EP1980742B1 - Injecteur de carburant doté d'un amplificateur de pression intégré - Google Patents

Injecteur de carburant doté d'un amplificateur de pression intégré Download PDF

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Publication number
EP1980742B1
EP1980742B1 EP08101824A EP08101824A EP1980742B1 EP 1980742 B1 EP1980742 B1 EP 1980742B1 EP 08101824 A EP08101824 A EP 08101824A EP 08101824 A EP08101824 A EP 08101824A EP 1980742 B1 EP1980742 B1 EP 1980742B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
piston
seat
chamber
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
EP08101824A
Other languages
German (de)
English (en)
Other versions
EP1980742A1 (fr
Inventor
Juergen Frasch
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 EP1980742A1 publication Critical patent/EP1980742A1/fr
Application granted granted Critical
Publication of EP1980742B1 publication Critical patent/EP1980742B1/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
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing

Definitions

  • the invention is based on a fuel injector according to the preamble of claim 1.
  • a fuel injector with an integrated pressure booster is for example out DE 103 35 340 A1 known.
  • the pressure booster has a pressure intensifier piston guided in a housing of the fuel injector, which is exposed to a compression space, a differential pressure chamber and a high-pressure chamber.
  • a first control valve With a first control valve a rear control chamber of a nozzle needle is controlled and derived the control volume in a low pressure / return system.
  • a second control valve also connects the differential pressure chamber of the booster to the low pressure / return system.
  • the second control valve which controls the differential pressure chamber of the pressure intensifier, is a 3/2-way valve with a flat seat / slide seat.
  • a fuel injection valve is known with a pressure booster, wherein the control valve is designed as a direct-switching 3/2-way valve and having both a sealing seat and a slide seal.
  • a control valve for a fuel injector having a valve seat formed by a conical valve seat surface formed on a valve piston is off DE 199 40 300 A1 known.
  • the valve piston with the conical valve seat surface in a pressurized with high pressure valve chamber.
  • the object of the present invention is to provide a control valve whose valve seat holding a control volume of the pressure intensifier is exposed to no or only very little cavitation erosion.
  • the object of the invention is achieved with the characterizing features of claim 1.
  • the fuel injector according to the invention has the advantage that the cavitation erosion is largely prevented at the valve seat switching the control amount of the pressure intensifier.
  • a throttle effect is realized, which decreases with increasing opening movement of the valve piston.
  • This throttling effect acts on the flow conditions at the valve seat, whereby cavitation phenomena are prevented there.
  • the necessary for use in a motor vehicle endurance goals for a fuel injector are achieved.
  • the closing force is expediently generated by a pressure spring arranged in the low-pressure space, which presses the conical sealing surface against the valve piston seat.
  • the valve piston of the second control valve has a first piston section, a second piston section designed with a smaller diameter and a third piston section, wherein the conical sealing surface for the valve piston seat is formed on the third piston section.
  • the diameter of the second valve seat on the valve piston seat and the diameter of the first piston portion, with which the valve piston is guided in the housing substantially same size.
  • the valve seat is closed when the control valve is de-energized.
  • the control valve has an electromagnetic actuator with a plunger armature.
  • FIG. 1 a sectional view through a fuel injector and FIG. 2 an enlarged section X of the second control valve in FIG. 1 ,
  • the in FIG. 1 shown fuel injector has a housing 10 with, for example, a first housing part 11, a second housing part 12, a third housing part 13, a fourth housing part 14 and a connecting part 15 and a nozzle body 16.
  • the nozzle body 16, the housing part 14 and the housing part 13 are clamped hydraulically tight by means of a nozzle lock nut 17.
  • the nozzle body 16 includes an injection valve member 20 having a nozzle needle 21 which is guided axially displaceably in the nozzle body 16.
  • the nozzle needle 21 cooperates with a non-illustrated nozzle nozzle 16 formed on the nozzle needle sealing seat, which separates a nozzle needle pressure chamber 22 in the closed state of the nozzle needle 21 of injection openings 23.
  • a control chamber sleeve 24 is guided, which presses by means of a compression spring 25 against a sealing surface and thereby encloses a control chamber 26.
  • the control chamber 26 is exposed to the nozzle needle 21 with a control surface 27 acting in the closing direction.
  • a high-pressure bore 18 is arranged, which leads into the nozzle needle pressure chamber 22.
  • the housing 10 further comprises, for example, on the housing part 12 a high pressure port 19 with a high pressure supply line 29, with which the fuel injector is connected to a common rail of a diesel injection device.
  • a designed as a stepped piston pressure booster piston 31 for pressure amplification of the system pressure of the common rail is further arranged with a designed as a stepped piston pressure booster piston 31 for pressure amplification of the system pressure of the common rail.
  • the pressure booster piston 31 is exposed to a working space 32, a differential pressure chamber 33 and a compression space 34.
  • the working space 32 and the compression space 34 are connected via a connecting channel 35 with a check valve 36 in connection.
  • the high pressure supply line 29 so that in Working space 32 permanently applied system pressure of the common rail.
  • a return spring 38 is arranged, which the pressure booster piston 31 in the in FIG. 1 resets the initial position shown.
  • the fuel injector further comprises a first control valve 40 designed as a servo valve and a second control valve 50 likewise designed as a servo valve.
  • the first control valve 40 is a 2/2-way valve and comprises a first electromagnetic control element 41, which controls the control chamber by means of a first valve piston 43 26 is controlled by the control chamber 26 is connected to a first low pressure chamber 46 and from there via hydraulic connections 48 to a first return port 49 which is hydraulically in communication with a first low pressure / return system. Via the first return connection 49, the control quantity of the control chamber 26 of the nozzle needle 21 switched by the first control valve 40 is discharged into the first low-pressure / return system.
  • the second control valve 50 is a 3/2-way valve and includes a second electromagnetic actuator 51 with a second valve piston 52.
  • the second valve piston 52 has according to FIG. 2 a first piston portion 52.1 a second piston portion 52.2 and a third piston portion 52.3.
  • the valve piston 52 is guided with the first piston portion 52.1 in a housing part of the housing 10.
  • the electromagnetic actuator 51 comprises a magnetic coil 53 which is enclosed by an upper magnetic disk 53.1 and by a lower magnetic disk 53.2.
  • the valve piston 52 is connected to a magnetic armature 54, wherein the valve piston 52 is guided by the lower magnetic disk 53.2, so that the magnet armature 54 is enclosed by the magnetic coil 53 and thereby forms a so-called plunger armature.
  • the control valve 50 has a first valve seat 55 and a second valve seat 56.
  • the first valve seat 55 is formed by a slide edge 57 formed between the first piston section 52. 1 and the smaller diameter piston section 52. 2, which cooperates with a control edge 58 on the housing side.
  • the second valve seat 56 is formed by a valve piston 52 formed on the conical sealing surface 70 and a housing-side valve piston seat 71, wherein the conical sealing surface 70 between the second piston portion 52.2 and the one larger diameter third piston portion 52.3 runs. As a result, a so-called A-seat is formed.
  • the valve piston 52 is exposed to the slide edge 57 a high pressure chamber 61 and with the conical sealing surface 70 of a valve chamber 62 and a low pressure chamber 63.
  • the valve piston projects with the third piston section 52.3 into the low-pressure space 63.
  • the third piston section 52.3 engages a compression spring 73 arranged in the low-pressure space 63, which is supported on a housing part of the housing 10 and presses the conical sealing surface 70 against the housing-side valve piston seat 71.
  • the high pressure chamber 61 communicates via a high pressure line 64 with the working space 32 of the pressure booster 30 in connection.
  • the valve chamber 62 is connected via a first hydraulic connection 65 to the differential pressure chamber 33 of the pressure booster 30.
  • a second hydraulic connection 66 and a third hydraulic connection 67 lead to a second return connection 69, which communicates with a second low-pressure / return system.
  • the magnet armature 54 is, for example, pressed, welded or peeled with the valve piston 52.
  • a leakage chamber 68 of the second control valve 50 From the first low-pressure chamber 46 of the first control valve 40 lead through the individual housing parts 11, 12, 13, 14 different unspecified further hydraulic connections to a leakage chamber 68 of the second control valve 50.
  • the leakage chamber 68 expands in the second actuator 51 to the second valve piston 52 off.
  • a bypass channel 74 is arranged, so that the two hydraulic chambers are hydraulically connected.
  • the second control valve 50 is placed in the second valve seat 56 in the currentless state of the magnetic actuator 51 of the low pressure chamber 63 from the valve chamber 62 and the acted upon by system pressure high-pressure chamber 61 with the valve chamber 62nd hydraulically connected.
  • the differential pressure chamber 33 also has system pressure.
  • the diameter of the second valve seat 56 on the valve piston seat 71 and the guide diameter of the valve piston 52 in the first piston section 52.1 are expediently the same, so that the second control valve 50 operates pressure-balanced. This has a positive effect on the actuating forces for driving the second control valve 50 by means of the second electromagnetic actuating element 51.
  • the armature 54 When energizing the solenoid 53 of the second control valve 50, the armature 54 is moved in the direction of the lower magnetic disk 53.2, so that the second valve seat 56 opens and at the same time the slide edge 57 closes the first valve seat 55.
  • the valve chamber 62 is hydraulically separated from the high-pressure chamber 61 and at the same time the valve chamber 62 is hydraulically connected to the low-pressure chamber 63.

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 (2)

  1. Injecteur de carburant pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion interne, comprenant un boîtier (10), dans lequel sont disposés un organe de soupape d'injection (20) avec une aiguille de buse (21), un dispositif d'amplification de la pression (30) ainsi qu'au moins une soupape de commande (50), la soupape de commande (50) commandant un espace de pression différentielle (33) du dispositif d'amplification de la pression (30) et présentant un premier siège de soupape (55) et un deuxième siège de soupape (56), un espace haute pression (61) sollicité au moyen du premier siège de soupape (55) avec une pression du système pouvant être séparé d'une chambre de soupape (62) connectée à l'espace de pression différentielle (33), la chambre de soupape (62) pouvant être séparée d'un espace basse pression (63) raccordé à un système de retour/basse pression au moyen du deuxième siège de soupape (56), le deuxième siège de soupape (56) présentant une surface d'étanchéité conique (70) réalisée sur le piston de soupape (52), le piston de soupape (52) présentant une première portion de piston (52.1), une deuxième portion de piston (52.2) réalisée avec un plus petit diamètre et une troisième portion de piston (52.3), la surface d'étanchéité conique (70) étant réalisée sur la troisième portion de piston (52.3) pour un siège de piston de soupape (71), et le piston de soupape (52) pénétrant avec la troisième portion de piston (52.3) dans l'espace basse pression (63) connecté au système de retour/basse pression, et la surface d'étanchéité conique (70) pressant depuis l'espace basse pression (63) contre un siège de piston de soupape (71) du côté du boîtier, caractérisé en ce que le diamètre du deuxième siège de soupape (56) sur le siège de piston de soupape (71) et le diamètre de la première portion de piston (52.1), avec laquelle le piston de soupape (52) est guidé dans le boîtier (10), sont essentiellement identiques, de sorte qu'une soupape de commande équilibrée en pression (50) soit réalisée, la soupape de commande (50) présentant un actionneur électromagnétique (51) avec un noyau plongeur (54) et le deuxième siège de soupape (56) étant fermé dans l'état non alimenté en courant de la soupape de commande (50).
  2. Injecteur de carburant selon la revendication 1, caractérisé en ce qu'un ressort de pression (73) est disposé dans l'espace basse pression (63), lequel produit la force de fermeture pour la surface d'étanchéité conique (70) avec le siège de piston de soupape (71).
EP08101824A 2007-04-13 2008-02-21 Injecteur de carburant doté d'un amplificateur de pression intégré Not-in-force EP1980742B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007018040A DE102007018040A1 (de) 2007-04-13 2007-04-13 Kraftstoffinjektor mit integriertem Druckverstärker

Publications (2)

Publication Number Publication Date
EP1980742A1 EP1980742A1 (fr) 2008-10-15
EP1980742B1 true EP1980742B1 (fr) 2011-07-27

Family

ID=39643195

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08101824A Not-in-force EP1980742B1 (fr) 2007-04-13 2008-02-21 Injecteur de carburant doté d'un amplificateur de pression intégré

Country Status (3)

Country Link
EP (1) EP1980742B1 (fr)
AT (1) ATE518057T1 (fr)
DE (1) DE102007018040A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008002474A1 (de) 2008-06-17 2009-12-24 Robert Bosch Gmbh Ventilsitz für Kraftstoffinjektor
DE102011004640A1 (de) * 2011-02-24 2012-08-30 Robert Bosch Gmbh Steuerventil für einen Kraftstoffinjektor sowie Kraftstoffinjektor

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19940300A1 (de) 1999-08-25 2001-03-01 Bosch Gmbh Robert Steuerventil für einen Injektor
DE10315016A1 (de) * 2003-04-02 2004-10-28 Robert Bosch Gmbh Kraftstoffinjektor mit leckagefreiem Servoventil
DE10334771A1 (de) 2003-07-30 2005-02-24 Robert Bosch Gmbh Schaltventil mit Druckausgleich für einen Kraftstoffinjektor mit Druckverstärker
DE10335340A1 (de) 2003-08-01 2005-02-24 Robert Bosch Gmbh Steuerventil für einen Druckübersetzer enthaltenden Kraftstoffinjektor
JP4286770B2 (ja) 2004-12-02 2009-07-01 株式会社日本自動車部品総合研究所 制御弁およびそれを備えた燃料噴射弁

Also Published As

Publication number Publication date
ATE518057T1 (de) 2011-08-15
EP1980742A1 (fr) 2008-10-15
DE102007018040A1 (de) 2008-10-16

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