WO2008049667A1 - Injecteur pour injecter du carburant dans des chambres de combustion de moteurs à combustion interne - Google Patents

Injecteur pour injecter du carburant dans des chambres de combustion de moteurs à combustion interne Download PDF

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Publication number
WO2008049667A1
WO2008049667A1 PCT/EP2007/058948 EP2007058948W WO2008049667A1 WO 2008049667 A1 WO2008049667 A1 WO 2008049667A1 EP 2007058948 W EP2007058948 W EP 2007058948W WO 2008049667 A1 WO2008049667 A1 WO 2008049667A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
valve sleeve
injector
sleeve
fuel
Prior art date
Application number
PCT/EP2007/058948
Other languages
German (de)
English (en)
Inventor
Andreas Rettich
Friedrich Boecking
Francois Rossignol
Friedrich Howey
Olivier Charvet
Tony Dumont
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2008049667A1 publication Critical patent/WO2008049667A1/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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0073—Pressure balanced valves
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided

Definitions

  • Injector for injecting fuel into combustion chambers in internal combustion engines
  • the invention relates to an injector according to the preamble of claim 1.
  • EP 1 612 403 A1 describes a common-rail injector with a pressure-balanced control valve in the axial direction for blocking and opening a fuel discharge path from a control chamber.
  • the fuel pressure can be influenced within the control chamber, wherein the control chamber is supplied via a pressure channel with fuel from a high-pressure fuel storage. Due to the variation of the fuel pressure within the control chamber, a nozzle needle whose upper end face protrudes into the control chamber, moved between an open position and a closed position, wherein the nozzle needle in its open position releases the fuel flow into the combustion chamber of an internal combustion engine.
  • the control valve has an adjustable in the axial direction by means of an electromagnetic actuator valve sleeve, which cooperates sealingly with a conically shaped valve seat surface.
  • the valve seat surface of the control valve is formed on a component which is defined within the injector body, through which the fuel discharge path for fuel is led out of the control chamber and on which a bolt penetrating the sleeve and receiving axial pressure forces is formed.
  • a disadvantage of the known injector is that the axially displaceable valve sleeve is guided in the axial direction exclusively by its inner circumference on the outer circumference of the bolt. As a result, high leakage losses occur on the valve seat surface and / or in the radial guide gap between the valve sleeve and the bolt. The leakage quantity can be reduced by using smaller guide diameters. Due to the internal pressure in the fuel passage and the associated strength problems a minimum diameter is not to fall below.
  • the invention is therefore based on the object to propose an injector in which the leakage losses in the region of the control valve are minimized.
  • the invention is based on the idea to support the bolt passing through the valve sleeve on the opposite side of the valve seat on an injector, to attach to this or form integrally with this.
  • a solution in which the bolt is supported only on the injector body is preferred, or is attached to the injector body, since in this case the bolt can be manufactured as a separate component and thus easier to manufacture.
  • the fuel discharge from the control chamber is not integrated in the bolt, whereby smaller diameter and thus smaller leakage quantities can be realized.
  • a throttle body is disposed within which the pressure channel with inlet throttle for supplying the control chamber with fuel, for example, from a control chamber surrounding Pressure chamber or directly from a connected to a high-pressure fuel storage supply line and / or a drain passage with outlet throttle for hydraulic connection of the control chamber are introduced to the control valve.
  • the drainage channel forms the fuel drainage path for fuel from the control chamber to a low pressure chamber or is at least part of the same.
  • both the pressure channel with inlet throttle and the outlet channel with outlet throttle are introduced within the throttle body.
  • valve sleeve is formed integrally with the anchor plate.
  • integrally formed with the anchor plate valve sleeve is received within a receiving bore, wherein not the sleeve is guided radially outwardly on the peripheral wall of the receiving bore, but only the anchor plate.
  • a first guide portion of the valve sleeve and anchor plate combination is located relatively far from the valve seat surface, thereby eliminating the need for a long cylindrical guide on the outer surface of the valve sleeve.
  • valve seat surface is formed partially spherical, so at least in the contact region of the valve sleeve describes a spherical shape. This will provide an optimal center ration of the valve sleeve on the valve seat surface, which in combination with the guidance of the armature plate within the receiving bore effectively prevents radial displacement and tilting of the valve sleeve about the center of the valve seat.
  • the receiving bore within the armature plate and the valve sleeve receiving member is designed as a stepped bore, wherein the electromagnet is supported on an annular shoulder of the stepped bore within the component.
  • the parallelism between the armature plate and electromagnet is improved.
  • the electromagnet on the, preferably flat, surface of the component, in particular the throttle plate is supported.
  • the armature plate and the valve sleeve are formed as separate components, wherein the bolt enclosed by the valve sleeve additionally passes through the armature plate. Also in this embodiment variant can be dispensed with an immediate axial guidance of the valve sleeve over its entire outer circumference.
  • the bolt has the task of roughly centering the armature plate in the radial direction.
  • the valve spring for closing the control valve acts in the axial direction on the armature plate, whereby the armature plate is spring-loaded on the valve sleeve and this in turn in the direction of the valve seat surface.
  • the valve spring counteracts a weaker spring, which exerts a spring force in the opening direction on the valve sleeve. Due to the separate design of anchor plate and valve sleeve, the two components can be made of different lent materials are formed. In particular, the anchor plate is formed of highly magnetically conductive material, whereas the valve sleeve is wear-optimized.
  • a Convex-concave pairing is realized.
  • the adjusting ring is supported with a concave recess on a convex elevation on the end face of the valve sleeve, so that a kind of ball joint is realized, whereby angular errors can be compensated.
  • a radial gap is provided between a component enclosing the armature plate and the armature plate, ie the armature plate with its peripheral surface does not bear directly on the component surrounding it and thereby freely alignable on the electromagnet.
  • the recess in which the anchor plate is received is dimensioned such that assuming exactly parallel alignment between anchor plate and a parallel surface of the recess, in particular a (bottom) shoulder of the recess, and at the same time on the valve seat Veriqueer valve sleeve axial gap between the anchor plate and the parallel surface remains.
  • Double plank grinding of the anchor plate and the shoulder (parallel surface) of the holding sleeve makes it possible to produce very small parallelism errors which can only be achieved in the case of conventional injectors by means of severely limited axial runs.
  • a lifting gap is provided between the armature plate and the electromagnet, which plate is overcome when the electromagnet is energized by the armature plate (together with the valve sleeve).
  • the residual air gap ie the remaining gap between the armature plate and the magnet in the open control valve state, can be represented by a coating of the electromagnet or a step in the armature plate.
  • the anchor plate strikes in the case of providing a coating directly to this.
  • valve sleeve With small seat angles of approximately 90 ° total angle, the valve sleeve can move only slightly in the radial direction from its centric position with open control valve.
  • This larger seat angle so comparatively flat valve seat surfaces can be realized, is in an embodiment of the invention, an additional guide sleeve provided radially adjacent to the valve seat surface, which prevents radial pivoting of the valve sleeve when the control valve is open. Even with this solution, the valve sleeve is not guided cylindrically over its entire length, but only in a short, lower section.
  • valve sleeve and / or the valve sleeve surrounding the guide sleeve must be formed such, for example, by providing flats that a fuel flow from the valve sleeve interior is ensured in the low pressure chamber.
  • this Abströmitzkeit the fuel can be realized by extending in the axial direction of the grooves on the outer diameter of the valve sleeve or on the inner diameter of the guide sleeve.
  • valve sleeve passes through a guide ring and is guided over this on a peripheral wall of a bore.
  • the valve sleeve is thus supported only indirectly on the peripheral wall.
  • a cylindrical guide of the valve sleeve over its entire outer circumferential surface is avoided, whereby the guide surfaces to be ground are minimized.
  • the valve sleeve is guided on the bolt enclosed by it, which is preferably designed in two parts, wherein the two axially adjacent portions of the bolt via a kind of ball joint (convex-concave pairing) support each other, inter alia, to compensate for angular errors.
  • the guide ring is spring-loaded via the valve spring in the axial direction.
  • the guide ring is supported indirectly or directly on the valve sleeve.
  • a retaining ring is provided for indirect support, which is held in a circumferential groove of the valve sleeve.
  • the armature plate is received with radial clearance in a receiving bore, in particular a valve body, so that the alignment of the valve sleeve takes place only over the guide ring and the seat.
  • valve seat surface is flat, i. just, is formed, whereby the valve seat surface is aligned parallel to the valve seat surface or the component comprising this, in particular the throttle plate due to the valve spring acting on the valve sleeve shortly thereabove.
  • FIG. 1a a sectional partial view of a first exemplary embodiment of an injector, in which the
  • FIG. 1b is a further sectioned partial view of the embodiment according to FIG. 1a, FIG.
  • FIG. 2 shows a second exemplary embodiment of an injector, in which also the anchor plate and the
  • Valve sleeve are integrally formed and in which an electromagnet of an electromagnet ⁇ drive is supported on a flat top of a Dros ⁇ selplatte,
  • FIG. 3a shows a sectional partial view of a third embodiment of an injector, in which the anchor plate and the valve sleeve are formed separately, and in which the anchor plate via an adjusting ring hinged to the
  • FIG. 3b shows a sectional view of a detail from FIG. 3a, which shows the arrangement of the anchor plate within the injector body
  • FIG. 4a shows a sectional partial view of a fourth embodiment of an injector with ge ⁇ separated trained anchor plate and valve sleeve, wherein radially adjacent to the valve seat ⁇ surface an additional guide ring is provided for the valve sleeve,
  • 4c a side view of the valve sleeve
  • 4d shows a plan view of a possible embodiment of the guide ring
  • FIG. 5a shows a sectional partial view of a fifth embodiment, in which the anchor plate is formed integrally with the valve sleeve, wherein the valve sleeve is guided via a radial guide ring on a peripheral wall,
  • Fig. 5b a perspective view of the unit
  • an injector 1 is shown in fragmentary form.
  • the injector 1 has an injector body 2, a nozzle body 3 and a cylindrical throttle body 4 accommodated between the injector body 2 and the nozzle body 3.
  • a nozzle retaining nut 5 is screwed to the injector body 2 and thus clamps the nozzle body 3 and the throttle body 4 against the injector body 2.
  • the lower portion of the injector 1 is not completely shown, but can be described, for example, as in DE 100 24 703 A1 be executed. It is not shown that the nozzle retaining nut 5 is penetrated by the nozzle body 3 in the axial direction.
  • a bore 6 is introduced, in which an elongated nozzle needle 7 is guided axially movable.
  • a closing surface is provided, with which the nozzle needle can be brought into tight contact with a needle seat formed within the nozzle body 3.
  • the nozzle needle 8 rests against the needle seat (not shown) (see DE 100 24 703 A1), ie is in a closed position, the fuel outlet from a nozzle hole arrangement is blocked. If, on the other hand, it has been lifted from the needle seat, fuel can flow from the annular space 8 formed between the nozzle needle 7 and the inner circumference of the bore 6 past the needle seat to the nozzle hole arrangement, where it is sprayed into a combustion chamber substantially under high pressure (rail pressure) become.
  • the nozzle needle 7 is biased by a biasing spring 9 in the direction of its closed position.
  • the biasing spring is supported on the one hand on the nozzle needle
  • the sleeve-shaped component is in this case formed by the annular space formed as a pressure chamber
  • a control chamber 12 Radially within the sleeve-shaped component 10 and in the axial direction of the throttle body 4 and an upper end face 11 of the nozzle needle 7 is limited a control chamber 12 which is connected via a pressure channel 13 with inlet throttle 14 within the throttle body 4 with a supply line 15, via the fuel can flow from a high-pressure fuel storage, not shown. Fuel can flow out of the control chamber 12 through a control valve 18 into a low-pressure chamber 19 and from there via a return channel, not shown, via an outlet channel 16 with outlet throttle 17 within the throttle body 4. Depending on the operating state, the fuel pressure within the low-pressure space is approximately between 0 and 10 bar, whereas fuel flows through the supply channel 15 at a pressure between approximately 1800 and 2000 bar.
  • control valve 18 By means of an electromagnetic actuator 20, which comprises an electromagnet 21 and an axially relative thereto adjustable armature plate 22, the control valve 18 can be adjusted from the illustrated closed position to an open position.
  • the flow cross sections of the inlet throttle 14 and the outlet throttle 17 are matched to one another such that the inflow through the pressure channel 13 is weaker than the outflow through the outlet channel 16 and thus results in a net outflow of fuel when the control valve 18 is open.
  • the resulting pressure drop in the control chamber 12 causes the amount of closing force falls below the amount of the opening force and the nozzle needle 7 lifts from the needle seat.
  • the anchor plate 22 is formed integrally with a valve sleeve 23 of the control valve 18, the valve sleeve 23 sealingly cooperating with a valve seat surface 24 that is partially spherical in this embodiment.
  • the valve sleeve 23 encloses an elongated (guide) pin 25, which is axially spaced from the valve seat surface 24 supported on the injector body 2.
  • the bolt 25 is pressed against the valve body 2 by the fuel pressure inside the valve sleeve 25 and thus forwards all axial forces to the injector body 2, so that only a fuel pressure in the radial direction acts on the valve sleeve 23, whereby the control valve 18 in the axial direction pressure balanced.
  • the valve sleeve 23 is centered over the part-spherical valve seat surface 24 and leads over its inner circumference on the outer circumference of the bolt 25.
  • An additional guide is in Area of the peripheral wall 26 of the anchor plate 22 is provided.
  • the peripheral wall 26 is guided on an inner wall 27 of a receiving bore 28 within the throttle body 4.
  • the bolt is aligned by the anchor. When pressurized, the bolt is pushed up and its upper end assumes a fixed position due to the static friction. Thus, in the open state, the upper end of the bolt defines a fixed point. The orientation of the armature thus takes place via the bolt with its upper fixed end and also over the outer diameter of the anchor plate.
  • the valve sleeve 23 has no contact with the valve seat, whereby the valve seat can no longer center the
  • the electromagnet 21 of the actuator 20 is received in a bore 29 of the injector body 2 and is spring-loaded in the direction of the armature plate 22 via a spring element 30 which is supported on the one hand on the injector body 2 and on the other hand on an end face of the electromagnet 21.
  • the receiving bore 28 within the throttle body 4 is designed as a stepped bore, so that an annular shoulder 31 arises within the receiving bore 28, on which the electromagnet 21 is supported.
  • the receiving bore 28 has in the region in the plane above the paragraph 31 the same diameter as the bore 29 within the injector body. 2
  • a passage opening 32 is provided, which is penetrated by the bolt 25.
  • a valve spring 33 is arranged, which is supported on the one hand on a setting ring 34 for adjusting the valve spring force and on the other hand on the plane in the drawing upper, the electromagnet 21 facing side of the armature plate 22, whereby the armature plate 22 is spring-loaded on the valve seat surface 24.
  • Fig. Ib which is an offset sectional view of the injector shown in Fig. Ia
  • a portion of the supply line 15 is shown within the throttle body 4, which supplies the pressure chamber formed as an annular space 8 with high-pressure fuel. From the annular space 8, this fuel can flow out of the nozzle hole arrangement (not shown) in the region of the needle point when the needle needle 7 is lifted from the needle seat.
  • the throttle body simultaneously forms a valve body and thus a separate component can be saved. At the same sealing surfaces are saved and due to the support of the electromagnet 21 within the receiving bore 28, a high accuracy of the concentricity between the electromagnet and armature plate 22 is achieved.
  • the embodiment according to FIG. 2 essentially corresponds to the exemplary embodiment according to FIGS. 1a and 1b, so that only the differences will be discussed below. Concerning the similarities reference is made to the previous description.
  • the receiving bore 28 is not formed as a stepped bore, so that the electromagnet 21 is not supported in the axial direction within the receiving bore 28. As a support surface for the electromagnet 21 is rather the electromagnet 21 facing planar surface 36 of the throttle body. 4
  • FIGS. 3a and 3b show a further exemplary embodiment of an injector 1.
  • the anchor plate 22 and the valve sleeve 23 are designed as separate components.
  • the anchor plate 22 is formed by a simple symmetrical disc.
  • the armature plate 22 of the valve spring 33 which is received in the central passage opening 32 of the electromagnet 21, spring-loaded axially in the direction of an adjusting ring 36, which in turn is supported in the axial direction of the valve sleeve 23, thereby the flat conical valve seat 24th is pressed.
  • a concave recess 38 is provided, via which the adjusting ring 36 and thus the armature plate 22 on the convex, for the recess 38 formkongruenten end face 39 of the valve sleeve 23 is supported.
  • valve sleeve 23 Via a coil spring 40, which is supported on the one hand at the bottom 41 of a bore 42 in the throttle body 4 and on the other hand on an annular shoulder 43 of the valve sleeve 23, the valve sleeve 23 is spring-loaded in the opening direction.
  • the electromagnetic actuator 20 only has to overcome the difference of the spring forces, the valve spring 33 and the weaker spring 40.
  • the armature plate 22 is accommodated within a retaining sleeve 44, which is supported on the throttle body 4 in the axial direction.
  • the electromagnet 21 is spring-loaded on the retaining sleeve 44 and pressed together with the retaining sleeve 44 on the throttle body 4. From an annular shoulder 45 within the holding sleeve 44, a parallel surface is formed to the bottom surface 46 of the anchor plate 2 in the plane of the drawing.
  • a radial gap 48 is provided between the peripheral wall 26 of the anchor plate 22 and the inner wall 47 of the holding sleeve 44.
  • a full axial gap 49 is present.
  • an axial stroke gap 50 is provided between the electromagnet 21 and the armature plate 22.
  • the lower axial gap 49 (orientation gap) is realized in that the adjusting ring 36 slightly projects beyond the shoulder 45 in the axial direction. This ensures that the spring force of the valve spring 33 is introduced into the valve sleeve 23 and not in the paragraph 45.
  • the Hubspalt 50 ensures a free Alignment between solenoid 21 and armature plate 22, whereas the ball-joint connection between the valve sleeve 32 and adjusting 36 allows large-scale power transmission between the armature plate 22 and valve sleeve 23 and a compensation of angular errors.
  • the exemplary embodiment according to FIG. 4 a substantially corresponds to the exemplary embodiment according to FIG. 3 a, so that reference is made to the previous description with regard to the similarities.
  • the valve seat surface 24 is less inclined, whereby the valve sleeve 23 can slip more easily in the radial direction.
  • a guide sleeve 51 is provided, which is arranged radially adjacent to the valve seat surface 24 and the valve sleeve 23 leads over a small axial portion.
  • the guide sleeve 51 is centered with the valve closed by the valve sleeve, which in turn is centered by the valve seat. In the open state, the guide sleeve maintains its position, since it is spring-loaded by the coil spring 40 in the direction throttle body 4 and thus held in position.
  • valve sleeve 23 In order to allow a fuel drain from the drain passage 16 via the interior 52 of the valve sleeve 23 in the low-pressure chamber 19, the valve sleeve is in a lower portion, as shown in Fig. 4b, with three staggered by 120 °, extending in the axial direction flats 53 provided by the axial direction between the guide sleeve 51 and valve sleeve 23 channels 54 are formed, can flow through the fuel in the low-pressure chamber 19.
  • a flattening 53 of the valve sleeve 23 is shown in a side view.
  • grooves 55 extending in the axial direction can be provided on the inner circumference of the guide ring 21, through which the fuel can flow into the low-pressure space 19.
  • FIG. 5 a shows a further exemplary embodiment of an injector 1.
  • valve spring 33 is not received within the passage opening 32 in the electromagnet 21, whereby the passage opening 32 may have a smaller cross section, which in turn higher magnetic forces can be realized with the same width of the electromagnet 21.
  • the anchor plate 22 is designed in one piece with the valve sleeve 23, as shown in FIG.
  • a radial play is provided between the peripheral wall 26 of the anchor plate 22 and the circumferential wall 56 of a bore 57 within a valve body 58.
  • the valve body 28 is arranged in the axial direction between the valve body 2 and the throttle body 4. Through the valve body 58 passes through the supply line 15, which opens into a pocket 59, from where under high pressure fuel on the one hand in the pressure chamber formed as an annular space 8 and the inlet channel 14 with inlet throttle 15 in the control chamber 12 and from there via the Outflow channel 16 with outlet throttle 17 can flow into the low-pressure chamber 19.
  • the assembly of anchor plate 22 and valve sleeve 23 receives a two-piece formed bolt 25, wherein the bolt 25, which also passes through the electromagnet 21, on the injector 2 supports.
  • An upper bolt part 60 in this case has a smaller cross-section than an axially adjacent lower bolt part 61.
  • the lower bolt part 61 is supported via a convex-concave pairing 62 (a kind of ball joint) on the upper bolt part 60, whereby angular errors can be compensated.
  • the valve spring 33 which acts on the valve sleeve 23 in the closing direction by spring force, is supported, on the one hand, on a shoulder 63 within the valve body 58 and, on the other hand, on a guide ring 64.
  • the guide ring 64 in turn is supported on a securing ring 65 in the axial direction, wherein the securing ring 65 is held in a circumferential groove 66 in the region of the lower end of the valve sleeve 23 in the plane of the drawing.
  • the valve sleeve 23 cooperates with a flat seat seat formed valve seat 24.
  • the valve sleeve 23 is automatically aligned parallel to the surface of the throttle body 4 by the valve spring force acting on the valve sleeve 23 just above the valve seat surface 24.
  • valve sleeve 23 is guided on the inner circumferential wall 67 of a valve body bore 68 via the guide ring 64, which serves as a setting disk for adjusting the spring force of the valve spring 33.
  • a guide of the entire outer surface of the valve sleeve 23 is not necessary. As a result, only a small portion of the inner peripheral wall 67 of the valve body bore needs to be ground.
  • valve sleeve 23 The positioning of the valve sleeve 23 over the guide tion ring 64 in the radial direction must be so accurate that the radial gap between the peripheral wall of the anchor plate 22 and valve body is fully present, ie over 360 ° to avoid disturbing forces and tilting moments on the armature plate 22 and thus on the valve sleeve 23.
  • the guide surfaces on the valve sleeve 23 and the guide ring 58 and the inner circumference 67 can be manufactured with relatively large tolerances.
  • Fig. 5b the unit of anchor plate 22 and valve sleeve 23 is shown in a perspective view, wherein the valve sleeve 23 is wrapped over an axial portion of the valve spring designed as a helical spring 33 which extends radially in the drawing plane down to the guide ring 64 and this in turn supported on the retaining ring 65. It can be seen that the retaining ring 65 is supported in the circumferential groove 66 in the region of the lower end of the valve sleeve 23.

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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)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

La présente invention concerne un injecteur (1) pour injecter du carburant dans des chambres de combustion de moteurs à combustion interne, en particulier un injecteur rampe commune (common rail). Selon l'invention, un boulon (25) qui pénètre dans la douille (23) d'une soupape de commande (18) prend appui sur un élément d'injecteur, en particulier sur un corps d'injecteur (2) ou forme une seule pièce avec celui-ci, à distance d'une chambre de commande (12).
PCT/EP2007/058948 2006-10-24 2007-08-29 Injecteur pour injecter du carburant dans des chambres de combustion de moteurs à combustion interne WO2008049667A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006050045.8 2006-10-24
DE200610050045 DE102006050045A1 (de) 2006-10-24 2006-10-24 Injektor zur Einspritzung von Kraftstoff in Brennräume in Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
WO2008049667A1 true WO2008049667A1 (fr) 2008-05-02

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PCT/EP2007/058948 WO2008049667A1 (fr) 2006-10-24 2007-08-29 Injecteur pour injecter du carburant dans des chambres de combustion de moteurs à combustion interne

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DE (1) DE102006050045A1 (fr)
WO (1) WO2008049667A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008155275A1 (fr) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Soupape de commande pour une soupape d'injection de carburant

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010001486A1 (de) * 2010-02-02 2011-08-04 Robert Bosch GmbH, 70469 Steuerventilanordnung eines Kraftstoffinjektors
DE102013227063A1 (de) * 2013-12-23 2015-06-25 Robert Bosch Gmbh Kraftstoffinjektor

Citations (5)

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DE3943183A1 (de) * 1988-12-28 1990-07-05 Diesel Kiki Co Elektromagnetisches ventil und kombinierte kraftstoffpumpe mit elektromagnetischem ventil
EP0781913A2 (fr) * 1995-12-23 1997-07-02 LUCAS INDUSTRIES public limited company Dispositif de soupape
EP1612403A1 (fr) 2004-06-30 2006-01-04 C.R.F. Societa' Consortile per Azioni Soupape servo pour controller l'injecteur d'un moteur à combustion interne

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Publication number Priority date Publication date Assignee Title
DE2647744A1 (de) * 1975-10-24 1977-04-28 Karl Marx Stadt Automobilbau Elektromagnetisches einspritzventil fuer brennkraftmaschinen mit einem elektromagnetisch gesteuerten wegeventil fuer die be- und entlastung der duesennadelrueckseite
JPS63251678A (ja) * 1987-04-03 1988-10-19 Nachi Fujikoshi Corp ソレノイドバルブ
DE3943183A1 (de) * 1988-12-28 1990-07-05 Diesel Kiki Co Elektromagnetisches ventil und kombinierte kraftstoffpumpe mit elektromagnetischem ventil
EP0781913A2 (fr) * 1995-12-23 1997-07-02 LUCAS INDUSTRIES public limited company Dispositif de soupape
EP1612403A1 (fr) 2004-06-30 2006-01-04 C.R.F. Societa' Consortile per Azioni Soupape servo pour controller l'injecteur d'un moteur à combustion interne

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WO2008155275A1 (fr) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Soupape de commande pour une soupape d'injection de carburant
EP2171258B1 (fr) * 2007-06-21 2014-12-17 Robert Bosch GmbH Soupape de commande pour une soupape d'injection de carburant

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