EP1407136A1 - Brennstoffeinspritzventil - Google Patents
BrennstoffeinspritzventilInfo
- Publication number
- EP1407136A1 EP1407136A1 EP02745049A EP02745049A EP1407136A1 EP 1407136 A1 EP1407136 A1 EP 1407136A1 EP 02745049 A EP02745049 A EP 02745049A EP 02745049 A EP02745049 A EP 02745049A EP 1407136 A1 EP1407136 A1 EP 1407136A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- coupler
- valve
- pressure
- fuel injection
- pressure cylinder
- 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
- 239000000446 fuel Substances 0.000 title claims abstract description 87
- 238000002347 injection Methods 0.000 title claims abstract description 41
- 239000007924 injection Substances 0.000 title claims abstract description 41
- 238000002485 combustion reaction Methods 0.000 claims abstract description 11
- 238000007789 sealing Methods 0.000 claims description 22
- 239000012530 fluid Substances 0.000 description 7
- 230000002349 favourable effect Effects 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 230000003044 adaptive effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
-
- 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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/08—Fuel-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
-
- 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
- F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
Definitions
- the invention relates to a fuel injection valve according to the preamble of the main claim.
- EP 0 477 400 AI discloses a displacement transformer for a piezoelectric actuator, in which the actuator transmits a lifting force to a master cylinder, which is completed by a cylinder carrier.
- a slave piston is guided in this master cylinder, which also closes the master cylinder and thereby forms the hydraulic chamber.
- a spring is arranged in the hydraulic chamber, which holds the master cylinder and the slave piston apart prints.
- the slave piston mechanically transmits a stroke movement to, for example, a valve needle.
- a disadvantage of this known prior art is that the hydraulic chamber can only be filled slowly. Long injection times occur in particular when cold starting with low pressure, so that more hydraulic fluid escapes via the annular gap and then has to be refilled in a shorter time at low pressure. If this does not happen, the injection valve loses injection at the stroke until it completely loses its function.
- Another disadvantage is that the hydraulic fluid can evaporate if the hydraulic chamber does not have a sufficiently high pressure.
- em gas is compressible and only builds up a correspondingly high pressure after a considerable reduction in volume.
- Fuel injection valve for gasoline when the gasoline also serves as hydraulic fluid.
- E Fuel injection system now loses its pressure.
- the gasoline evaporates particularly easily. At the If the internal combustion engine is attempted to start again, this can result in the stroke movement of the actuator not being transmitted to the needle, since the after-flowing cool fuel does not get into the hydraulic chamber quickly enough.
- the fuel injector according to the invention with the characterizing features of claim 1 has the advantage that the coupler valve seat body lifts off the coupler valve seat when the coupler takes up the possible length after transmission as a transmission element between the actuator and the valve needle and thus an inflow possibility for the fuel via the inlet bore releases to the pressure room. Since the cross-sectional area occupied by the coupler valve sealing seat is smaller than the cross-sectional area of the pressure piston, both the coupler spring element and the increased pressure in the coupler chamber when actuated have a closing effect on the coupler valve sealing seat.
- the coupler valve seat is released when the actuator is reset. This quickly fills the coupler space until it reaches its starting position and the coupler valve sealing seat closes.
- the expansion of the fuel be ⁇ due to temperature changes and changes in the pressure of the fuel
- Fuel injection valve are automatically balanced on the transmission path between the actuator and valve needle.
- the stroke of the valve needle can always be the same.
- the coupler valve closing body can advantageously be designed as a spherical surface and the corresponding coupler valve seat flat on the valve needle as a conical surface.
- the inlet bore is formed on the pressure cylinder carrier and the Coupler valve closing body with the pressure cylinder support and the pressure cylinder e molded in one piece.
- the coupler valve seat surface is formed on the valve needle and the pressure piston is connected to a guide piston which is guided in a bore in a cutting disc which separates the fuel feed from an actuator chamber. It is also favorable to provide a corrugated tube on the guide piston for sealing this actuator space.
- the stroke of the valve needle can be limited by a stop of an actuator head or alternatively by a stop of the valve needle or alternatively by a stop of the pressure piston or the pressure cylinder.
- the same and defined stroke of the valve needle can always be achieved, regardless of the extension and expansion of a valve body of the fuel injection valve, if the stroke limited by the stop is always less than the minimum stroke of the actuator under all operating conditions.
- Fig. 1 shows a schematic section through em
- fuel injection valve 1 has a valve needle 2, which is connected to a valve closing body 3 and via this valve closing body 3 cooperates with a valve seat surface 5 formed into a valve body 4 to form a valve sealing seat.
- the fuel injection valve 1 is an e outward opening fuel injection valve which has an outward opening valve needle 2.
- the valve needle 2 is guided by a guide section 7, which has a spring system 8 for a valve closing spring 9, of a valve needle guide 10.
- the valve closing spring 9 is braced against a second spring system 11 on the valve body 4 and biases the valve needle 2 with a force that presses the valve closing body 3 against the valve seat surface 5.
- a ring 13 arranged in a groove 12 seals the annular gap (not shown here) between the valve body 4 and a bore (also not shown) in a cylinder head of an internal combustion engine.
- a piezoelectric or magnetostrictive actuator 14 is arranged in a valve body part 17, which can be supplied with a voltage via a bore 15 m to the valve body part 17 and an electrical feed line 16.
- the actuator 14 has a larger overall length, around one to achieve a noticeable stroke when applying a voltage to the actuator 14. The majority of the overall length of the actuator 14 is not shown in FIG. 1.
- the actuator 14 is followed by an actuator head 18 which has a spring contact surface 19 against which an actuator tension spring 20 bears, which in turn rests against a cutting disc 21. A preload is exerted on the actuator 14 by the actuator spring 20, so that the stroke of the actuator 14 is transmitted to the actuator head 18 when a voltage is applied to the electrical supply line 16.
- a pressure plunger 22 is formed in one piece with the actuator head 18, which transmits the stroke of the actuator 14.
- the actuator head 18 is guided through an actuator head sleeve 23 m to the valve body part 17 and this actuator head sleeve 23 strikes the cutting disc 21 after a maximum stroke h. This limits the maximum stroke h of the actuator 14.
- the actuator head tappet 22 transmits the stroke movement of the actuator 14 to a pressure piston carrier 24, to which a blind hole 25 is made centrally.
- the pressure piston carrier 24 is guided by a guide bore 27 which penetrates the carrier plate 21.
- the carrier plate 21 is sealed off from the valve body part 17 by a sealing ring 26.
- a corrugated tube 28 concentrically surrounds the pressure piston carrier 24 and is fastened to the pressure piston carrier 24 with a weld seam 29.
- the corrugated tube 28, on the other hand, is fastened to the carrier plate 21 with a weld seam 30.
- the pressure cylinder carrier 24 With a stroke of the actuator 14 and a resulting movement of the actuator head 18 with the actuator head tappet 22 formed thereon, the pressure cylinder carrier 24 is moved in the longitudinal direction and the corrugated tube 28 follows this movement and expands accordingly. At the same time, the corrugated tube 28, which with the weld seams 30 and 29 is sealed to the pressure cylinder carrier 24 and the carrier plate 21, seals an actuator chamber 31 from a fuel chamber 32.
- a pressure piston 33 acting as a master piston is formed, which m a printing cylinder 34 acting as a slave cylinder.
- the pressure cylinder 34 is integrally formed with a pressure cylinder carrier 35.
- An inlet bore 36 is guided centrally through the pressure cylinder carrier 35.
- a pressure chamber 37 is located inside the pressure cylinder 34, which is closed off by the pressure piston 33.
- the pressure piston 33, the pressure cylinder 34 and the pressure cylinder carrier 35 form the hydraulic coupler 35a.
- Concentric around the pressure piston 33 and the pressure cylinder of FIG. 34, the hydraulic coupler 35a Concentric around the pressure piston 33 and the pressure cylinder of FIG. 34, the hydraulic coupler 35a has a coupler spiral spring 38 between a spring stop 39 on the pressure cylinder carrier 35 and a further spring stop 40 on the pressure piston carrier 24.
- the inlet bore 36 is separated from the fuel chamber 32 by a coupler valve closing body, which is designed as a hemispherical surface on the pressure cylinder support 35, and with a coupler valve seat surface 42, which is shaped as a conical surface on the guide section 7 of the valve needle 2, to form a coupler valve sealing seat.
- the coupler valve sealing seat results in a disk-shaped surface with the diameter d that is not subjected to the pressure of the fuel that is located in the fuel chamber 32.
- the fuel flows into the fuel chamber 32 via a fuel inlet bore 44.
- the actuator 14 m When a voltage is applied to the actuator 14 via the electrical supply line, the actuator 14 m extends in the longitudinal direction of the fuel injection valve 1 and presses the actuator head 18 with the actuator plunger 22 m formed thereon Actuator head sleeve 23 limited on the cutting disc 21 after a path h. The movement is transferred to the pressure piston carrier 24 and the pressure piston 33.
- the fuel contained in the pressure chamber 37 is m-compressible as a liquid and therefore transfers the movement further to the pressure cylinder carrier 35.
- valve needle 2 opens outward from the valve sealing seat 6.
- the actuator is pressed back by the actuator spring 23 and the valve needle 2 is pressed by the valve needle spring 9 m of its valve sealing seat 6.
- the pressure piston carrier 24 is held against the actuator head tappet 22 by the prestressed corrugated tube 28.
- the coupler valve sealing seat 43 now opens, since the diameter of the cross-sectional area of the coupler valve sealing seat 43 is opposite Fuel pressure in the fuel chamber 32 is completed, is smaller than the diameter of the pressure piston 33 and the spring force of the coupler coil spring 38 is overcome. Pressurized fuel can now pass from the fuel chamber 32 past the coupler valve sealing seat 43 through the inlet bore 36 m to the pressure chamber 37.
- the coupler spiral spring 38 pulls the pressure piston 33 out of the pressure cylinder 34 until the coupler valve closing body 41 sits on the coupler valve seat surface 42 and the coupler valve sealing seat 43 is closed again.
- the fuel injection valve 1 with the described transmission path of the lifting force from the actuator 14 to the valve needle 2, thus automatically adapts to the expansion of the valve body 4 and the valve body upper part 17 in the event of pressure fluctuations in the fuel pressure. Temperature-related expansions are also compensated for. Furthermore, advantageously failure of the fuel injection valve 1, e.g. B. can be prevented at a restart after an internal combustion engine has been switched off in the warm operating state. After turning off an internal combustion engine. ne in the warm operating condition, the fuel chamber 32 slowly loses fuel pressure. This can cause fuel to evaporate in the pressure chamber 37.
- the vaporized fuel in the pressure chamber 37 was compressed as gas without the inventive design of the fuel injection valve 1, without building up the necessary pressure to open the valve needle 2.
- the fuel is first put under pressure in the fuel chamber 32 by an external pump, not shown here, and consequently, as described above, the coupler valve sealing seat 43 is opened in a fuel injection valve 1 according to the invention, and fuel flows through the inlet bore 36 m into the pressure chamber 37. This results in cooling and the vaporized fuel condenses.
Landscapes
- Engineering & Computer Science (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 |
---|---|---|---|
DE10133265A DE10133265A1 (de) | 2001-07-09 | 2001-07-09 | Brennstoffeinspritzventil |
DE10133265 | 2001-07-09 | ||
PCT/DE2002/001640 WO2003006820A1 (de) | 2001-07-09 | 2002-05-07 | Brennstoffeinspritzventil |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1407136A1 true EP1407136A1 (de) | 2004-04-14 |
EP1407136B1 EP1407136B1 (de) | 2008-07-02 |
Family
ID=7691147
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02745049A Expired - Lifetime EP1407136B1 (de) | 2001-07-09 | 2002-05-07 | Brennstoffeinspritzventil |
Country Status (6)
Country | Link |
---|---|
US (1) | US6883725B2 (de) |
EP (1) | EP1407136B1 (de) |
JP (1) | JP4116542B2 (de) |
KR (1) | KR100853645B1 (de) |
DE (2) | DE10133265A1 (de) |
WO (1) | WO2003006820A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1571328A3 (de) * | 2004-03-02 | 2006-06-14 | Siemens Aktiengesellschaft | Einspritzventil |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10310499A1 (de) * | 2003-03-11 | 2004-09-23 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE10310788A1 (de) * | 2003-03-12 | 2004-09-23 | Robert Bosch Gmbh | Brennstoffeinspritzventil und Verfahren zu dessen Montage |
DE10310790A1 (de) * | 2003-03-12 | 2004-09-23 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE10341810B4 (de) | 2003-09-10 | 2016-04-07 | Robert Bosch Gmbh | Brennstoffeinspritzventil und Verfahren zum Betrieb eines Brennstoffeinspritzventils |
DE10344880A1 (de) * | 2003-09-26 | 2005-04-14 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE10353639A1 (de) * | 2003-11-17 | 2005-06-16 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE10353641B4 (de) * | 2003-11-17 | 2016-12-01 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE102004009460A1 (de) * | 2004-02-27 | 2005-09-15 | Robert Bosch Gmbh | Ventil |
DE102005025952B4 (de) * | 2005-06-06 | 2009-01-29 | Continental Automotive Gmbh | Verfahren zum Herstellen eines Ventils |
US7665445B2 (en) * | 2008-04-18 | 2010-02-23 | Caterpillar Inc. | Motion coupler for a piezoelectric actuator |
DE102008042850A1 (de) * | 2008-10-15 | 2010-04-22 | Robert Bosch Gmbh | Einspritzvorrichtung |
US8201543B2 (en) * | 2009-05-14 | 2012-06-19 | Cummins Intellectual Properties, Inc. | Piezoelectric direct acting fuel injector with hydraulic link |
DE102013219225A1 (de) * | 2013-09-25 | 2015-03-26 | Continental Automotive Gmbh | Piezo-Injektor zur Kraftstoff-Direkteinspritzung |
US10484598B2 (en) * | 2015-08-20 | 2019-11-19 | Sony Corporation | System and method for controlling capture of images |
DE102015219912B3 (de) * | 2015-10-14 | 2017-04-06 | Continental Automotive Gmbh | Piezo-Injektor zur Kraftstoffeinspritzung |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0477400B1 (de) * | 1990-09-25 | 2000-04-26 | Siemens Aktiengesellschaft | Anordnung für einen in Hubrichtung wirkenden adaptiven, mechanischen Toleranzausgleich für den Wegtransformator eines piezoelektrischen Aktors |
DE19519191C2 (de) * | 1995-05-24 | 1997-04-10 | Siemens Ag | Einspritzventil |
DE19743640A1 (de) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19743669A1 (de) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19746143A1 (de) * | 1997-10-18 | 1999-04-22 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
GB9725804D0 (en) * | 1997-12-06 | 1998-02-04 | Lucas Ind Plc | Fuel injector |
DE19817320C1 (de) * | 1998-04-18 | 1999-11-11 | Daimler Chrysler Ag | Einspritzventil für Kraftstoffeinspritzsysteme |
DE19946732B4 (de) | 1999-09-29 | 2004-07-15 | Siemens Ag | Vorrichtung zum Übertragen einer Auslenkung eines Aktors auf ein Stellglied und Kraftstoffinjektor mit einer solchen Vorrichtung |
DE19950760A1 (de) * | 1999-10-21 | 2001-04-26 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE19954802A1 (de) * | 1999-11-13 | 2001-05-17 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE19958704C2 (de) * | 1999-12-06 | 2002-10-02 | Siemens Ag | Vorrichtung zum Übertragen einer Aktorbewegung und Fluiddosierer mit einer solchen Vorrichtung |
LU90684B1 (en) * | 2000-11-28 | 2002-05-29 | Delphi Tech Inc | Fuel injector with piezoelectric actuator |
-
2001
- 2001-07-09 DE DE10133265A patent/DE10133265A1/de not_active Withdrawn
-
2002
- 2002-05-07 KR KR1020037003392A patent/KR100853645B1/ko not_active IP Right Cessation
- 2002-05-07 EP EP02745049A patent/EP1407136B1/de not_active Expired - Lifetime
- 2002-05-07 US US10/363,961 patent/US6883725B2/en not_active Expired - Fee Related
- 2002-05-07 DE DE50212447T patent/DE50212447D1/de not_active Expired - Lifetime
- 2002-05-07 WO PCT/DE2002/001640 patent/WO2003006820A1/de active IP Right Grant
- 2002-05-07 JP JP2003512553A patent/JP4116542B2/ja not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO03006820A1 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1571328A3 (de) * | 2004-03-02 | 2006-06-14 | Siemens Aktiengesellschaft | Einspritzventil |
Also Published As
Publication number | Publication date |
---|---|
KR20030036762A (ko) | 2003-05-09 |
KR100853645B1 (ko) | 2008-08-25 |
JP4116542B2 (ja) | 2008-07-09 |
WO2003006820A1 (de) | 2003-01-23 |
EP1407136B1 (de) | 2008-07-02 |
US6883725B2 (en) | 2005-04-26 |
JP2004521271A (ja) | 2004-07-15 |
DE10133265A1 (de) | 2003-01-23 |
DE50212447D1 (de) | 2008-08-14 |
US20040011892A1 (en) | 2004-01-22 |
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