EP3184802B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP3184802B1
EP3184802B1 EP16197773.1A EP16197773A EP3184802B1 EP 3184802 B1 EP3184802 B1 EP 3184802B1 EP 16197773 A EP16197773 A EP 16197773A EP 3184802 B1 EP3184802 B1 EP 3184802B1
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EP
European Patent Office
Prior art keywords
coupler
sleeve
fuel injector
piston
fuel
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.)
Active
Application number
EP16197773.1A
Other languages
German (de)
English (en)
Other versions
EP3184802A1 (fr
Inventor
Andreas Rau
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3184802A1 publication Critical patent/EP3184802A1/fr
Application granted granted Critical
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Active legal-status Critical Current
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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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion

Definitions

  • the invention relates to a fuel injector of a fuel injection system of an internal combustion engine, wherein the fuel injector comprises a hydraulic coupler having a movable in a coupler body coupler piston and a coupled thereto via a coupler gap also movable in the coupler body working piston, and wherein the coupler gap via at least one filling channel with a is connected outside the coupler body arranged low pressure space.
  • Such a fuel injector is from the DE 10 2009 001 266 A1 known.
  • This fuel injector of a common rail fuel injection system has a hydraulic coupler which has a coupler piston movable in a coupler body and a piston which is also coupled to it in the coupler body via a coupler gap.
  • the coupler gap is connected via a filling channel with a arranged outside the coupler body low pressure space.
  • This filling channel is arranged in the coupler body, that the filling channel is closed during a downward movement of the coupler piston, while the filling channel is opened during an upward movement of the coupler piston.
  • a fuel injection device with a hydraulic coupler wherein the filling of the filling space via a connecting line, in which a check valve may be arranged.
  • the invention has for its object to provide a fuel injector with a coupler, wherein the filling of the coupler gap space is improved with hydraulic fluid.
  • This object is achieved in that in the region of a connection of the filling channel with the Kopplerspaltraum a one-piece, non-deformable and switching by a change in position valve is arranged, which is designed as a sleeve or disc.
  • This embodiment is based on the finding that with each switching operation in the coupler, a significantly higher pressure than in the surrounding low-pressure space arises. This results in the games on the piston guides of the coupler piston and the working piston in the coupler body to a leakage from the coupler, more precisely from the Kopplerspaltraum out.
  • a hydraulic coupler has a speed limit, with which it can be operated at a required number of injections in dependence on the pressure of the fuel.
  • the inventive design of the coupler a significantly improved refilling is achieved, which significantly improves the speed resistance of the coupler.
  • the valve is designed as a sleeve.
  • a sleeve is easy to manufacture and also has a high closing accuracy of the filling channel.
  • the outer diameter of the sleeve or the disk is slightly smaller than the inner diameter of the coupler body in the region of the mouth of the filling channel in the coupler gap. Due to this slightly smaller outer diameter of the sleeve or the disc than the inner diameter of the coupler body that is the sleeve or disc in the case of closing flat against the inner wall of the coupler body in the region of the mouth of the filling channel at a higher pressure in the coupler gap than in the low pressure chamber and seals thus reliable from the filling channel.
  • an actuator of the fuel injector is actuated, a movement of the coupler piston into the coupler gap space results in an immediate buildup of pressure in the coupler, which, as described above, improves the function of the coupler.
  • the valve can - as already stated - be formed as a disc. With such a trained valve, the same advantageous properties are achieved as with the sleeve.
  • the valve designed as a sleeve or disk on the outer circumference on a frustoconical portion which cooperates with a corresponding conical wall portion of the coupler body in the region of the mouth of the filling channel in the coupler gap.
  • the valve for the switching operation is moved axially.
  • This section may extend in a further embodiment over the entire axial extent of the outer circumference of the sleeve or the disc.
  • a channel is also embedded in a development, which connects the two subspaces adjacent to the coupler piston and the working piston with each other.
  • the material of the valve is a metallic material.
  • FIG. 1 shows a fuel injector 1 of a common rail injection system for injecting fuel into a combustion chamber, not shown, of an internal combustion engine.
  • a high-pressure pump 2 conveys fuel from a tank 3 into a high-pressure accumulator 4.
  • fuel in particular diesel fuel
  • the high-pressure accumulator 4 of the fuel injector 1 is connected in addition to other, not shown fuel injectors via a high pressure line 5.
  • the high-pressure line 5 opens into an axial supply channel 6 belonging to a high-pressure region of the fuel injector 1, through which fuel flows into a pressure chamber 7.
  • the fuel flows from the pressure chamber 7 in the axial direction past an injector needle 8 through injection bores 16 into the combustion chamber of the internal combustion engine.
  • the fuel injector 1 is connected via an injector return port 9 to a return line 10.
  • About the return line 10 may be a subsequently explained control amount Flow fuel from the fuel injector 1 to the tank 3 and are fed from there again to the high-pressure circuit.
  • the injector needle 8 is guided axially adjustable within a stepped bore 11 of an injector needle body 12.
  • the Injektornadelraj 12 is clamped in conjunction with a throttle plate and a valve body against a holding body 13 by means of a clamping nut.
  • the Injektornadel 8 has at its needle tip 15 designed as a sealing surface closing surface with which the Injektornadel 8 is adjustable in a tight contact with a trained within the Injektornadel stressess 12 Injektornadelianusitz. If the Injektornadel 8 rests against the Injektornadelianusitz, so is in the closed position, the fuel outlet from the at least one injection hole 16 is locked. By contrast, if the injector needle 8 is lifted off the injector needle body seat, fuel can flow from the pressure chamber 7, which is at least approximately under the pressure of the fuel in the high-pressure accumulator 4, into the combustion chamber.
  • a control chamber 17 is limited, which is supplied via an inlet throttle 18 with fuel under high pressure from the supply channel 6.
  • the pressure chamber 14 encloses a control chamber 17 limiting, spring-loaded sleeve body 32 radially outward.
  • the formed in the sleeve body 32 control chamber 17 is connected via an outlet throttle 19 with a control valve chamber 20 which is connected by means of an axially adjustable control valve element 21 with a low-pressure chamber 22 and thus with the injector return port 9.
  • the control valve element 21 is part of a control valve 23 which is normally designed as a 3/2-way valve.
  • a control valve element 21 located in a first (lower) switching position fuel can flow from the control chamber 17 via the outlet throttle 19 and the control valve chamber 20 to the injector return port 9 in the low-pressure region , At the same time an opening out of the pressure chamber 14 and into the control valve chamber 20 opening bypass 35 of the control valve element 21 locked.
  • a second (upper) switching position befindliches control valve element 21, the connection between the control valve chamber 20 and the low pressure chamber 22 is blocked and the bypass 35 is released, so that the control chamber 17 via the bypass 35, the control valve chamber 20, the outlet throttle 19 and the inlet throttle 18 is quickly brought to high pressure.
  • a piezoelectric actuator 24 is provided, which is coupled via a hydraulic coupler 25 with the control valve element 21.
  • the control valve 23 can be actuated directly by the hydraulic coupler 25, more precisely by a working piston 28 of the hydraulic coupler 25 which will be explained below.
  • the piezoelectric actuator 24 is energized and expands.
  • the working piston 28 presses on the control valve element 21, which is moved away in the sequence counter to the force of a control closing spring 30 from its upper control valve seat 26 and thus releases the flow of fuel from the control chamber 17 to the injector return port while blocking the bypass 35.
  • a control closing spring 30 By adjusting the flow cross-sections of the pressure in the control chamber 17 decreases rapidly, whereby the injector needle 8 lifts from her Injektornadel stresses so that fuel can flow out of the pressure chamber 7 through the injection hole 16.
  • the energization of the piezoelectric actuator 24 is terminated, whereby the piezocrystal stack of the actuator 24 contracts and the coupler piston 27 is supported by the spring force of a Bourdon tube 38 in the drawing plane moves upward.
  • the working piston 28 presses supported by the control closing spring 30 in the plane of the drawing down against the control valve element 21. Between the working piston 28 and the control valve element 21 thus a permanent contact is ensured.
  • the working piston 28 and the control valve element 21 are moved at not energized actuator 24 upwards into the upper switching position in which the control valve element 21 rests against its upper control valve seat 26 and the hydraulic connection from the control chamber 17 to the injector return port 9 blocks.
  • the fuel flowing in through the inlet throttle 18 and via the bypass 35 into the control chamber 17 ensures a rapid pressure increase in the control chamber 17 and a hydraulic closing force acting on the injector needle 8.
  • the resulting closing movement of the Injektornadel 8 is supported by a closing spring 31 which is supported at one end to the Injektornadel 8 and the second end to a control chamber 17 limiting sleeve body 32.
  • FIGS. 2 to 4 show a first embodiment of the coupler 25 with the arranged in a stepped recess 34 in a coupler body 33 coupler piston 27 and working piston 28 in different switching positions.
  • the coupler piston 27 has a larger outer diameter than the working piston 28 and is thus arranged in the stepped recess 34 with the larger inner diameter.
  • the coupler piston 27 may also have a same or smaller diameter than the working piston 28.
  • the coupler piston 27 protrudes with an actuation-side end, on which an actuation plate 36 is arranged, out of the coupler body 33 and cooperates with the actuator 24 by means of the actuation plate 36.
  • the working piston 33 has an actuating nose 37, which - as described above - the control valve element 21 from the control valve seat 26 down ( FIG. 1 ) can press.
  • the coupler 25 has a Bourdon tube 38 which is supported on a lower annular shoulder 39 of the coupler body 33 and the actuator plate 36 and presses apart the two components.
  • a retaining ring for a working piston spring 40 is arranged on the working piston 28, the working piston 28th down from the coupler body 33 until the abutment of the actuating lug 37 presses on the control valve element 21.
  • a filling channel 41 is inserted into the wall of the coupler body 33.
  • the filling channel 41 is closed in the region of an orifice in the coupler gap 29 by a one-piece undeformable valve which opens in the direction of the coupler gap 29 and is switched by a position change in the form of a sleeve 42.
  • the sleeve 42 has a slightly smaller outer diameter than the inner diameter of the coupler body 33 and the step recess 34. Due to the slightly smaller outer diameter of the sleeve 42, the pressure in the coupler gap 29 at rest is at least approximately equal to the pressure in the low pressure chamber 22 and the sleeve 42 is normally in this state the connection between the coupler gap 29 through the filling channel 41 to the low pressure space freely ( FIG. 2 ).
  • the sleeve 42 is arranged in the region of a stepped shoulder 43 of the coupler piston 27, which saves space and has no effect on the function of the coupler 25. With regard to the arrangement of the sleeve 42 but other solutions are conceivable.
  • coupler gap space 29 is only very slightly increased by the exact fit of the sleeve 42, which is why an exact execution of the coupler function is ensured.
  • FIG. 4 the operating state is shown in which in the injection pauses the pressure in the low pressure chamber 22 is greater or higher than in the coupler gap 29, which is why the sleeve 42 is pushed away by the pressure in the filling channel 41 of the inner wall in the region of the stepped recess 34 and the hydraulic Connection between the low-pressure chamber 22 and the coupler gap 29 space is released.
  • the result is a very rapid refilling between injection processes or partial injection processes of the fuel injector 1 with a quasi-constant, non-decreasing coupler function.
  • FIG. 11 which applies to all embodiments of the valve according to the invention, is shown, wherein in the diagram the resulting needle stroke Nh of successive injections of a fuel injector 1 is reproduced.
  • the needle stroke Nh of a conventional coupler 25 is shown with a solid line and the needle stroke Nh of a coupler 25 according to the invention is shown with a dashed line. It can be seen that in the second injection, the needle stroke Nh of the injector needle 8 with the conventional coupler 25 is significantly lower than in the first injection. In contrast, the dashed needle lift Nh, which can be represented by the embodiments according to the invention, shows no degradation.
  • FIGS. 5 to 7 show an embodiment of the valve as a disc 44.
  • the disc 44 performs the same function as the sleeve 42.
  • FIGS. 8 to 10 show an embodiment of the valve as a sleeve 42a or disc 44a, wherein on the outer periphery in the in FIG. 8 a frusto-conical portion 45 is provided, which cooperates with a corresponding conical wall portion 46 of the coupler body 33 in the region of the mouth of the filling channel 41 in the coupler gap space 29.
  • the filling channel 41 is disposed obliquely in the coupler body 33 and terminates in the wall portion 46.
  • the disc 44a and the sleeve 42a is axially moved to close and open the mouth of the filling channel 41.
  • a channel 47 is inserted, which connects the two subspaces adjacent to the coupler piston 27 and the working piston 28 with each other.
  • the portion 45a extends over the entire axial extent of the outer circumference of the sleeve (42a) or the disc (44a).
  • the valve in the embodiment according to FIG. 9 formed as a sleeve 42a and the filling channel 41 has a larger diameter.
  • the filling channel 41 is again arranged at right angles in the coupler body 33.

Landscapes

  • 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 (6)

  1. Injecteur de carburant (1) d'un système d'injection de carburant d'un moteur à combustion interne, l'injecteur de carburant (1) présentant un coupleur hydraulique (25) qui présente un piston de coupleur (27) déplaçable dans un corps de coupleur (33) et un piston de travail (28) accouplé à celui-ci par le biais d'un interstice de coupleur (29), également déplaçable dans le corps de coupleur (33), et l'interstice de coupleur (29) étant raccordé par le biais d'au moins un canal de remplissage (41) à un espace basse pression (22) disposé à l'extérieur du corps de coupleur (33),
    caractérisé en ce que dans la région d'un raccordement du canal de remplissage (41) à l'interstice de coupleur (29) est disposée une soupape monobloc non déformable et commutant par une variation de position, la soupape étant réalisée sous forme de douille (42) ou sous forme de disque (44) et le diamètre extérieur de la douille (42) ou du disque (44) étant seulement légèrement inférieur au diamètre intérieur du corps de coupleur (33) dans la région de l'embouchure du canal de remplissage (41) dans l'interstice de coupleur (29), de sorte qu'un faible débit volumique de carburant s'écoule depuis l'interstice de coupleur (29) à travers le canal de remplissage (41) jusque dans l'espace basse pression (22).
  2. Injecteur de carburant (1) selon la revendication 1,
    caractérisé en ce que la soupape réalisée sous forme de douille (42) est disposée sur un épaulement étagé (43) du piston de coupleur (27).
  3. Injecteur de carburant (1) selon la revendication 1,
    caractérisé en ce que la soupape réalisée sous forme de douille (42a) ou de disque (44a) présente, sur la périphérie extérieure, une portion de forme tronconique (45) qui coopère avec une portion de paroi de forme conique correspondante (46) du corps de coupleur (33) dans la région de l'embouchure du canal de remplissage (41) dans l'interstice de coupleur (29).
  4. Injecteur de carburant (1) selon la revendication 3,
    caractérisé en ce que la portion (45a) s'étend sur toute l'étendue axiale de la périphérie extérieure de la douille (42a) ou du disque (44a).
  5. Injecteur de carburant (1) selon la revendication 1 ou 3,
    caractérisé en ce que le disque (44a) présente un canal axial (47).
  6. Injecteur de carburant (1) selon l'une quelconque des revendications précédentes,
    caractérisé en ce que le matériau de la soupape est un matériau métallique.
EP16197773.1A 2015-12-22 2016-11-08 Injecteur de carburant Active EP3184802B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015226427.0A DE102015226427A1 (de) 2015-12-22 2015-12-22 Kraftstoffinjektor

Publications (2)

Publication Number Publication Date
EP3184802A1 EP3184802A1 (fr) 2017-06-28
EP3184802B1 true EP3184802B1 (fr) 2019-01-09

Family

ID=57256158

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16197773.1A Active EP3184802B1 (fr) 2015-12-22 2016-11-08 Injecteur de carburant

Country Status (2)

Country Link
EP (1) EP3184802B1 (fr)
DE (1) DE102015226427A1 (fr)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10101800A1 (de) * 2001-01-17 2002-07-18 Bosch Gmbh Robert Ventil zum Steuern eines Fluids
DE10333699A1 (de) * 2003-07-24 2005-03-03 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE102009001266A1 (de) 2009-03-02 2010-09-09 Robert Bosch Gmbh Kraftstoff-Injektor mit piezoelektrischem Aktuator sowie hydraulischem Koppler

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
DE102015226427A1 (de) 2017-06-22
EP3184802A1 (fr) 2017-06-28

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