WO2007098986A1 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant Download PDF

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Publication number
WO2007098986A1
WO2007098986A1 PCT/EP2007/050454 EP2007050454W WO2007098986A1 WO 2007098986 A1 WO2007098986 A1 WO 2007098986A1 EP 2007050454 W EP2007050454 W EP 2007050454W WO 2007098986 A1 WO2007098986 A1 WO 2007098986A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
fuel injection
spring sleeve
recesses
injection valve
Prior art date
Application number
PCT/EP2007/050454
Other languages
German (de)
English (en)
Inventor
Uwe Bruetsch
Dietmar Uhlmann
Christoph Radsak
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2007098986A1 publication Critical patent/WO2007098986A1/fr

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
    • 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
    • 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
    • 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
    • F02M63/0045—Three-way 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves

Definitions

  • the invention relates to a fuel injection valve for fuel injection systems of internal combustion engines. Specifically, the invention relates to an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a fuel injection valve in which a nozzle needle is indirectly controlled by a valve.
  • a control chamber is provided, which can be filled by a high-pressure region by means of an inlet throttle and connected via an outlet throttle with a valve chamber.
  • a bypass is provided, via which the valve space communicates directly with the high pressure area.
  • a valve pin serves to control a passage from the valve space to a low pressure area, while controlling the flow through the bypass.
  • the fuel injection valve known from DE 101 45 862 A1 has the disadvantage that, especially in the unpressurised state, the passage to the low-pressure region can not be completely closed. When commissioning the fuel injection valve, in which the pressure is built up, it can therefore come to a certain delay until a readiness to operate occurs. It is conceivable that a valve spring is used to act on the valve pin in a starting position. However, such a valve spring has the disadvantage that lateral forces occur, so that an undesirable wear on a seat to the low pressure area occurs and possibly damage to the seat caused by cavitation or the like.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that the valve pin is at least substantially applied without lateral forces or with vanishing transverse forces in the direction of the starting position, so that wear of a sealing edge is reduced to the low pressure region. Damage to the seat, for example due to cavitation, can also be prevented or reduced.
  • the valve has a valve seat body, which cooperates with a sealing cone of the valve pin to a sealing seat to close the connection between the valve chamber and the low-pressure region via the drain opening.
  • the sealing seat is preferably formed on a sealing edge of the formed on a valve plate valve seat body, wherein the spring sleeve uniformly acts on the sealing cone of the valve pin against the sealing edge.
  • the sealing cone is pressed uniformly in the initial state against the sealing edge of the valve seat body, in particular a punctual loading of the sealing edge, as may occur with lateral forces, is prevented, so that wear of the sealing cone and the valve seat body, in particular in the region of the sealing edge, is prevented ,
  • the valve chamber is closed in the initial state with respect to the low-pressure region, so that when the fuel injection valve is put into operation a rapid pressure buildup is made possible and the occurrence of cavitation on the seat is prevented.
  • the spring sleeve has at least two recesses extending in a circumferential direction.
  • the recesses allow compression of the spring sleeve and at the same time a flow of fuel so that, for example, fuel from the bypass channel can get into the part of the valve chamber between the spring sleeve and a wall of the valve chamber.
  • the recesses are preferably designed substantially slit-shaped, wherein the slot ends of the recesses are designed rounded to avoid cracks and the like in the material of the spring sleeve. It is particularly advantageous that the Spring sleeve has a plurality of recesses which lie in a same height and which are arranged sequentially in the circumferential direction.
  • two recesses may be provided at a certain height, each having a radian measure of almost 180 °, wherein webs are formed between the recesses.
  • Such webs preferably have at least approximately the same width in the circumferential direction.
  • the spring sleeve has at several heights in each case such recesses, which are arranged successively in the circumferential direction. As a result, the spring rate of the spring sleeve can be further reduced. In a longitudinal or vertical direction seen adjacent arrangements of recesses are preferably arranged offset in the circumferential direction to each other, so that an occurrence of shear forces is prevented.
  • the spring sleeve may be formed from a sleeve-shaped metal sheet having, for example, a sheet thickness of 0.1 mm, 0.15 mm or 0.2 mm.
  • Fig. 1 shows a first embodiment of an inventive
  • Fig. 2 shows in Fig. 1 with Il designated section of the fuel injection valve of the first embodiment in further detail
  • Fig. 1 shows an embodiment of a fuel injection valve 1 of the invention in a partial, schematic sectional view.
  • the fuel injection valve 1 can serve, in particular, as an injector for fuel injection systems of mixture-compression, self-igniting internal combustion engines.
  • the fuel injection valve 1 is suitable for commercial vehicles or passenger cars.
  • a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail, the diesel fuel under high pressure leads to a plurality of fuel injection valves 1.
  • the fuel injection valve 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has a multi-part housing 2, which is connected to a nozzle body 3.
  • the nozzle body 3 is connected by means of a nozzle lock nut 5 with a holding body 10 of the housing 2.
  • a needle seat 4 is formed, which cooperates with a nozzle needle 6 to a sealing seat.
  • the valve needle 6 is formed so that it encloses a control chamber 9 at a side facing away from the sealing seat with a sleeve 7 and a throttle plate 8.
  • a holding body 5 of the valve housing 2 has a fuel inlet 12, which is connectable by means of a suitable fuel line with a common rail. Through the fuel inlet 12, fuel enters a provided in the interior of the holding body 5 of the valve housing 2 fuel passage 13 and via this into a fuel chamber 14.
  • the fuel passage 13 and the fuel Räum 14 are part of a high pressure area 15. In operation of the fuel injection valve is located in the high pressure area 15th high pressure fuel.
  • the control chamber 9 is connected via an inlet throttle 16 to the fuel channel 13 of the high-pressure region 15.
  • an outlet throttle 17 is provided, via which the control chamber 9 is connected to a valve chamber 18 of a valve 19.
  • the valve chamber 18 is formed in a valve plate 20.
  • the valve chamber 18 communicates via a bypass channel 21 with the fuel chamber 14 of the high-pressure region 15.
  • the bypass channel 21 is a bypass 21 and in particular as Bypass bore 21 configured. Therefore, there is a direct connection between the high-pressure region 15 and the valve chamber 18 of the valve 19 via the bypass channel 21.
  • the valve 19 has a valve pin 22 which has a pin section 23 and a sealing cone 24.
  • the valve 19 has a spring sleeve 25, which acts on the sealing cone 24 of the valve pin 22 against a valve seat body 26 of the valve plate 20 with a closing force.
  • a piezoelectric actuator 30 arranged in the interior of the holding body 5 of the valve housing 2 acts on the valve pin 22 via a hydraulic coupler 31, which may be designed in particular as a stroke transmission device 31.
  • the valve pin 22 by means of an actuating element (piston) 32, which acts on a contact element 33 of the valve pin 22, against the force of the spring sleeve 25 is acted upon by an actuating force.
  • actuating element actuating element
  • a sealing seat formed between the sealing cone 24 and the valve seat body 26 of the valve plate 20 is opened at a sealing edge 37 (FIG. 2), so that a connection between a valve chamber 18 and a low-pressure region 34 is opened.
  • the sealing seat of the valve pin 22 is opened, so that the pressure in the valve chamber 18 drops and fuel flows through the outlet throttle 17 from the control chamber 9. Due to the pressure drop in the control chamber 9, there is an opening of the nozzle needle 6, so that the sealing seat formed between the nozzle needle 6 and the needle seat 4 of the nozzle body 3 is opened and fuel from the fuel chamber 14 via the open sealing seat and at least one nozzle opening 35 from the Fuel injection valve 1 is injected.
  • valve pin 22 After actuation of the fuel injection valve 1, the valve pin 22 is reset due to the force of the spring sleeve 25 in the starting position, in which the Connection of the valve chamber 18 is interrupted to the low pressure region 34 and the connection to the high-pressure region 15 is opened via the bypass channel 21, so that a rapid increase in pressure in the valve chamber 18 is generated. It can also come to fill the control chamber 9 with fuel (fuel) via the outlet throttle 17. The conditional increase in the pressure in the control chamber 9 then leads to the closing of the nozzle needle 6, so that the injection process is completed.
  • the valve 19 allows an advantageous specification of the course of injection and in particular short injection times.
  • Fig. 2 shows the designated in Fig. 1 with Il section of the fuel injection valve 1 in more detail.
  • the bolt portion 23 of the valve pin 22 is provided inside the valve space 18.
  • the sealing cone 24 connected to the bolt portion 23 is partially provided within the valve chamber 18 and closes in the starting position shown in FIG. 2, a drain opening 36 of the valve chamber 18.
  • Via the drain opening 36 of the valve chamber 18 is connected to the low pressure region 34, wherein the compound can be opened and closed by means of the valve pin 22. From the low-pressure region 36, the fuel can be conducted via a return line into a tank of the internal combustion engine.
  • a sealing seat is formed between a sealing edge 37 of the control valve seat body 26 of the valve plate 20 and the sealing cone 24, so that the discharge opening (channel) 36 is closed.
  • this sealing seat is opened so that fuel can flow out of the valve chamber 18 into the low-pressure region 36.
  • the spring sleeve 25 surrounds the pin portion 23 of the valve pin 22 circumferentially, wherein an inner diameter 38 of the spring sleeve 25 is slightly larger than a diameter 39 of the pin portion 23 is selected so that between the pin portion 23 and the spring sleeve 25, a narrow gap 40 of the width 41 is provided ,
  • the spring sleeve 25 is centered with respect to an axis 42 of the pin portion 23 of the valve pin 22, wherein due to the small width 41 of the narrow gap 40, a substantial change in the position of the spring sleeve 25 over the life of the fuel injection valve 1 is prevented.
  • an installation height Hl of the spring sleeve 25 is selected to be smaller than an initial height HO (FIG. 3).
  • the spring sleeve 25 has a plurality of recesses 43, 44, 45, 46, 47, 48, 49, in order to allow compression of the spring sleeve 25 under a dynamic load.
  • the recesses 43 to 49 also allow a flow of Fuel from the gap 40 in the remaining part of the valve chamber 18. This allows fuel from the bypass passage 21 into the valve chamber 18 flow when an opening 55 of the bypass passage 21 is at least partially open. In the initial state shown in FIG. 2, in which the sealing cone 24 bears against the sealing edge 37, the opening 55 of the bypass channel 21 is maximally opened.
  • the spring rate of the spring sleeve 25 can be specified.
  • the recesses 43 to 49 are distributed uniformly over the spring sleeve 25 in order to achieve a uniform force development of the spring sleeve 25 for the uniform application of the sealing edge 37 by means of the sealing cone 24 of the valve pin 22.
  • the loading of the valve pin 22 takes place at least substantially in the direction of the axis 42 and without the occurrence of transverse forces. This also ensures that in the initial state shown in FIG. 2, a complete closure of the drain opening 36 is achieved, so that in particular damages due to cavitation are prevented.
  • the end faces 56, 57 of the spring sleeve 25 are designed flat and optionally ground. As a result, a uniform contact of the spring sleeve 25 is achieved on the throttle plate 8 and the sealing cone 24 so that an axial alignment of the spring sleeve 25 achieved and a uniform force transmission can be achieved.
  • FIG. 3 shows the spring sleeve shown in FIG. 2 in a side view from the viewing direction designated III in FIG.
  • FIG. 3 further recesses 50, 51, 52 of the spring sleeve 25 are shown, while the recesses 48, 49 are located behind the recesses 44 and 46.
  • two of the recesses 43 to 52 lie at the height 70, the recesses 43, 50, each having an arc length of almost 180 °, so that a web 58 remains with a width 59 between them.
  • the recesses 43, 50 are arranged one after the other in a circumferential direction 60.
  • the recesses 43, 50 closest to the recesses 44, 58, which are arranged at the height 71 are seen in the circumferential direction 60 offset by 90 ° to the recesses 43, 50 arranged to ensure a uniform force development of the spring sleeve 25. Accordingly, the recesses 45, 51, which lie at the height 72, 90 ° offset from the recesses 44, 48 are arranged, so that their arrangement in the circumferential direction 60 seen matches the arrangement of the recesses 43, 50. This also applies to the recesses 47, 52, while the recesses 46, 49 seen in the circumferential direction 60 according to the recesses 44, 48 are arranged.
  • the recesses 43 to 52 are all configured the same.
  • the recesses 43 to 52 are formed as slot-shaped recesses, wherein in the region of the ends of the recesses 43, 52 rounded 61 are provided, as shown by the example of the recess 52.
  • the spring rate of the spring sleeve 25 can be specified within certain limits.
  • a substantial influence is made possible by the web width 59 of the web 58 and further webs between the recesses 43 to 52, of which in FIG. 3 the webs 80, 81 are marked.
  • the biasing force of the spring sleeve 25 is determined by the difference between the output length HO and the installation length Hl.
  • the spring sleeve 25 can be additionally set to at least reduce a decrease in the biasing force over the life of the fuel injection valve 1.
  • the setting of the spring sleeve 25 can be done, for example, by applying the spring sleeve 25 with 1.3 to 1.5 times the biasing force.
  • the spring rate of the spring sleeve 25 can be specified with the possibilities described above in a wide range.
  • the spring sleeve 25 can be made, for example, from a seamless drawn pipe section from a sheet with a wall thickness of 0.1 mm, 0.15 mm or 2 mm.
  • the inner diameter 38 of the spring sleeve and the initial height HO can be, for example, a few millimeters each.

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  • 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

L'invention concerne une soupape d'injection de carburant (1) servant en particulier d'injecteur dans des systèmes d'injection de carburant de moteurs à combustion interne à autoallumage par compression, lequel injecteur comprend un actionneur (30) qui régule la pression régnant dans une chambre de commande (9) par l'intermédiaire d'un dispositif de multiplication de course (31) et d'une soupape (19). Cette soupape (19) présente une goupille (22) et une douille élastique (25) qui entoure une section (23) de la goupille de soupape (22). Une arête d'étanchéité (37) d'un corps de siège de soupape, formant un siège d'étanchéité avec un cône d'étanchéité (24) de la goupille de soupape (22), est sollicitée de façon régulière par la douille élastique (25), ce qui permet d'éviter une détérioration de l'arête d'étanchéité (37).
PCT/EP2007/050454 2006-02-28 2007-01-17 Soupape d'injection de carburant WO2007098986A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610009071 DE102006009071A1 (de) 2006-02-28 2006-02-28 Brennstoffeinspritzventil
DE102006009071.3 2006-02-28

Publications (1)

Publication Number Publication Date
WO2007098986A1 true WO2007098986A1 (fr) 2007-09-07

Family

ID=37907464

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/050454 WO2007098986A1 (fr) 2006-02-28 2007-01-17 Soupape d'injection de carburant

Country Status (2)

Country Link
DE (1) DE102006009071A1 (fr)
WO (1) WO2007098986A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009130065A1 (fr) * 2008-04-23 2009-10-29 Robert Bosch Gmbh Injecteur de carburant pour moteurs à combustion interne

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999061779A1 (fr) * 1998-05-28 1999-12-02 Siemens Aktiengesellschaft Soupape d'injection de carburant pour moteurs a combustion interne
EP1164283A2 (fr) * 2000-06-15 2001-12-19 Toyota Jidosha Kabushiki Kaisha Soupape d'injection de combustible
DE10145862A1 (de) * 2001-09-18 2003-04-03 Bosch Gmbh Robert Verfahren zum Einspritzen von Kraftstoff sowie Ventil zum Steuern von Flüssigkeiten
EP1424492A2 (fr) * 2002-11-26 2004-06-02 Robert Bosch Gmbh Vanne de commande de liquides avec une buse et une valve de commande
US20050224604A1 (en) * 2002-03-26 2005-10-13 Dietmar Uhlmann Fuel injection valve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999061779A1 (fr) * 1998-05-28 1999-12-02 Siemens Aktiengesellschaft Soupape d'injection de carburant pour moteurs a combustion interne
EP1164283A2 (fr) * 2000-06-15 2001-12-19 Toyota Jidosha Kabushiki Kaisha Soupape d'injection de combustible
DE10145862A1 (de) * 2001-09-18 2003-04-03 Bosch Gmbh Robert Verfahren zum Einspritzen von Kraftstoff sowie Ventil zum Steuern von Flüssigkeiten
US20050224604A1 (en) * 2002-03-26 2005-10-13 Dietmar Uhlmann Fuel injection valve
EP1424492A2 (fr) * 2002-11-26 2004-06-02 Robert Bosch Gmbh Vanne de commande de liquides avec une buse et une valve de commande

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009130065A1 (fr) * 2008-04-23 2009-10-29 Robert Bosch Gmbh Injecteur de carburant pour moteurs à combustion interne
CN102016285A (zh) * 2008-04-23 2011-04-13 罗伯特·博世有限公司 内燃机用燃料喷射阀
JP2011518979A (ja) * 2008-04-23 2011-06-30 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング 内燃機関に用いられる燃料噴射弁
US8662411B2 (en) 2008-04-23 2014-03-04 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Also Published As

Publication number Publication date
DE102006009071A1 (de) 2007-08-30

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