EP1637727A1 - Soupape de contrôle pour un injecteur - Google Patents

Soupape de contrôle pour un injecteur Download PDF

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Publication number
EP1637727A1
EP1637727A1 EP05106592A EP05106592A EP1637727A1 EP 1637727 A1 EP1637727 A1 EP 1637727A1 EP 05106592 A EP05106592 A EP 05106592A EP 05106592 A EP05106592 A EP 05106592A EP 1637727 A1 EP1637727 A1 EP 1637727A1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
control valve
actuator
valve
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.)
Granted
Application number
EP05106592A
Other languages
German (de)
English (en)
Other versions
EP1637727B1 (fr
Inventor
Friedrich Boecking
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 EP1637727A1 publication Critical patent/EP1637727A1/fr
Application granted granted Critical
Publication of EP1637727B1 publication Critical patent/EP1637727B1/fr
Expired - Fee Related 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
    • 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
    • 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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve

Definitions

  • the present invention relates to a control valve for an injector of a fuel injection system of an internal combustion engine, in particular in a motor vehicle.
  • an injector which contains a nozzle needle for controlling the injection of fuel through at least one injection hole.
  • the nozzle needle can be acted upon in a control chamber with a pressure acting in the closing direction. By the pressure prevailing in the control room pressure, the nozzle needle can be controlled.
  • the at least one spray hole communicates with an outlet pressure chamber of a hydraulic pressure booster.
  • a high-pressure fuel which is provided via a common supply line (so-called "common rail system").
  • the output pressure chamber is limited by a booster piston with a comparatively small output pressure surface.
  • the booster piston On a side facing away from the outlet pressure chamber side, the booster piston also has a comparatively large input pressure surface which limits an inlet pressure chamber.
  • the inlet pressure chamber is connected to the supply line, so that there is high pressure in the inlet pressure chamber. Due to the area ratio between input pressure surface and output pressure surface, there is an increase in pressure in the outlet pressure chamber, as long as the booster piston can move.
  • this is also equipped with a control surface that limits a control room. The control surface is dimensioned so that the booster piston is biased to its initial position when in the control room of high fuel pressure prevails.
  • the booster piston is thus controlled by the pressure prevailing in the control chamber.
  • both the control chamber of the nozzle needle and the control chamber of the pressure booster are now connected via a high-pressure line to the supply line.
  • a control valve of the type mentioned is arranged therein.
  • the control valve according to the invention with the features of claim 1 has the advantage that with the aid of the translator provided in the control valve, the stroke of an actuator for driving a valve member can be over or stocked, allowing extremely short positioning times for the valve member.
  • a nozzle needle arranged downstream of the control valve or a pressure translator arranged downstream of the control valve can be controlled with a high degree of dynamics. This allows the execution of precise injection operations.
  • the translator is arranged in a high-pressure chamber which communicates with the high-pressure line or through which the high-pressure line is led. In this way, the translator "floats" in the high pressure, so that in the translator's the risk of leaks is reduced.
  • a particularly compact construction can be achieved for the translator and thus for the entire control valve in that the translator has an actuator piston connected to the actuator and a valve piston drivingly connected to the valve piston, wherein the actuator piston and valve piston are arranged coaxially with one another. Due to the compact design of the translator and thus the control valve can This can be easily installed in an injector, which is also equipped with a hydraulic pressure booster.
  • a control valve 1 according to the invention in an only partially indicated valve body 2 includes an actuator 3, which may be preferably designed as a piezoelectric actuator.
  • the control valve 1 is used to control a high pressure line 4, by means of which in an otherwise not shown injector of a fuel injection system of an internal combustion engine, in particular in a motor vehicle, at least one nozzle needle and / or a hydraulic pressure booster can be controlled.
  • the control valve 1 includes for controlling the high pressure line 4, a valve member 5 which cooperates in a first switching position shown here with a first valve seat 6 and thereby separates a high pressure input 7 of the control valve 1 from a high pressure outlet 8 of the control valve 1.
  • the first switching position forms an end position of the valve member 5.
  • the valve member 5 can also be converted into a second switching position, in which the high pressure input 7 is connected to the high pressure outlet 8. Since the high pressure line 4 via the high pressure inlet 7 and the high pressure outlet. 8 is passed through the control valve 1, the high-pressure line 4 can be controlled by means of the valve member 5.
  • the control valve 1 also includes a hydraulically operated translator 9, which is arranged substantially completely in a high-pressure chamber 10.
  • This high-pressure chamber 10 communicates with the high-pressure line 4.
  • the high-pressure chamber 10 is connected to the high-pressure line 4.
  • the high pressure line 4 is passed through the high pressure space 10.
  • the translator 9 is drive connected to the input side of the actuator 3 and the output side with the valve member 5. In this way, the translator 9 can translate or reduce an input-side axial Aktorhub generated by the actuator 3 in an output-side valve. Preferably, it is reduced, that is, the output-side valve lift is greater than the intake-side Aktorhub. In this way, a relatively small actuating movement of the actuator 3 can be converted into a larger adjusting movement of the valve member 5.
  • the control valve 1 preferably also has a low-pressure outlet 11, which is connected to a comparatively pressure-free return 12.
  • the return 12 prevails within an injection system system pressure, which is small compared to the pressure prevailing in the high-pressure line 4 high pressure.
  • the low-pressure outlet 11 is separated from the high-pressure inlet 7 and connected to the high-pressure outlet 8 for this purpose.
  • a section 4 "of the high-pressure line 4 arranged downstream of the high-pressure outlet 8 communicates with the return 12 in the first switching position of the valve element 5, so that the relatively low system pressure of the return line 12 prevails in this section 4".
  • the translator 9 comprises an actuator piston 14 and a valve piston 15, which are arranged coaxially with one another and axially adjustable to each other. While the actuator piston 14 is drivingly connected to the actuator 3, the valve piston 15 is drivingly connected to the valve member 5. For example, the actuator piston 14 is welded to the actuator 3, while the valve piston 15 may be made in one piece with the valve member 5.
  • the actuator piston 14 is arranged on the outside, while the valve piston 15 is arranged in each case inside.
  • the valve piston 15 is arranged on the outside, so that there the actuator piston 14 is arranged inside.
  • a first booster chamber 16 is formed in the interior of the externally arranged actuator piston 14, which is axially limited by the valve piston 15 arranged in the interior in the stroke direction.
  • a wall 17 delimits the high-pressure chamber 10.
  • the valve piston 15 is guided through this wall 17.
  • the internally arranged valve piston 15 is enclosed or enveloped axially between the actuator piston 14 and said wall 17 by an annular second translator chamber 18.
  • the second booster chamber 18 is bounded radially on the outside by a sleeve 19, which thus separates the second booster chamber 18 from the high-pressure chamber 10.
  • Said sleeve 19 is axially movably mounted on the actuator piston 14 disposed on the outside and biased axially against the wall 17 by means of a spring 20.
  • the spring 20 is supported axially on the sleeve 19 and on the actuator piston 14 and the actuator 3 from.
  • the two translator rooms 16 and 18 are communicatively connected to each other. This can be realized, for example, via a corresponding radial clearance between the actuator piston 14 and the valve piston 15 or by at least one longitudinal groove on the outside of the valve piston 15 and / or inside of the actuator piston 14.
  • the communicating connection between the booster chambers 16 and 18 is realized thereby in that the internally arranged valve piston 15 contains at least one bore 21 which connects the two booster chambers 16, 18 to one another.
  • the control valve 1 according to FIG. 1 operates as follows:
  • the valve member 5 In an initial position, the valve member 5 is in its second switching position in which the low-pressure outlet 11 is blocked and the high-pressure inlet 7 is connected to the high-pressure outlet 8. Consequently, the high pressure line 4 has high pressure in the portion 4 "located downstream of the control valve 1. Since the control valve 1 serves to control at least one nozzle needle and / or to control a hydraulic pressure booster, the high pressure line 4 is downstream of the control valve 1 to a control space of the nozzle needle In the second switching position, therefore, the high pressure also prevails in the respective control chamber To open the nozzle needle and, if necessary, to activate the pressure booster, the pressure in the respective control chamber must be lowered.
  • the actuator 3 can drive the actuator piston 14 to carry out an actuator stroke, in which the actuator piston 14 moves away from the wall 17.
  • the pressure reduction in the first booster chamber 16 finally leads to a valve lift of the valve piston 15, in which the valve piston 15 follows the actuator piston 14.
  • valve member 5 The adjustment movement of the valve member 5 from the second switching position to the first switching position and the holding of the valve member 5 in the first switching position is thereby supported by the system pressure of the return 12, which drives the valve member 5 in the direction of the actuator piston 14.
  • the switching of the control valve 1 in the second switching position is effected by a corresponding actuation of the actuator 3, which adjusts the actuator piston 14 in the direction of the wall 17.
  • the valve piston 15 and thus the valve member 5 are hydraulically translated or reduced in the second switching position.
  • control valve 1 downstream nozzle needle or the downstream pressure booster is controlled by means of a pressure reduction in the respective control chamber for initiating an injection process.
  • other injection systems or other injectors are known in which the initiation of the injection process can be controlled by an increase in pressure in the respective control chamber of the nozzle needle and the pressure booster. It is clear that in such an embodiment, the control valve 1 shown here can also be used.
  • the embodiment according to FIG. 2 differs from that according to FIG. 1 inter alia in that here the valve piston 15 is arranged on the outside, while the actuator piston 14 is arranged inside.
  • the position of the second booster chamber 18, which according to FIG. 2 is arranged on a wall 17 'opposite the valve piston 15 and penetrated by the actuator piston 14, is also changed. Consequently, here the sleeve 19 is mounted on the valve piston 15.
  • the high-pressure line 4 is passed through the high-pressure chamber 10.
  • a special feature here is the design of the valve member 5, which is assembled from several components.
  • the valve member 5 comprises a central pin 22 which is fixedly connected to the valve piston 15 in a suitable manner or made in one piece therewith and to which a valve sleeve 23 is attached and fixed by means of a nut 24.
  • Figs. 3 and 4 differ from those of Figs. 1 and 2 in that there are no two different translator spaces 16 and 18. Instead, a common translator room 25 is provided.
  • this booster chamber 25 is arranged axially between the actuator piston 14 arranged on the outside and the wall 17 opposite the actuator piston 14, wherein the booster chamber 25 also circumferentially surrounds the internally arranged valve piston 15 radially outward.
  • the common booster chamber 25 is radially bounded by the sleeve 19 which is mounted in a stroke-adjustable manner on the actuator piston 14.
  • the internally arranged valve piston 15 is equipped with a pressure stage 26 which limits the booster chamber 25 with respect to the wall 17. This pressure step 26 is arranged next to an end wall 27 of the axial end face 27 of the externally arranged actuator piston 14.
  • a stroke adjustment of the actuator piston 14 in the direction of the valve piston 15 thus leads to a pressure increase in the booster chamber 25, which drives the valve piston 15 in the direction of the actuator piston 14 via the pressure stage 26.
  • an actuator stroke which removes the actuator piston 14 from the valve piston 15, leads to a reduction in pressure in the booster chamber 25, whereby the valve piston 15 is additionally driven via the pressure stage 26 in such a way that it moves away from the actuator piston 14.
  • the valve member 5 can be switched between its switching positions, which respectively represent end positions of the valve member 5, particularly quickly and easily.
  • the translator 9 In contrast to the embodiments of Figs. 1 and 2, the translator 9 generates in the embodiments of Figs. 3 and 4, a reversal of direction of movement, while in the embodiments of Figs. 1 and 2, the direction of movement remains the same. That is, a Aktorhub to the right leads in the embodiments of FIGS. 1 and 2 to a correspondingly over- or under-staggered valve also to the right, while in the embodiments of Figs. 3 and 4 to a correspondingly over- or under-staggered valve leads to the left.
  • the actuator 4 designed as a piezoactuator by way of example, can thus be energized for setting the first switching position or for setting the second switching position.
  • a cylinder space 28 is formed in the interior of the externally arranged piston, that is to say in FIG. 3 of the actuator piston 14 and in FIG. 4 of the valve piston 15, in which the piston 15 (FIG ) or 14 (FIG. 4) is mounted.
  • a return spring 29 is also housed, which is axially supported on both nested pistons 14, 15 and pushes them away from each other.
  • the cylinder chamber 28 is connected in a suitable manner to the return 12, z. B. by means of a leakage line 30, which is indicated by way of example in Fig. 4 and is guided, for example, through the valve piston 15 and through the valve member 5 through to the low-pressure outlet 11.
  • a leakage line 30 which is indicated by way of example in Fig. 4 and is guided, for example, through the valve piston 15 and through the valve member 5 through to the low-pressure outlet 11.
  • the embodiment shown in FIG. 4 differs from that according to FIG. 3 inter alia in that in the embodiment according to FIG. 3 the high-pressure line 4 is passed through the high-pressure space 10, while in the embodiment according to FIG. 4 the high-pressure space 10 adjoins the high-pressure space 10 High pressure line 4 is connected. While in the variant according to FIG. 3 the actuator piston 14 is arranged on the outside and the valve piston 15 on the inside, in the embodiment according to FIG. 4 the actuator piston 14 is arranged on the inside and the valve piston 15 on the outside.
  • the sleeve 19 is provided with an annular sealing edge 31 on that axial end face, with which it cooperates with the associated wall 17 or 17 '.
  • a sealing edge 31 improves the achievable sealing effect.
  • the sealing edge 31 is arranged in each case on a radially inner edge of the end face of the sleeve 19. In this way, the sleeve 19 is hydraulically seen in the axial direction, almost in equilibrium, since the pressure forces acting axially on it can substantially cancel. The bias of the sleeve 19 is thus almost exclusively by the spring force of the spring 20.

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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)
EP20050106592 2004-09-15 2005-07-19 Soupape de contrôle pour un injecteur Expired - Fee Related EP1637727B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200410044462 DE102004044462A1 (de) 2004-09-15 2004-09-15 Steuerventil für einen Injektor

Publications (2)

Publication Number Publication Date
EP1637727A1 true EP1637727A1 (fr) 2006-03-22
EP1637727B1 EP1637727B1 (fr) 2009-07-08

Family

ID=35159860

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050106592 Expired - Fee Related EP1637727B1 (fr) 2004-09-15 2005-07-19 Soupape de contrôle pour un injecteur

Country Status (3)

Country Link
EP (1) EP1637727B1 (fr)
JP (1) JP2006083863A (fr)
DE (2) DE102004044462A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150211456A1 (en) * 2012-07-13 2015-07-30 Continental Automotive Gmbh Fluid Injector
WO2016074888A1 (fr) * 2014-11-11 2016-05-19 Delphi International Operations Luxembourg S.À R.L. Dispositif de réglage de jeu hydraulique disposé dans un servo-injecteur
US9855591B2 (en) 2012-07-13 2018-01-02 Continental Automotive Gmbh Method for producing a solid actuator

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19951004A1 (de) * 1999-10-22 2001-04-26 Bosch Gmbh Robert Hydraulische Steuervorrichtung, insbesondere für einen Injektor
US6240905B1 (en) * 1998-08-06 2001-06-05 Robert Bosch Gmbh Unit fuel injector
DE10218904A1 (de) 2001-05-17 2002-12-05 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung
WO2005010342A1 (fr) * 2003-07-24 2005-02-03 Robert Bosch Gmbh Dispositif d'injection de carburant
WO2005068820A1 (fr) * 2004-01-16 2005-07-28 Robert Bosch Gmbh Injecteur de carburant a commande de pointeau directe
WO2005075811A1 (fr) * 2004-02-04 2005-08-18 Robert Bosch Gmbh Injecteur de carburant avec obturateur d'injection a commande directe

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6240905B1 (en) * 1998-08-06 2001-06-05 Robert Bosch Gmbh Unit fuel injector
DE19951004A1 (de) * 1999-10-22 2001-04-26 Bosch Gmbh Robert Hydraulische Steuervorrichtung, insbesondere für einen Injektor
DE10218904A1 (de) 2001-05-17 2002-12-05 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung
WO2005010342A1 (fr) * 2003-07-24 2005-02-03 Robert Bosch Gmbh Dispositif d'injection de carburant
WO2005068820A1 (fr) * 2004-01-16 2005-07-28 Robert Bosch Gmbh Injecteur de carburant a commande de pointeau directe
WO2005075811A1 (fr) * 2004-02-04 2005-08-18 Robert Bosch Gmbh Injecteur de carburant avec obturateur d'injection a commande directe

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150211456A1 (en) * 2012-07-13 2015-07-30 Continental Automotive Gmbh Fluid Injector
US9856843B2 (en) * 2012-07-13 2018-01-02 Continental Automotive Gmbh Fluid injector
US9855591B2 (en) 2012-07-13 2018-01-02 Continental Automotive Gmbh Method for producing a solid actuator
WO2016074888A1 (fr) * 2014-11-11 2016-05-19 Delphi International Operations Luxembourg S.À R.L. Dispositif de réglage de jeu hydraulique disposé dans un servo-injecteur

Also Published As

Publication number Publication date
EP1637727B1 (fr) 2009-07-08
DE102004044462A1 (de) 2006-03-30
DE502005007651D1 (de) 2009-08-20
JP2006083863A (ja) 2006-03-30

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