EP0872636A2 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

Info

Publication number
EP0872636A2
EP0872636A2 EP98106006A EP98106006A EP0872636A2 EP 0872636 A2 EP0872636 A2 EP 0872636A2 EP 98106006 A EP98106006 A EP 98106006A EP 98106006 A EP98106006 A EP 98106006A EP 0872636 A2 EP0872636 A2 EP 0872636A2
Authority
EP
European Patent Office
Prior art keywords
valve
valve member
pressure
characterized
fuel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP98106006A
Other languages
German (de)
French (fr)
Other versions
EP0872636A3 (en
Inventor
Stephan Haas
Thomas Kuegler
Roger Potschin
Detlev Dr. Potz
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 DE1997116226 priority Critical patent/DE19716226C2/en
Priority to DE19716226 priority
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0872636A2 publication Critical patent/EP0872636A2/en
Publication of EP0872636A3 publication Critical patent/EP0872636A3/en
Withdrawn legal-status Critical Current

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
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • 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
    • F02M51/005Arrangement of electrical wires and connections, e.g. wire harness, sockets, plugs; Arrangement of electronic control circuits in or on fuel injection apparatus
    • 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
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042The valves being provided with fuel passages
    • F02M61/045The valves being provided with fuel discharge orifices

Abstract

The arrangement includes an, axial in a drill hole (7) of a valve body (1) adjustable valve element (9) which comprises a valve head (11) at its end towards the combustion chamber, forming a valve closing element. The valve head comprises a sealing surface (13) on its side facing the valve body, with which it works together with a valve seat surface (17) provided at the front of the valve body facing the combustion chamber and with injection apertures (29) in the valve element head. The injection apertures lead away from a pressure chamber (19) formed between the valve element and the wall of the drill hole. The injection apertures are blocked by the wall of the drill hole when the valve element seats on the valve seat, and are opened by emerging the valve element from the drill hole through an outward directed movement of the valve element. The valve element is activated by a control element from the outside, independent of a high fuel pressure in the pressure chamber.

Description

State of the art

The invention relates to a fuel injection valve for Internal combustion engines according to the preamble of claim 1 out. In such a known from DE-OS 44 42 764 Outward-opening type fuel injector is an axially displaceable piston-shaped valve member in guided a bore of a valve body. The valve member points to his in the combustion chamber to be supplied Internal combustion engine protruding end from the bore replacing valve member head with an enlarged diameter on, which forms a valve closing member and at whose the Valve body facing side at least indirectly one Sealing surface is arranged. This valve member sealing surface acts with one on the front of the combustion chamber of the valve seat surface provided together, which borders on the bore in the valve body. It is between the stem of the valve member and the wall of the Bore in the valve body formed a pressure chamber that over an inlet line with a high-pressure feed pump promoted high pressure fuel is acted upon. While the injection phases, i.e. supplied to the injector High fuel pressure will counter the valve member Force of a return or closing spring to the outside from lifted off its valve seat and gives an opening cross-section on the valve head between the sealing surface and the Valve seat surface over which the fuel from the Pressure chamber in the valve body in the combustion chamber of the supply Internal combustion engine can flow. To do one for different speeds and load ranges of the internal combustion engine to achieve variable injection cross section the known injection valve on the valve head a variety of Injection ports on axially one above the other are arranged and which are now during the outward directed opening stroke movement of the valve member in succession are taxable, so that overall different Have large injection opening cross sections set. The Injection openings are thus in the valve head of the valve member arranged that they are in contact with the valve seat Valve member from the wall of the bore in the valve body are closed and only during the outward facing Opening stroke movement of the valve member by immersion controlled from the hole.

However, the known fuel injection valve the disadvantage that the control of the valve member opening stroke movement only depending on the pressure increase in the pressure chamber he follows. Certain partial stroke positions can be used of the valve member in the known injection valve only very much difficult to adjust so that reproducible partial opening stroke positions the valve member, or a persistence of the valve member in partial opening positions with the known fuel injection valve are not possible.

Advantages of the invention

The fuel injection valve according to the invention for internal combustion engines with the characterizing features of the claim 1 has the advantage that the operation of the valve member regardless of the high fuel pressure in Pressure chamber is carried out by an additional actuator. This separately actuated actuator is advantageous Formed as a piezo actuator, but can also by other electromechanical actuators are replaced. Around the relatively small axial movement of the Piezo actuator in a sufficiently large axial Converting the adjustment movement of the valve member is between the piezo actuator and the valve member in an advantageous manner a hydraulic translation space is provided, through which the relatively small adjustment movement of the piezo actuator in one relatively larger adjustment stroke movement converted on the valve member becomes. It is particularly advantageous between the Piezo actuator and the valve member another control piston to be provided by means of a spring with its first end face is constantly kept in contact with the piezo actuator and pre-stressed this and the one with its second averted Front surface protrudes into the hydraulic work area. Here this hydraulic work area does not only act as Translation space but also takes on the function of a Temperature compensation on the piezo actuator. To do the Keeping actuating forces on the valve member as small as possible is the valve member is pressure balanced, for which purpose in advantageously the two the pressure chamber in the valve body limiting pressure shoulders have the same pressure application area exhibit. The closing force on the valve member becomes alone applied by the valve spring, creating a special simple construction is achieved and also the piezo actuator only has to overcome the force of this valve spring. In a further embodiment has the valve member one acting in the closing direction of the valve member additional third pressure shoulder on, which is also constant is connected to the high-pressure fuel supply line, so that the closing force on the valve member is more advantageous Always proportional to the pressure in the High pressure fuel supply system rises.

The fuel injector can be a so-called Vario register nozzle with a multitude of one above the other arranged spray holes or as a so-called Vario slot nozzle with a rectangular slit-shaped Injection cross section can be formed depending different from the valve member opening stroke Release injection opening cross sections. The Injection cross section or injection course freely selected and be adapted to a corresponding engine map, where both partial strokes, rate shaping and pilot injections possible are. The valve member can now by Actuation by the separate actuator, preferably one Piezo actuator independent of the high fuel pressure in its Opening stroke position can be set. The injection takes place compared to other types of nozzles, even when activated of a partial stroke without throttling, so that the full Pressure energy benefits the jet preparation.

Further advantages and advantageous configurations of the object the invention are the description, the drawing and the patent claims.

drawing

Four embodiments of the fuel injection valve according to the invention for internal combustion engines are in the Drawing shown and are in the following description explained in more detail. 1 shows a longitudinal section by a first embodiment with only two Pressure application surfaces on the valve member, Figure 2 a Enlarged sectional view of Figure 1 in the area the valve member head, the injection opening at first embodiment as a rectangular slot 3, a second embodiment analogous to the representation of Figure 2, in which the Injection openings through axially one above the other Injection bores are formed, Figure 4 is a third Embodiment analogous to the representation of Figure 1, at which an additional third pressure application surface on the valve member is provided and Figure 5 shows a fourth embodiment analogous to the representation of Figure 1, in which the valve member via an attached intermediate piston in the hydraulic working space protrudes.

Description of the embodiments

The first embodiment shown in Figure 1 of the fuel injection valve according to the invention for internal combustion engines has a valve body 1, which by means of a union nut 3 on a valve holding body axially is clamped. The valve body 1 has an axial Guide bore 7 in which a piston-shaped valve member 9 is guided axially displaceably, as in FIG. 2 shown enlarged, at its in a combustion chamber supplying internal combustion engine projecting lower end has valve head 11 acting as a valve closing member. This protruding from the bore 7 valve head 11 has one the conical sealing surface 13 facing the valve body 1, which in the first embodiment by one on the Valve member head 11 seat ring 15 is formed and which with a corresponding valve seat 17 on the Front side of the valve body on the combustion chamber side 1 cooperates. It is between the wall of the bore 7 and a pressure chamber 19 in part of the shaft of the valve member 9 in the valve body 1 formed axially by one Pressure shoulder on the valve member 9 is limited. It points a first upper pressure shoulder 21 at the end remote from the combustion chamber of the pressure chamber 19 the same pressure application area as a second lower pressure shoulder 23 near the combustion chamber so that Valve member 9 pressure balanced in the first embodiment is. The valve member 9 has, as in FIG. 2 shown enlarged, at least one injection channel 25 in the valve head 11, each by one of the lower Pressure shoulder 23 outgoing axial blind bore 27 and a formed by this radial injection opening 29 is. This radial injection opening 29 points in the first Embodiment a rectangular or slit-shaped Cross-section and opens out from the blind bore 27 so on the peripheral surface of the valve head 11 that the Injection opening 29 when the valve member 17 bears against the valve seat 9 is closed by the wall of the bore 7 and during the outward opening stroke movement of the Valve member 9 only after lifting the sealing surface 13 from Valve seat 17 from overlap with bore 7 emerges.

The valve member 9 protrudes with a shaft part 31 in a Valve holding body 5 provided spring space 33 and points there a spring plate 35 firmly connected to the valve member 31 on. A valve spring 37 acts on this spring plate 35, on the other hand, with the interposition of spacer rings 39 on the end face 41 facing away from the combustion chamber Valve body 1 supports and so the valve member 9 in contact holds biased on valve seat 17. That sticks out End of the upper shaft part 31 facing away from the combustion chamber Valve member 9 with its end face facing away from the combustion chamber 43 in a hydraulic translation space 45, the preferably in an axially on the valve holding body 5 attached guide body 47 is arranged. In these hydraulic translation space 45 protrudes on the End face 43 of the valve member 9 opposite side a two-part adjusting piston 49 with its combustion chamber side End face 51, the end face 51 being a larger one Cross section has as the end face 43 of Valve element 9. The actuating piston 49 is replaced by one that Actuator biasing return spring 53 via a Ring 55, a sealing washer 57 and a spring plate 59 kept constantly in contact with an electrical actuator, which in the exemplary embodiment is designed as a piezo actuator 61 is. This piezo actuator 61 is designed so that it Applying an electrical voltage to its axial length enlarged and so the actuating piston 49 in the direction of the valve member 9 moves.

The high-pressure fuel supply to the fuel injector takes place via a pressure channel 63 in the valve holding body 5, the continues in the valve body 1 and there in the pressure chamber 19 opens. The pressure channel 63 is not one Connection piece shown in more detail to an injection line 65 connected, which in turn from one for all injectors Common high-pressure storage space (common rail) 67 dissipates. This high-pressure storage space 67 is in known manner from a high pressure fuel delivery pump High pressure fuel filled from a storage tank.

The fuel injection valve according to the invention for internal combustion engines works in the following way. In closed Condition, i.e. when the piezo actuator 61 is not energized, this becomes Valve member 9 of the valve spring 37 with its sealing surface 13 held in contact with valve seat 17. Here are the Injection openings 29 of the injection channel 25 from the wall the bore 7 in the valve body 1 closed. The one in the high-pressure storage room 67 located high fuel pressure sets itself via the injection line 65 and the pressure channel 63 into the pressure chamber 19 and is therefore also in the Injection channel 25 or at the injection openings 29. There the pressure shoulders 21 and 23 on the valve member 9 have the same pressure application surface, the valve member 9 pressure equalized and is by the valve spring 37 in Closed position maintained. Should now be an injection on The piezo actuator 61 is energized and injected immediately increases its axial extent. As a result of axial expansion of the piezo actuator 61 becomes the two-part Actuating piston 49 in the direction of the hydraulic working space 45 shifted and displaced a relative in this space large volume of liquid. Through the filled with leak oil Liquid cushion in the hydraulic translation space 45 is now also the valve member 9 against the Restoring force of the valve spring 37 from its valve seat 17th moved so that the sealing surface 13 from the valve seat 17th takes off and the injection openings 29 from the overlap with immerse the wall of the bore 7 of the valve body 1. Here begins with the injection opening 29 emerging from the Bore 7 of the injection process in the combustion chamber supplying internal combustion engine. It is now through the regulated energization of the piezo actuator 61 possible axial expansion and thus the opening stroke movement of the Valve member 9 continuously adjust so that with the any fuel injector according to the invention Partial opening cross section at the injection opening 29 can be adjusted. The full one Injection opening cross-section reached when the radial Injection openings 29 completely out of bore 7 are out. Closing the injector again takes place by de-energizing the piezo actuator 61 as a result, the axial expansion of the piezo actuator 61 decreased again. The return movement of the actuating piston 49 and the piezo actuator 61 are thereby fixed to the housing supporting return spring 53 supports. As a result of Reset of the actuating piston 49 is now also by the Force of the valve spring 37 again engages the valve member 9 moved to the valve seat 17 and the injection valve closes.

The second embodiment shown in Figure 3 differs from that shown in FIGS. 1 and 2 first embodiment only in the training of Valve head 11 and the injection channel provided therein 25. The injector is now not as in the Figures 1 and 2 as a so-called Vario slot nozzle but as Vario register nozzle designed. The function of the seat ring is now taken over by a sleeve 69 with a section 71 facing away from the combustion chamber protrudes into the guide bore 7 in the valve body 1. Of the Injection channel 25 is now through axial recesses 73 formed at the valve head end of the valve member 9, the extend into the area 71 of the sleeve 69. Here are two in the region 71 of the sleeve 69 in the embodiment Rows of axially superimposed radial injection bores 75 provided in the sleeve 69, which is analogous to the Injection openings 29 of the first embodiment so in the peripheral wall of the valve member head 11 or the sleeve 69 flow into a valve member lying against the valve seat 17 9 closed by the wall of the bore 7 in the valve body 1 and during the outward opening stroke movement the valve member 9 by emerging from the bore 7 are controllable one after the other. To do a variety of Connect injection bores 75 to the recesses 73 is also an annular groove 77 in the area of Injection bores 75 are provided on valve member 9. The sleeve 69 is firmly attached to the valve member 9, preferably pressed on or shrunk on.

The third embodiment shown in Figure 4 differs from the first one shown in FIG Embodiment by providing another additional fuel pressurized Attack surface on the valve member 9, through which the injector pending high fuel pressure in the closing direction the valve member 9 acts. This additional pressure application area is in the third embodiment by a additional third pressure shoulder 79 formed by a lower end face of a pressure sleeve 81 on the combustion chamber side is formed. This pressure sleeve 81 is on the top Shaft part 31 of the valve member 9 pushed on and lies with its upper face away from the combustion chamber at a stop on the valve member 9. This stop of the pressure sleeve 81 in The closing direction of the valve member 9 is determined by a into a corresponding receiving groove on the valve member 9 inserted circlip 83 formed. In addition, the third pressure shoulder 79 a closing pressure space 85 is provided, between the end face of the pressure sleeve on the combustion chamber side 81 and the combustion chamber end face 41 of the valve body 1 is limited and that via a connecting channel 87 from the pressure channel 63 filled with high fuel pressure becomes. It has the formation of the third embodiment the advantage that the acting on the valve member 9 Closing force always proportional to the high fuel pressure in the Pressure storage system rises.

In the fourth exemplary embodiment of the fuel injection valve according to the invention for internal combustion engines shown in FIG. 5, an intermediate piston 93 projects with its upper end face 95 into the hydraulic working space 45 at the end face 91 of the control piston 49 directly connected to the piezo actuator 61, the end face 95 of the bottom lying intermediate piston 93 is formed smaller than the end face 91 of the actuating piston 49. With its lower end facing the combustion chamber, the intermediate piston 93 is axially fitted onto the upper shaft part 31 of the valve member 9, which has the advantage that the valve member 9 itself is no longer in the hydraulic Translation space 45 protrudes. In this way, different valve elements can be adapted to different actuating pistons without major conversion measures, with different hydraulic ratios in the hydraulic translation space 45 being adjustable via their design of donor and acceptor piston cross sections.
Analogous to the previous exemplary embodiments, there is always a gap between the piston parts 49, 93 projecting into the hydraulic working space 45, which is ensured by the static pressure in the working space 45. In the fourth exemplary embodiment, the axial play compensation of the piezo actuator 61 likewise takes place via the hydraulic translation space 45, a throttle gap between the intermediate piston 93 and the wall of the bore preventing the valve member 9 from being opened inadvertently. In order to achieve a bias of the piezo actuator 61, a corresponding spring can also be provided on the piezo actuator 61.

Claims (8)

  1. Fuel injection valve for internal combustion engines with one in a bore (7) of a valve body (1) axially Slidable valve member (9) on its combustion chamber side End one forming a valve closing member Has valve head (11) on its the valve body (1) facing side has a sealing surface (13) with which he with a on the combustion chamber side of the Valve body (1) provided valve seat surface (17) cooperates and with injection openings (29) in the valve member head (11) by one between the valve member (9) and the wall of the bore (7) formed pressure chamber (19) laxative on the peripheral wall of the valve member head (11) emerge, the injection openings (29) at the valve seat (17) adjacent valve member (9) from the wall of the Bore (7) are closed and during the outward directed opening stroke movement of the valve member (9) by Diving out of the bore (7) can be controlled thereby characterized in that the valve member (9) from an outside controllable actuator, regardless of high fuel pressure can be actuated in the pressure chamber (19).
  2. Fuel injection valve according to claim 1, characterized characterized in that the actuator as an electromechanical Actuator, preferably designed as a piezo actuator (61) is.
  3. Fuel injection valve according to claim 2, characterized characterized in that between the piezo actuator (61) and the Valve member (9) a hydraulic translation space (45) is provided, via which an axial adjustment movement of the Piezo actuator (61) in a relatively larger axial adjustment movement the valve member (9) is reinforced.
  4. Fuel injection valve according to claim 1, characterized characterized in that two axially the pressure chamber (19) delimiting mutually facing pressure shoulders (21, 23) on piston-shaped valve member (9) are provided, each have the same pressure application area.
  5. Fuel injection valve according to claim 4, characterized characterized in that an additional on the valve member (9) third pressure shoulder acted on by the high pressure fuel (79) is provided, at which the high fuel pressure in Closing direction of the valve member (9) to the valve seat (17) attacks.
  6. Fuel injection valve according to claim 5, characterized characterized in that the third pressure shoulder (79) on a Face of one arranged on the valve member (9) Pressure sleeve (81) is formed which in the closing stroke direction of the Valve member (9) firmly connected to the valve member (9) is.
  7. Fuel injection valve according to claim 1, characterized characterized in that the high-pressure fuel supply from a common high pressure storage space for all fuel valves (67), which in turn is via a high-pressure fuel pump can be filled.
  8. Fuel injection valve according to claim 3, characterized characterized in that the piston-shaped valve member (9) over an actuating piston (49) is operatively connected to the piezo actuator (61) the actuating piston (49) by means of a spring (37, 53) is held in contact with the piezo actuator (61) and with its lower end face 51 near the combustion chamber in the hydraulic Translation space (45) protrudes.
EP98106006A 1997-04-18 1998-04-02 Fuel injection valve for internal combustion engines Withdrawn EP0872636A3 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE1997116226 DE19716226C2 (en) 1997-04-18 1997-04-18 Fuel injection valve for internal combustion engines
DE19716226 1997-04-18

Publications (2)

Publication Number Publication Date
EP0872636A2 true EP0872636A2 (en) 1998-10-21
EP0872636A3 EP0872636A3 (en) 2002-01-23

Family

ID=7826893

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98106006A Withdrawn EP0872636A3 (en) 1997-04-18 1998-04-02 Fuel injection valve for internal combustion engines

Country Status (2)

Country Link
EP (1) EP0872636A3 (en)
DE (1) DE19716226C2 (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2782795A1 (en) * 1998-08-27 2000-03-03 Siemens Ag Device for controlling fluid addition, especially applicable to fuel injection, has a hydraulic based controller system for regulating the opening and closing of the fuel injection nozzle
FR2786269A1 (en) * 1998-11-25 2000-05-26 Siemens Ag Device for the injection of a fluid comprising a variation in the pressure of the fluid injected
EP1077326A2 (en) * 1999-08-18 2001-02-21 Delphi Technologies, Inc. Fuel injector
DE19943142A1 (en) * 1999-09-09 2001-04-12 Siemens Ag Direct fuel injection dosing/proportioning device especially for petrol and diesel-powered combustion engines
WO2001057393A2 (en) * 2000-02-04 2001-08-09 Robert Bosch Gmbh Hydraulic lift translation system
WO2003085253A1 (en) * 2002-04-04 2003-10-16 Siemens Aktiengesellschaft Injection valve

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19905152C1 (en) * 1999-02-08 2000-07-27 Univ Dresden Tech Fuel injection nozzle for internal combustion engine has pressure accumulator with nozzle body in which nozzle needle, with central bore open to combustion chamber, is fitted
DE19922964C2 (en) * 1999-05-19 2003-03-27 Daimler Chrysler Ag Method of injecting diesel fuel
DE19946603B4 (en) * 1999-09-29 2009-01-15 Robert Bosch Gmbh Fuel injection valve with compensating sealing elements
DE10007735A1 (en) * 2000-02-19 2001-09-06 Daimler Chrysler Ag Fuel injection valve for IC engines has pressure-reducing throttle between high-pressure fuel in fuel chamber/line and lower pressure fuel in valve needle actuator area

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4442764A1 (en) 1994-12-01 1996-06-05 Bosch Gmbh Robert Fuel injection valve for internal combustion engines

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01187363A (en) * 1988-01-21 1989-07-26 Toyota Motor Corp Fuel injection valve for internal combustion engine
US5031841A (en) * 1989-02-28 1991-07-16 Volkswagen Ag Metering valve, particularly fuel injection valve
DE4306072C2 (en) * 1993-02-26 1994-12-08 Siemens Ag Device for opening and closing a passage opening in a housing
DE4325904C2 (en) * 1993-08-02 1995-07-20 Daimler Benz Ag Fuel injection system provided for a diesel internal combustion engine with a high-pressure pump delivering the fuel into a common supply line (common rail) for all injection nozzles
DE19500706C2 (en) * 1995-01-12 2003-09-25 Bosch Gmbh Robert Metering valve for dosing liquids or gases
DE19534445C2 (en) * 1995-09-16 1998-07-30 Man Nutzfahrzeuge Ag Injection valve for internal combustion engines

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4442764A1 (en) 1994-12-01 1996-06-05 Bosch Gmbh Robert Fuel injection valve for internal combustion engines

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2782795A1 (en) * 1998-08-27 2000-03-03 Siemens Ag Device for controlling fluid addition, especially applicable to fuel injection, has a hydraulic based controller system for regulating the opening and closing of the fuel injection nozzle
FR2786269A1 (en) * 1998-11-25 2000-05-26 Siemens Ag Device for the injection of a fluid comprising a variation in the pressure of the fluid injected
EP1077326A2 (en) * 1999-08-18 2001-02-21 Delphi Technologies, Inc. Fuel injector
EP1077326A3 (en) * 1999-08-18 2003-01-22 Delphi Technologies, Inc. Fuel injector
DE19943142A1 (en) * 1999-09-09 2001-04-12 Siemens Ag Direct fuel injection dosing/proportioning device especially for petrol and diesel-powered combustion engines
WO2001057393A2 (en) * 2000-02-04 2001-08-09 Robert Bosch Gmbh Hydraulic lift translation system
WO2001057393A3 (en) * 2000-02-04 2001-12-20 Bosch Gmbh Robert Hydraulic lift translation system
WO2003085253A1 (en) * 2002-04-04 2003-10-16 Siemens Aktiengesellschaft Injection valve
US7886993B2 (en) 2002-04-04 2011-02-15 Siemens Aktiengesellschaft Injection valve

Also Published As

Publication number Publication date
DE19716226C2 (en) 1999-04-22
DE19716226A1 (en) 1998-10-29
EP0872636A3 (en) 2002-01-23

Similar Documents

Publication Publication Date Title
US5685483A (en) Fuel injection valve for internal combustion engines
US6499669B2 (en) Fuel injection valve for internal combustion engines
US5890471A (en) Fuel injection device for engines
EP1693562B1 (en) Fuel injector
US5803361A (en) Fuel injector for internal combustion engines
US6612508B2 (en) Fuel injector
US6220528B1 (en) Fuel injector including an outer valve needle, and inner valve needle slidable within a bore formed in the outer valve needle
DE60126380T2 (en) Fuel injection valve
JP2601977B2 (en) Electromagnetic fuel injection valve
US6340121B1 (en) Fuel injector
EP1041272B1 (en) Fuel injector
EP0823550B1 (en) Injector
US5551634A (en) Fuel injection nozzle for an internal combustion engine
US6085719A (en) Fuel injection system for internal combustion engines
EP2171258B1 (en) Control valve for a fuel injection valve
EP1692393B1 (en) Injector used to inject fuel into internal combustion chambers in internal combustion engines, particularly, a piezo-actuator controlled common-rail-injector
US6427968B1 (en) Valve for controlling fluids
US6745750B2 (en) Fuel injection system for internal combustion engines
DE102004005452B4 (en) Nozzle holder combination with direct-operated injection valve member
EP1339966B1 (en) Injection nozzle comprising two separately controllable nozzle needles
EP1303697B1 (en) Fuel injection valve
US6789743B2 (en) Injection valve having a bypass throttle
EP0898650B1 (en) Fuel injection device for internal combustion engines
EP0657642B1 (en) Fuel injection device for internal combustion engines
US6076800A (en) Valve for controlling fluids

Legal Events

Date Code Title Description
AX Request for extension of the european patent to

Free format text: AL;LT;LV;MK;RO;SI

AK Designated contracting states:

Kind code of ref document: A2

Designated state(s): DE FR GB IT

Kind code of ref document: A2

Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AK Designated contracting states:

Kind code of ref document: A3

Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent to

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20020723

AKX Payment of designation fees

Free format text: DE FR GB IT

17Q First examination report

Effective date: 20030110

18D Deemed to be withdrawn

Effective date: 20030521