EP2218906B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2218906B1
EP2218906B1 EP20090180310 EP09180310A EP2218906B1 EP 2218906 B1 EP2218906 B1 EP 2218906B1 EP 20090180310 EP20090180310 EP 20090180310 EP 09180310 A EP09180310 A EP 09180310A EP 2218906 B1 EP2218906 B1 EP 2218906B1
Authority
EP
European Patent Office
Prior art keywords
sleeve
coupler
fuel injector
spring element
spring
Prior art date
Legal status (The legal status 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 status listed.)
Not-in-force
Application number
EP20090180310
Other languages
German (de)
English (en)
Other versions
EP2218906A1 (fr
Inventor
Andreas Gruenberger
Martin Kiontke
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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 EP2218906A1 publication Critical patent/EP2218906A1/fr
Application granted granted Critical
Publication of EP2218906B1 publication Critical patent/EP2218906B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • Such fuel injectors are known from the prior art.
  • the publication DE 10 2006 042 601 A1 discloses an injector for injecting fuel into a combustion chamber of an internal combustion engine, in which an injection valve member for releasing or closing at least one injection port is driven by an actuator-operated control valve.
  • a hydraulic coupler unit is arranged, which in the example known from the prior art comprises a first piston operatively connected to the actuator with a first diameter and a second piston with a second, smaller diameter, so that corresponding to the diameter ratio the two pistons of the stroke of the actuator for controlling the control valve is translated hydraulically.
  • Both pistons are guided in a coupler body, which in turn is surrounded by a spring sleeve for axially biasing the first piston relative to the actuator.
  • the second piston is biased axially relative to the control valve via a coil spring which is supported on the coupler body.
  • a arranged between the actuator and the first piston shim serves to compensate for production-related length tolerances.
  • a fuel injector of the type described above has a certain overall construction length due to its complex structure. He may therefore not be used in all internal combustion engines. There is therefore a general interest in reducing the overall construction length of a fuel injector.
  • Object of the present invention is to provide such a length-optimized fuel injector with a hydraulic coupler unit, which is also easy and inexpensive to manufacture.
  • the proposed fuel injector comprises an actuator unit and a hydraulic coupler unit, which communicates via an adjusting piece with the actuator unit.
  • the hydraulic coupler unit comprises an axially displaceably guided and biased by a first spring element valve piston and according to the invention further comprises a coupler sleeve which is biased by a second spring element against the adjusting piece and limits together with the valve piston and the adjusting piece a pressure chamber.
  • the hydraulic coupler unit of the fuel injector according to the invention has only one piston. In the absence of a second piston and a coupler gap formed between the pistons, the pressure space formed between the valve piston, the adjusting piece and the coupler sleeve serves as a hydraulic coupler.
  • the fuel injector according to the invention therefore preferably has one pressure balanced control valve, whose operation is essentially independent of system pressure and thus requires a lower pressure force.
  • the control valve may, for example, be pressure balanced in that the valve closure member of the control valve is guided in a sleeve, wherein valve closure member and sleeve define a pressure chamber, which is always depressurized.
  • a pressure balanced control valve is the subject of another application of the same applicant and should therefore not be further explored in the context of this application.
  • the overall length of the hydraulic coupler unit and thus the total length of the fuel injector according to the invention can be significantly reduced.
  • an extension of the valve piston may be required to compensate for the omitted second piston, but even then length reductions of the coupler unit to about 6.5 mm are possible.
  • a highly accurate guide for example in the form of a coupler body, is dispensed with. This contributes to the simplification of the hydraulic coupler unit and thus to the cost-effective production of the fuel injector.
  • the fuel injector according to the invention can be dispensed with the arrangement of a shim for adjusting the spring force of the spring sleeve and thus to compensate for length tolerances, since on the one hand, the incoming in the spring force tolerances are reduced, on the other hand, the spring force is no longer dependent on tolerances collar heights , As a result, the structure of a fuel injector according to the invention is further simplified and the costs optimized.
  • the coupler gap that is, the pressure space between the coupler sleeve, the adjusting piece and the valve piston, which is provided on the adjusting piece sealingly fitting surface of the coupler sleeve with a biting edge.
  • the required surface pressure is effected by the second spring element, which acts on the coupler sleeve in the axial direction with a compressive force and thus holds in sealing contact with the setting piece.
  • the coupler sleeve on the inner peripheral side has a circumferential radial shoulder, with which the coupler sleeve bears sealingly on the adjusting piece.
  • the radial shoulder is provided with a biting edge.
  • the adjoining the radial shoulder region preferably has an inner diameter which is slightly larger than the outer diameter of the adjusting piece, so that the guided over the adjusting coupler sleeve undergoes a centering.
  • the coupler sleeve has a radially outwardly guided collar for supporting the second spring element, wherein the second spring element is preferably a spring sleeve. While one end of the second spring element is supported on the collar of the coupler sleeve, the other end is preferably located on a valve plate receiving the control valve.
  • the distance between the collar surface and the biting edge of the coupler sleeve is the only measure influencing the spring force of the second spring element. Since the influence is minimal, the adjusting disk already mentioned in connection with the prior art can be omitted for adjusting the spring force. Thus, the complex adjustment process itself is unnecessary. By this measure, not only simplifies the construction of the hydraulic coupler unit, but allows by dispensing with a dial another Reduction in the length of the coupler unit and thus the total length of the fuel injector.
  • the guide gap between coupler sleeve and valve piston is less than 10 microns, preferably less than 5 microns. This ensures a highly accurate guidance of the valve piston via the coupler sleeve. Since the coupler sleeve is preferably designed such that it comprises only a portion of the valve piston, namely the end facing the adjusting piece, further measures can be taken to guide the other, the control valve facing the end of the valve piston.
  • the control valve receiving valve plate may be formed with a serving as a guide collar. However, the formation of the valve plate with a collar requires a higher manufacturing effort. Subsequently, alternative measures are shown.
  • valve piston for example, by the spring force acting in the axial direction of the first spring element, by means of which the valve piston is biased against the closing element of the control valve.
  • first spring element is supported on the one hand on the coupler sleeve, on the other hand on the valve piston.
  • the valve piston is equipped with a collar sleeve, on the radially extending collar surface, the coil spring is supported.
  • the first spring element is a helical spring.
  • the hydraulic coupler unit may comprise a centering sleeve for centering the coupler sleeve and / or the valve piston. If the valve piston experiences centering via the centering sleeve, it also experiences a guide, since the valve piston is preferably arranged to be axially movable relative to the centering sleeve.
  • the centering sleeve can be arranged for example instead of a collar on the upper side of the valve plate.
  • the valve plate can for receiving and fixing the position of the centering, at least in the radial direction, further have a concentric bore into which the centering sleeve is inserted.
  • the centering sleeve extends from the valve plate to the coupler sleeve or beyond, so that primarily the coupler sleeve and indirectly via the coupler sleeve of the valve piston undergoes a centering or guiding.
  • the centering sleeve preferably has on the inner peripheral side a circumferential radial shoulder on which the first spring element is supported. To form such a shoulder, the centering sleeve may for example have sections with different inner diameters.
  • the centering sleeve On the outer circumference side, the centering sleeve preferably has a cylindrical lateral surface.
  • hydraulic coupler unit 3 comprises two guided in a coupler body 20 piston, a valve piston 7 having a first diameter D 1 and a Coupler piston 22 having a second diameter D 2 , wherein D 1 ⁇ D 2 , so that according to the diameter ratio, a translation of the force and the stroke of an actuator 1 via a formed between the two pistons 7, 22 coupler gap 23, which is provided with a hydraulic fluid is filled.
  • the coupler body 20 serves to guide the two pistons 7, 22 and is therefore adapted to the inner circumference of the respective piston diameters. With a radially extending collar surface of the coupler body rests against a valve plate 16, in which a control valve 2 is received.
  • the valve seat facing away end is guided in a sleeve 19 and limited together with the sleeve 19 and the valve plate 16, a low-pressure space 24, so that guided in the sleeve 19 portion of the closing element 6 of the control valve 2 is not acted upon by the system pressure.
  • a compressive force is required, which essentially corresponds to the spring force of a helical spring 18, by means of which the closing element 6 is biased relative to the valve seat 25.
  • the coil spring 18 is supported on the one hand on the sleeve 19, on the other hand on a spring collar 17 of the closing element 6.
  • the valve piston 7 is also biased by a coil spring against the closing element 6.
  • the helical spring is for this purpose supported on the valve piston 7 and on an inner peripheral side radially extending shoulder of the coupler body.
  • a second spring element 9 is provided in the form of a spring sleeve, by means of which the coupler piston 22 is biased against an adjusting piece 4 and thus relative to the actuator unit 1.
  • the spring sleeve is supported on the one hand on a radially extending collar surface of the coupler body 20, on the other hand on a shim 21, which in turn rests against a circumferential radial collar surface of the coupler piston 22.
  • the shim 21 serves to adjust the spring force since the different collar heights of the coupler body 20 and the coupler piston 22 are subject to tolerances.
  • the hydraulic coupler unit 3 of a fuel injector according to the invention has only one valve piston 7 (see FIG Fig. 2 and 3 ).
  • the arrangement of a second piston 22 and a coupler body 20 according to the example described above is deliberately omitted.
  • the translation is thus in the ratio 1: 1.
  • the control valve 2 is in turn pressure balanced, because the closing member 6 of the control valve 2 is guided in a sleeve 19, which define a low-pressure space 24 together with the valve plate 16, an amplification of the actuator force or deshubes is not required.
  • a coupler gap 23 is now formed between a valve piston 7 and 4 setting piece pressure chamber 10 which is bounded radially by a coupler sleeve 8.
  • the valve piston 7 is movably guided.
  • the guide gap 13 is designed with only a small clearance and in the present example is about 4 ⁇ m.
  • the coupler sleeve 8 is further provided with a biting edge with which the coupler sleeve 8 rests sealingly on the adjusting piece 4.
  • the necessary surface pressure is effected by a second spring element 9, by means of which the coupler sleeve 8 is biased against the adjusting piece 4.
  • the second spring element 9 is also in this example a spring sleeve which is supported on the one hand directly to the valve plate 16, on the other hand to the coupler sleeve 8.
  • the coupler sleeve 8 has for this purpose a collar 12 with a radially extending collar surface. The distance between this collar surface and the adjoining adjoining 4 biting edge is the only tolerant degree that affects the spring force. Since the influence is minimal, a dial 21 has also been dispensed with in the case of the hydraulic coupler unit 3 according to the invention. By waiving one Second piston 22 and a shim 21, the length of the coupler unit 3 according to the embodiment of Fig. 2 by 4.5 mm compared to the known design accordingly Fig. 1 be shortened.
  • the hydraulic coupler unit 3 of the Fig. 2 a centering sleeve 14 for centering the coupler sleeve 8 and thus indirectly for centering and guiding the valve piston 7.
  • the hydraulic coupler unit 3 of the Fig. 1 also has the centering sleeve 14 of the hydraulic coupler unit 3 of Fig. 2 an inner peripheral side radially extending shoulder 15, on which one end of the first spring element 5 is supported, by means of which the valve piston 7 is biased against the closing element 6 of the control valve 2.
  • a further centering of the coupler sleeve 8 and thus indirectly also of the valve piston 7 takes place in that the adjusting piece 4 is at least partially embedded in an inner peripheral side recess of the coupler sleeve so that it rests against an inner peripheral side radially extending shoulder 11 of the coupler sleeve 8.
  • the centering sleeve can also be reduced to an annular body, which surrounds only the valve piston 7 in the region of the valve plate 16 and this centered as a result or leads.
  • the first spring element 5 has an axial position, so that it is supported on one side on the coupler sleeve 8.
  • the embodiment differs Fig. 3 not from the Fig. 2 , However, the reduction of the centering sleeve 14 allows an applied to the valve piston 7 annular body a reduction in length of the coupler unit 3 of up to 6.5 mm.
  • valve plate 16 can also be equipped with a collar or shoulder which allows axial guidance of the valve piston 7.

Landscapes

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

Claims (8)

  1. Injecteur de carburant pour injecter du carburant dans une chambre de combustion d'un moteur à combustion interne, comprenant une unité d'actionneur (1) pour l'actionnement d'une soupape de commande (2) et comprenant une unité d'accouplement hydraulique (3) qui est en liaison avec l'unité d'actionneur (1) par l'intermédiaire d'une pièce de réglage (4) et qui comporte un piston de soupape (7) guidé de manière axialement coulissante et précontraint contre un élément de fermeture (6) de la soupape de commande (2) au moyen d'un premier élément ressort (5),
    caractérisé en ce que
    l'unité d'accouplement hydraulique (3) comporte en outre une douille d'accouplement (8) qui est précontrainte contre la pièce de réglage (4) au moyen d'un deuxième élément ressort (9) et qui, conjointement avec le piston de soupape (7) et la pièce de réglage (4), délimite une chambre de pression (10).
  2. Injecteur de carburant selon la revendication 1, caractérisé en ce que la surface de la douille d'accouplement (8) qui s'applique de manière étanche contre la pièce de réglage (4) est pourvue d'une arête d'attaque.
  3. Injecteur de carburant selon la revendication 1 ou 2, caractérisé en ce que la douille d'accouplement (8) possède du côté de la périphérie intérieure un épaulement radial périphérique (11) pour recevoir partiellement la pièce de réglage (4), par l'intermédiaire duquel épaulement la douille d'accouplement s'applique contre la pièce de réglage.
  4. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que la douille d'accouplement (8) possède un rebord (12) guidé radialement vers l'extérieur pour l'appui du deuxième élément ressort (9), le deuxième élément ressort étant de préférence une douille élastique.
  5. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que l'interstice de guidage (13) entre la douille d'accouplement (8) et le piston de soupape (7) vaut moins de 10 µm, de préférence moins de 5 µm.
  6. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier élément ressort (5) s'appuie d'une part contre la douille d'accouplement (8) et s'appuie d'autre part contre le piston de soupape (7), le premier élément ressort étant de préférence un ressort hélicoïdal.
  7. Injecteur de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité d'accouplement hydraulique (3) comporte en outre une douille de centrage (14) pour le centrage de la douille d'accouplement (8) et/ou du piston de soupape (7).
  8. Injecteur de carburant selon la revendication 7, caractérisé en ce que la douille de centrage (14) possède du côté de la périphérie intérieure un épaulement radial périphérique (15) contre lequel s'appuie le premier élément ressort (5), le premier élément ressort étant de préférence un ressort hélicoïdal.
EP20090180310 2009-02-16 2009-12-22 Injecteur de carburant Not-in-force EP2218906B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910000875 DE102009000875A1 (de) 2009-02-16 2009-02-16 Kraftstoffinjektor

Publications (2)

Publication Number Publication Date
EP2218906A1 EP2218906A1 (fr) 2010-08-18
EP2218906B1 true EP2218906B1 (fr) 2013-02-20

Family

ID=41718754

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20090180310 Not-in-force EP2218906B1 (fr) 2009-02-16 2009-12-22 Injecteur de carburant

Country Status (2)

Country Link
EP (1) EP2218906B1 (fr)
DE (1) DE102009000875A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010043360A1 (de) * 2010-11-04 2012-05-10 Robert Bosch Gmbh Kraftstoffinjektor
DE102014226673A1 (de) * 2014-12-19 2016-06-23 Robert Bosch Gmbh Hydraulische Kopplereinheit zur Steuerung eines Ventils

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004044812A1 (de) * 2004-09-16 2006-03-23 Robert Bosch Gmbh Steuerventil einer Einspritzdüse für eine Brennkraftmaschine
DE102006042601A1 (de) 2006-09-11 2008-03-27 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff
DE102006049533A1 (de) * 2006-10-20 2008-04-24 Robert Bosch Gmbh Steuerventil für einen Injektor und Injektor

Also Published As

Publication number Publication date
EP2218906A1 (fr) 2010-08-18
DE102009000875A1 (de) 2010-08-19

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