EP1636485B1 - Injector for fuel injection systems of internal combustion engines, especially direct injection diesel engines - Google Patents

Injector for fuel injection systems of internal combustion engines, especially direct injection diesel engines Download PDF

Info

Publication number
EP1636485B1
EP1636485B1 EP20040726421 EP04726421A EP1636485B1 EP 1636485 B1 EP1636485 B1 EP 1636485B1 EP 20040726421 EP20040726421 EP 20040726421 EP 04726421 A EP04726421 A EP 04726421A EP 1636485 B1 EP1636485 B1 EP 1636485B1
Authority
EP
European Patent Office
Prior art keywords
nozzle
injector
nozzle needle
intensifier piston
space
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.)
Expired - Fee Related
Application number
EP20040726421
Other languages
German (de)
French (fr)
Other versions
EP1636485A1 (en
Inventor
Sebastian Kanne
Godehard Nentwig
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
Priority to DE2003126259 priority Critical patent/DE10326259A1/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to PCT/DE2004/000738 priority patent/WO2004111434A1/en
Publication of EP1636485A1 publication Critical patent/EP1636485A1/en
Application granted granted Critical
Publication of EP1636485B1 publication Critical patent/EP1636485B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603Injectors peculiar thereto with means directly operating the valve needle using piezo-electric or magnetostrictive operating means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions

Description

    State of the art
  • The invention relates to an injector according to the preamble of claim 1.
  • An injector for fuel injection systems with a directly controlled nozzle needle and with a pulling actuator for opening the nozzle needle according to the features of the preamble of claim 1 is made EP 1174 615 A2 known. The nozzle needle is designed with a nozzle needle piston, which is guided in a sleeve-shaped booster piston. The sleeve-shaped booster piston includes a control chamber to which the nozzle needle piston is exposed. To open the nozzle needle of the booster piston performs a pulling movement, so that increases the volume of the control chamber, whereby the force acting in the opening direction of the nozzle needle opening force exceeds the force acting in the control chamber on the nozzle needle piston closing force. This lifts the nozzle needle off the nozzle needle seat and injects fuel.
  • Another injector for fuel injection systems with a directly controlled nozzle needle and with a pushing actuator to open the nozzle needle is off JP 102 88 117 A known. The injector has a nozzle needle piston with two piston sections, wherein one piston section is exposed to the high pressure of the fuel supply line and the other piston section is separated from the high pressure hydraulic chamber as a control chamber. On the separated from the high pressure control chamber and the associated with the piezoelectric actuator booster piston acts. If the pressure is increased by actuating the piezo actuator and the booster piston in the control chamber, this acts on the opening direction acting piston surface of the nozzle needle piston and the nozzle needle is lifted from the nozzle needle seat, so that fuel is injected.
  • An injector for fuel injection systems with a directly controlled nozzle needle and with a pushing actuator for opening the nozzle needle is still off DE 43 060 73 C1 known. Here, the nozzle needle is surrounded by a nozzle needle pressure chamber which is connected to a fuel supply. In a separate hydraulic chamber, a translation device with a booster piston and a nozzle needle piston is arranged in a piston-in-piston system. The nozzle needle piston here also has a piston surface which acts in the opening direction of the nozzle needle and is exposed to the hydraulic chamber. If the pressure is increased by actuating the actuator and the booster piston in the hydraulic chamber, this acts on the piston surface of the nozzle needle piston acting in the opening direction and the nozzle needle is lifted off the nozzle needle seat, so that fuel is injected.
  • Another injector with a directly controlled nozzle needle is also off DE 195 19 191 C2 known. The subject matter of this document sitting piezoelectric actuator and booster piston at the upper end of the injector body and the power transmission to the arranged at the lower end of the injector nozzle needle via a long plunger. The plunger is in hydraulic communication with the fuel inlet. Piezo actuator and booster piston are separated from the fuel inlet. An incorporated into the injector pressure channel leads to the nozzle exit. In addition, an annular space surrounding the plunger in the lower region is provided, from which a fuel return duct emerges. The fuel return passage is hydraulically connected to an interior of the booster piston extending above the ram. A trained under the booster piston control chamber is fed by the fuel inlet via a plunger surrounding the injector body leakage gap.
  • At one off JP 11 200 981 A known injector for fuel injection systems with a directly controlled nozzle needle booster piston and nozzle needle are arranged spatially separated from each other.
  • Advantages of the invention
  • Based on the above-described prior art, it is an object of the present invention to provide a suitable also for common rail systems injector, which is relatively simple in construction, manages with a minimum of individual parts and works efficiently.
  • According to the invention the object is achieved in an injector of the type described by the features of claim 1.
  • Advantageous embodiments of the basic concept of the invention include claims 2-4.
  • A significant advantage of the invention lies in the direct control of the nozzle needle by the piezoelectric actuator. The speed of the nozzle needle movement can be adjusted via the voltage curve of the piezo actuator. For a dosage of particularly small pre-injection amounts and a partial stroke can be specified. Another advantage of the injector according to the invention is also to be seen in the fact that this manages without a fuel return.
  • drawing
  • The invention is illustrated by means of an embodiment in the drawing and described in detail below. It shows schematically in each case:
  • Fig. 1
    an embodiment of a direct-controlled common rail injector with piezoelectric actuator, in vertical longitudinal section, and
    Fig. 2
    a lower portion of the injector after Fig. 1 , in opposite Fig. 1 enlarged view.
    Description of the embodiment
  • It denotes a cylindrical injector body with a continuous, on the predominant part of its longitudinal extent cylindrical recess 11. At its upper end, the recess 11 first has a conically tapered portion 12, which in a right angle bent, finally outwardly opening section 13, the fourteenth passes. In the cylindrical portion of the recess 11, which is numbered 15, a likewise cylindrical piezoactuator 16 of relatively large longitudinal extension is arranged, whose diameter is smaller than the inner diameter of the recess section 15. This results in an annular space 17 between the outer wall of the piezoactuator 16 and the inner wall of the injector body 10 For the purpose of centering the piezoactuator 16 within the injector body 10, the conical section 12 of the axial recess 11 is used for one. On the other hand, fluid-permeable spacers can be provided in the annular space 17 at certain axial distances as required (not shown).
  • The upper, angled portion 13, 14 of the recess 11 acts as a cable bushing for the power supply of the piezoelectric actuator 16th
  • At the upper end of the injector body 10 is a fuel supply 18, e.g. High-pressure connection of a common rail system, provided, which is connected via a pressure channel 19 with the annular space 17 in hydraulic communication.
  • At the lower end of the injector body 10 and coaxial with this, a nozzle body 20 connects, which receives a nozzle needle 21. The nozzle body 20 is attached by means of a union nut (clamping nut) 22 on the injector body 10, such that it comes with a rear end face 23 sealingly abutting a lower end face 24 of the injector body 10.
  • To accommodate the nozzle needle 21, the nozzle body 20 has an upwardly open, multi-stepped interior 25, which forms a bottom opening into two nozzle outlet holes 26, 27 conical valve seat 28. The valve seat 28 cooperates with a conical end section 29 of the nozzle needle 21 functioning as a closing body.
  • At its upper end, the nozzle needle 21 has a portion 30 of larger diameter, which is fitted into a cylindrical interior 31 of a sleeve-shaped, downwardly open booster piston 32. The upper end of the booster piston .32 forms a collar 33. A in the annular space 17 - in this case the booster piston 32 surrounding - arranged on the one hand on the end face 23 of the nozzle body 20, on the other hand on the collar 33 of the booster piston 32 supporting the compression coil spring 34 holds the booster piston 32nd with the piezoelectric actuator 16 at the front in contact. By acting from the compression spring 34 via the booster piston 32 to the piezoelectric actuator 16 in the direction of arrow 35 pressure of the piezoelectric actuator 16 is sealed at its upper side 36 against the injector body 10, and the electrical connection (not shown) can thus by the angled holes 13, 14th be led out of the injector body 10.
  • As the drawing further shows, in the lower part of the nozzle body 20 - as part of the nozzle body interior 25 - a nozzle needle 21 concentrically surrounding cylindrical pressure chamber 37 is formed, which via holes 38, 39 in the nozzle body 20 and between the nozzle body 20 and the clamping nut 22 formed annular space 40 is hydraulically connected to the annular space 17 of the injector body 10.
  • Another special feature is that the interior 25 of the nozzle body 20 at the top has a stepped diameter extension 41, in which the booster piston 32 is guided so that a in the extended interior part 41st formed below the booster piston 32 control chamber 42 via a leakage gap 43 (see in particular Fig. 2 ) is in hydraulic communication with the annular space 17 of the injector body 10. A section 44 of the nozzle body interior 25 with a comparatively small diameter serves to guide the nozzle needle 21 within the nozzle body 20. Also, this section 44 is designed so that a leakage gap 45th (see, in particular Fig. 2 ). The control chamber 42 is thus hydraulically connected via the second leakage gap 45 with the cylindrical space 37, which in turn - via the recesses 38 to 40 - from the annular space 17 of the injector 10 is pressurized high.
  • A special feature is further that the above the nozzle needle 21 extending interior 31 of the booster piston 32 is also hydraulically connected to the high pressure-loaded annular space 17 of the injector body 10, via a lateral bore 46 in the booster piston 32nd
  • The upper (thickened) portion 30 of the nozzle needle 21 is now guided in the booster piston 32 that a (further) leakage gap 47 (see Fig. 2 ). A hydraulic connection between the control chamber 42 and the high-pressure-loaded annulus 17 of the injector body 10 is thus also produced via this (third) leakage gap 47.
  • Another special feature is that in the interior 31 of the booster piston 32, a (second) helical compression spring 48 is arranged, which exerts on the nozzle needle 21 in the closing direction (arrow 49) directed force. By the (second) compression spring 48 so the nozzle needle 21 is kept closed during the pauses between the injections and at rest of the vehicle. In Fig. 1 and 2 the closed position of the nozzle needle 21 is shown. In the open position, however, the injection process takes place, whereby from the cylindrical pressure chamber 37 fuel passes through the outlet holes 26, 27 in the (not shown) cylinder combustion chamber of the internal combustion engine.
  • The trained at the lower end of the booster piston 32 control chamber 42 is used for hydraulic length compensation and as a hydraulic translator for the expansion movement of the piezoelectric actuator 16th
  • The transport of the fuel from the injector body 10 to the nozzle outlet bores via the (relatively short) recess 38 (or more such recesses) through the nozzle body 20, which connects the injector body 10 with the annulus 40 between the clamping nut 22 and nozzle body 20. From the annular space 40, the fuel is passed through the further (comparatively short) bore 39 (or a plurality of such bores) to the nozzle outlet bores 26, 27.
  • The injector described above operates as follows. During the pauses between the individual injection processes, the piezoelectric actuator 16 is de-energized. Now, if the piezoelectric actuator 16 is electrically driven, it expands and moves the booster piston 32 against the force of the two compression springs 34, 48 down (in the direction of arrow 49). In this case, the volume of the control chamber 42 is reduced, and the pressure in the control chamber 42 increases. As a result, an opening force (in the direction of arrow 35) is exerted on the nozzle needle 21. As soon as the opening force exceeds the closing pressure forces and the force of the compression spring 48, the nozzle opens by the nozzle needle 21 assumes the (upper) position shown in the drawing and thus the outlet holes 26, 27 releases. By translating by means of the booster piston 32, the nozzle needle 21 can perform a maximum stroke, which is significantly greater than the expansion stroke of the electrically controlled piezoelectric actuator 16th
  • Once the nozzle needle 21 has left the stroke range of seat throttling (see Fig. 1 and 2 ), a balance of the compressive forces acting on them occurs. The piezoelectric actuator 16 then has to hold the pressure in the control chamber 42 only so far above the pressure prevailing at the pressure port 18 high pressure (rail pressure) via the booster piston 32, that the resistance of the compression spring 48 is overcome.
  • The longest possible activation duration is determined by the leakage (43, 45, 47) from the control chamber 42.
  • If the pressure in the control chamber 42 drops to the rail pressure, the nozzle needle 21 moves downward (in the direction of arrow 49) until it closes the outlet bores 26, 27 with the lateral surface of its conical tip 29. To close the nozzle needle 21, the electrical control of the piezoelectric actuator 16 is interrupted. The piezoelectric actuator 16 then contracts, and the pressure in the control chamber 42 drops below the rail pressure. As a result, the nozzle needle 21 undergoes the necessary closing forces and closes.
  • The compression spring 34 prevents this, that the piezoelectric actuator 16 separates from the booster piston 32. Piezo actuator 16 and booster piston 32 thus remain constantly in the (off Fig. 1 and 2 apparent) non-positive abutment position to each other.

Claims (4)

  1. Injector for fuel injection systems of internal combustion engines, in particular of direct-injection diesel engines, with a piezoactuator which is arranged in an injector body (10) and which via first spring means (34) is held in bearing contact, on the one hand, with the injector body (10) and, on the other hand, with a sleeve-like intensifier piston (32), with a nozzle body (20) which is connected to the injector body (10) and has at least one nozzle outlet orifice (26, 27) and in which a stepped nozzle needle (21) is guided axially displaceably, with second spring means (48) which are arranged within the intensifier piston (32) and which, together with the fuel pressure acting on the nozzle needle (21) on the rear side, hold the nozzle needle (21) in the closing position, and with a control space (42) which is formed at the nozzle needle-side end of the intensifier piston (32) and which is connected via at least one leakage gap (43, 45, 47) to a fuel feed (18) which is under high pressure, the nozzle needle (21) being acted upon in the opening direction (35) by the fuel located in the control space (42), the intensifier piston (32) actuated by the piezoactuator (16) being spatially assigned directly to the nozzle needle (21), in such a way that the nozzle needle (21) is fitted with a rear region (30), which has a larger diameter than a nozzle outlet-side region of the nozzle needle (21), in an inner space (31) of the intensifier piston (32), an annular space (17) being provided, which is directly connected hydraulically to the fuel feed (18) which is under high pressure, which annular space extends into the region of the intensifier piston (32) axially adjacent to the piezoactuator (16), the inner space (31) of the intensifier piston (32) being connected hydraulically to the annular space (17) and consequently to the fuel feed (18), the nozzle body (20) being fastened to the injector body (10) by means of a union nut (22), and the piezoactuator (16) being centred in an axial cylindrical recess (15) of the injector body (10) in such a way as to give rise to the annular space (17) between the outer wall of the piezoactuator (16) and the inner wall of the cylindrical recess (15) of the injector body (10), characterized in that the intensifier piston (32) is guided in the nozzle body (20), thereby forming a leakage gap (43), in such a way that a hydraulic connection is made between the annular space (17) which is under high pressure and the control space (42), and in that, between the outer wall of the nozzle body (20) and the inner wall of the union nut (22), a cylindrical gap (40) is formed, which is connected hydraulically via recesses (38, 39) incorporated into the nozzle body (20), on the one hand, to the annular space (17) and, on the other hand, to a cylindrical pressure space (37) concentrically surrounding the nozzle needle (21) in the nozzle outlet-side region of the nozzle body (20).
  2. Injector according to Claim 1, characterized in that, in that region of the annular space (17) which is assigned to the intensifier piston (32), a compression spring (34) is arranged which concentrically surrounds the intensifier piston (32) and which is supported on the piezoactuator side against a collar (33) of the intensifier piston (32) and on the nozzle-outlet side against a rear end face (23) of the nozzle body (20), in such a way that the piezoactuator (16) and intensifier piston (32) are held non-positively in bearing contact.
  3. Injector according to Claim 1, characterized in that the nozzle needle (21) is guided in the inner space (31) of the intensifier piston (32), thereby forming a cylindrical leakage gap (47), in such a way that a hydraulic connection is made between the inner space (31), under high pressure, of the intensifier piston (32) and the control space (42).
  4. Injector according to one or more of the preceding claims, characterized in that in the nozzle body (20), on the rear side of the cylindrical pressure space (37), a portion (44) is formed, in which the nozzle needle (21) is guided, thereby forming a leakage gap (45), in such a way that a hydraulic connection is made between the cylindrical pressure space (37) which is under high pressure and the control space (42).
EP20040726421 2003-06-11 2004-04-08 Injector for fuel injection systems of internal combustion engines, especially direct injection diesel engines Expired - Fee Related EP1636485B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE2003126259 DE10326259A1 (en) 2003-06-11 2003-06-11 Injector for fuel injection systems of internal combustion engines, in particular direct injection diesel engines
PCT/DE2004/000738 WO2004111434A1 (en) 2003-06-11 2004-04-08 Injector for fuel injection systems of internal combustion engines, especially direct injection diesel engines

Publications (2)

Publication Number Publication Date
EP1636485A1 EP1636485A1 (en) 2006-03-22
EP1636485B1 true EP1636485B1 (en) 2009-01-14

Family

ID=33494946

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20040726421 Expired - Fee Related EP1636485B1 (en) 2003-06-11 2004-04-08 Injector for fuel injection systems of internal combustion engines, especially direct injection diesel engines

Country Status (7)

Country Link
US (1) US7431220B2 (en)
EP (1) EP1636485B1 (en)
JP (1) JP2006510850A (en)
KR (1) KR20060021357A (en)
CN (1) CN100432420C (en)
DE (2) DE10326259A1 (en)
WO (1) WO2004111434A1 (en)

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10346242B4 (en) * 2003-10-06 2012-04-12 Robert Bosch Gmbh Injector body for a common rail injector
DE102004004006A1 (en) * 2004-01-27 2005-08-11 Robert Bosch Gmbh Integrated hydraulic intensifier for fuel injectors on high-pressure accumulator injection systems
DE102005015997A1 (en) * 2004-12-23 2006-07-13 Robert Bosch Gmbh Fuel injector with direct control of the injection valve member
DE102005007543A1 (en) * 2005-02-18 2006-08-24 Robert Bosch Gmbh Fuel injector with direct needle control for an internal combustion engine
DE102005012929A1 (en) * 2005-03-21 2006-09-28 Robert Bosch Gmbh Fuel injector with direct control of the injection valve member and variable ratio
DE102005015735A1 (en) * 2005-04-06 2006-10-12 Robert Bosch Gmbh Fuel injector
DE102005015731A1 (en) * 2005-04-06 2006-10-12 Robert Bosch Gmbh Fuel injector with piezo actuator
DE102006006889A1 (en) 2006-02-15 2007-08-23 Robert Bosch Gmbh Fuel injector
EP1837515A1 (en) 2006-03-20 2007-09-26 Delphi Technologies, Inc. Damping arrangement for a fuel injector
AT511014T (en) * 2006-03-20 2011-06-15 Delphi Tech Holding Sarl Damping assembly for an injection valve
DE102006018032A1 (en) 2006-04-19 2007-10-31 Robert Bosch Gmbh Actuator module
DE102006036780A1 (en) 2006-08-07 2008-02-21 Robert Bosch Gmbh Fuel injector with direct needle control and servo valve support
DE102007004380A1 (en) 2007-01-29 2008-07-31 Robert Bosch Gmbh Injector with piezoelectric actuator
DE102007044361A1 (en) * 2007-09-17 2009-03-19 Robert Bosch Gmbh Control valve for a fuel injector
FR2922406A1 (en) * 2007-10-12 2009-04-17 Commissariat Energie Atomique Liquid charge injection device for mixing / converting within a dard plasma or a gaseous flow
DE102008003851A1 (en) * 2008-01-10 2009-07-16 Robert Bosch Gmbh Fuel injector
DE102008003838A1 (en) * 2008-01-10 2009-07-16 Robert Bosch Gmbh Piezoelectric actuator and piezoelectric injector and a method for producing a piezoelectric actuator
DE102008002438A1 (en) 2008-06-16 2009-12-17 Robert Bosch Gmbh Injector for injection of fuel into combustion chamber of internal combustion engine, has actuator connected with control piston
CN101649797B (en) * 2008-08-16 2013-05-29 柳州福尔曼汽车电子有限公司 Zero-backpressure electronically-controlled diesel injector driven by magnetostrictive component
CN101649796B (en) * 2008-08-16 2013-08-07 柳州福尔曼汽车电子有限公司 Zero-backpressure electronically-controlled diesel injector driven by magnetostrictive component
DE102008041645A1 (en) 2008-08-28 2010-03-04 Robert Bosch Gmbh Actuator module for fuel injection valve, particularly injector for air-compression, auto-ignition internal combustion engine, has piezoelectric actuator and transition piece connected with actuator
DE102008044164A1 (en) 2008-11-28 2010-06-02 Robert Bosch Gmbh Actuator module for fuel injection valve, particularly injector for fuel injection system, has actuator, where adapter is fixed to actuator, and centering element has bolt-shaped centering extension
US8201543B2 (en) * 2009-05-14 2012-06-19 Cummins Intellectual Properties, Inc. Piezoelectric direct acting fuel injector with hydraulic link
DE102009054682A1 (en) 2009-12-15 2011-06-16 Robert Bosch Gmbh Injection valve i.e. injector, for fuel injection system in e.g. air-compressing, self-ignited internal combustion engine of motor vehicle, has valve element whose joining section is partially inserted into actuator head
DE102010063219B4 (en) 2010-12-16 2018-05-24 Robert Bosch Gmbh Piezoelectric actuator module and fuel injection valve
US9284930B2 (en) * 2011-06-03 2016-03-15 Michael R. Harwood High pressure piezoelectric fuel injector
DE102012005319A1 (en) * 2012-03-19 2013-09-19 L'orange Gmbh Injector assembly for fuel injector of motor vehicle, has actuating element that generates pressure in fluid, which is increased with respect to system high pressure, where injector assembly is formed to be effective against pressure force
DE102012209616A1 (en) 2012-06-08 2013-12-12 Robert Bosch Gmbh Arrangement with a piezoelectric actuator and a controller, and method for driving a piezoelectric actuator
CN103244321B (en) * 2013-04-28 2015-03-11 哈尔滨工程大学 Dual-fuel dual-piezoelectric control type injector
CN103244322B (en) * 2013-04-28 2015-03-11 哈尔滨工程大学 Dual-fuel electromagnetic and piezoelectric control type injector
DE102014211334B3 (en) * 2014-06-13 2015-08-27 Continental Automotive Gmbh Method for characterizing a hydraulic coupling element of a piezo injector

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022166A (en) * 1975-04-03 1977-05-10 Teledyne Industries, Inc. Piezoelectric fuel injector valve
DE2931874C2 (en) * 1979-08-06 1983-08-04 Audi Nsu Auto Union Ag, 7107 Neckarsulm, De
DE3518945A1 (en) * 1985-05-25 1986-11-27 Bosch Gmbh Robert Fuel injection nozzle for internal combustion engines
DE4306073C1 (en) 1993-02-26 1994-06-01 Siemens Ag Metering system for dosing of fluids with injection valve for IC engine - has piston acting on closing unit, and spring with actuator acting on large dia. piston moving in cylinder
US5482213A (en) * 1993-05-31 1996-01-09 Aisin Seiki Kabushiki Kaisha Fuel injection valve operated by expansion and contraction of piezoelectric element
JP3814935B2 (en) * 1997-04-18 2006-08-30 日産自動車株式会社 Engine fuel injection valve
US5947380A (en) * 1997-11-03 1999-09-07 Caterpillar Inc. Fuel injector utilizing flat-seat poppet valves
JP3922780B2 (en) * 1998-01-08 2007-05-30 株式会社デンソー Fuel injection valve and driving method thereof
JP2000161175A (en) 1998-11-26 2000-06-13 Hitachi Car Eng Co Ltd Injector and fuel injection system
DE19946840A1 (en) * 1999-09-30 2001-05-03 Bosch Gmbh Robert Valve for controlling liquids
US20020053611A1 (en) * 2000-06-29 2002-05-09 Friedrich Boecking High-pressure injector with reduced leakage
DE60126380T2 (en) 2000-07-18 2007-11-15 Delphi Technologies, Inc., Troy Fuel injection valve
JP2002202022A (en) * 2000-10-30 2002-07-19 Denso Corp Valve driving device and fuel injection valve
US6766965B2 (en) * 2001-08-31 2004-07-27 Siemens Automotive Corporation Twin tube hydraulic compensator for a fuel injector
DE10151688A1 (en) 2001-10-19 2003-04-30 Bosch Gmbh Robert Valve for controlling liquids
DE10326046A1 (en) * 2003-06-10 2004-12-30 Robert Bosch Gmbh Injection nozzle for internal combustion engines
DE102005004738A1 (en) * 2005-02-02 2006-08-10 Robert Bosch Gmbh Fuel injector with direct needle control for an internal combustion engine
DE102005012929A1 (en) * 2005-03-21 2006-09-28 Robert Bosch Gmbh Fuel injector with direct control of the injection valve member and variable ratio

Also Published As

Publication number Publication date
US7431220B2 (en) 2008-10-07
CN1806116A (en) 2006-07-19
CN100432420C (en) 2008-11-12
DE10326259A1 (en) 2005-01-05
EP1636485A1 (en) 2006-03-22
KR20060021357A (en) 2006-03-07
US20060255184A1 (en) 2006-11-16
JP2006510850A (en) 2006-03-30
DE502004008875D1 (en) 2009-03-05
WO2004111434A1 (en) 2004-12-23

Similar Documents

Publication Publication Date Title
EP1478840B1 (en) Fuel injection valve for internal combustion engines
EP0925440B1 (en) Fuel injector
EP1636484B1 (en) Injector for internal combustion engines
CN100432420C (en) Injector for fuel injection systems of internal combustion engines, especially direct injection diesel engines
US6843464B2 (en) Valve for controlling liquids
DE19519191C2 (en) Injector
EP1307651B1 (en) Metering valve with a hydraulic transmission element
CN100416082C (en) Fuel injection device
EP1771651B1 (en) Fuel injector comprising a direct multi-stage injection valve member control system
US7513440B2 (en) Pressure-boosted fuel injection device comprising an internal control line
US7267109B2 (en) Fuel injection device for an internal combustion engine
EP1963659B1 (en) Fuel injector having a directly actuable injection valve element
US6810857B2 (en) Fuel injection system for an internal combustion engine
US7309027B2 (en) Fuel injector for internal combustion engines
EP0959243B1 (en) Control valve for a fuel injector
EP1269008B1 (en) Injection valve with bypass throttle
EP1435453A1 (en) Inward opening dual mode nozzle
US20090108093A1 (en) Fuel injector
JP2007506897A (en) Injector for fuel injection system of internal combustion engine, especially direct injection type diesel engine
EP0937891B1 (en) Fuel Injector
EP1399666B1 (en) Fuel injection device
US20060186221A1 (en) Fuel injector with direct needle control for an internal combustion engine
EP0745764A2 (en) Fuel injection valve for internal combustion engines
DE10155271A1 (en) Common rail injector
EP1458970B1 (en) Fuel-injection device for an internal combustion engine

Legal Events

Date Code Title Description
AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 20060111

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

DAX Request for extension of the european patent (to any country) (deleted)
17Q First examination report despatched

Effective date: 20060413

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 502004008875

Country of ref document: DE

Date of ref document: 20090305

Kind code of ref document: P

26N No opposition filed

Effective date: 20091015

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

PGFP Annual fee paid to national office [announced from national office to epo]

Ref country code: FR

Payment date: 20170424

Year of fee payment: 14

PGFP Annual fee paid to national office [announced from national office to epo]

Ref country code: IT

Payment date: 20170420

Year of fee payment: 14

PGFP Annual fee paid to national office [announced from national office to epo]

Ref country code: DE

Payment date: 20170623

Year of fee payment: 14

PGFP Annual fee paid to national office [announced from national office to epo]

Ref country code: GB

Payment date: 20180403

Year of fee payment: 15

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004008875

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180408

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180430

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190408

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190408