EP1235980A1 - Vanne de commande de liquides - Google Patents

Vanne de commande de liquides

Info

Publication number
EP1235980A1
EP1235980A1 EP00984898A EP00984898A EP1235980A1 EP 1235980 A1 EP1235980 A1 EP 1235980A1 EP 00984898 A EP00984898 A EP 00984898A EP 00984898 A EP00984898 A EP 00984898A EP 1235980 A1 EP1235980 A1 EP 1235980A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
pressure
chamber
controlling liquids
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.)
Withdrawn
Application number
EP00984898A
Other languages
German (de)
English (en)
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 EP1235980A1 publication Critical patent/EP1235980A1/fr
Withdrawn legal-status Critical Current

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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/04—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure using fluid, other than fuel, for injection-valve actuation
    • F02M47/043—Fluid pressure acting on injection-valve in the period of non-injection to keep it closed
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric operating means
    • 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
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0061—Single actuator acting on two or more valve bodies
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/004—Actuating devices; Operating means; Releasing devices actuated by piezoelectric means
    • F16K31/007—Piezoelectric stacks
    • F16K31/008—Piezoelectric stacks for sliding valves

Definitions

  • the invention relates to a valve for controlling liquids according to the preamble of claim 1.
  • EP 0 477 400 AI describes a valve which is customary today.
  • an actuating piston of the valve member is slidably arranged in a part of the stepped bore with a small diameter in a stepped bore of the valve housing.
  • a larger piston movable by a piezo actuator is arranged in part of the stepped bore with a larger diameter.
  • a hydraulic pressure chamber filled with a pressure medium is formed between the two pistons, so that a hydraulic translation of a movement of the piezo actuator takes place. That is, if the larger piston is moved by the piezo actuator by a certain distance, the actuating piston of the valve member makes a stroke which is enlarged by the ratio of the piston diameters, since the piston of the piezo actuator has a larger stroke
  • a hydraulic unit inside the injector supplies fuel to the injector housing under pressure.
  • the hydraulic unit includes an electromagnetically actuated control valve for the hydraulic fluid and can open and close the hydraulic fluid inlet.
  • a needle valve element includes a hydraulic closure surface exposed to the pressure of the needle control chamber.
  • a needle control valve that uses the electromagnet is provided, which is mounted in the injector housing and can connect or shut off the needle control chamber with a high-pressure fluid source. The slow response behavior of the hydraulic fluid control valve enables direct control of the fast-responding needle valve by the only fast-acting electromagnet used.
  • this system is disadvantageous in that only the control pressure side is controlled.
  • a second control element on the high pressure side is necessary.
  • two such control elements are to be viewed very critically in the energy balance of the control device.
  • valve according to the invention with the characterizing features of claim 1 has the advantage that the system only has to be supplied with current once by actuating the two control elements by the piezo actuator, so that the energy balance can be optimized in the direction of low power consumption.
  • the use of a single control element as process control requires also a simple structure and thus a smaller scope of costs and costs for the entire system.
  • the first and second valve elements are connected in series, which means that the space required by the three components, i.e. of the piezo actuator and also of the first and second control elements can be reduced to a minimum, since the first control element serves as an actuating element of the second valve element. Consequently, no additional actuation element between the piezo actuator and the second valve element is necessary.
  • a gap is advantageously provided between the first and second valve elements. As a result, the first valve element and then the second valve element can be switched first. In other words, it is possible to switch the first valve element without simultaneously switching the second valve element.
  • a first control chamber which can be acted upon by pressure from a control rail, is preferably arranged between the first valve element and the high-pressure chamber.
  • the control chamber enables an adequate transmission of a pressure applied via the first valve element to the high-pressure chamber.
  • the first control room can be
  • the pressure specified by the control rail can be transferred to the high-pressure chamber with a suitable transmission ratio, for example of 1: 3.
  • a suitable transmission ratio for example of 1: 3.
  • the degree of transmission is freely selectable, depending on the requirements to be met.
  • the first control chamber is advantageously connected to a leakage oil channel that can be opened or closed by the first valve element. So can Depending on the position of the first valve element, a high pressure is generated in the first control chamber and consequently in the high-pressure chamber, or the pressure in the control chamber and thus in the high-pressure chamber are released.
  • a second control chamber is arranged between the second valve element and the valve member, which in turn is acted upon by pressure from the control rail.
  • the second control chamber is connected to an outlet throttle which is opened or closed by the second valve element. This enables the pressure in the second control chamber to be varied and thus the pressure to be applied to the valve member.
  • control rail is preferably connected to a decentralized control pressure pump, which, depending on the requirements of the system, offers the possibility of replacing only the valve according to the invention for controlling liquids, but maintaining the same decentralized control pressure pump.
  • decentralized control pressure pump which, depending on the requirements of the system, offers the possibility of replacing only the valve according to the invention for controlling liquids, but maintaining the same decentralized control pressure pump.
  • the separation between the actual valve for controlling liquids and the decentralized control pressure pump also enables better use of space with regard to the respective installation conditions.
  • the first control room and / or second control room is / are preferably designed as hydraulic translators. Hydraulic boosters are available in a wide variety of dimensions and gear ratios at low cost and also lead to a simple construction of the entire valve. drawing
  • Figure 1 is a schematic view of a fuel injector according to an embodiment of the invention.
  • FIG. 2 shows an enlarged section of the arrangement of the first and second control valve according to FIG. 1;
  • Fig. 3 in diagram form the interaction between the switching position of the piezo actuator, the pressure at the nozzle and the nozzle stroke.
  • the valve according to the invention is used in a fuel injection system in which the injection pump and the injection nozzle form a unit (so-called pump-nozzle unit (PDE)).
  • PDE pump-nozzle unit
  • the injection valve 1 consists of a decentralized pump unit, not shown, and a control unit 2.
  • the control unit 2 comprises a piezo actuator 3, arranged in a housing, not shown, with a piston 4, which controls a pump control valve 6 by means of hydraulic transmission 5.
  • the pump control valve 6 in Figure 1 is biased by a spring 7 in the closed position of the pump control valve 6.
  • the pump control valve 6 is followed in series by an injector control valve 8 in FIG. 1, which in turn is closed by a spring 9 Position is biased.
  • a gap hv is formed between the pump control valve 6 and the injector control valve 8. Its mode of operation will be described later.
  • the pump control valve 6 in FIG. 1 is hydraulically connected on the one hand to the control rail 10 and on the other hand to a first control chamber 11.
  • a piston 12 adjoins the control chamber 11 downward in FIG. 1 and is biased into the control chamber 11 by means of a spring 13.
  • the piston 12 is formed with a central piston 14 which opens into a high-pressure chamber 15.
  • the control chamber 11, together with pistons 12, 14, act as a high-pressure pump.
  • the high-pressure chamber 15 is designed with a generally known inlet valve 16, which controls the inlet 17 of the fuel into the high-pressure chamber 15. Finally, the high-pressure chamber 15 in FIG. 1 is connected to a nozzle 18 constructed in a known form.
  • control rail 10 is also connected to the second control chamber 19 via an inlet throttle 20.
  • the control chamber 19 in this case has an outlet throttle 21 which opens into the injector control valve 8 and, if this control valve 8 is in the appropriate position, a drain into one
  • Leakage oil channel 22 allows. This leakage oil channel 22 is also connected to the first control chamber 11, wherein the connection can be interrupted by the pump control valve 6.
  • FIG. 1 two pistons 23, 24 adjoin the control chamber 19 in the form of a hydraulic transmission with pressure chamber 25 connected between them.
  • a further piston 27 is arranged between the valve member 26 and the piston 24 and biases the valve member 26 into its closed position via a sealing spring 28.
  • FIG. 2 the interaction between the pump control valve 6 and the injector control valve 8 is shown in an enlarged view.
  • a gap hv is formed between these two components.
  • injection valve 1 In the present exemplary embodiment of injection valve 1 according to the invention, a 3/2-seat slide valve is used as pump control valve 6 and a 2/2 valve with inlet 20 and outlet throttle 21 is used as injector control valve 8.
  • the pressure of the control rail 10 is also applied to the second control chamber 19 and by means of the hydraulic transmission of the pistons 23, 24 and 27 with a transmission ratio of d3 / d4 to the valve member 26.
  • the gear ratios between dl / d2 and d3 / d4 are selected such that the valve member 26 remains in its closed position.
  • the pressure transmitted from the high-pressure chamber 15 to the valve member 26 continues to increase.
  • the control valve 6 executes a further movement to the right in FIG. 1, so that the connection between the first control chamber 11 and the leakage oil channel 22 is closed, as a result of which the same pressure in the first control chamber 11 as in the control rail 10 established.
  • control valve 8 is moved to the right against the spring 9 in FIG. 1 and opens the connection between the outlet throttle 21 and the leakage oil channel 22, as a result of which the pressure in the second control chamber 19 decreases. Consequently, the pressure acting on the valve member 26 in the "right leg” of FIG. 1 also decreases, whereas the pressure on the valve member 26 applied by the "left leg” in FIG. 1 increases. Accordingly, the inlet opening of the nozzle 18 is opened and a pre-injection VE occurs, as can be seen from the three diagrams in FIG.
  • the pressure drop in the main injection is greater than in the pre-injection, since a larger volume of liquid is withdrawn.
  • the present invention can of course also be used in valves of a different design with hydraulic but also mechanical translators.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrically Driven Valve-Operating Means (AREA)

Abstract

La présente invention concerne une vanne de commande de liquides, comprenant un premier élément de vanne (6), qui commande l'alimentation en pression d'une chambre à haute pression (15), un élément de commande (3), qui commande l'actionnement du premier élément de vanne (6), ainsi qu'un second élément de vanne (8), qui commande l'alimentation en pression d'un organe de vanne (26). Selon cette invention, l'élément de commande (3) est conçu sous forme d'actionneur piézo-électrique et commande également l'actionnement du second élément de vanne (8).
EP00984898A 1999-11-25 2000-11-23 Vanne de commande de liquides Withdrawn EP1235980A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19956598 1999-11-25
DE19956598A DE19956598A1 (de) 1999-11-25 1999-11-25 Ventil zum Steuern von Flüssigkeiten
PCT/DE2000/004146 WO2001038720A1 (fr) 1999-11-25 2000-11-23 Vanne de commande de liquides

Publications (1)

Publication Number Publication Date
EP1235980A1 true EP1235980A1 (fr) 2002-09-04

Family

ID=7930216

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00984898A Withdrawn EP1235980A1 (fr) 1999-11-25 2000-11-23 Vanne de commande de liquides

Country Status (6)

Country Link
EP (1) EP1235980A1 (fr)
JP (1) JP2003515047A (fr)
CZ (1) CZ20021776A3 (fr)
DE (1) DE19956598A1 (fr)
HU (1) HUP0203401A2 (fr)
WO (1) WO2001038720A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE10134529C2 (de) * 2001-07-16 2003-07-03 Bosch Gmbh Robert Injektor mit hintereinandergeschalteten, nach innen öffnenden Ventilen
DE10141110A1 (de) * 2001-08-22 2003-03-20 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE10141111B4 (de) * 2001-08-22 2005-10-13 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE10145822B4 (de) * 2001-09-17 2004-08-19 Robert Bosch Gmbh Injektor einer Kraftstoffeinspritzeinrichtung
DE10212396A1 (de) * 2002-03-20 2003-10-09 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung mit 3/2-Wege-Ventil
DE10229413A1 (de) * 2002-06-29 2004-01-29 Robert Bosch Gmbh Druckübersetzersteuerung durch Bewegung eines Einspritzventilgliedes
GB0215488D0 (en) 2002-07-04 2002-08-14 Delphi Tech Inc Fuel injection system
MXPA05002622A (es) 2002-09-09 2005-09-08 Johnson & Johnson Derivados de 1,3,8,-triazaespiro [4.5]decan-4-ona sustituidos con hidroxialquilo utiles para el tratamiento de desordenes mediados por el receptor opioide huerfano.
TW200418836A (en) * 2002-09-10 2004-10-01 Pharmacia Italia Spa Formulations comprising an indolinone compound
JP4003770B2 (ja) 2004-10-01 2007-11-07 トヨタ自動車株式会社 燃料噴射装置
DE102004057610A1 (de) * 2004-11-29 2006-06-01 Fev Motorentechnik Gmbh Kraftstoff-Injektor
US8703948B2 (en) 2006-11-28 2014-04-22 Janssen Pharmaceutica Nv Salts of 3-(3-amino-2-(R)-hydroxy-propyl)-1-(4-fluoro-phenyl)-8-(8-methyl-naphthalen-1-ylmethyl)-1,3,8-triaza-spiro[4.5]decan-4-one
DE102007004745A1 (de) * 2007-01-31 2008-08-14 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Kraftstoffeinspritzsystem für eine Verbrennungskraftmaschine
CA2683598C (fr) 2007-04-09 2015-11-17 Janssen Pharmaceutica Nv Derives de 1,3,8-trisubstitue-1,3,8-triaza-spiro[4.5]decan-4-one utilises comme ligands du recepteur orl-i dans le traitement de l'anxiete et de la depression

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US5241935A (en) * 1988-02-03 1993-09-07 Servojet Electronic Systems, Ltd. Accumulator fuel injection system
EP0477400B1 (fr) * 1990-09-25 2000-04-26 Siemens Aktiengesellschaft Dispositif compensateur de tolérance dans la direction de mouvement du transformateur de déplacement d'un dispositif d'actionnement piézoélectrique
US5738071A (en) * 1991-05-22 1998-04-14 Wolff Controls Corporation Apparatus and method for sensing movement of fuel injector valve
US5697342A (en) * 1994-07-29 1997-12-16 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
DE19742320A1 (de) * 1997-09-25 1999-04-01 Bosch Gmbh Robert Kraftstoffeinspritzventil

Non-Patent Citations (1)

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Title
See references of WO0138720A1 *

Also Published As

Publication number Publication date
DE19956598A1 (de) 2001-06-13
CZ20021776A3 (cs) 2003-11-12
WO2001038720A1 (fr) 2001-05-31
HUP0203401A2 (en) 2003-02-28
JP2003515047A (ja) 2003-04-22

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