EP1504189A1 - Fuel injection valve for internal combustion engines - Google Patents
Fuel injection valve for internal combustion enginesInfo
- Publication number
- EP1504189A1 EP1504189A1 EP03729812A EP03729812A EP1504189A1 EP 1504189 A1 EP1504189 A1 EP 1504189A1 EP 03729812 A EP03729812 A EP 03729812A EP 03729812 A EP03729812 A EP 03729812A EP 1504189 A1 EP1504189 A1 EP 1504189A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- fuel injection
- reinforcement
- valve body
- bore
- 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
- 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
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1866—Valve seats or member ends having multiple cones
-
- 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
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
-
- 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
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
-
- 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
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
- F02M61/1833—Discharge orifices having changing cross sections, e.g. being divergent
-
- 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
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
Definitions
- the invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
- Such fuel injection valves have a valve body in which a bore is formed which is delimited at its combustion chamber end by a conical valve seat.
- a piston-shaped valve needle is arranged so as to be longitudinally displaceable, which cooperates with a likewise conical valve sealing surface with the valve seat and thereby controls the opening of at least one injection channel which starts from the valve seat and leads into the combustion chamber of the internal combustion engine.
- fuel may or may not flow to the injection channels from a pressure space formed between the valve needle and the wall of the bore.
- the conical valve seat has an axis of symmetry that coincides with the longitudinal axis of the bore.
- a fuel injection valve in which the valve body has a uniform wall thickness in the entire end region, also in the region in which the valve needle rests in its closed position and in the end region of the bore on the combustion chamber side. This is the stability of the valve body is not always guaranteed, since high mechanical loads can occur in the end region of the valve body: on the one hand, by fitting the valve needle when the injection channels are closed, the valve body is deformed, which causes the valve body to vibrate. On the other hand, the pressure in the pressure chamber fluctuates considerably when the fuel injection valve is in operation, since the high injection pressure - depending on the type of fuel injection valve - is only present in the pressure chamber when an injection is to take place.
- valve body is periodically widened and thus mechanical stress is exerted.
- valve needle lies somewhat differently on the valve seat than is the case in the depressurized state.
- the known fuel injection valves therefore have the disadvantage that the deformations due to pressure oscillation and mechanical loading by the valve needle can lead to excessive wear between the valve needle and the valve seat.
- the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the valve body in the area of the valve seat is significantly reinforced compared to the prior art, which reduces the expansion due to the mechanical loads and thus less wear occurs in the area of the valve seat ,
- the valve body has a reinforcement in the end region with a wall thickness that is at least a factor of 1.2 greater than the wall thickness on the adjacent wall region. Due to the relatively small wall thickness at the intersection point of the longitudinal axis a certain flexibility of the Ventilkorpers is maintained, which is indispensable to a mechanical failure of the valve body by the ' Prevent the valve needle from hitting when the fuel injector closes.
- the reinforcement is formed in the region of the valve seat.
- the injection channels which start from the valve seat advantageously open into recesses which are formed on the outside of the valve body. This shortens the effective length of the injection channels without significantly affecting the stability of the valve body. A not too long length of the injection channels is necessary so that the throttling of the fuel flow in the injection channels does not become too great.
- the formation of the recesses as a conical countersink is particularly advantageous, since this is easy to manufacture and it can be ensured via a sufficiently large opening angle that the injection jet emerging from the injection channel is not impaired by the valve body.
- the recess is designed as an annular groove into which all the injection channels open. It is not necessary to produce a separate recess for each injection channel, which is generally more complicated.
- the reinforcement is formed on the combustion chamber end section of the bore on the inner wall and adjoins the valve seat. Widening of the bore, which also leads to deformation of the valve seat, is thereby significantly reduced.
- the annular gap that is between the valve needle and the wall of the bore is formed in the area of the reinforcement at least approximately the same as in the adjacent area of the bore so as not to impede the flow of fuel to the injection openings.
- FIG. 1 shows a fuel injection valve in longitudinal section, only one side being shown in full
- Figure 2 shows a further embodiment of a fuel injection valve in longitudinal section, with only one side is fully shown here and
- Figure 3 is an external view of the valve body tip of another embodiment.
- a fuel injector according to the invention is shown in longitudinal section in FIG. 1, only the left half being fully drawn.
- the fuel injection valve comprises a valve body 1, which is rotationally symmetrical with respect to a longitudinal axis 4 and has a bore 5, the axis of which coincides with the longitudinal axis 4.
- the bore 5 is narrowed at its end on the combustion chamber side by a first reinforcement 22, so that a conical surface 26 and a reduced diameter cylinder section 24 are formed on the inner wall of the bore 5.
- the first reinforcement 22 of the valve body 1 is shown in FIG a dashed line shows.
- a conical valve seat 8 adjoins the cylinder section 24 and forms the end of the bore 5 on the combustion chamber side.
- At least one injection channel 18 extends from the valve seat 8, which penetrates the valve body 1 and opens directly into the combustion chamber of the internal combustion engine.
- a piston-shaped valve needle 3 is arranged so as to be longitudinally displaceable, a pressure chamber 7 being formed between the valve needle 3 and the wall of the bore 5, which can be filled with fuel under high pressure via an inlet channel (not shown in the drawing).
- the valve needle 3 has a pressure shoulder 6 at the level of the conical surface 26 and then merges into a tapered section 103, which is followed by a conical valve sealing surface 10.
- the tip of the valve needle 3 on the combustion chamber side is formed by a conical surface 14 which is separated from the valve sealing surface 10 by an annular groove 12.
- the edge at the transition from the annular groove 12 to the valve sealing surface 10 functions as a sealing edge which, when the valve needle 3 rests on the valve seat 8, first bears on the latter. Due to the elastic deformation of the valve needle 3 and the valve body 1 in the region of the valve seat 8, the valve needle 3 finally rests in its closed position with a large part of the valve sealing surface 10 on the valve seat 8.
- the valve needle 3 interacts with the valve seat 8 for controlling the injection channels 18.
- the valve needle 3 is acted upon by a device, not shown in the drawing, with a closing force, for example by a prestressed spring, in the direction of the valve seat 8, so that it rests with the valve sealing surface 10 on the valve seat 8.
- a closing force for example by a prestressed spring
- the injection channels 18, of which several are generally arranged distributed over the circumference of the valve body 1 are against the Pressure chamber 7 closed. If fuel is to be injected into the combustion chamber, fuel is injected into the pressure chamber 7 under injection pressure, so that the pressure there rises considerably, depending on the type of fuel injection valve, to 100 MPa and more.
- the hydraulic force on the valve needle 3 results in a force that is opposite to the closing force.
- valve needle 3 lifts off the valve seat 8, so that fuel can flow from the pressure chamber 7 between the valve sealing surface 10 and the valve seat 8 to the injection channels 18.
- the closing force on valve needle 3 prevails again and this slides back into its closed position.
- the increasing pressure in the pressure chamber 7 results in a slight expansion of the valve body 1 in the area of the valve seat 8 and the cylinder section 24.
- the shape of the valve needle 3, however, remains practically unchanged, since it is solid.
- the shape of the valve body 1 thus changes slightly in the area of the valve seat 8, so that the valve seat 8 moves slightly relative to the valve sealing surface 10, which over time leads to wear in this area.
- the impact of the valve needle 3 on the valve seat 8 also results in vibrations of the valve body 1, which lead to a relative movement of the valve sealing surface 10 and the valve seat 8.
- the valve body 1 is thickened in the region of the valve seat 8 by a second reinforcement 23, so that there is greater stability and thus less widening.
- the wall thickness of the valve body 1 in the region of the valve seat 8 is equal to a thickness hg at the point where the piercing point 30 of the longitudinal axis 4 lies.
- the valve body 1 is thickened by the second reinforcement 23, so that there is a wall thickness perpendicular to the valve sealing surface 8 which is at least a factor of 1.2 the wall thickness is hg.
- the wall thickness H ] _ in the area of the first reinforcement 22 is greater than the wall thickness Hg of the adjacent wall area by at least a factor of 1.2, ie a ratio of
- FIG. 2 shows a further exemplary embodiment of the fuel injection valve according to the invention.
- the valve body 1 is again shown in longitudinal section, only one half of the rotationally symmetrical valve body 1 being drawn. Instead of an annular groove and a conical surface, the valve needle 3 has only a single conical valve sealing surface 10, which is pressed into the conical valve seat 8 by the contact pressure of the closing force.
- the valve seat 8 is thickened by a second reinforcement 23, the proportion of which in the valve body 1 is illustrated by a dashed line.
- the wall thickness h ] _ in the area of the injection channels 18 is here also at least a factor 1.2 greater than the wall thickness hg am Puncture point 30 of the longitudinal axis 4.
- the length of the injection channels 18 increases correspondingly, but this is only possible to a limited extent: if the injection channel 18 is too long, the fuel flow during the injection is throttled too much and the effectively effective injection pressure Decreases.
- recesses 20 are formed in the valve body 1 from the outside, which are designed as countersinking and into each of which an injection channel 18 opens. The effective length of the injection channels 18 is thus less, since the opening angle of the cone countersink 20 is so large that the emerging injection jet does not touch the wall of the cone countersink 20.
- a countersink 20 with a strictly conical outer wall other shapes are also conceivable, for example cylindrical recesses which have a sufficiently large diameter.
- the taper countersinks 20 can be formed, for example, by drilling or electrical discharge machining.
- FIG. 3 shows an external view of the tip of the valve body 1 on the combustion chamber side of a further exemplary embodiment.
- annular groove 32 instead of different recesses 20, only a single recess in the form of an annular groove 32 is formed here, which surrounds the valve body 1 over its entire circumference and into which all the injection channels 18 open.
- the cross section of the annular groove 32 is dimensioned such that the injection jets do not touch the wall of the annular groove 32 here either.
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 |
---|---|---|---|
DE10219608 | 2002-05-02 | ||
DE2002119608 DE10219608A1 (en) | 2002-05-02 | 2002-05-02 | Fuel injection valve for internal combustion engines |
PCT/DE2003/000936 WO2003093669A1 (en) | 2002-05-02 | 2003-03-21 | Fuel injection valve for internal combustion engines |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1504189A1 true EP1504189A1 (en) | 2005-02-09 |
EP1504189B1 EP1504189B1 (en) | 2007-07-04 |
Family
ID=29264993
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03729812A Expired - Lifetime EP1504189B1 (en) | 2002-05-02 | 2003-03-21 | Fuel injection valve for internal combustion engines |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1504189B1 (en) |
DE (2) | DE10219608A1 (en) |
WO (1) | WO2003093669A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007051408A1 (en) | 2007-10-25 | 2009-05-28 | Prelatec Gmbh | Method for drilling holes of defined geometries by means of laser radiation |
WO2010121767A1 (en) * | 2009-04-20 | 2010-10-28 | Prelatec Gmbh | Nozzle having at least one spray hole for vaporizing fluids |
DE102011077268A1 (en) * | 2011-06-09 | 2012-12-13 | Robert Bosch Gmbh | Injection valve for internal combustion engines |
DE102012211459A1 (en) * | 2012-07-03 | 2014-01-09 | Robert Bosch Gmbh | Fuel injection valve with improved spray hole |
DE102013220917A1 (en) * | 2013-10-15 | 2015-04-16 | Continental Automotive Gmbh | injection |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3306078A1 (en) * | 1983-02-22 | 1984-08-23 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES |
JP2819702B2 (en) * | 1989-12-12 | 1998-11-05 | 株式会社デンソー | Fuel injection valve |
DE4025542A1 (en) * | 1990-08-11 | 1992-02-13 | Kloeckner Humboldt Deutz Ag | Method for operating self-igniting IC engine - involves pre- and main fuel injection and combustion chamber |
DE4200709A1 (en) * | 1992-01-14 | 1993-07-15 | Bosch Gmbh Robert | FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES |
JPH07224739A (en) * | 1994-02-15 | 1995-08-22 | Nissan Motor Co Ltd | Fuel injection nozzle |
JPH09177640A (en) * | 1995-12-15 | 1997-07-11 | Caterpillar Inc | Combustion exhaust emission control system by fuel injector having high suck capacity and its method |
DE19729827A1 (en) * | 1997-07-11 | 1999-01-14 | Bosch Gmbh Robert | Fuel injector |
DE10000501A1 (en) | 2000-01-08 | 2001-07-19 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
-
2002
- 2002-05-02 DE DE2002119608 patent/DE10219608A1/en not_active Withdrawn
-
2003
- 2003-03-21 EP EP03729812A patent/EP1504189B1/en not_active Expired - Lifetime
- 2003-03-21 DE DE50307613T patent/DE50307613D1/en not_active Expired - Lifetime
- 2003-03-21 WO PCT/DE2003/000936 patent/WO2003093669A1/en active IP Right Grant
Non-Patent Citations (1)
Title |
---|
See references of WO03093669A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP1504189B1 (en) | 2007-07-04 |
DE50307613D1 (en) | 2007-08-16 |
WO2003093669A1 (en) | 2003-11-13 |
DE10219608A1 (en) | 2003-11-20 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2480783B1 (en) | Fuel injection valve for an internal combustion engine | |
WO1987000889A1 (en) | Fuel injection nozzle for internal combustion engines | |
EP2470771B1 (en) | Fuel injection valve | |
EP1509693B1 (en) | Fuel injection valve for internal combustion engines | |
EP0116864A2 (en) | Fuel injection nozzle for internal-combustion engines | |
DE2814999A1 (en) | FUEL INJECTION NOZZLE FOR COMBUSTION MACHINES | |
DE102004060552A1 (en) | Fuel injection valve for an internal combustion engine | |
WO2000019088A1 (en) | Fuel injection valve for an internal combustion engine | |
WO2002077445A1 (en) | Fuel-injection valve for internal combustion engines | |
EP1627147B1 (en) | Fuel injection valve for combustion engines | |
EP1518049B1 (en) | Fuel injection valve for an internal combustion engine | |
DE102005034879B4 (en) | Nozzle assembly for an injection valve | |
EP1574701A1 (en) | Common rail injector | |
EP1504189B1 (en) | Fuel injection valve for internal combustion engines | |
EP1043496B1 (en) | Injector for fuel injection in an internal combustion engine | |
EP1422418B1 (en) | Fuel injector for an internal combustion engine | |
DE19843912B4 (en) | fuel Injector | |
DE10318989A1 (en) | Fuel injection valve, for an IC motor, has a ring groove at the valve needle in a constant hydraulic link with the fuel-filled pressure zone and its downstream edge acting a sealing edge, to reduce wear at the valve seat | |
WO2004057180A1 (en) | Fuel injection valve for internal combustion engines | |
EP2439398A1 (en) | Fuel injector valve | |
EP2156044A1 (en) | Injector having a pressure-compensated control valve | |
AT414159B (en) | INJECTOR | |
WO2003038271A1 (en) | Fuel injection valve | |
DE10338093A1 (en) | Fuel injection valve especially for internal combustion engine has nozzle body and/or shut-off component designed so that mixture cloud injected into combustion chamber is formed asymmetrically with at least one jet gap | |
DE10213384A1 (en) | Fuel injection valve for internal combustion engines |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20041202 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL LT LV MK |
|
DAX | Request for extension of the european patent (deleted) | ||
RBV | Designated contracting states (corrected) |
Designated state(s): DE FR GB |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REF | Corresponds to: |
Ref document number: 50307613 Country of ref document: DE Date of ref document: 20070816 Kind code of ref document: P |
|
ET | Fr: translation filed | ||
GBV | Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed] |
Effective date: 20070704 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20070704 |
|
26N | No opposition filed |
Effective date: 20080407 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20140319 Year of fee payment: 12 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20151130 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150331 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20170529 Year of fee payment: 15 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 50307613 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20181002 |