WO2001096732A1 - Vanne de commande de liquides - Google Patents

Vanne de commande de liquides Download PDF

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Publication number
WO2001096732A1
WO2001096732A1 PCT/DE2001/001327 DE0101327W WO0196732A1 WO 2001096732 A1 WO2001096732 A1 WO 2001096732A1 DE 0101327 W DE0101327 W DE 0101327W WO 0196732 A1 WO0196732 A1 WO 0196732A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
piston
spring
spring element
controlling liquids
Prior art date
Application number
PCT/DE2001/001327
Other languages
German (de)
English (en)
Inventor
Wolfgang Stoecklein
Dietmar Schmieder
Friedrich Boecking
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 WO2001096732A1 publication Critical patent/WO2001096732A1/fr

Links

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

Definitions

  • the present invention relates to a valve for controlling liquids according to the preamble of patent claim 1.
  • Valves for controlling liquids are known in a wide variety of configurations.
  • a valve 1 for controlling liquids is shown in FIG. 2, which has a hydraulic intensifier 2, which has a first piston 3, a second piston 4, and a pressure chamber 5 arranged between the two pistons 3, 4.
  • the first piston 3 can be actuated via an actuating piston 10 by a piezo element (not shown).
  • the second piston 4 is connected via a tappet 9 to a valve ball 6 which is pressed against a valve seat 7 by means of a spring 8.
  • the piezo actuator is actuated, the valve ball is moved via the hydraulic intensifier 2 and the plunger 9
  • valve seat 7 thereby providing a pressure increase in an injection region of a valve needle in order to lift the valve needle from an injection opening and to supply fuel into a combustion chamber (not shown).
  • the ball 6 pressed against the upper valve seat 7 by the spring force of the spring 8, and remains in this position until the engine is restarted. Since, as shown in FIG. 2, a volume 11 in the region of the valve ball 6 is relatively large due to the position of the valve ball 6 on the upper valve seat 7, the function of the injector is partially restricted, since certain delays occur during actuation. In order to provide a small volume 11, unfavorable spring designs have to be used, which have a complicated structure and lead to increased costs.
  • valve ball 6 must be designed with a spring seat 18 in its lower region. This also increases the manufacturing costs. Since the spring 8 is arranged in the high-pressure region of the valve 1, it is also constantly exposed to high pressure loads, which can lead to a reduced service life of the spring 8.
  • valve according to the invention for controlling liquids with the features of claim 1 has the advantage that the spring element is directly coupled to the second piston of the hydraulic translator. In other words, the spring element is arranged directly on the second piston. This allows the valve member
  • Valve closing element are arranged spaced from the spring element. This separation of the spring element from the valve member makes it possible to provide a very small volume in the region of the valve member without complex structural measures. Furthermore, the valve member can also be produced simply and inexpensively, since it does not have to have receptacles or spring seats for the spring element that are expensive to produce. Furthermore, the spring element is arranged according to the invention in the low pressure region of the valve. Therefore, the installation space for the spring element be designed large; the latter has a long lifespan.
  • the second piston of the hydraulic translator is preferably constructed in two parts. This enables a first part of the two-part piston to be designed as a standard part, e.g. meets high tolerance requirements for the diameter. A second part of the piston can then be designed accordingly for optimal coupling with the spring element.
  • the two-part piston preferably has a cylindrical element and a plunger element. This means that a standard part such as e.g. Rolling bearing rollers or the like can be used.
  • Tappet element can then be adapted to the spring element. It is possible that the tappet element is integrally formed with a tappet for actuating the valve ball. However, it is also possible to design the plunger element as a disk-shaped element. A plunger for actuating the valve member is then formed as a separate element.
  • the spring element preferably has an opening in order to guide the tappet for actuating the valve member.
  • the spring element can be designed as a diaphragm spring or as a plate spring or as a coil spring.
  • the valve is designed as a single switching valve or as a double switching valve.
  • the valve here has only one valve seat against which the valve member bears or is lifted off.
  • Two valve seats are provided, the valve member either resting on one valve seat or the other valve seat or occupying an intermediate position in which both valve seats are open.
  • the valve according to the invention is preferably used in a common rail injector. In this way, in particular the loads on the valve parts caused by the high pressures can be avoided.
  • FIG. 1 shows a valve for controlling liquids according to a first embodiment of the present invention
  • Figure 2 shows a valve for controlling liquids according to the prior art.
  • FIG. 1 shows a valve according to the invention for controlling liquids, which is used as a fuel injection valve.
  • the valve 1 comprises a holder 16, a valve piece 17, an intermediate disk 19 and a nozzle body 20 which are connected to one another via a nozzle clamping nut 22.
  • the valve 1 comprises a hydraulic booster 2, which has a first piston 3, a second piston 4 and a pressure chamber 5 arranged between the two pistons 3, 4.
  • the second piston 4 is connected via a tappet 9 to a valve member 6 designed as a ball.
  • the valve ball 6 is such designed that it can be placed on an upper valve seat 7 and a lower valve seat 12.
  • the first piston 3 of the hydraulic translator is arranged in a receiving body 15 which is firmly positioned in the holder 16.
  • the second piston 4 of the hydraulic translator is arranged axially offset from the first piston 3.
  • a valve needle 21 is arranged in the nozzle body 20, which opens and closes an inlet opening through which fuel is injected into a combustion chamber (not shown).
  • the second piston 4 of the hydraulic translator 2 is formed in two parts.
  • the second piston 4 consists of a cylindrical pin 4a and a pressure ram 4b.
  • the cylindrical bolt 4a has a simple structure and thus high demands on tolerances or the like. can meet. This also means the use of
  • the pressure ram 4b directly adjoins the cylindrical bolt 4a. Furthermore, the pressure tappet 4b is directly coupled to a spring element 8.
  • the spring element 8 has a central opening in order to guide the plunger 9. Furthermore, the spring element 8 is designed such that it presses the pressure ram 4b against the cylindrical bolt 4a. If the engine of a motor vehicle is now switched off in the valve according to the exemplary embodiment shown, the second piston 4 is pressed into the pressure chamber 5 due to the spring force of the spring 8, since the fluid in the pressure chamber 5 passes through leakage gaps 13 and 14 at the two Pistons 3 and 4 escape. Since the valve ball 6 is not acted upon by spring force, it lies against the lower seat 12 undefined.
  • Pressure chamber 5 of the hydraulic translator is filled with fluid again. Compared to the movement of the valve ball 6, however, this filling is a relatively slow process.
  • the second piston 4 therefore only moves in the direction of the valve ball 6 after a certain time. However, the valve is only ready for operation when the second piston 4 is in contact with the valve ball 6 via the tappet 9.
  • the arrangement of the spring element 8 directly on the second piston 4 of the hydraulic booster 2 enables a volume 11 in the region of the valve ball 6 to be made very small. It is also achieved that the spring element 8 is in the low pressure region of the valve. It is also not necessary to use a valve ball that is expensive to manufacture with spring receiving surfaces or spring seats. As a result, the manufacturing costs of the valve according to the invention are reduced and the individual parts of the valve can have simple designs. This also has advantages with regard to quick and inexpensive installation.
  • a valve 1 for controlling liquids which comprises a piezo actuator and a hydraulic booster 2.
  • the hydraulic translator 2 has a first piston 3, a second Piston 4 and a pressure chamber 5 arranged between the two pistons 3, 4.
  • a valve member 6 and a spring element 8 are also provided.
  • the spring element 8 is directly coupled to the second piston 4 of the hydraulic booster 2.
  • the valve member 6 is not in contact with the spring element.
  • the valve according to the invention is used in particular in a common rail injector. Furthermore, a diaphragm spring or a plate spring or a helical spring can be used as the spring element 8.

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)

Abstract

La présente invention concerne une vanne (1) permettant de commander des liquides. Cette vanne comprend un piézo-actionneur et un intensificateur de pression hydraulique (2). Ledit intensificateur de pression hydraulique (2) présente un premier piston (3), un second piston (4), ainsi qu'une enceinte sous pression (5), située entre les deux pistons (3, 4). Ladite vanne comprend également un élément de vanne (6) et un élément élastique (8), qui est directement connecté au second piston (4) de l'intensificateur de pression hydraulique (2).
PCT/DE2001/001327 2000-06-14 2001-04-05 Vanne de commande de liquides WO2001096732A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000129297 DE10029297A1 (de) 2000-06-14 2000-06-14 Ventil zum Steuern von Flüssigkeiten
DE10029297.6 2000-06-14

Publications (1)

Publication Number Publication Date
WO2001096732A1 true WO2001096732A1 (fr) 2001-12-20

Family

ID=7645703

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2001/001327 WO2001096732A1 (fr) 2000-06-14 2001-04-05 Vanne de commande de liquides

Country Status (2)

Country Link
DE (1) DE10029297A1 (fr)
WO (1) WO2001096732A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10122245A1 (de) * 2001-05-08 2002-12-12 Bosch Gmbh Robert Leckagereduzierter druckgesteuerter Kraftstoffinjektor
DE10250720A1 (de) * 2002-10-31 2004-05-13 Robert Bosch Gmbh Einspritzventil
JP4428357B2 (ja) 2006-04-03 2010-03-10 株式会社デンソー 燃料噴射弁
DE102006037175A1 (de) * 2006-08-09 2008-02-14 Robert Bosch Gmbh Kraftstoffinjektor mit verbessert geführter Hubbewegung des Ventilschließgliedes
DE102015211705A1 (de) * 2015-06-24 2016-12-29 Robert Bosch Gmbh Kraftstoffinjektor mit Steuerventil

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0816670A1 (fr) * 1996-07-02 1998-01-07 Siemens Automotive Corporation Injecteur commande par élément piézoélectrique avec amplification de la course
WO1999015783A1 (fr) * 1997-09-24 1999-04-01 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59010904D1 (de) * 1990-09-25 2000-05-31 Siemens Ag Anordnung für einen in Hubrichtung wirkenden adaptiven, mechanischen Toleranzausgleich für den Wegtransformator eines piezoelektrischen Aktors
DE4306073C1 (de) * 1993-02-26 1994-06-01 Siemens Ag Zumeßvorrichtung für Fluide
DE19732802A1 (de) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19813983A1 (de) * 1998-03-28 1999-09-30 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19821768C2 (de) * 1998-05-14 2000-09-07 Siemens Ag Dosiervorrichtung und Dosierverfahren
DE19839125C1 (de) * 1998-08-27 2000-04-20 Siemens Ag Vorrichtung und Verfahren zur Dosierung von Fluid

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0816670A1 (fr) * 1996-07-02 1998-01-07 Siemens Automotive Corporation Injecteur commande par élément piézoélectrique avec amplification de la course
WO1999015783A1 (fr) * 1997-09-24 1999-04-01 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne

Also Published As

Publication number Publication date
DE10029297A1 (de) 2001-10-18

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