the feed line to the valve carrier, and this to the high pressure inlet.
  • the valve carrier preferably further has an inner cone on an input-side front side, which also forms a sealing surface.
  • the feed line In its end region facing the fuel valve, the feed line has an outer cone forming a sealing surface, which sealingly bears against the inner cone of the valve carrier.
  • valve carrier is held quasi clamped between the feed line and the housing.
  • the high-pressure sealing concerns on the one hand of the valve carrier on the housing and on the other hand, the feed line on the valve carrier is achieved in that the fastener, such as a union nut, the supply line tensioned in the direction against the high pressure inlet.
  • valve carrier it may be advantageous to fix the valve carrier to the housing.
  • this fixation need not - but can - apply such a force that the valve carrier sealingly abuts the conical sealing surface of the high pressure inlet.
  • the valve carrier has a funnel-shaped end flange on which both the conical outer sealing surface and the inner cone are formed.
  • the conical sealing surface of the high pressure inlet on the housing itself - as a portion of the recess - formed leads to a particularly simple and space-saving embodiment.
  • valve carrier is formed together with the check valve and attached to the valve carrier, preferably a further fuel passage having retaining element as a cartridge-like, self-contained unit.
  • This preassembled unit can then as such in the recess or the high-pressure chamber of the housing Fuel injector are used, or is used as such.
  • the assembly comprises a filter for the fuel, which is preferably carried by the holding member and secured thereto.
  • the assembly of the valve carrier, the check valve, the holding element and the filter is formed.
  • the filter has a cup-like filter body, with the further fuel passage opening into the cavity defined by the filter body.
  • the filter body is provided with a large number, for example at least 2,000, microholes.
  • an annular check valve seat is formed on the valve carrier, which cooperates with a check valve member which is arranged between the valve carrier and the holding element.
  • the check valve member is formed as a valve plate, and this is preferably provided centrally with a throttle passage. This is even with closed check valve with the fuel passage and thus the feed line fluidly connected.
  • a compression spring which acts on the valve plate with a force acting in the closed position force.
  • this is low and only ensures that when pressure equalization, the valve plate rests against the check valve seat.
  • the valve plate has at least one in the direction of radially outwardly open and continuous in the direction of the longitudinal axis breakthrough - preferably three (or more) circumferentially distributed such breakthroughs - on. This allows a low-resistance, unthrottled flow through the fuel between the valve plate located in the open position and the surrounding valve carrier or holding element.
  • the breakthrough is located or the openings are located radially outside the check valve seat.
  • the retaining element preferably has, in its end region facing the valve plate, at least one groove open in the direction of the valve plate and extending in the radial direction, preferably three such grooves (or more) distributed in the circumferential direction. This allows, with open check valve, as low as possible flow of the fuel.
  • the high-pressure chamber of the injection valve has a discrete storage chamber for storing fuel.
  • a discrete storage chamber for storing fuel.
  • the above-mentioned structural unit in particular with the filter, projects into the discrete storage chamber.
  • the housing of the fuel injection valve carries a nozzle body, which is connected to the high-pressure chamber and on which an injection valve is formed. With the latter acts in the direction of the longitudinal axis adjustable arranged injection valve member together.
  • A preferably designed as a compression spring, closing spring is supported on the injection valve member and acts upon this with a directed in the direction against the injection valve seat closing force.
  • a hydraulically controlled control device is provided in the housing to lift the injection valve member against the closing force of the compression spring from the injection valve seat for injecting fuel.
  • the hydraulic control device is controlled by means of a likewise arranged in the housing, electrically controlled actuator in a known manner.
  • the actuator and the hydraulic control device can be designed in any manner, in particular such as, for example, in the above-mentioned CH patent application no. 2012 0174/12 , in the pamphlets WO 2007/009279 . WO 2010/088781 A1 . WO 2008/046238 A . WO 2006/108309 A . WO 2006/058444 A . WO 2005/080785 A . WO 2005/019637 A . WO 2005/003550 A or WO 2004/099603 A disclosed.
  • the housing has on the one hand a valve housing, which carries the nozzle body and in which the injection valve member, the closing spring, the actuator and the control device are arranged, and on which a conical pressing surface, which serves as a sealing surface is formed. From this sealing surface runs in the valve housing, the high-pressure chamber for the fuel.
  • the housing has a discharge nozzle, at the nozzle housing of which the high-pressure inlet is formed and whose longitudinal axis extends transversely, preferably at right angles to the longitudinal axis of the valve housing.
  • the pressure port has, in an end region facing away from the high-pressure inlet, a conical counter-contact surface, which likewise forms a sealing surface.
  • valve carrier with its conical outer sealing surface bears against the conical sealing surface, which is preferably integrally formed on the pressure nozzle housing.
  • the outer cone of the feed line preferably abuts against the inner cone of the valve carrier, and the feed line by means of the fastener is in the direction towards the high pressure inlet, i. clamped against the nozzle housing.
  • the housing or the nozzle housing has a high-pressure inlet which is arranged next to the high-pressure inlet and which is flow-connected to the high-pressure inlet, preferably without throttling and in order to supply a further injection valve with fuel via a high-pressure connection line connected to the high-pressure outlet.
  • a high-pressure inlet which is arranged next to the high-pressure inlet and which is flow-connected to the high-pressure inlet, preferably without throttling and in order to supply a further injection valve with fuel via a high-pressure connection line connected to the high-pressure outlet.
  • the high-pressure outlet preferably has an inner cone molded onto the housing or connecting piece housing, against which the outer cone of the connecting line rests sealingly.
  • valve carrier between the inner cone and the check valve on a radial outlet from the fuel passage, which is flow-connected via a connecting line in the housing or nozzle housing with the high pressure outlet.
  • the supply line is connected to the connecting line low-resistance free throttling.
  • valve carrier seen in the flow direction of the fuel in the injection valve, downstream of the radial outlet with the housing or nozzle housing defines a narrow gap.
  • the high-pressure chamber or the discrete storage chamber is separated from the connecting line hydraulically, at least for transient processes.
  • FIGS. 1 to 3 show a fuel injection valve 10 for the intermittent injection of fuel under high pressure into the combustion chamber 12 of an internal combustion engine 14 and connected to the fuel injection valve 10 feed line 16 of a first embodiment of the inventive device.
  • this device may have a plurality of fuel injection valves 10 with feed lines 16 associated therewith.
  • the fuel injector 10 includes a housing 18 having a storage body 20 on which is integral, i. in one piece, a connection section 22 and storage section 24 are formed.
  • the housing 18 has an intermediate body 26, which on the connecting portion 22, in the direction seen a longitudinal axis 28 of the fuel injection valve 10, the opposite side abuts the storage section 24.
  • the housing 18 carries a nozzle body 30, which abuts against the storage body 20 side facing away from the intermediate body 26 and is secured by means of a union nut 32 on the housing 18.
  • the intermediate body 26 is disposed inside the union nut 32, and this is screwed to the storage body 22 such that the nozzle body 30 sealingly abut the intermediate body 26 and the latter on the storage body 20.
  • a high-pressure inlet 34 is formed in the connection portion 22 on the housing 18, and this is connected to a high-pressure chamber 36 of the fuel injection valve 10.
  • This high-pressure chamber 36 has a discrete storage chamber 38 in the storage body 20.
  • the design and operation of such a storage chamber 38 is from the document WO 2007/009279 A known, the disclosure of which is incorporated by reference in this specification.
  • connection-side end face of the storage body 20 From the connection-side end face of the storage body 20 extends in this one to the longitudinal axis 28 rotationally symmetrical, in the direction of the longitudinal axis 28 long, blind hole, the discrete storage chamber 38 limiting recess 40, from the bottom of a longitudinal axis 28 obliquely extending duct section 42 to the intermediate body 26, for the supply of fuel to the nozzle body 30, runs.
  • the recess 40 is in the connection portion 22, seen in the direction of the longitudinal axis 28 against the free end of the storage body 20 out, widening, so that a conical sealing surface 44 (see Fig. 2 ) of the high pressure inlet 34 is formed.
  • the opening angle ⁇ (see Figure 3 ) of this conical sealing surface 44 has approximately 60 ° in the exemplary embodiment shown.
  • the conical sealing surface 44 forms an inner cone on the storage body 20 and thus on the housing 18th
  • the fuel injection valve 18 has a valve carrier 46 and a non-return valve 48 arranged therein.
  • a holding element 50 is fixed, which in turn carries a filter 52 for the fuel, which is formed in the present case as a cup-shaped filter body 52 'with microholes 54.
  • a filter 52 for the fuel which is formed in the present case as a cup-shaped filter body 52 'with microholes 54.
  • the filter 52 may also be formed as a rod filter 53, as in the Fig. 10 to 13 shown and described below.
  • valve carrier 46 is formed together with the check valve 48, holding member 50 and filter 52 as a cartridge-like, self-contained unit 56, similar to those in Fig. 9 is shown.
  • the assembly 56 is inserted as such in the discrete storage chamber 38 limiting recess 40 and thus in the high-pressure chamber 36.
  • valve carrier 46 has on its outer lateral surface 58 a conical outer sealing surface 60, which in the embodiment shown on a Input side, funnel-shaped end flange 62 of the valve carrier 46 is formed.
  • the valve carrier 46 lies with its outer sealing surface 60, which forms an outer cone, on the sealing surface 44 sealingly, wherein the angle ß of the conical outer sealing surface 60 is formed smaller than the angle ⁇ , preferably this cone angle difference is 0.5 ° to 2 °.
  • valve carrier 46 on an input side end face 66 on a sealing surface forming inner cone 68, which is also formed in the illustrated embodiment, the end flange 62.
  • the opening angle of this inner cone 68 is again about 60 °.
  • the feed power 16 is double-walled for monitoring any possible leakage of fuel, as is frequently required, in particular for marine applications.
  • An inner tube 70 is designed to guide the under very high pressure fuel. It has in its two end regions depending on a sealing surface forming outer cone 72, which tapers towards the end of the inner tube 70.
  • the angle of the outer cone 72 of the Inner tube 70 formed smaller than the angle of the inner cone 68 of the valve carrier 46, preferably by a cone angle difference of 0.5 ° to 2 °, in turn to form a ring sealing surface at the smallest diameter of the contact surface of the cone.
  • the feed line 16 is fastened to the storage body 20 by means of a fastening element 74 'designed as a fastening element 74, and in particular so that the inner tube 70 is stretched in the direction against the fuel injection valve 10.
  • the inner tube 70 bears with its outer cone 72 on the inner cone 68 of the valve carrier 46, and with its outer sealing surface 60 sealingly against the sealing surface 44 of the fuel injection valve 10.
  • the valve carrier 46 and thus the assembly 56 is thus kept clamped directly between the housing 18 of the fuel injection valve 10 and the feed line 16.
  • valve carrier 46 has a fuel passage 76, which leads from the outer cone 72 centric to the longitudinal axis 28 in a check valve chamber 78. This is bounded on the one hand by the valve carrier 46 and on the other hand by the holding element 50, which is threaded from the inner cone 68 facing away from the end face of the valve carrier 46 forth in this.
  • valve carrier 46 At the mouth of the fuel passage 76 into the check valve space 78, a flat, annular check valve seat 80 is formed on the valve carrier 46, which surrounds the mouth of the fuel passage 76. Further In the embodiment shown, the valve carrier 46 has a circumferential undercut 82 which surrounds the check valve seat 80.
  • the check valve 48 has a check valve member 84 (see Fig. 4 ), which is arranged in the check valve chamber 78 and in the embodiment shown as a valve plate 84 'is formed.
  • a check valve member 84 see Fig. 4
  • the check valve member 84 or the valve plate 84 ' is sealingly against the check valve seat 80.
  • the check valve member 84 is provided with a throttle passage 86, which is formed in the embodiment shown as a central through hole through the valve plate 84 '.
  • a throttle passage 86 By means of this restrictor passage 86, the high-pressure chamber 36 or the discrete storage chamber 38 is also flow-connected to the high-pressure inlet 34 (throttled) even when the check valve 48 is closed.
  • a compression spring 88 On the side facing away from the fuel passage 76 of the check valve member 84 is supported on this a compression spring 88 from one end, which is supported at its other end on the support member 50.
  • the compression spring 88 acts as a closing spring for the check valve 48 and ensures that the check valve member 84 rests against the check valve seat 80 when the compensation pressure.
  • the holding element 50 has centric to the longitudinal axis 28 to a further fuel passage 90, which leads from the check valve chamber 78 to the free end of the retaining element 50.
  • the cross section of this further Fuel passage 90 is equal to or greater than the cross section of the fuel passage 76.
  • the further fuel passage 90 has a step-like widening, into which the pressure spring 88 engages, and at whose step the compression spring 88 is supported on this side.
  • the check valve-side end of the holding member 50 is spaced from the check valve seat 80 so that the holding member 50 for the valve plate 84 'in the open position forms a stop and while the non-return valve seat 80 and valve plate 84' limited flow cross section is at least as large, preferably larger than the cross section of the fuel passage 76.
  • valve plate 84 'in the illustrated embodiment 3 - see also Fig. 4 - Distributed uniformly in the circumferential direction and in the direction of radially outwardly open, in the direction of the longitudinal axis 28 through openings 92. Between the openings 92 of the radially outer edge of the valve plate 84 'to the longitudinal axis 28 is circular. It is thus a sufficiently large passage between the valve plate 84 'and the wall of the holding member 50, regardless of the rotational position and the lateral position of the valve plate 84' created.
  • FIG. 4 has the holding element 50 in a subsequent to the thread 94, the check valve chamber 78 facing End region to a reduced outer diameter, to form between it and the wall of the support member 50 has a sufficiently large annular fluid space.
  • the holding element 50 in this area three, distributed in the circumferential direction, in the radial direction continuous and in the direction of the valve plate 84 'open grooves 96.
  • the holding element 50 is formed between the thread 94, with which it is threaded into a corresponding internal thread of the valve carrier 46, and a free end portion as a polygonal, in particular hexagon, by means of a tool, the holding member 50 on the valve carrier 46 to be able to tighten.
  • a step 98 between the thread 94 and the polygon serves as a stop on the valve carrier 46 and determines the mutual axial position in the mounted state.
  • the filter 52 On the cylindrical free end portion of the holding member 50, the filter 52 is placed. This has a cup-shaped filter body 52 'with the microholes 54 on. Preferably, the filter body 52 'is welded to the holding element 50.
  • the valve carrier 46 then has radially outward to the end flange 62 to the holding element 50 facing the end of a circular cylindrical shape, with approximately in the middle of a step.
  • the outer diameter in the section adjacent to the end flange 62 up to the step is smaller than in FIG. seen in the direction of the interior of the fuel injection valve 10, the stage following section, a guide portion 100.
  • a narrow gap 102 is present between this and the housing 18 and the storage body 20, a narrow gap 102 is present.
  • the guide portion 100 facilitates during assembly the insertion of the assembly 56 in the high pressure chamber 36 and the recess 40 and the storage chamber 38 and aligns the unit.
  • the guide section 100 could also be dispensed with here.
  • the fuel injection valve 10 is held by means of a claw 106 in a known manner to the cylinder head of the internal combustion engine 14.
  • an electrical connection 108 is arranged, from which by the storage chamber 38 bounding wall parallel to the longitudinal axis 28, a channel 110 extends to the intermediate body 26 facing end side. From the electrical connection 108, a control line 112 is guided through the channel 110, which carries connection contacts 114 at the other end.
  • the storage body 20 on this side has an opening, which is open toward the intermediate body 26, in the form of a center hole-like recess, in which a compression spring 116 is arranged. This serves the holding of an electrically controlled, connected to the terminal contacts 114 actuator assembly 118 which is received in a corresponding recess in the intermediate body 26.
  • actuator assemblies 118 are well known, and in the present case, they are configured as in FIG FIG. 5 of the document WO 2008/046238 A shown and described in detail. With regard to structure and operation, reference is expressly made to this document. However, differently configured actuator arrangements can be used.
  • a further duct section 42 ' which is fluidly connected to the duct section 42 and on the other hand opens into the limited part of the nozzle body 30 of the high-pressure chamber 36.
  • a needle-like trained injection valve member 120 is slidably disposed in the direction of the longitudinal axis 28, which cooperates with an integrally formed on the nozzle body 30 in a known manner injection valve seat 122.
  • the injection valve member 120 In the idle state, the injection valve member 120 abuts against the injection valve seat 122 and thus prevents the escape of fuel from the high pressure chamber 36 into the combustion chamber 12.
  • the injection valve member 120 is briefly lifted from the injection valve seat 122, whereby fuel through the nozzle body 30 in a known manner and Way trained injectors is injected into the combustion chamber 12.
  • the injection valve member 120 In its end region facing away from the injection valve seat 122, the injection valve member 120 forms a piston 124, which is guided in a guide sleeve 126 in close sliding fit. On the guide sleeve 126 is formed as a compression spring closing spring 128, which at the other end is supported on the injection valve member 120 and this is acted upon by a directed toward the injection valve seat 122 spring force.
  • the guide sleeve 126 is pressed sealingly against an intermediate plate.
  • the piston 124, the guide sleeve 126 and the intermediate plate define a control chamber 130th
  • the control device 132 has an intermediate valve 134 with an intermediate valve member, which in the open position releases a high-pressure passage formed on the intermediate plate which leads from the high-pressure chamber 36 into the control chamber 130 and closes in the closed position in order to separate the control chamber 130 from the high-pressure chamber 36.
  • the intermediate valve member permanently separates the control chamber 130 from a valve chamber 136, with the exception of a throttle passage, via which the control chamber 130 is permanently connected to the valve chamber 136 via a small flow cross section.
  • the actuator assembly 118 has an electromagnet 138 connected to the control line 112, which actuates a control shaft 140. At rest closes the control shaft 140 a low-pressure outlet from the valve chamber 136. In the activated state of the solenoid 138, that is, for an injection, the control shaft 140 releases the low-pressure outlet; the fuel leaving the valve space 136 through this fuel is passed through a low pressure return line in a known manner to a low pressure fuel tank.
  • the structure and operation of the double-walled feed line 16 corresponds to the prior art and is for example in the earlier international patent application WO 2013/117311 A shown and described in detail.
  • the feed line 16 is double-walled.
  • the inner tube 70 is intended to guide the under very high pressure fuel. It runs within a (thin-walled) outer tube 142, wherein between this and the inner tube 70, a leakage return gap 144 is present; see in particular Fig. 2 ,
  • the feed line 16 has at its two ends depending on a connecting nut 74 and 75, wherein the fuel injection valve side, the fastening element 74 forming the connecting nut 74 'has an internal thread for Screwing onto a corresponding external thread on the housing 18 or storage body 20 and the other connection nut 75 has an external thread for insertion into, for example, a distributor element or a distributor block, as is known from the document WO 2007/009279 A is known; one could therefore also speak of a connection screw 75.
  • the fuel injection valve 10 associated with the connecting nut 74 ' has a radially inwardly open circumferential groove into which an O-ring 146 is inserted, which cooperates in the mounted state with a corresponding sealing surface on the housing 18 and the storage body 20 to the leakage to avoid fuel through the thread.
  • the other connection nut 75 has an outwardly open circumferential groove with an O-ring 146 'inserted therein.
  • an end region of the inner tube 70 which adjoins the outer cone 72 is provided with an end region of the mother passage 148 facing the fuel injection valve 10 Attachment sleeve 150 threaded with its center section.
  • the fastening sleeve 150 has four cross-shaped, groove-shaped leakage recesses 152 running through in the radial direction.
  • the fastening sleeve 150 is provided on the outside with a conical taper, which cooperates with a corresponding conical surface on the connecting nut 74 '.
  • the outer cone 72 of the inner tube 70 on the inner cone 68 of the valve carrier 46 and the outer sealing surface 60 on the conical sealing surface 44 of the housing 18 or its storage body 20 are held in tight contact by means of the connecting nut 74 'on the mounting sleeve 150. Should one or both of these gaskets leak, the leakage fuel will flow through the mother passage 148 into the leakage return gap 144, and from there in a known manner back to a leakage monitoring sensor, preferably in the low pressure fuel tank.
  • FIG. 5 and 6 Another embodiment of the inventive device is in the Figures 5 and 6 shown, wherein the housing 18 of the fuel injection valve 10, a valve housing 154 and a nozzle housing 156 of a pressure port 158 has.
  • a fuel injector 10 with such a valve housing 154 and a discharge nozzle 158 is from the document WO 2009/033304 A known.
  • the structure and operation of the fuel injection valve 10 are disclosed in detail in that document, and the disclosure of which is incorporated by reference into the present specification.
  • the nozzle housing 156 is formed by the storage body 20 with the discrete storage chamber 38, but without the electrical connection 108, channel 110, control line 112, connection contacts 114 and recess for a compression spring 116 in the present case.
  • valve housing 154 in the embodiment according to the Figures 5 and 6 instead of the storage body 20 on a connection body 160, at whose the nozzle body 30 facing end face (as in FIG. 1 shown) abuts the intermediate body 26 with the actuator assembly 118 received therein.
  • This is arranged in the interior of the union nut 32, which on the one hand is supported on the nozzle body 30 and on the other hand is threaded onto the connection body 160, analogously as in FIG. 1 shown and described above.
  • connection body 160 the electrical connection 108 is attached to the connection body 160.
  • a lateral, designed as a sealing surface, conical pressing surface 162 is integrally formed on the connecting body 160.
  • the high-pressure hydraulic connection from the feed line 16 to the valve housing 154 is realized via the pressure port 158.
  • the longitudinal axis 158 'of the pressure port 158 extends at right angles to the longitudinal axis 28 of the valve housing 154.
  • the longitudinal axis 158' also forms the axis of rotation for the pressure surface 162.
  • the nozzle housing 156 is formed at its end region facing the valve housing 154 as a conical abutment surface 164, which also acts as a sealing surface and bears sealingly against the pressure surface 162.
  • the recess 40 is formed with the discrete storage chamber 38 or at least a portion of the discrete storage chamber 38, from which or from which to the free end a duct section extends and is connected there to the high-pressure chamber inside the valve housing 154.
  • Analogous to the execution according to Fig. 1 may be present in the valve housing 154, a second part of the discrete storage chamber 38.
  • a mounting flange 166 protrudes from the nozzle housing 156, which has two through-holes 168. These are intended to be penetrated by clamping screws, which are supported with their head on the mounting flange 166 and are threaded into the cylinder head to hold the discharge nozzle 158 in close contact with the valve housing 154.
  • Fig. 6 and analogously to the embodiment according to the FIGS. 1 to 3 , see in particular FIG. 3 , has in the direction of the longitudinal axis 158 'extending recess 40 of the nozzle housing 156, which also forms at least a portion of the discrete storage chamber 38, the connection side in the connection section 22, the conical sealing surface 44.
  • the independent assembly 56 is used, which is exactly the same design and sealing, as described above and in the Fig. 1 to 3 shown.
  • the valve carrier 46 is located with its outer sealing surface 60 on the conical sealing surface 44 at. In the assembled state also engages the inner tube 70 of the feed line 16 with its outer cone 72 in the inner cone 68 of the valve carrier 46 and is located on this sealingly.
  • connection region of the feed line 16 to the nozzle housing 156 is the difference from the embodiment according to the FIGS. 1 to 3 only in that at the nozzle housing 156 in a connection recess, an internal thread is formed, in which, instead of the connection nut 74 ', a, otherwise the same as the connection nut 74' formed, the fastening element 74 forming connection screw 74 "is threaded with its external thread Words, the terminal portion of the feed line 16 is formed as the terminal portion in the fuel injection valve 10 remote from the end of the feed line 16 according to the embodiment according to the FIGS. 1 to 3 ,
  • FIGS. 7 and 8th show the connecting portion 22 of the housing 18, or the storage body 20 or the nozzle housing 156 of a further embodiment of the inventive device, wherein the fuel injection valve 10 - with the exception in the connection portion 22 - may be formed as in the FIGS. 1 to 3 respectively 5 and 6 are shown and described accordingly.
  • a high pressure outlet 172 is formed. Accordingly, the housing 18 is formed head-like in the connection portion 22 and it has a lateral extension.
  • the geometry of the high pressure outlet 172 is analogous to that of the high pressure inlet 34. From the bottom of the high pressure outlet 172 is a conical, tapered sealing surface 174 of which has the same geometry as the inner cone 68 on the valve carrier 46. It cooperates with an outer cone 72 at one , same as the feed line 16 formed connecting line 176. This serves to feed a further fuel injection valve 10 and is only indicated schematically.
  • a hydraulic connection 177 to the recess 40.
  • the junction is in the recess 40, seen in the direction of the longitudinal axis 28 and 158 ', the valve carrier 46, at its reduced outside diameter, that is, between the end flange 62nd or the outer sealing surface 60 and the guide portion 100; see also Figure 3 ,
  • connection 177 consists of a radial bore 178 opening into the recess 40 and a longitudinal bore 178 'extending from the latter and extending to the connection axis 172' of the high-pressure outlet 172, starting from the end of the conical sealing surface 174.
  • the transverse bore 178 has a larger cross-section in an end region adjoining the lateral outer surface of the housing 18 and, in this region, has a step-like tapering inwards.
  • a sealing ball 180 is arranged, which is held by means of an indented and sealed in the end region Andrückstopfens 182 such that the radial bore 178 seals high pressure moderately.
  • the radial bore 178 may have, subsequent to the end region, a conically tapered sealing surface against which the sealing ball 180 is pressed.
  • leakage bevels 186 which open into one another.
  • the openings of the Leckageeschrägbohrungen 186 lie in the radial direction outside the sealing surface 174 and the conical sealing surface 44 and also form leakage monitoring openings.
  • leakage bores such as the leakage longitudinal bore 184 and LeckescheCgbohrept 186, not necessary if a leakage monitoring is omitted.
  • the feed line 16 and connecting line 176 must not be double-walled; it then has no outer tube 142.
  • the illustrated embodiments of the valve carrier 46 in the direction of the longitudinal axis 28 between on the one hand the end flange 62 and the outer sealing surface 60 and inner cone 68 and on the other hand the guide portion 100 (FIG. Fig. 8 ) is at least one radial outlet 190, in the embodiment shown four cross-like extending radial outlets 190. This is or these are thus also disposed between the inner cone 68 and the check valve 48 and a preferably throttle-free connection between the fuel passage 76 and thus the feed line 16 and the high pressure outlet 172 and the connecting line 176 is possible.
  • the unit 56 is formed exactly the same as in the other embodiments of the fuel injection valve 10th
  • FIG. 9 shows the assembly 56 of the embodiment according to the FIGS. 7 and 8th in perspective view. As described above, this consists of the valve carrier 46, the non-return valve 48 present in it, the holding element 50 which is inserted in the valve carrier 46 and the filter 52 carried by the holding element 50.
  • two opposite chamfers 192 are integrally formed on the valve carrier 46, which serve to attack a fork wrench in order to be able to tighten the holding element 50.
  • the assembly 56 in the embodiments according to the FIGS. 1 to 6 is exactly the same, but with the valve carrier 46 has no radial outlet 190 and the length of the guide portion 100 may be less.
  • This preassembled, self-contained unit 56 can be easily inserted into the recess 40 until it rests with the outer sealing surface 60 of the valve carrier 46 on the conical sealing surface 44 of the housing 18.
  • the filter body 52 'with the microholes 54 may be provided as a filter 52 of the rod filter 53 - also in the other embodiments.
  • the rod filter 53 and the holding element 50 are integrally formed, ie integrally, with one another.
  • the rod filter 53 is also part of the assembly 56 and can accordingly be inserted into the recess 40 from the high-pressure inlet 34 together with the valve carrier 36 and the check valve 48.
  • the assembly 56 comprises the valve carrier 46, the check valve 48 and the holding member 50 with a further fuel passage 90th
  • the holding element 50 with its further fuel passage 90, the thread 94, the open grooves 96 and the step 98 with the polygon is the same, as in connection with FIGS FIGS. 1 to 3 and particularly FIGS. 4 to 7 shown and described.
  • integrally Bar filter 53 which closes the further fuel passage 90 in the axial direction blind hole.
  • the other fuel passage 90, inclined in the flow direction of the fuel here three radial passages 194 in the annular space between the support member 50 and the housing 18 and the storage body 20 or nozzle housing 156th
  • the rod filter 53 is cylindrical and has at its circumference, distributed in the circumferential direction, longitudinal grooves 196, 196 'which alternately open to the high-pressure chamber 36 and the radial passages 194 out, on the other hand, however, are almost closed and each other, measured in the axial direction over overlap a substantial part of the length of the rod filter 53.
  • the outer diameter of the rod filter 53 is formed slightly smaller than in the two axial end portions 198 and 198 ', which close the longitudinal grooves 196 and 196' almost.
  • the reduced diameter in the overlap region, together with the housing 18 or accumulator body 20 or stub housing 156, defines filter gaps 200 which allow the fuel to flow from the longitudinal grooves 196 'into the longitudinal grooves 196, but retain solid particles.
  • the width of the filter gaps 200 between the rod filter 53 and the housing 18 or storage body 20 or nozzle housing 156 is preferably about 30 to 40 micrometers, in particular about 35 micrometers.
  • the feed line 16 and the inner tube 70 with respect to the in the FIGS. 1 to 3 and 6 to 8 shown embodiments of smaller outer diameter and, if required by the pressure conditions (which is practically always the case), even smaller inner diameter form; see also Fig. 15 , 16 and 17.
  • the volume of the discrete storage chamber 38 is formed correspondingly large or larger.
  • the feed line 16 and the inner tube 70 is pressed with its outer cone 72 by means of the fastener 74 sealingly against the inner cone 68 of the valve carrier 46 and its end flange 62.
  • the valve carrier 46 and its end flange 62 is pressed with the conical outer sealing surface 60 on the conical sealing surface 44 of the housing 18.
  • the Fig. 14 and 15 show two embodiments in which the valve carrier 46 is pressed by means of a connecting piece 202 with its conical outer sealing surface 60 to the conical sealing surface 44 of the high pressure inlet 34 sealingly.
  • These embodiments are preferably used when the (not double-walled) feed line 16 and the inner tube 70 of the double-walled feed line 16 are formed with relatively small diameters; compare in this regard the supply line 16 in the Fig. 1 to 3 and 6 to 8 with larger diameters.
  • the outer diameter of the feed line 16 and the inner tube 70 is greater than the diameter of the recess 40 (outside the conical connecting portion) in the cylindrical region.
  • the outer diameter of the feed line 16 and the inner tube 70 is smaller than the diameter of the recess 40 in the cylindrical region.
  • the fuel injection valve 10, in particular the assembly 56 with the valve carrier 46 is the same design as shown in the other figures and described above.
  • the recess 40 in the housing 18 or accumulator body 20 or nozzle housing 156 has in the connection section 22, the conical sealing surface 44, against which the valve carrier 46 sealingly abuts with its conical outer sealing surface 60; as described above.
  • valve carrier 46 facing end portion of the outer adapter 72 is integrally formed on the connecting piece 202, which cooperates sealingly with the inner cone 68 of the valve carrier 46, as above, in particular in connection with the Fig. 1 to 3 and 6 to 8 , is disclosed.
  • the corresponding outer cone 72 is formed on the feed line 16 and on the inner tube 70.
  • an inner cone sealing surface 204 is integrally formed on the integrally formed connection piece 202, against which the inner tube 70 of the feed line 16 sealingly abuts with its outer cone 72.
  • connection adapter 202 projects beyond the housing 18 or the accumulator body 20 or the stub housing 156.
  • the connecting nut 74 ' which presses the inner tube 70 sealingly against the inner cone sealing surface 204 via the fastening sleeve 150, is screwed onto a corresponding external thread of the connecting intermediate piece 202.
  • an external bead 206 is integrally formed on the connecting intermediate piece 202 which, in the radial direction, protrudes beyond the connecting nut 76 and the downstream end region of the housing 18 and at which engaging surfaces for a tool, For example, a hexagon for the attack of a fork wrench are formed.
  • connection adapter 202 can be sufficiently strongly threaded into the housing 18 or the accumulator body 20 or the stub housing 156 in a simple manner.
  • the connecting adapter 202 two in corresponding radially outwardly open circumferential grooves inserted O-rings 146 are provided which between the terminal adapter 202 and on the one hand the housing 18 or the storage body 20 or nozzle housing 156 and on the other hand, the connecting nut 74 'seal.
  • a leakage bore 210 is formed on the connection intermediate piece 202, which has the leakage return gap 144, via the parent passage 148, with a housing 18 or storage body 20 or support housing 156, the valve carrier. 46 and the connecting piece 202 limited, gap-shaped leakage chamber 212 connects.
  • the terminal adapter 202 is shorter in the axial direction than in the embodiment according to FIG Fig. 14 and arranged in the interior of the housing 18 or storage body 20 or nozzle housing 156 in its connection portion 22.
  • the fastener 74 is the same as in the embodiments according to the FIGS. 6 to 8 formed as a fastening screw 74 ", which via the mounting sleeve 150, the inner tube 70 of the feed line 16 with its outer cone 72 sealingly against the Inner cone sealing surface 204 of the terminal adapter 202 presses.
  • valve carrier 46 is provided with the radial outlets 190, as in connection with the FIGS. 7 and 8th is shown and explained to supply via a connecting line 176, another fuel injection valve 10 with fuel.
  • the valve carrier 46 may be formed without the radial outlets 190 as shown in FIGS FIGS. 1 to 3 . 6 and 13 is shown.
  • connection portion 22 of the housing 18 or storage body 20 or nozzle housing 156 may be formed the same as in Fig. 7 shown and described above, namely with a high pressure outlet 178th
  • the housing 18 or the storage body 20 or nozzle housing 156 is encompassed by a clamp 216, which is arranged such that its radial passage 218 is aligned with the radial bore 178.
  • the clamp 216 is provided in the region of the radial passage 218 with an internal thread into which the fastening element 74 designed as a connection screw 74 "is screwed in order to press the inner tube 70 sealingly against the housing 18 or the accumulator body 20 or stub housing 156.
  • clamp 216 In order to fix the clamp 216 additionally on the housing 18 or on the accumulator body 20 or stub housing 156, it may have, preferably on the side opposite the radial passage 218 side, a threaded hole into which a preferably sealing screw 220 is inserted, which with its blunt point engages at the free end of the shaft in a corresponding recess on the housing 18 or storage body 20 or nozzle housing 156.
  • seal O-rings 146 above and below the radial bore 178 and the radial passage 218 between the housing 18 or accumulator body 20 or nozzle housing 156 and the clamp 216 to the Avoid leakage of leakage fuel.
  • connection piece 202 and the fastening element 74 of the feed line 16 designed as a terminal screw 74 are threaded into the same thread in the connection section 22 of the housing 18 or storage body 20 or socket housing 156.

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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 (18)

  1. Dispositif pour l'injection intermittente de carburant sous haute pression dans la chambre de combustion d'un moteur à combustion interne, comportant une soupape d'injection de carburant (10) qui présente un carter (18) qui a une admission de haute pression (34) avec une surface d'étanchéité (44) conique, un évidement (40) et une chambre de haute pression (36), comportant une soupape de retenue (48) admettant un flux le moins entravé possible du carburant de l'admission de haute pression (34) à travers le passage de carburant (76) jusque dans la chambre de haute pression (36) et au moins étranglant ledit flux dans la direction contraire, comportant une conduite d'alimentation (16) pour amener le carburant à la soupape d'injection de carburant (10) et comportant un élément de fixation (74) serrant la conduite d'alimentation (16) dans la direction allant vers l'admission de haute pression (34), caractérisé par un support de soupape (46) comportant un passage de carburant (76), lequel support de soupape comportant à une surface d'enveloppe (58) placée à l'extérieur une surface d'étanchéité extérieure (60) conique en contact de façon étanche avec la surface d'étanchéité (44) conique de l'admission de haute pression (34), et l'élément de fixation (74) comprime la conduite d'alimentation (16) contre le support de soupape (46) et le comprime celui-ci contre l'admission de haute pression (34).
  2. Dispositif selon la revendication 1, caractérisé en ce que le support de soupape (46) comporte à un côté frontal (66) situé du côté d'entrée un cône intérieur (68) formant une surface d'étanchéité, le passage de carburant (76) étant connecté au dit cône intérieur, et en ce que la conduite d'alimentation (16) comporte dans sa zone d'extrémité orientée vers la soupape d'injection de carburant (10) un cône extérieur (72) formant une surface d'étanchéité, ledit cône extérieur étant en contact de façon étanche contre le cône intérieur (68) du support de soupape (46).
  3. Dispositif selon la revendication 2, caractérisé en ce que la surface d'étanchéité extérieure (60) conique et le cône intérieur (68) sont réalisés à une flasque d'extrémité (62), en forme d'entonnoir, du support de soupape (46).
  4. Dispositif selon la revendication 2 ou 3, caractérisé en ce qu'une différence d'angle de cône (α ; β) de 0,5° à 2° est présente d'une part entre la surface d'étanchéité (44) conique de l'admission de haute pression (34) et la surface d'étanchéité extérieure (60) conique du support de soupape (46) et d'autre part entre le cône intérieur (68) du support de soupape (46) et le cône extérieur (72) de la conduite d'alimentation (16), de sorte qu'une surface d'étanchéité annulaire (64) soit formée chaque fois au plus petit diamètre de la surface de contact des cônes (44, 60 ; 68, 72) respectifs.
  5. Dispositif selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la surface d'étanchéité (44) conique de l'admission de haute pression (34) est formée au niveau du carter (18).
  6. Dispositif selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le support de soupape (46) est réalisé conjointement avec la soupape de retenue (48) et un élément de maintien (50) fixé au support de soupape (46) sous la forme d'une unité de construction (56) autonome de type cartouche et est inséré en tant que tel dans l'évidement (40) du carter (18).
  7. Dispositif selon la revendication 6, caractérisé en ce que l'unité de construction (56) est insérée depuis l'admission de haute pression (34) jusque dans l'évidement (40).
  8. Dispositif selon la revendication 6 ou 7, caractérisé en ce que l'élément de maintien (50) comporte un passage de carburant (90) supplémentaire.
  9. Dispositif selon l'une quelconque des revendications 6 à 8, caractérisé en ce que l'unité de construction (56) comporte un filtre (52) pour le carburant, en particulier un corps de filtre (52') de type bécher avec des microtrous (54) ou un filtre à tige (52"), supporté par l'élément de maintien (50) et vers lequel le carburant s'écoule le cas échéant à travers le passage de carburant (90) supplémentaire.
  10. Dispositif selon l'une quelconque des revendications 6 à 9, caractérisé en ce que l'évidement (40) forme au moins une partie de la chambre de haute pression (36) et en ce que l'unité de construction (56) est insérée dans la chambre de haute pression (36).
  11. Dispositif selon l'une quelconque des revendications 6 à 10, caractérisé en ce qu'un siège de soupape de retenue (80) de forme annulaire de la soupape de retenue (48) est réalisé au niveau du support de soupape (46) et en ce qu'un élément de soupape de retenue (84) interagissant avec le siège de soupape de retenue (48), réalisé de préférence sous la forme d'une plaquette de soupape (84') et pourvu d'un passage d'étranglement (86), est disposé entre le support de soupape (46) et l'élément de maintien (50).
  12. Dispositif selon la revendication 11, caractérisé en ce que l'élément de soupape de retenue (84) réalisé sous la forme d'une plaquette de soupape (84') comporte au moins un passage (92) ouvert dans la direction radiale vers l'extérieur et traversant dans la direction de l'axe longitudinal (28) - de préférence trois tels passages (92) répartis dans la direction périphérique - et en ce que l'élément de maintien (50) comporte dans sa zone d'extrémité orientée vers la plaquette de soupape (84') au moins une rainure (96) ouverte et traversante dans la direction radiale en direction de la plaquette de soupape (84') - de préférence trois telles rainures (96) réparties dans la direction périphérique -, pour permettre un passage le moins entravé possible de carburant en cas de soupape de retenue (48) ouverte.
  13. Dispositif selon l'une quelconque des revendications 1 à 12, caractérisé en ce que la chambre de haute pression (36) comporte une chambre d'accumulation (38) distincte pour accumuler du carburant et en ce que de préférence l'unité de construction (56) se prolonge dans cette chambre d'accumulation (38).
  14. Dispositif selon l'une quelconque des revendications 1 à 13, caractérisé en ce que le carter (18) de la soupape d'injection de carburant (10) supporte un corps de buse (30) avec un siège de soupape d'injection (122) qui est relié à la chambre de haute pression (36) et avec lequel un élément de soupape d'injection (120) disposé de façon mobile dans la direction de l'axe longitudinal (28) interagit, un ressort de fermeture (128) butant contre l'élément de soupape d'injection (120) et le chargeant avec une force de fermeture orientée dans la direction vers le siège de soupape d'injection (122), et en ce que dans le carter (18), un dispositif de commande (132) hydraulique commandé à l'aide d'un actionneur (118) à commande électrique est présent pour décoller l'élément de soupape d'injection (120) à l'encontre de la force de fermeture du ressort de fermeture (128) hors du siège de soupape d'injection (122) pour l'injection de carburant.
  15. Dispositif selon la revendication 14, caractérisé en ce que le carter (18) comporte d'une part un carter de soupape (154), lequel supporte le corps de buse (30) et dans lequel l'élément de soupape d'injection (120), le ressort de fermeture (128), l'actionneur (118) et le dispositif de commande (132) sont disposés, et sur lequel une surface de compression (162) conique servant de surface d'étanchéité est réalisée, et d'autre part un raccord de pression (158), sur le carter de raccord (156) duquel l'admission de haute pression (34) est réalisée et dont l'axe longitudinal (158') s'étend transversalement, de préférence à angle droit, par rapport à l'axe longitudinal (28) du carter de soupape (154), le carter de raccord (156) comportant dans une zone d'extrémité opposée à l'admission de haute pression (34) une surface de contre-compression (164) conique, laquelle est en contact de façon étanche contre la surface de compression (162), et le cas échéant l'unité de construction (56) étant insérée dans le carter de raccord (156) et le cas échéant la chambre d'accumulation (20) distincte étant réalisée au moins en partie dans le carter de raccord (156).
  16. Dispositif selon l'une quelconque des revendications 1 à 15, caractérisé en ce que le carter (18) respectivement le carter de raccord (156) comporte une sortie de haute pression (172) disposée à côté de l'admission de haute pression (34), cette sortie de haute pression étant reliée sur le plan de l'écoulement, de préférence sans étranglement, à l'admission de haute pression (34), pour alimenter en carburant, via une conduite de liaison de haute pression (176) connectée à la sortie de haute pression (172), une soupape d'injection (10) supplémentaire.
  17. Dispositif selon la revendication 2 et 16, caractérisé en ce que le support de soupape (46) comporte entre le cône intérieur (68) et la soupape de retenue (48) une sortie radiale (190) sortant du passage de carburant (76), laquelle est reliée pour l'écoulement, via une conduite de liaison (176) dans le carter (18) respectivement le carter de raccord (156) à la sortie de haute pression (172).
  18. Dispositif selon la revendication 17, caractérisé en ce que le support de soupape (46) délimite, conjointement avec le carter (18) respectivement le carter de raccord (156), un interstice (102) étroit en direction de la chambre de haute pression (36) en aval de la sortie radiale (190), pour séparer hydrauliquement la chambre de haute pression (36) respectivement le cas échéant la chambre d'accumulation (38) distincte de la conduite de liaison (176) au moins pour les processus transitoires.
EP14708195.4A 2013-03-01 2014-02-19 Dispositif pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion Active EP2961977B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH5342013 2013-03-01
PCT/EP2014/000447 WO2014131497A1 (fr) 2013-03-01 2014-02-19 Dispositif permettant d'injecter un carburant dans la chambre de combustion d'un moteur à combustion interne

Publications (2)

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EP2961977A1 EP2961977A1 (fr) 2016-01-06
EP2961977B1 true EP2961977B1 (fr) 2017-06-21

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EP14708195.4A Active EP2961977B1 (fr) 2013-03-01 2014-02-19 Dispositif pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion

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US (1) US9803603B2 (fr)
EP (1) EP2961977B1 (fr)
JP (1) JP6441824B2 (fr)
KR (1) KR102098354B1 (fr)
WO (1) WO2014131497A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH710127A1 (de) 2014-09-17 2016-03-31 Ganser Crs Ag Brennstoffeinspritzventil für Verbrennungskraftmaschinen.
LT6299B (lt) * 2015-09-04 2016-08-25 UAB "Aukšto slėgio filtravimo sprendimai" Didelio slėgio filtras skysčiui filtruoti turintis tvirtumo strypą ir to filtro panaudojimas kuro tiekimo sistemoje
TR201516233A2 (tr) * 2015-12-17 2017-03-21 Bosch Sanayi Ve Tic A S Fi̇ltreye sahi̇p bi̇r yakit enjektörü
WO2017102179A1 (fr) * 2015-12-17 2017-06-22 Robert Bosch Gmbh Injecteur de carburant ayant un filtre
EP3990770A1 (fr) 2019-06-25 2022-05-04 Ganser-Hydromag AG Soupape d'injection de carburant pour des moteurs à combustion interne
CN114761681B (zh) 2019-12-03 2024-01-16 甘瑟-许德罗玛格股份公司 用于内燃机的具有滑阀的燃料喷射阀
CN115087802A (zh) 2020-02-17 2022-09-20 甘瑟-许德罗玛格股份公司 用于内燃机的燃料喷射阀
US11346313B2 (en) * 2020-09-03 2022-05-31 Caterpillar Inc. Fuel flow limiter assembly having integral fuel filter and fuel system using same
WO2023073140A1 (fr) 2021-10-29 2023-05-04 Ganser Crs Ag Soupape d'injection de carburant pour moteurs à combustion interne
WO2023166139A1 (fr) 2022-03-03 2023-09-07 Ganser-Hydromag Ag Soupape d'injection de carburant pour moteurs à combustion interne
US11959444B2 (en) * 2022-08-25 2024-04-16 Caterpillar Inc. Method and apparatus for ventilating a fuel inlet connection for a fuel injector

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5819951Y2 (ja) * 1978-08-29 1983-04-25 トヨタ自動車株式会社 車輌用座席のシ−トベルト引出孔
JPS6016784Y2 (ja) * 1980-03-17 1985-05-24 日産自動車株式会社 燃料噴射弁装置
CH689282A5 (de) * 1994-03-29 1999-01-29 Christian Dipl-Ing Eth Mathis Einspritzventil fuer eine insbesondere als Dieselmotor vorgesehene Brennkraftmaschine.
DE19727543A1 (de) * 1997-06-28 1999-01-07 Bosch Gmbh Robert Kraftstoffzuleitungseinrichtung
IT1295462B1 (it) * 1997-10-02 1999-05-12 Elasis Sistema Ricerca Fiat Iniettore di combustibile a comando elettromagnetico per motori a combustione interna.
EP1118765A3 (fr) * 2000-01-19 2003-11-19 CRT Common Rail Technologies AG Injecteur de combustible pour moteur à combustion interne
US6463909B2 (en) * 2000-01-25 2002-10-15 Usui Kokusai Sangyo Kaisha Limited Common rail
US6830034B2 (en) * 2000-02-07 2004-12-14 Siemens Automotive Corporation Fuel injector and fuel rail check valves
JP2003049741A (ja) * 2001-08-07 2003-02-21 Otics Corp コモンレール
EP1620645B1 (fr) 2003-05-08 2009-10-07 Ganser-Hydromag Ag Soupape d'injection de carburant sans perte
WO2005003550A1 (fr) 2003-07-01 2005-01-13 Ganser-Hydromag Ag Soupape d'injection de carburant pour moteurs a combustion interne
EP1656498B1 (fr) 2003-08-22 2008-11-26 Ganser-Hydromag Ag Soupape d'injection de carburant commandee par une soupape pilote
ES2355146T3 (es) 2004-02-25 2011-03-23 Ganser-Hydromag Ag Válvula de inyección de combustible para una máquina de combustión interna.
ATE493577T1 (de) 2004-12-03 2011-01-15 Ganser Hydromag Brennstoffeinspritzventil mit druckverstärkung
US7891584B2 (en) 2005-04-14 2011-02-22 Ganser-Hydromag Ag Fuel injection valve
ATE488690T1 (de) 2005-07-18 2010-12-15 Ganser Hydromag Speichereinspritzsystem für brennkraftmaschine
WO2008046238A2 (fr) 2006-10-16 2008-04-24 Ganser-Hydromag Ag Soupape d'injection de carburant pour moteurs à combustion interne
EP2188516B1 (fr) 2007-09-13 2011-10-26 Ganser-Hydromag AG Dispositif d'injection de carburant
US8196967B2 (en) * 2009-02-04 2012-06-12 Robert Bosch Gmbh Improvements to high pressure fuel fittings
CH700396A1 (de) 2009-02-09 2010-08-13 Ganser Hydromag Brennstoffeinspritzventil für Verbrennungskraftmaschinen.
CH702496B1 (de) 2010-05-07 2011-07-15 Liebherr Machines Bulle Sa Hochdruckinjektor.
EP2812559B1 (fr) 2012-02-07 2016-05-04 Ganser-Hydromag AG Injecteur de carburant et dispositif d'injection de carburant
AT512162B1 (de) * 2012-05-08 2013-06-15 Bosch Gmbh Robert Verschlussbolzen mit Durchflussbegrenzer
DE202012104347U1 (de) * 2012-11-12 2012-11-28 Ti Automotive (Heidelberg) Gmbh Schraubverbindungsvorrichtung für Rohrleitungen, insbesondere für Kraftfahrzeugrohrleitungen

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EP2961977A1 (fr) 2016-01-06
JP6441824B2 (ja) 2018-12-19
JP2016508576A (ja) 2016-03-22
US9803603B2 (en) 2017-10-31
KR102098354B1 (ko) 2020-04-09
KR20150121116A (ko) 2015-10-28
US20160010609A1 (en) 2016-01-14
WO2014131497A1 (fr) 2014-09-04

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