EP0988447A1 - Brennstoffeinspritzventil - Google Patents
BrennstoffeinspritzventilInfo
- Publication number
- EP0988447A1 EP0988447A1 EP98958204A EP98958204A EP0988447A1 EP 0988447 A1 EP0988447 A1 EP 0988447A1 EP 98958204 A EP98958204 A EP 98958204A EP 98958204 A EP98958204 A EP 98958204A EP 0988447 A1 EP0988447 A1 EP 0988447A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- armature
- valve
- balls
- valve needle
- fuel injection
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
- F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
- F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
- F02M51/0685—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature and the valve being allowed to move relatively to each other or not being attached to each other
-
- 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
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
- F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical means
Definitions
- the invention relates to a fuel injector according to the preamble of the main claim.
- an electromagnetically actuated fuel injection valve is already known, in which an armature interacts with an electrically excitable solenoid for electromagnetic actuation and the stroke of the armature is transmitted to a valve closing body via a valve needle.
- the valve closing body interacts with a valve seat surface to form a sealing seat.
- the valve needle is acted upon by a first return spring in the spray direction, so that the valve closing body is held in sealing contact on the valve seat surface when the solenoid coil is not energized.
- the armature is not firmly connected to the valve needle, but is held against a driver piece of the valve needle by a second return spring acting counter to the spray direction and in the stroke direction of the armature.
- the valve needle is therefore carried along by the armature via the driver piece, so that the valve closing body lifts off the valve seat surface in order to open the fuel injection valve.
- the valve needle can still move slightly against the first return spring by lifting the driver piece from the armature.
- the direction of movement of the valve needle is reversed by the first return spring.
- the armature bounces back slightly from the stop surface, its direction of movement being reversed by the second return spring.
- valve needle and the armature then meet in opposite directions of movement, and the kinetic energy of the two-mass and two-spring system is dissipated.
- the kinematic separation of the armature and the valve needle causes the valve needle and the armature to bounce in comparison with a conventional fuel injector connected armature and valve needle significantly reduced. As a result, the metering accuracy of the fuel injector can be improved.
- the armature When the fuel injector known from DE-OS 33 14 899 closes, the armature also lifts off from the driver piece of the valve needle when the valve needle is suddenly braked by the valve closing body striking the valve seat surface. The armature then moves against the second return spring, which returns the armature in the opposite direction to the closing direction, until the armature is flush again with the driver piece of the valve needle. Bouncing of the fuel injector is therefore also significantly reduced in the closing direction.
- the fuel injector according to the invention with the characterizing features of the main claim has the advantage that the friction between the armature and the valve needle is significantly reduced. At the same time, an exact guidance of the valve needle on the armature or vice versa of the armature on the valve needle is achieved.
- the kinematics of the two-mass and two-spring system are considerably improved by the at least one slide bearing according to the invention between the armature and the valve needle, as a result of which a fuel injection valve with a particularly low bruise is produced.
- a particularly cost-effective solution is achieved since the balls of the at least one plain bearing can be mass-produced particularly cheaply.
- the balls can be produced from hard bearing steel, which can be pressed into the soft, ferromagnetic metal of the armature in a production-technically simple manner.
- the precise manufacture of the ball diameter of the balls ensures precise guidance of the valve needle on or in the armature.
- the armature has a stepped bore into which the balls of the two slide bearings provided can be inserted at each end.
- a passage provided between two balls of the slide bearing extensions of the stepped bore of the armature enables the fuel to flow centrally through the armature, so that the flow passage for the fuel is solved in a particularly simple manner without additional holes or grooves in or on the armature or flattening must be provided.
- the fuel lubricates the balls of the plain bearings particularly effectively.
- the extensions of the stepped bore of the armature receiving the balls of the slide bearings can be closed after insertion of the balls by a preferably annular caulking so that the balls cannot escape from the extensions.
- the caulking can be realized particularly easily and inexpensively in terms of production technology, since the armature is preferably made of a ferromagnetic soft iron and is therefore relatively easy to machine.
- the diameter of the balls of the plain bearings essentially corresponds to the diameter of the valve needle, which is cylindrical at least in this region, there is the advantage that the balls close the valve needle close to each other so that the balls touch.
- the inside diameter of the plain bearings is then precisely determined by the diameter of the balls, inaccuracies in the production of the bore being compensated for by the armature.
- valve needle for the stop of the balls of the slide bearing has a thickening with a continuously tapering transition section, the radius of curvature of which essentially corresponds to the radius of the balls, this has the advantage that the balls strike the thickening relatively softly.
- Figure 1 shows a first embodiment of a fuel injector according to the invention in a sectional view.
- FIG. 2 shows an enlarged section of the armature, the valve needle and the return springs in accordance with the exemplary embodiment shown in FIG. 1 in a partially sectioned illustration;
- FIG. 3 shows a section along the lines III-III in Fig. 2.
- Fig. 4 shows a second embodiment of the fuel injector according to the invention in a sectional view.
- the electromagnetically actuated valve shown in FIG. 1 in the form of an injection valve for fuel injection systems of mixture-compressing, spark-ignition internal combustion engines has a tubular, largely hollow cylindrical core 2, which is at least partially surrounded by a magnetic coil 1 and serves as the inner pole of a magnetic circuit.
- the fuel injection valve is suitable especially for the direct injection of fuel into a combustion chamber of an internal combustion engine.
- An example of a stepped coil body 3 receives a winding of the magnetic coil 1 and, in conjunction with the core 2 and an annular, non-magnetic intermediate piece 4 with an L-shaped cross section partially surrounded by the magnetic coil 1, enables a particularly compact and short structure of the injection valve in the region of the magnetic coil 1.
- the intermediate piece 4 projects with one leg in the axial direction into a step 5 of the coil former 3 and with the other leg radially along an end face of the coil former 3 lying below in the drawing.
- a continuous longitudinal opening 7 is provided in the core 2 and extends along a longitudinal valve axis 8.
- the sleeve 10 lies directly on the wall of the longitudinal opening 7 or has a play in relation to this and has a sealing function to the core 2.
- existing sleeve 10 is an annular disk-shaped ferritic pole part 13 firmly and tightly connected, which abuts the lower end face 11 of the core 2 and the core 2 in downstream direction limited.
- the sleeve 10 and the pole part 13, the z. B. is formed as a pressed part and connected by welding or soldering to the sleeve 10, form an encapsulation of the core 2 in the direction of the longitudinal valve axis 8 or in the downstream direction, which effectively prevents contact of fuel on the core 2.
- the sleeve 10 projects, for example, with its downstream end up to a shoulder 17 of an inner passage opening 12 of the pole part 13 and is connected to this shoulder 17, for example. Together with the also firm and dense z. B. by welding or brazing, for example with the axially extending leg of the pole part 13 connected intermediate piece 4, this encapsulation also ensures that the magnetic coil 1 remains completely dry in the fuel flowed state and is not wetted with fuel.
- the sleeve 10 also serves as a fuel supply channel, and together with an upper metal (for example ferritic) housing part 14, which largely surrounds the sleeve 10, forms a fuel inlet connection.
- an upper metal (for example ferritic) housing part 14 which largely surrounds the sleeve 10, forms a fuel inlet connection.
- a through-opening 15 which, for example, has the same diameter as the longitudinal opening 7 of the core 2.
- the sleeve 10, which projects through the housing part 14, the core 2 and the pole part 13 in the respective openings 7, 12 and 15, is adjacent the fixed connection with the pole part 13 also tight and firm with the housing part 14 z. B. connected by welding or flanging at the upper end 16 of the sleeve 10.
- the housing part 14 forms the inlet-side end of the fuel injection valve and envelops the sleeve 10, the core 2 and the magnet coil 1 at least partially in the axial and radial directions and extends, for example in the axial direction downstream, beyond the magnet coil 1.
- the z. B. an axially movable valve part consisting of an armature 19 and a valve needle 20 or a valve seat support 21 encloses or receives.
- the two housing parts 14 and 18 are in the region of the lower end 23 of the upper housing part 14 z. B. firmly connected to each other with a circumferential weld.
- the lower housing part 18 and the largely tubular valve seat support 21 are firmly connected to one another by screwing; Welding, flanging or soldering are also possible joining methods.
- the seal between the housing part 18 and the valve seat support 21 is made, for. B. by means of a sealing ring 22.
- the valve seat support 21 has an inner through opening 24 over its entire axial extent, which runs concentrically to the longitudinal axis 8 of the valve. With its lower end 25, which also represents the downstream termination of the entire fuel injection valve, the valve seat carrier 21 surrounds a valve seat body 26 fitted in the through opening 24. In the through opening 24 is the z. B.
- valve closing body 28 acts in a known manner with a valve seat body 26 provided in the flow direction z.
- B. frustoconical tapered valve seat surface 29 which is formed in the axial direction downstream of a guide opening 30 located in the valve seat body 26. Downstream of the valve seat surface 29 is or are at least one, for. B. but also introduced two or four outlet openings 32 for the fuel.
- flow areas (depressions, grooves or the like), which are not shown, are provided, which ensure an unimpeded fuel flow from the through opening 24 to the valve seat surface 29.
- valve assembly Following the magnetic circuit downstream. It is emphasized that the most diverse valve assemblies together with the training according to the invention can be combined. In addition to valve assemblies of an inward opening injection valve, valve assemblies of an outward opening injection valve can also be used. Spherical valve closing bodies 28 or spray perforated disks are also conceivable in such valve assemblies. In the illustrated embodiment, the valve closing body 28 is formed in one piece with the valve needle 20. The valve closing body 28 can, however, also be designed as a separate component and connected to the valve needle 20, e.g. B. connected by welding, soldering or the like.
- the injection valve is actuated electromagnetically in a known manner.
- the electromagnetic circuit with the magnet coil 1, the core 2, the pole part 13 and the armature 19 is used for the axial movement of the valve needle 20 and thus for opening against the spring force of a first return spring 33 arranged inside the sleeve 10 or closing the injection valve Armature 19 is positively connected to the end of the valve needle 20 facing away from the valve closing body 28 only in the lifting direction, ie in the direction of the core 2, and is freely movable in the opposite direction, ie in the direction of the valve closing body 28, against a second return spring 50.
- the second return spring 50 holds the armature 19 in the rest position of the fuel injection valve in contact with a thickening 51 of the valve needle 20.
- the thickening 51 is formed on the end of the valve needle 20 opposite the valve closing body 28.
- the first return spring 33 acts on an end face 52 of the thickening 51.
- the guide opening 30 of the valve seat body 26 is used along the longitudinal axis 8 of the valve.
- the armature 19 is guided in the precisely manufactured, non-magnetic intermediate piece 4 during its axial movement. As shown on the left side of FIG.
- a one-piece version can also be provided, in which a circumferential, narrow web 35 extends from the pole part 13 in the axial direction as a transition to Housing part 18 extends and all sections together (pole part 13, sleeve-shaped web 35, lower housing part 18) form a one-piece, ferritic component. Accordingly, the inner boundary surface of the web 35 then serves as a guide for the armature 19.
- An adjusting sleeve 38 is inserted, pressed or screwed into an inner flow bore 37 of the sleeve 10, which runs concentrically to the valve longitudinal axis 8 and serves to supply the fuel in the direction of the valve seat surface 29.
- the adjusting sleeve 38 is used to adjust the spring preload of the first return spring 33 abutting the adjusting sleeve 38, which in turn is supported with its opposite side on the upstream end face 52 of the thickening 51 of the valve needle 20.
- a fuel filter 42 protrudes into the flow bore 37 of the sleeve 10 on the inlet side and filters out those fuel components which, because of their size, could cause blockages or damage in the injection valve.
- the fuel filter 42 is e.g. B. fixed by pressing in the housing part 14.
- the stroke of the valve needle 20 is predetermined by the valve seat body 26 and the pole part 13.
- a static end position of the valve needle 20 is determined when the solenoid coil 1 is not energized by the valve closing body 28 bearing against the valve seat surface 29 of the valve seat body 26, while the other static end position of the valve needle 20 when the solenoid coil 1 is energized by the armature 19 resting on the pole part 13 results.
- the surfaces of the components in these stop areas are chrome-plated, for example.
- the electrical contacting of the magnetic coil 1 and thus its excitation takes place via contact elements 43 which are also provided with a plastic encapsulation 45 outside of the actual coil body 3 made of plastic.
- the plastic encapsulation can also extend over other components (z. B. housing parts 14 and 18) of the fuel injection valve.
- An electrical connection cable 44 runs out of the plastic encapsulation 45, via which the energization of the magnetic coil 1 takes place.
- the core 2 is tubular, but is not designed with a constant outside diameter. Only in In the area of the plastic encapsulation 45, the core 2 has a constant outer diameter over its entire axial extent. Outside the plastic encapsulation 45, the core 2 is configured with a radially outwardly facing collar 46, which extends partially over the magnet coil 1 in a cover-like manner. The plastic encapsulation 45 thus protrudes through a groove in the collar 46.
- the core 2 preferably consists of a material which reduces eddy currents, eg. B. a powder composite.
- the second return spring 50 extends in a cylindrical step section 53 of the through opening 24 of the valve seat carrier 21 which is designed as a step bore and is supported at its downstream end on a step 54 of the through opening 24 of the valve seat carrier 21 which is designed as a step bore. At its upstream end, the second return spring 50 acts on a downstream end face 55 of the armature 19.
- the armature 19 is connected to the valve needle 20 via an upstream sliding bearing 56 and a downstream sliding bearing 57.
- the mode of operation of the fuel injector shown in FIG. 1 is as follows:
- valve needle 20 and the valve closing body 28 which is connected to the valve needle 20 or, in the exemplary embodiment shown, is formed in one piece with the valve needle 20 is likewise accelerated in the stroke direction indicated by the arrow 58.
- the balls 59 of the upstream plain bearing 56 bear against the thickening 51 of the valve needle 20 in a form-fitting manner, so that the valve needle 20 and thus also the valve closing body 28 are carried along by the lifting movement of the armature 19.
- the armature 19 and the pole part 13 there is a slight gap which specifies the valve lift and cannot be seen in FIG. 1.
- valve needle 20 and the valve closing body 28 connected to the valve needle 20 initially continue to move in the stroke direction 58 against the first return spring 33 due to their inert mass. This is made possible by the fact that the armature 19 on the valve needle 20 only in the stroke direction 58 positively attacks.
- the thickening 51 of the valve needle 20 can therefore stand out from the balls 59 of the upstream slide bearing 56 which form the stop surface in the exemplary embodiment shown, the balls of the two slide bearings 56 and 57 sliding on the outer surface of the cylindrical valve needle 20.
- the first return spring 33 reverses the movement of the valve needle 20 counter to the lifting direction 58, while the direction of movement of the armature 19 which initially runs counter to the lifting direction 58 after the rebounding of the armature 19 is reversed by the second return spring 50.
- the valve needle 20 with the valve closing body 28 and the armature 19 consequently move towards one another again after the reversal of movement, the inertial mass of the armature 19, the inertial mass of the valve needle 20 and the valve closing body 28 and the spring constants of the two return springs 33 and 50 preferably thus are designed so that when the armature 19 and the valve needle 20 meet again, the impact energy dissipates almost completely.
- the bouncing of the fuel injection valve is therefore significantly reduced by the separation of the armature 19 from the valve needle 20 and the formation of a two-mass and two-spring system compared to a conventionally designed fuel injector.
- the slide bearings 56 and 57 according to the invention ensure a kinematic movement sequence largely undisturbed by the effects of friction. At the same time, exact guidance of the valve needle 20 via the slide bearings 56 and 57 on the armature 19 is achieved.
- the armature 19 and the valve needle 20 are accelerated in the closing direction by the first return spring 33 until the valve closing body 28 strikes the valve seat surface 29 of the valve seat body 26.
- the bouncing that occurs in conventional fuel injection valves is reduced in the embodiment according to the invention in that the armature 19 swings through in the closing direction against the second return spring 50.
- the second return spring 50 guides the armature 19 back in the stroke direction 58 until the balls 59 of the upstream slide bearing 56 strike the thickening 51 of the valve needle 20.
- the fuel injector is now ready for the next opening cycle.
- the mass of the armature 19 is substantially larger than the mass of the valve needle 20 and the valve closing body 28, the kinematic separation of the movement of the armature 19 and the valve needle 20 effectively suppresses the bouncing of the fuel injection valve.
- the slide bearings 56 and 57 according to the invention effectively reduce the sliding friction between the armature 19 and the valve needle 20, so that the armature 19 can slide freely and undisturbed on the outer surface of the valve needle 20. The guidance of the valve needle 20 on the armature 19 is retained due to the high accuracy of fit of the slide bearings 56 and 57.
- the described relative movement of the armature 19 with respect to the valve needle 20 is significantly larger in the closing direction than in the opening direction and can be negligible in the opening direction due to the low inertial mass of the valve needle 20.
- the armature 19, the upstream section of the valve needle 20, the first return spring 33 and the second return spring 50 are shown enlarged for a better understanding of the invention. Elements already described are provided with the same reference numerals.
- the armature 19 has a stepped bore 74 in the exemplary embodiment shown.
- the stepped bore 74 connects the upstream end face 72 of the armature 19 to the downstream end face 55 of the armature 19.
- the stepped bore 74 widens to an upstream extension 73, into which the balls 59 of the upstream plain bearing 56 are pressed.
- the stepped bore 74 widens on the downstream end face 55 to form a downstream extension 75, into which the balls 70 of the downstream slide bearing 57 are pressed.
- the diameter of the annular extensions 73 and 75 is the sum of two ball diameters d ⁇ of the balls 59 and 70 and the diameter d v of the valve needle 20 which is cylindrical in the region of the armature 19.
- the valve needle 20 is therefore the ball 59 and 70 of the two plain bearings 56 and 57 guided on the armature 19 practically without play. Since the balls 59 and 70 of the slide bearings 56 and 57 can be produced with high accuracy, the valve needle 20 is guided in an extremely precise manner.
- the upstream extension 73 opening at the upstream end face 72 and the downstream extension 75 opening at the downstream end face 55 are connected in the exemplary embodiment by means of a passage 76 which is part of the stepped bore 74.
- the diameter of the passage 76 is larger than the diameter d v of the valve needle 20, so that the passage 76 is not completely filled by the valve needle 20.
- This enables the fuel to flow axially through the stepped bore 74 of the armature 19.
- the fuel flows in the Area of the upstream extension 73 past the circumferentially distributed balls 59, through the passage 76 into the downstream extension 75 and past the likewise circumferentially distributed balls 70.
- no additional measures, such as additional axial bores, circumferential grooves or flattenings are to be provided, as a result of which the production costs can be reduced further.
- the edge on the upstream end face 72 near the extension 73 is caulked by caulking indicated by the reference numeral 77, so that the balls 59 cannot escape from the extension 73.
- the caulking 77 is preferably annular.
- the edge of the downstream extension 75 is caulked by a likewise preferably circular encircling, indicated by the reference numeral 78, such that the balls 70 of the downstream slide bearing 57 cannot escape from the downstream extension 75.
- the armature 19 is preferably made of a ferromagnetic or ferritic soft metal that is easy to machine, the caulking 77 and 78 can be carried out without major manufacturing effort.
- the balls 59 and 70 can be formed from a hardened bearing steel and z. B. be additionally coated by chrome plating.
- the balls 59 of the upstream slide bearing 56 lie flush against a transition section 79 of the thickening 51 which tapers continuously toward the armature 19.
- the transition section 79 preferably has a radius of curvature r which is half the ball diameter d of the balls 59 of the upstream plain bearing 56, i.e. H. the radius of the balls 59 essentially coincides with the radius of curvature r of the transition section 79.
- the passage 76 can also have the same diameter as the extensions 73 and 75, so that the bore of the armature 19 is not stepped. This has the advantage of simplifying production.
- 3 shows a section along the line III-III in FIG. 2 for a better understanding of the invention. Elements that have already been described are provided with matching reference numerals in order to facilitate the assignment.
- the relatively hard balls 59 and 70 are pressed into the relatively imprecise bore of the armature 19.
- the inner diameter of the plain bearings 56 and 57 is determined exclusively by the ball diameter d ⁇ when the balls are close together.
- the inner diameter d v of the slide bearing 56 and 57 formed from the six balls 59 and 70 corresponds exactly to the diameter d of the individual balls 59 and 70.
- the inner diameter d v of the slide bearings 56 and 57 therefore depends essentially on the manufacturing tolerance of the ball diameter d ⁇ from.
- the slide bearings 56 and 57 according to the invention have a high level of guidance accuracy.
- FIG. 4 shows an expanded exemplary embodiment which essentially corresponds to the exemplary embodiment shown in FIG. 1 and has already been described.
- the extension consists in that the valve needle 20 is mounted in additional balls 90 of a further slide bearing 91 arranged in the valve seat carrier 21.
- the valve needle 20 is guided in the valve seat carrier 21 by means of the slide bearing 91.
- the armature 19 is designed with a somewhat smaller diameter, so that, in contrast to the exemplary embodiment shown in FIG. 1, its outer surface is not guided in the intermediate piece 4. Rather, the upstream guidance of the component consisting of the valve needle 20 and the armature 19 takes place in the additional slide bearing 91.
- FIG. 1 shows an expanded exemplary embodiment which essentially corresponds to the exemplary embodiment shown in FIG. 1 and has already been described.
- the extension consists in that the valve needle 20 is mounted in additional balls 90 of a further slide bearing 91 arranged in the valve seat carrier 21.
- the armature 19 is designed with a somewhat smaller diameter, so that, in contrast to the
- the through opening 24 has a taper 92 downstream of the slide bearing 91.
- Upstream of the balls 90 of the slide bearing 91 is a z. B. provided by caulking after insertion of the balls 90 taper 93.
- the taper 92 and 93 effect an axial fixation of the balls 90 of the slide bearing 91 in the through opening 24.
- the invention is not limited to the exemplary embodiments shown. In particular, it may be sufficient to mount the armature 19 on the valve needle 20 by means of a single plain bearing instead of two plain bearings.
- the armature 19 does not necessarily have to stop against the valve needle 20 by means of the balls 59. It can e.g. B. also strike a projection of the armature 19 on the thickening 51 or another section of the valve needle 20 in order to positively carry the valve needle 20 in the stroke direction 58.
- the slide bearings 56 and 57 can also be formed as a separate finished component and on the armature 19 z. B. be attached by welding.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19756103 | 1997-12-17 | ||
DE19756103A DE19756103A1 (de) | 1997-12-17 | 1997-12-17 | Brennstoffeinspritzventil |
PCT/DE1998/003076 WO1999031379A1 (de) | 1997-12-17 | 1998-10-21 | Brennstoffeinspritzventil |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0988447A1 true EP0988447A1 (de) | 2000-03-29 |
EP0988447B1 EP0988447B1 (de) | 2003-09-10 |
Family
ID=7852251
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98958204A Expired - Lifetime EP0988447B1 (de) | 1997-12-17 | 1998-10-21 | Brennstoffeinspritzventil |
Country Status (6)
Country | Link |
---|---|
US (1) | US6170767B1 (de) |
EP (1) | EP0988447B1 (de) |
JP (1) | JP2001511868A (de) |
KR (1) | KR20000071121A (de) |
DE (2) | DE19756103A1 (de) |
WO (1) | WO1999031379A1 (de) |
Families Citing this family (25)
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DE19946602A1 (de) | 1999-09-29 | 2001-04-12 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE19948238A1 (de) * | 1999-10-07 | 2001-04-19 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE19957172A1 (de) * | 1999-11-27 | 2001-08-09 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE10140795A1 (de) * | 2001-08-20 | 2003-03-06 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE102004028523A1 (de) * | 2004-06-11 | 2005-12-29 | Robert Bosch Gmbh | Kraftstoffinjektor mit Spannhülse als Anschlag für Ventilnadel |
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US8704387B2 (en) * | 2010-01-06 | 2014-04-22 | Tremont Electric, Inc. | Electrical energy generator |
JP2011190798A (ja) * | 2010-02-17 | 2011-09-29 | Denso Corp | 燃料噴射弁 |
US8215573B2 (en) | 2010-05-14 | 2012-07-10 | Continental Automotive Systems Us, Inc. | Automotive gasoline solenoid double pole direct injector |
JP5516140B2 (ja) * | 2010-06-29 | 2014-06-11 | 株式会社デンソー | 燃料噴射弁 |
DE102012202253A1 (de) * | 2012-02-15 | 2013-08-22 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE102013220877A1 (de) * | 2013-10-15 | 2015-04-16 | Continental Automotive Gmbh | Ventil |
DE102013220913A1 (de) * | 2013-10-15 | 2015-04-16 | Continental Automotive Gmbh | Ventil |
EP3153700A1 (de) * | 2015-10-08 | 2017-04-12 | Continental Automotive GmbH | Ventilgruppe für ein einspritzventil, einspritzventil und verfahren zur montage eines einspritzventils |
DE102015220383A1 (de) * | 2015-10-20 | 2017-04-20 | Robert Bosch Gmbh | Elektromagnetisch betätigbares Saugventil für eine Hochdruckpumpe sowie Hochdruckpumpe |
JP2022064483A (ja) | 2020-10-14 | 2022-04-26 | トヨタ自動車東日本株式会社 | 塗料噴射ノズル |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1878749A (en) * | 1929-12-03 | 1932-09-20 | Abramson Alexander | Valve |
DE2613664A1 (de) * | 1976-03-31 | 1977-10-13 | Schultz Wolfgang E | Elektromagnetisches regelventil |
DE3314899A1 (de) | 1983-04-25 | 1984-10-25 | Mesenich, Gerhard, Dipl.-Ing., 4630 Bochum | Federanordnung mit zusatzmasse zur verbesserung des dynamischen verhaltens von elektromagnetsystemen |
US5088467A (en) | 1984-03-05 | 1992-02-18 | Coltec Industries Inc | Electromagnetic injection valve |
JPH0772520B2 (ja) * | 1987-02-13 | 1995-08-02 | 株式会社日立製作所 | 圧電式燃料噴射弁 |
DE3843467A1 (de) * | 1988-12-23 | 1990-06-28 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen |
DE3904480A1 (de) * | 1989-02-15 | 1990-08-16 | Bosch Gmbh Robert | Ventil zum intermittierenden einbringen von kraftstoff |
JPH04209964A (ja) * | 1990-12-10 | 1992-07-31 | Honda Motor Co Ltd | 燃料噴射弁 |
FR2726036A1 (fr) * | 1994-10-19 | 1996-04-26 | Nazare Edgard | Dispositif de transformation des moteurs a combustion interne, utilisant les combustibles liquides, en moteurs a gaz surpresses |
DE19726382A1 (de) * | 1997-06-21 | 1998-12-24 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
-
1997
- 1997-12-17 DE DE19756103A patent/DE19756103A1/de not_active Withdrawn
-
1998
- 1998-10-21 DE DE59809577T patent/DE59809577D1/de not_active Expired - Fee Related
- 1998-10-21 US US09/367,621 patent/US6170767B1/en not_active Expired - Fee Related
- 1998-10-21 KR KR1019997007409A patent/KR20000071121A/ko not_active Application Discontinuation
- 1998-10-21 JP JP53186599A patent/JP2001511868A/ja active Pending
- 1998-10-21 WO PCT/DE1998/003076 patent/WO1999031379A1/de not_active Application Discontinuation
- 1998-10-21 EP EP98958204A patent/EP0988447B1/de not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
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See references of WO9931379A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE19756103A1 (de) | 1999-06-24 |
DE59809577D1 (de) | 2003-10-16 |
WO1999031379A1 (de) | 1999-06-24 |
US6170767B1 (en) | 2001-01-09 |
KR20000071121A (ko) | 2000-11-25 |
JP2001511868A (ja) | 2001-08-14 |
EP0988447B1 (de) | 2003-09-10 |
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