EP1424492A2 - Ventil zum Steuern von Flüssigkeiten mit einem Düsen- und einem Steuerventil - Google Patents
Ventil zum Steuern von Flüssigkeiten mit einem Düsen- und einem Steuerventil Download PDFInfo
- Publication number
- EP1424492A2 EP1424492A2 EP03014694A EP03014694A EP1424492A2 EP 1424492 A2 EP1424492 A2 EP 1424492A2 EP 03014694 A EP03014694 A EP 03014694A EP 03014694 A EP03014694 A EP 03014694A EP 1424492 A2 EP1424492 A2 EP 1424492A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- actuator
- spring
- control
- spring device
- 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- Withdrawn
Links
- 239000012530 fluid Substances 0.000 title abstract 2
- 239000007788 liquid Substances 0.000 claims description 7
- 230000004913 activation Effects 0.000 claims 1
- 239000000446 fuel Substances 0.000 abstract description 40
- 238000002347 injection Methods 0.000 description 29
- 239000007924 injection Substances 0.000 description 29
- 238000002485 combustion reaction Methods 0.000 description 11
- 239000012528 membrane Substances 0.000 description 5
- 239000000919 ceramic Substances 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 229910000639 Spring steel Inorganic materials 0.000 description 1
- 230000003213 activating effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 230000002123 temporal effect Effects 0.000 description 1
Images
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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/167—Means for compensating clearance or thermal expansion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
Definitions
- the invention relates to a valve for controlling liquids with a nozzle module and with a control module to control the nozzle module according to the in the preamble of Claim 1 defined in more detail.
- valves When using such valves in a common rail system as a common rail injector, an injection starts, an injection duration and an injection quantity via force ratios set in the valves.
- a valve member will each controlled by an actuator that is located on a valve control and side of the valve member facing away from the combustion chamber is arranged.
- the two pistons are axially displaceable in a longitudinal bore of a valve housing arranged, the first piston being an actuating piston the actuator system of the valve and the second piston, which actuates a valve closing member, a so-called actuating piston which represents actuator technology.
- the hydraulic chamber provides a hydraulic translation between the actuating piston and the actuating piston, so that a deflection of the actuator is sufficient displacement of the valve closing member.
- the hydraulic chamber closes between the two delimiting them Pistons where the diameter of the second piston is smaller is a common as the diameter of the first piston Compensation volume.
- the hydraulic chamber is there clamped between the pistons such that the second piston of the valve member one around the transmission ratio the piston diameter makes the stroke larger when the larger first pistons through the actuator by a certain distance is moved.
- the valve member, its pistons and the Actuators are arranged in a row.
- Tolerances can be set via the compensation volume of the hydraulic chamber due to temperature gradients in the component or different coefficients of thermal expansion of the used materials as well as possible setting effects in Valve can be compensated without making a change the position of the valve closing element to be controlled occurs.
- Valves modified in this way have in addition, significantly more space is required, but this is particularly so is not available for internal combustion engines.
- the valve for controlling liquids according to the invention with a nozzle module and with a control module for actuation of the nozzle module the control module being an actuator and a control valve which can be actuated directly by the actuator has, and wherein to compensate for temperature and component tolerances a compensation device is provided, which on a side of the actuator facing away from the control valve is arranged has the advantage that the valve has a high degree of rigidity and requires little installation space and has a simple constructive design.
- the higher rigidity of the valve according to the invention results from the fact that when the valve is opened, which via control of the nozzle module by the actuator takes place, the actuator directly accesses the control valve. Movements of the actuator, which trigger the control valve will advantageously not result as with valves known from practice via the compensating device transferred to the control valve.
- the compensation device with a hydraulic chamber and one between the hydraulic chamber and the Actuator can be moved longitudinally in a housing of the valve arranged compensating element executed.
- the Actuator is against when the control valve is activated a rigid medium of the hydraulic chamber is supported, whereby a movement of the compensating element to control the Control valve is not required.
- the compensation element is only for length compensation in the axial direction of the Valve moves.
- valve for controlling liquids according to the invention is schematic in the drawing is shown in simplified form and is described in the following Description explained in more detail.
- the only figure in the drawing shows a partial longitudinal section through an inventive valve in a fuel injection valve for internal combustion engines of motor vehicles.
- Valve for controlling liquids shows a use of the valve according to the invention in a fuel injection valve 1 of motor vehicles, which in the present Design as a common rail injector for injection of fuel in a combustion chamber of an internal combustion engine is trained.
- the fuel injection is above the pressure level in a valve control chamber 2 of a nozzle module 3, which connected to a high pressure supply.
- the Pressure level of the valve control room 2 is controlled by a control module 39 of the fuel injection valve 1 is set.
- an injection duration and an injection quantity over force ratios in the Fuel injector 1 becomes an actuator 4 via an actuator designed as a piezoelectric actuator 5 of the control module 39 driven, which on the Valve control chamber 2 of the fuel injector 1 and the Combustion chamber of an internal combustion engine facing away from the Actuator 4 is arranged.
- the piezoelectric actuator or the actuator 5 is in on known manner from several schematically represented built up ceramic layers 6 and points to the An actuator head 7 facing the actuating element 4 and on its side facing away from the actuating element 4 an actuator foot 8, the latter on a compensating element 9 a compensation device 12 supports.
- the actuator 5 consists of several Components, the piezoceramic layers 6 between the actuator head 7 and the actuator base 8 via a concentric arranged to the piezoceramic layers 6, extending in the axial direction, substantially cylindrical and thin-walled spring sleeve 15 firmly are clamped.
- the spring sleeve 15 is presently inexpensive stainless steel and is made with the Actuator head 7 and the actuator base 8 welded. Furthermore is the spring sleeve 15 to increase its resilient Properties with several arranged over their circumference Openings 40 executed and of a thin-walled Surrounded sleeve 16 to counter the piezoceramic layers 6 Areas of the fuel injector that carry fuel 1 seal.
- the actuator 5 is in the area of its actuator head 7 by means of a spring steel formed here Membrane 17 for sealing the piezoceramic layers 6 towards the fuel-guiding areas of the fuel injector 1 executed.
- the membrane 17 extends essentially in the radial direction ring-shaped and has a central breakthrough for a peg-shaped area 18 of the actuator head 7.
- the shape of the membrane 17 is essentially in the axial direction elliptical to arched.
- On the inside of the cone-shaped area 18 Limitation is the membrane 17 via a weld seam with the Actuator head 7 firmly connected.
- On the outer sleeve 16 facing boundary of the membrane 17 is a Weld seam connected to the sleeve 16 so that the piezoceramic Layers 6 do not come into contact with fuel.
- valve closing member 13 of a control valve 14 acts with a spherical segment-shaped area executed valve closing member 13 of a control valve 14 with a valve seat formed on a valve housing 19 20 together such that the valve closing member 13 at System on the valve seat 20 a connection between a Low pressure area 21 and an intermediate pressure area 22 separates.
- the valve seat 20 is in one of the valve housing 19 formed valve chamber 23 arranged, the intermediate pressure side via an outlet throttle 25 with the valve control chamber 2 of a high pressure area 26 is connected.
- the valve control chamber 2 is of the valve housing 19 and one partially illustrated nozzle needle 27, wherein depending on a pressure level in the valve control room 2 the nozzle needle 27 from a not shown Valve seat lifts off to seal several in one nozzle body of the nozzle module 3 distributed over its circumference arranged, not shown injection openings is provided.
- the valve control chamber 2 is connected via an inlet throttle 28 connected to the high pressure region 26, which in turn is connected to a provided for several fuel injectors together High-pressure storage space (common rail) in connection stands. From the high-pressure storage room, several Injection nozzles or nozzle modules of fuel injection valves an internal combustion engine supplied with fuel.
- the actuating element 4 via a second spring device 29 against the actuator head 7 pressed, the second spring device 29 being a spring 30, which is in the pretensioned installation position between the valve housing 19 and a collar 31 of the actuating element 4 is located.
- valve closing member 13 in the figure position shown by a third spring device 32 pressed sealingly against the valve seat 20.
- the third spring device 32 ensures that in the Valve control room 2 in particular when starting a motor vehicle or an internal combustion engine of the motor vehicle builds up pressure that works or the closing of the fuel injector 1 required is.
- the hydraulic chamber 10 forms together with the Compensating element 9 and the spring device 11, the compensating device 12, which to compensate for length tolerances, through manufacturing tolerances and in operation Temperature fluctuations in the fuel injection valve 1 occur.
- the compensation volume the hydraulic chamber 10 also due to tolerances of temperature gradients in the component due to different Thermal expansion coefficients of each Components of the fuel injection valve 1 occur as well as possible setting effects.
- the tolerances do not cause a position to change of the valve closing member 13 to be controlled, which under The fuel injector may malfunction 1 can lead. There is a functional failure for example, if due to changes in length in the valve, the control valve 14 no longer closes is possible and the valve closing member 13 due to the changed Component dimensions no longer on the valve seat 20 comes to the concern.
- the fuel injection valve 1 according to the figure operates in described below.
- the fuel injector is in the state shown in the figure 1 closed.
- An injection initiate the fuel injector 1, that Control valve 14 opened.
- the pressure level the valve control room 2 lowered to a value at which the nozzle needle 27 lifts from its valve seat and liquid or fuel through the injection openings of the nozzle module 3 in a combustion chamber of an internal combustion engine is injected.
- the switching valve 14 is opened in that the actuator 5 or its piezoceramic layers 6 are energized, causing elongation of the actuator's piezoelectric ceramic leads.
- the elongation of the piezoceramic layers 6 or the piezoelectric ceramic causes an axial adjustment that is operatively connected to the piezoelectric actuator 5 Actuator 4.
- the axial displacement of the actuating element 4 leads to a lifting of the valve closing member 13 from the valve seat 20 as well as to the here prevailing and described pressure conditions in Valve 1.
- the spring devices or their spring elements are present each designed as coil springs, it of course, is at the discretion of the professional who Spring devices depending on the present Application with other suitable resilient elements, such as disc springs.
- the spring force of the first spring device 11 is present 40 N.
- the spring force of the second spring device In the present case, 29 is set to a value of 30 N, and the spring force of the third spring device 32 has one Value of 20 N.
- the stated values of the spring forces of the Spring devices are exemplary and are hydraulic on the effective areas of the actuator system of the fuel injector Voted.
- the spring forces of the spring devices of the spring system of the fuel injector are depending on the area ratios and also the pressure conditions in the fuel injector adjust, the quantitative ratios described above between the spring forces of the individual spring devices for the functioning of the fuel injector are to be observed.
- the spring devices 11, 29 and 32 form a spring system of the fuel injection valve 1, which as the compensation piston executed compensation element 9, the actuator 5, the Actuator 4 and the valve closing member 13 in the closed Condition of fuel injector 1 without gaps presses against each other.
- the spring forces are the three Spring devices 11, 29 and 32 matched to one another in such a way that the valve closing member 13, the actuator 4 and the actuator 5 in the direction of the compensating element 9 are relocated. This ensures that the valve closing member 13 in the closed state of the fuel injector 1 rests sealingly on the valve seat 20 and the actuating element 4 at the same time without gaps on the valve closing member 13 and on the actuator 5 for Facility is coming.
- the gap-free system between the individual components of the Actuator system of fuel injector 1 leads to the fact that by activating or energizing the actuator 5 Control of the control valve 14 and thus the entire Fuel injection valve 1 is carried out without delay. In order to ensures that injection is extremely precise can be done and an undesirable temporal Delay in the start or end of injection is avoided.
- the first spring device 11 executed with such a spring force is that the compensating element 9 when closed Control valve 14 against the spring force of the second spring device 29 is pressed without a gap against the actuator 5.
- the mode of operation of the compensation device 12 is based on that the volume of the hydraulic chamber 10 or in the Hydraulic chamber 10 fuel available depending an operating temperature of the fuel injection valve 1 varies and the compensating element 9 more or less deep immersed in the hydraulic chamber 1.
- the one that occurs Supply or discharge of fuel into the hydraulic chamber 10 or out of this takes place via a between the compensating element 9 and the valve housing 19 formed Gap space 33, which is a connection between the hydraulic chamber 10 and a longitudinal bore 34 of the valve housing 19, in which the actuator 5 is arranged.
- a leakage drain channel branches from the longitudinal bore 34 24 in the direction of the low pressure region 21, wherein in a filling valve 35 is arranged in the leakage drain channel 24 is.
- the filling valve 35 is present as a check valve executed, which in the present case with a spherical Closing element 36 and one closing element 36 against one Filling valve seat 37 pressing spring element 38 executed is.
- the longitudinal bore 34 and the low pressure region 21st the filling valve 35 is either open or closed.
- the task of the filling valve 35 is that in the presence of a Pressure drop between the longitudinal bore 34 and the low pressure area 21 the leakage drain channel 24 is open and the pressure in the longitudinal bore 34 in the direction of the low pressure area 21 is reduced, the opening pressure of the filling valve 35 in the longitudinal bore 34 also in the present case is dependent on the spring force of the spring element 38. is however, the pressure difference is too small or the pressure of the Low pressure area 21 greater than the pressure in the longitudinal bore 34, the filling valve 35 and thus the Leakage drain channel 24 closed.
- the limit value represents a defined pressure value represents, in the presence of which the hydraulic chamber is not in one is filled in such an undesirable manner that the compensating element 9 too much in the direction of the actuator 5 is moved and the valve closing member 13 when de-energized Actuator 5 lifts off the valve seat 20.
- the fuel injection valve 1 described here with the spring system and the filling valve 35 compares to valves known from practice a much more compact and stiffer design, due to a combination a fuel filling of the compensation device 12 from, for example, a 30 bar leak oil system or the Low pressure area 21 and the three spring devices one Alignment of the actuator system of the fuel injection valve 1 on the valve seat 20 of the control valve 14.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
- Temperature-Responsive Valves (AREA)
Abstract
Description
Claims (8)
- Ventil (1) zum Steuern von Flüssigkeiten mit einem Düsenmodul (3) und mit einem Steuermodul (39) zum Ansteuern des Düsenmodules (3), wobei das Steuermodul (39) einen Aktuator (5) und ein von dem Aktuator (5) direkt betätigbares Steuerventil (14) aufweist, und wobei zum Ausgleich von Temperatur- und Bauteiltoleranzen eine Ausgleichseinrichtung (12) vorgesehen ist, welche auf einer dem Steuerventil (14) abgewandten Seite des Aktuators (5) angeordnet ist.
- Ventil nach Anspruch 1, dadurch gekennzeichnet, daß die Ausgleichseinrichtung (12) eine Hydraulikkammer (10) und ein zwischen der Hydraulikkammer (10) und dem Aktuator (5) in einem Ventilgehäuse (19) längsbeweglich verschieblich angeordnetes Ausgleichselement (9) hat.
- Ventil nach Anspruch 2, dadurch gekennzeichnet, daß das Ausgleichselement (9) über eine erste Federeinrichtung (11) gegen den Aktuator (5) angefedert ist.
- Ventil nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß zwischen einem Ventilschließglied (13) des Steuerventils (14) und dem Aktuator (5) ein Betätigungselement (4) angeordnet ist, welches über eine zweite, der ersten Federeinrichtung (11) entgegenwirkende Federeinrichtung (29) gegen den Aktuator (5) gedrückt ist.
- Ventil nach Anspruch 4, dadurch gekennzeichnet, daß das Ventilschließglied (13) bei geschlossenem Steuerventil (14) von einer dritten Federeinrichtung (32) gegen einen Ventilsitz (20) gedrückt ist.
- Ventil nach Anspruch 5, dadurch gekennzeichnet, daß eine Federkraft der dritten Federeinrichtung (32) größer als die Federkraft der ersten Federeinrichtung (11) und größer als die Federkraft der zweiten Federeinrichtung (29) ist.
- Verfahren nach Anspruch 5 oder 6, dadurch gekennzeichnet, daß die Federkraft der dritten Federeinrichtung (32) kleiner ist als die Summe der Federkräfte der ersten Federeinrichtung (11) und der zweiten Federeinrichtung (29).
- Ventil nach einem der Ansprüche 2 bis 7, dadurch gekennzeichnet, daß der Aktuator (5) in einer Längsbohrung (34) des Steuermodules (39) angeordnet ist, die mit der Hydraulikkammer (10) verbunden ist und über ein Befüllventil (35) mit einem Niederdruckbereich (21) gesteuert verbindbar ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE2002154985 DE10254985A1 (de) | 2002-11-26 | 2002-11-26 | Ventil zum Steuern von Flüssigkeiten mit einem Düsen- und einem Steuermodul |
DE10254985 | 2002-11-26 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1424492A2 true EP1424492A2 (de) | 2004-06-02 |
EP1424492A3 EP1424492A3 (de) | 2006-03-01 |
Family
ID=32240409
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03014694A Withdrawn EP1424492A3 (de) | 2002-11-26 | 2003-06-27 | Ventil zum Steuern von Flüssigkeiten mit einem Düsen- und einem Steuerventil |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1424492A3 (de) |
DE (1) | DE10254985A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007098986A1 (de) * | 2006-02-28 | 2007-09-07 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
EP2090771A1 (de) * | 2008-02-13 | 2009-08-19 | Robert Bosch Gmbh | Kraftstoffinjektor mit einer direkt gesteuerten Ventilnadel |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2001053693A2 (de) | 2000-01-20 | 2001-07-26 | Robert Bosch Gmbh | Ventil zum steuern von flüssigkeiten |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4529164A (en) * | 1982-03-05 | 1985-07-16 | Nippon Soken, Inc. | Piezo-type valve |
DE19727992C2 (de) * | 1997-07-01 | 1999-05-20 | Siemens Ag | Ausgleichselement zur Kompensation temperaturbedingter Längenänderungen von elektromechanischen Stellsystemen |
DE19821768C2 (de) * | 1998-05-14 | 2000-09-07 | Siemens Ag | Dosiervorrichtung und Dosierverfahren |
DE19946840A1 (de) * | 1999-09-30 | 2001-05-03 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
-
2002
- 2002-11-26 DE DE2002154985 patent/DE10254985A1/de not_active Withdrawn
-
2003
- 2003-06-27 EP EP03014694A patent/EP1424492A3/de not_active Withdrawn
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2001053693A2 (de) | 2000-01-20 | 2001-07-26 | Robert Bosch Gmbh | Ventil zum steuern von flüssigkeiten |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007098986A1 (de) * | 2006-02-28 | 2007-09-07 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
EP2090771A1 (de) * | 2008-02-13 | 2009-08-19 | Robert Bosch Gmbh | Kraftstoffinjektor mit einer direkt gesteuerten Ventilnadel |
Also Published As
Publication number | Publication date |
---|---|
DE10254985A1 (de) | 2004-06-03 |
EP1424492A3 (de) | 2006-03-01 |
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