EP1000240A1 - Kraftstoffeinspritzventil für brennkraftmaschinen - Google Patents
Kraftstoffeinspritzventil für brennkraftmaschinenInfo
- Publication number
- EP1000240A1 EP1000240A1 EP99936348A EP99936348A EP1000240A1 EP 1000240 A1 EP1000240 A1 EP 1000240A1 EP 99936348 A EP99936348 A EP 99936348A EP 99936348 A EP99936348 A EP 99936348A EP 1000240 A1 EP1000240 A1 EP 1000240A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- closing
- closing body
- fuel injection
- injection valve
- 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
- F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
-
- 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
Definitions
- the invention relates to a fuel injection valve according to the preamble of claim 1 and a method for its production.
- Such a fuel injection valve is known from document EP 0 816 670 AI.
- the known fuel injection valve contains a servo valve, which serves to hydraulically cause the fuel injection valve to open and close, in particular to precisely determine the start and end of the injection process.
- a spherical closing body is inserted in the valve chamber of the servo valve, which is operatively connected to an actuator via a tappet. Together with a conical, first valve seat of the valve chamber, the closing body forms a high-pressure-resistant seal. When the actuator is deflected, the closing body is lifted from the first valve seat, causing the servo valve to open (2/2-way valve).
- a further conical sealing seat is arranged in the valve chamber, opposite the first valve seat in the axial direction, the closing body covering the further valve seat when the actuator is deflected and thus creating a hydraulic lock (3/2-way valve).
- the object of the invention is to improve the design of the servo valve.
- An advantage of the invention is to increase the life of the servo valve. Another advantage is the small size of the servo valve and the simple manufacturing process of the closing body.
- the special design of the closing body as a rotationally symmetrical body is advantageous, which has a part-circular termination on one end face (head) and, in the longitudinal direction to the opposite end face, merges into a slim handle with a smaller diameter.
- the cross-sectional shape of the closing body is approximately mushroom-shaped.
- the head of the closing body preferably has a central flattened area on which a plunger rests, which is connected to an actuator. This results in an enlarged effective area between the plunger and the closing body, which advantageously leads to less wear and less risk of the closing body tilting.
- the stem of the closing body is encompassed by a valve spring which prestresses the closing body in the direction of the first valve seat. This advantageously achieves a compact size of the servo valve and stabilization of the closing body.
- the stem of the closing body is partially spherical, the partial spherical shape, together with a sealing seat, advantageously serving as a sealing surface.
- the closing body is preferably made from a solid ball. This results in low manufacturing tolerances and a simple manufacturing process.
- FIG. 1 shows a longitudinal section through a fuel injection servo valve with a servo valve in a first embodiment
- Figure 2 shows a longitudinal section through a fuel injection valve with a servo valve in a second embodiment
- Figure 3 a cross section of the closing body with a valve spring
- Figure 1 shows a fuel injection valve with a 2/2-way valve (servo valve).
- the fuel injection valve with a rotationally symmetrical basic body shape is divided axially into different bodies in the longitudinal direction.
- a controllable actuator 100 preferably a piezoelectric actuator, is operatively connected to a closing body 370 via a plunger 200.
- the plunger 200 is guided in a central guide bore 310 of a servo body 300.
- the servo body 300 additionally has a fuel anal 320, a return anal 330 and a central valve chamber 345.
- the return channel 330 projects laterally into the guide bore 310 and is connected to a fuel tank.
- the guide bore 310 merges into the valve chamber 345 via a conically opening first valve seat 350.
- the closing body 370 is introduced in the valve chamber 345 and, together with the first valve seat 350, forms a high-pressure-tight seal in the closed state.
- the closing body 370 is mushroom-shaped, the stem of the closing body 370 is comprised by a valve spring 390 which is arranged in the valve chamber 345 and which exerts a spring force directed towards the first valve seat 350 on the closing body 370.
- the shape of the closing body 370 is explained in more detail in the description of FIG. 3.
- valve chamber 345, the closing body 370, the valve spring 390 and the first valve seat 350 form a servo valve 340 which is actuated by the actuator 100 via the tappet 200.
- the servo valve 340 opens, as a result of which a hydraulic connection (outflow) between the valve chamber 345 and the fuel tank is established via the guide bore 310 and the return channel 330.
- the valve chamber 345 is delimited by an intermediate body 400 which adjoins the servo body 300 in the axial direction.
- the intermediate body 400 has a fuel channel 430, a connecting channel 420 and an inlet channel 410 which connects the fuel channel 430 to the valve chamber 345 and which has an inlet throttle 415 which limits the fuel flow into the valve chamber 345.
- the nozzle body 500 axially adjoining the intermediate body 400 has a central nozzle guide 510, in which a nozzle needle 600 is guided in the axial direction.
- the nozzle needle 600 and the nozzle body 500 form with their valve tip 640 or with its tapered second valve seat 540 a valve 640, 540 which controls the fuel injection into a combustion chamber via one or more spray holes 550 arranged at the tip of the nozzle body 500.
- ring shoulders are incorporated, which by the Fuel pressure causes an axial force directed away from the second valve seat 540 on the nozzle needle 600.
- the rear of the nozzle needle 600 projects into a control chamber 440, which is connected to the valve chamber 345 via the connecting channel 420.
- the pressure in the control chamber 440 exerts an axial force in the direction of the second valve seat 540 on the nozzle needle 600.
- FIG. 2 shows a fuel injection valve from FIG. 1 with a 3/2-way valve (servo valve).
- valve chamber 345 has a conically tapering sealing seat 360 at the end opposite the first valve seat 350, which, in conjunction with the lower body part of the closing member 370, the closing foot 386 (see FIG. 3), is highly pressure-resistant Sealing forms.
- This 3/2-way valve has the following mode of operation: In the non-deflected state of the actuator 100, the control chamber 440 is hydraulically connected to the high-pressure fuel in the fuel channel 430. The hydraulic connection between the valve chamber 345 and the return channel 330 is interrupted. In the deflected state of the actuator 100, the connection between the inlet channel 410 and the valve chamber 345 is interrupted, the control chamber 440 is hydraulically connected to the return channel 330 via the valve chamber 345. Due to the deflection of the actuator 100, a rapid pressure drop is achieved in the control chamber 440, as a result of which the fuel injection valve is opened quickly.
- the control chamber 440 builds up its pressure quickly via the valve chamber 345 and the inlet channel 410 and is not inhibited by any inlet throttle 415, as a result of which the fuel injection process is ended quickly. In addition, the amount of fuel that flows through the return channel 330 when the servo valve 340 is open is reduced.
- FIG. 3 shows a cross section of the closing body 370 with the valve spring 390 in a preferred embodiment.
- the closing body 370 is rotationally symmetrical along its longitudinal axis 371. As seen from the plunger 200 in FIG. 1, the closing body 370 is divided axially into a closing head 375, an indentation 380, a closing handle 384 and a closing foot 386.
- the closing head 375 is partially spherical on the side of the first valve seat 350 with a first radius R1 and has a central, preferably circular, head flattening 376, as a result of which the plunger 200 has an enlarged contact surface in comparison to the pure partial spherical shape.
- the end face with which the plunger 200 rests on the head flat 376 is also planar, so that the plunger 200 rests on the head flat 376 with a large area.
- the enlarged contact surface advantageously results in a lower material load on the closing body 370 and the plunger 200 and thus less wear on the material, which enables an increased service life.
- the head flat 376 improves
- the closing head 375 has a shoulder on its underside axially opposite the head flat 376, which leads to a reduction in the diameter and which represents the beginning of the indentation 380.
- the shoulder merges into a cylindrical stem, which widens conically via a further rounded portion and merges into a cylindrical closing stem 384 with an enlarged diameter via a first ring edge.
- the locking stem 384 ends at a further ring edge and merges into the locking foot 386, which preferably closes the locking stem 384 in a partially spherical manner with a second radius R2. closes.
- the indentation 380 is essentially formed by an annular recess.
- the first radius Rl is preferably equal to the second radius R2, since the closing body 370 is produced from a solid ball, which is indicated by the dashed line in FIG. 3.
- the solid ball is preferably made of metal and is machined by milling, turning or the like in such a way that the closing body 370 emerges therefrom, which advantageously represents a simple manufacturing method for the closing body 370.
- the part-spherical surfaces of the closing body 370 are designed such that, together with the first valve seat 350 or the sealing seat 360, they each enable a high-pressure-resistant seal, the part-spherical shape advantageously also providing a seal when the closing body 370 is slightly tilted.
- the surfaces of the partial spherical surfaces have a low roughness in order to make the seals highly pressure-resistant.
- the indentation 380 and the closing stem 384 are encompassed by a valve spring 390.
- the valve spring 390 rests on one end on the intermediate body 400 (the bottom of the valve chamber 345, see FIG. 1 or FIG. 2) and on the other end on the underside of the closing head 375, the spring force of the valve spring 390 resting the closing body 370 against the first Valve seat 350 and the plunger 300 presses.
- the indentation 380 serves to ensure that an end face of the valve spring 390 rests approximately perpendicularly on the underside of the closing head 375 and so essentially axial forces are advantageously exerted on the spring.
- the valve spring 390 engages in the indentation 380 and is therefore advantageously mechanically fixed to the closing member 370.
- the arrangement of the valve spring 390 and the closing body 370 relative to one another advantageously enables a compact design of the servo valve 340.
- the valve spring 390 is preferably close to the closing stem 384, so that the valve spring 390 and the closing body 370 are laterally stabilized.
- An advantageous, stabilized guidance of the closing body 370 improves the dynamic behavior of the servo valve 340 and accelerates its opening and closing, which is achieved by the following features:
- the plunger 200 lies with its end face on the head flattening 376 and causes a stabilizing force on the closing body 370, which makes it difficult for the closing body 370 to tilt.
- the valve spring 390 rests in a ring shape with one end face on the underside of the closing head 375 and with the opposite end face on the bottom of the valve chamber 345.
- the closing body 370 is stabilized by the axially directed spring force of the valve spring 390, which acts uniformly on the bottom of the valve chamber 345 and the underside of the closing head 375.
- valve spring 390 tightly embraces the closing stem 384 and thus prevents the closing body 370 from tilting.
- the valve spring 390 is preferably designed as a spiral spring or as a hollow spring.
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)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19823935 | 1998-05-28 | ||
DE19823935 | 1998-05-28 | ||
PCT/DE1999/001578 WO1999061779A1 (de) | 1998-05-28 | 1999-05-28 | Kraftstoffeinspritzventil für brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1000240A1 true EP1000240A1 (de) | 2000-05-17 |
EP1000240B1 EP1000240B1 (de) | 2004-03-24 |
Family
ID=7869220
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99936348A Expired - Lifetime EP1000240B1 (de) | 1998-05-28 | 1999-05-28 | Kraftstoffeinspritzventil für brennkraftmaschinen |
Country Status (5)
Country | Link |
---|---|
US (1) | US6250563B1 (de) |
EP (1) | EP1000240B1 (de) |
JP (1) | JP2002516952A (de) |
DE (1) | DE59908941D1 (de) |
WO (1) | WO1999061779A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2819022A1 (fr) * | 2000-12-28 | 2002-07-05 | Denso Corp | Dispositif de commande hydraulique, systeme et procede de commande d'un dispositif actionneur |
Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19837890B4 (de) * | 1998-08-20 | 2004-06-03 | Siemens Ag | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE19950224A1 (de) * | 1999-10-19 | 2001-04-26 | Bosch Gmbh Robert | Doppelschaltendes Steuerventil für einen Injektor eines Kraftstoffeinspritzsystems für Brennkraftmaschinen mit kugelförmigem Stellglied |
JP3551898B2 (ja) * | 2000-06-15 | 2004-08-11 | トヨタ自動車株式会社 | 燃料噴射弁 |
JP3829604B2 (ja) * | 2000-08-30 | 2006-10-04 | トヨタ自動車株式会社 | 燃料噴射装置 |
DE10101797A1 (de) | 2001-01-17 | 2002-07-18 | Bosch Gmbh Robert | Einspritzventil |
GB0107575D0 (en) * | 2001-03-27 | 2001-05-16 | Delphi Tech Inc | Control valve arrangement |
DE10122245A1 (de) * | 2001-05-08 | 2002-12-12 | Bosch Gmbh Robert | Leckagereduzierter druckgesteuerter Kraftstoffinjektor |
DE10131617A1 (de) * | 2001-06-29 | 2003-01-23 | Bosch Gmbh Robert | Kraftstoffinjektor-Schaltventil zur Druckentlastung/Belastung eines Steuerraumes |
DE102004049702B3 (de) * | 2004-10-12 | 2006-03-09 | Siemens Ag | Servoventil und Einspritzventil |
DE102004061800A1 (de) * | 2004-12-22 | 2006-07-06 | Robert Bosch Gmbh | Injektor eines Kraftstoffeinspritzsystems einer Brennkraftmaschine |
DE102005044087A1 (de) * | 2005-09-08 | 2007-03-15 | Schott Ag | Aktor zur Bewegung eines Werkzeuges |
DE102006009069A1 (de) * | 2006-02-28 | 2007-08-30 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE102006009071A1 (de) * | 2006-02-28 | 2007-08-30 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
JP4855946B2 (ja) * | 2006-06-08 | 2012-01-18 | 株式会社デンソー | 燃料噴射弁 |
JP2008002306A (ja) * | 2006-06-21 | 2008-01-10 | Denso Corp | 燃料噴射弁 |
DE502007002482D1 (de) | 2007-03-15 | 2010-02-11 | Ford Global Tech Llc | Injektor |
DE102007042466B3 (de) * | 2007-09-06 | 2009-04-09 | Continental Automotive Gmbh | Einspritzsystem mit reduzierter Schaltleckage und Verfahren zum Herstellen eines Einspritzsystems |
US8496191B2 (en) * | 2008-05-19 | 2013-07-30 | Caterpillar Inc. | Seal arrangement for a fuel injector needle valve |
JP2012202251A (ja) * | 2011-03-24 | 2012-10-22 | Denso Corp | インジェクタ |
US9293353B2 (en) | 2011-04-28 | 2016-03-22 | Lam Research Corporation | Faraday shield having plasma density decoupling structure between TCP coil zones |
US9490106B2 (en) | 2011-04-28 | 2016-11-08 | Lam Research Corporation | Internal Faraday shield having distributed chevron patterns and correlated positioning relative to external inner and outer TCP coil |
US9966236B2 (en) | 2011-06-15 | 2018-05-08 | Lam Research Corporation | Powered grid for plasma chamber |
DE102011078399A1 (de) * | 2011-06-30 | 2013-01-03 | Robert Bosch Gmbh | Kraftstoffinjektor |
US9029267B2 (en) | 2013-05-16 | 2015-05-12 | Lam Research Corporation | Controlling temperature of a faraday shield |
US9885493B2 (en) | 2013-07-17 | 2018-02-06 | Lam Research Corporation | Air cooled faraday shield and methods for using the same |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA1021225A (en) * | 1974-06-28 | 1977-11-22 | General Signal Corporation | Quick-acting valve assembly |
DE3627865A1 (de) * | 1986-04-12 | 1988-02-25 | Guenter Stein | Rueckschlagventil |
CH686845A5 (de) * | 1993-03-08 | 1996-07-15 | Ganser Hydromag | Steueranordnung fuer ein Einspritzventil fuer Verbrennungskraftmaschinen. |
US5564469A (en) * | 1994-03-23 | 1996-10-15 | Flow International Corporation | Erosion resistant high pressure relief valve |
JP3555264B2 (ja) * | 1995-07-14 | 2004-08-18 | いすゞ自動車株式会社 | 内燃機関の燃料噴射装置 |
US5779149A (en) * | 1996-07-02 | 1998-07-14 | Siemens Automotive Corporation | Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke |
-
1999
- 1999-05-28 JP JP2000551142A patent/JP2002516952A/ja not_active Withdrawn
- 1999-05-28 WO PCT/DE1999/001578 patent/WO1999061779A1/de active IP Right Grant
- 1999-05-28 DE DE59908941T patent/DE59908941D1/de not_active Expired - Lifetime
- 1999-05-28 EP EP99936348A patent/EP1000240B1/de not_active Expired - Lifetime
-
2000
- 2000-01-28 US US09/494,404 patent/US6250563B1/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO9961779A1 * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2819022A1 (fr) * | 2000-12-28 | 2002-07-05 | Denso Corp | Dispositif de commande hydraulique, systeme et procede de commande d'un dispositif actionneur |
US6895940B2 (en) | 2000-12-28 | 2005-05-24 | Denso Corporation | Hydraulic control device, system and method for controlling actuator device |
US7185828B2 (en) | 2000-12-28 | 2007-03-06 | Denso Corporation | Hydraulic control device, system and method for controlling actuator device |
Also Published As
Publication number | Publication date |
---|---|
DE59908941D1 (de) | 2004-04-29 |
JP2002516952A (ja) | 2002-06-11 |
US6250563B1 (en) | 2001-06-26 |
EP1000240B1 (de) | 2004-03-24 |
WO1999061779A1 (de) | 1999-12-02 |
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