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WO2002023036A1 - Configuration de soupapes de distribution - Google Patents

Configuration de soupapes de distribution Download PDF

Info

Publication number
WO2002023036A1
WO2002023036A1 PCT/EP2001/010685 EP0110685W WO0223036A1 WO 2002023036 A1 WO2002023036 A1 WO 2002023036A1 EP 0110685 W EP0110685 W EP 0110685W WO 0223036 A1 WO0223036 A1 WO 0223036A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
design according
bore
seat
pressure side
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.)
Ceased
Application number
PCT/EP2001/010685
Other languages
German (de)
English (en)
Inventor
Wolfgang Scheibe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LOrange GmbH
Original Assignee
LOrange 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 LOrange GmbH filed Critical LOrange GmbH
Priority to EP01978375A priority Critical patent/EP1319127B1/fr
Priority to DE50109103T priority patent/DE50109103D1/de
Publication of WO2002023036A1 publication Critical patent/WO2002023036A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated 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
    • 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
    • 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
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the invention relates to a valve design for control valves according to the preamble of claim 1.
  • Valve designs of the aforementioned type are known from practice.
  • the pressure gradient between the high and low pressure sides in the throttle point leads to high flow velocities with the tendency of the flow to cavitate with an increasing pressure drop in the outlet area on the blocking element, and when the impinging element hits the blocking element, pressure increases again due to the associated deflections and flow delays.
  • the invention has for its object to improve a valve design of the type mentioned with regard to the problems mentioned and in particular to reduce the risk of cavitation erosion in such valve designs.
  • this is achieved by the features of claim 1, wherein use is made of the idea of largely eliminating the conditions for cavitation by means of stepped pressure reduction.
  • the locking element adjacent to the seat contact zone is delimited against the low pressure side and throttled toward the low pressure side Connected recording room is assigned.
  • the delimitation of this space opposite the seat contact zone can expediently also be a guide for the locking member and / or serve as a throttling point, so that the desired stepped throttling can also be achieved structurally with simple means and with little effort.
  • the locking member can be an independent component, or it can also be connected to the actuating movement transducer assigned to it, whereby plungers with a relatively small diameter in relation to their length can serve as the actuating movement transducer, so that the mutual alignment with the seat surface via the pressure plunger is not impaired becomes.
  • Solid balls, ball segments or valve bodies tapering in the direction of the seat surface can be used as locking members in the context of the invention, a guide being expedient in particular for spherical locking members and especially for full-spherical locking members.
  • Low-pressure side valve seats in spherical or dome-shaped training or also in tapered training, in particular in flat-tapered training can prove to be expedient, so that different throttle paths, possibly also combined, can be implemented, and this regardless of the respective type of training of the guide Part, which may also be designed as an aperture.
  • the invention also makes it possible with simple means to make the throttle cross-section of the space delimited by the guide dependent on the stroke of the locking member, that is to say to create a throttle connection which varies in cross-section depending on the stroke, the corresponding cross-sectional changes also being made by appropriate shaping for the actuating movement transmitter in the form of an actuating plunger or pressure stamp and / or the locking member can be realized.
  • Figure 1 shows a schematic sectional view of the control valve
  • Injection injector between the nozzle part and a magnetic actuator arranged opposite to this
  • Control valve is located, wherein the magnetic actuator on the control valve acts on a lifting movement actuator for the locking member, which controls a throttled inlet from a pressure chamber, with which the nozzle needle of the injection nozzle, which is acted upon on the high-pressure side via the injection medium, communicates with an actuating surface via which in the pressure chamber current pressure, the nozzle needle is loaded in addition to the closing spring in the closing direction,
  • FIG. 2 shows an enlarged section A of an area of FIG. 1, which shows the actuating movement transmitter acting on the locking member and the associated area of the valve seat
  • FIG. 3 shows an embodiment of the invention corresponding to FIG
  • FIG. 4 shows a section according to IV-IV in FIG. 3 in a schematic representation
  • FIG. 7 shows a further embodiment according to FIG Invention in which the
  • FIG. 8 is a sectional view according to line Vll-Vll,
  • FIG. 9 shows another embodiment of the invention, in which the
  • Throttle cross sections are variable as a function of the stroke of the locking member, and FIG. 10 shows a schematic sectional illustration along line X-X in FIG. 9.
  • FIG. 1 illustrates the control valve 1 of an injection injector, not shown, by means of which the injection valve associated with the injection injector is controlled.
  • the high pressure side inlet connection to the control valve 1 is illustrated by the arrow 2.
  • the inlet takes place via a bore 4 provided in a valve plate 3, which opens out onto a valve seat 6 via a throttle point 5.
  • valve seat 6 tapers in the direction of the bore 4, that is, counter to the inflow direction according to arrow 2, and the valve seat 6 is assigned a locking member 7 which is supported in a stroke-movable manner (arrow 8).
  • the locking member 7 is supported in the exemplary embodiment (FIG. 1) via an actuating movement transmitter 9, which is shown in FIG
  • Diameter rod-shaped, thin actuating plunger is formed and which is applied and adjustable relative to the control valve 1 to the flow direction according to arrow 2 via a magnetic actuator of the injection injector, not shown here.
  • the locking member 7 In the closed position, the locking member 7 is seated in a seat contact zone 10 on the valve seat 6, to which a bore 11 in the valve plate 3 connects on the low pressure side, into which the locking member 7 supported by the actuating movement transmitter 9 is immersed and which, based on FIGS. 1 and 2, forms part of the low pressure side discharge path which, as in 1 shows, continues in transverse channels 12 which lie between the valve plate 3 and the housing 13 of the control valve 1, the valve plate 3 being centered and fixed against the housing 13 via a clamping ring 14 in the exemplary embodiment.
  • FIG. 3 illustrates that the locking member 7, which is designed as a spherical segment in the exemplary embodiments, has a diameter that is matched to the bore 11, such that there is a radial guidance through the bore 11 in the central plane 15 of the locking member 7, which is parallel to the seat contact zone 10 Stroke mobility - according to arrow 8 - of the locking member 7 in the sense of a low-friction sliding guide, but delimits a space 16 downstream of the seat surface 10 due to the guide serving as a gap seal, from which the connection to the low-pressure side follows throttled.
  • This throttled connection is illustrated in FIG. 3 by means of bores 17 which open onto the space 14 adjacent to the valve seat 6 and which run radially to the stroke axis 18 of the actuating motion transmitter 9.
  • Flow conditions with respect to the blocking member 7 contributes and also reduces the mechanical stresses between the blocking member 7 and the valve seat 6 in that deviations in the axial position are at least largely avoided.
  • the centering guide function for the locking member 7 proves to be expedient if the locking member 7 is firmly connected to the actuating movement transmitter 9 or, without a centering connection to the latter, is only acted upon via the latter. Furthermore, the guide function proves to be expedient in connection with full-spherical locking members, or also locking members designed as a spherical segment, wherein in the exemplary embodiment a spherical segment is provided as a locking member 7.
  • spherical locking members 7 in particular conical or conical locking members 7 tapering in the direction of the valve seat can also be provided.
  • FIGS. 5 and 6 represent solutions which functionally correspond to what has been explained with reference to FIGS. 3 and 4. In structural terms, they differ from the solution according to FIGS. 3 and 4 by the way in which the throttle chamber 16 is connected to the low-pressure side via corresponding throttle bores or throttle ducts, throttle ducts 20 being provided in the embodiment according to FIG open out the low-pressure side (arrow 19), in Figure 5 the throttle channels are formed by the fact that a valve plate 21 is provided to which a cover plate 22 is assigned, the valve plate 21 and cover plate 22 forming channels 20 between their mutually facing surfaces, which into the Cover plate 22, are incorporated into the valve plate 21 or in both plates and which run in the parting plane 23 of the two plates.
  • the division plane 23 corresponds to the sectional plane between the bore 11 and the conical valve seat 6, so that the bore 11 runs in the cover plate 22 and the valve seat 6 is incorporated into the valve plate 21. Overall, this leads to a simplified structure.
  • FIG. 6 again assumes a division into valve plate 24 and cover plate 25, as was explained with reference to FIG. 5.
  • the valve seat 26 is also incorporated into the valve plate 24 here, the bore 11 is assigned to the cover plate 25 and passes through it, opening out onto the valve seat 26 within the diameter thereof.
  • valve seat 26 which widens in the inflow direction according to arrow 2, has a radial overlap region with the cover plate 25, the partial plane between the valve plate 24 and the cover plate 25 being designated 27 and being offset against the inflow direction 2 to the central plane 15 of the blocking member 7, which is axially in the region the bore 11 lies, so that in this solution, too, the guide for the locking member 7 lies in the region of the bore 11, in FIG. 5 in the region of the cover plate 22, in FIG. 6 in the cover plate 25.
  • the throttle chamber 28 is partially covered by the side of the cover plate 25 facing the valve plate 24, so that the cover plate 25 is on the throttle chamber 28 can open axially penetrating throttle bores 30.
  • the invention thus shows a wide variety
  • FIGS. 7 and 8 A further possibility of the throttling connection to the low-pressure side is shown in FIGS. 7 and 8, with an initial situation also being given here, which corresponds in principle to that according to FIGS. 3 to 6.
  • a ball segment is also provided as the locking member 32, the central plane 15 of which runs parallel to the seat contact surface 10 and which is guided axially displaceably in the region of the central plane 15 and bears sealingly against the wall of the bore 33, which acts as a guide bore for the locking member 32 on the seat surface 6 connects and delimits the throttle space 34 to the seat 6 together with the locking member 32.
  • the locking member 32 is supported by an actuating movement transmitter 9 which can be moved in accordance with the arrow 8. As illustrated in FIG.
  • the throttle chamber 34 is connected to the low-pressure side via the circumference of the bore 33 provided axially extending recesses, which are designated by 35 and which extend in the stroke movement direction (arrow 8) on both sides of the central plane 15, such that, analogously to the throttle bores 17 or the throttle ducts 20 or the throttle bores 28, regardless of the respective stroke position the locking member 32 is a throttling connection of the space 34 to the low pressure side.
  • the actuating movement transmitter 9 which is designed as a punch or as an actuating rod, with a diameter smaller than the blocking member 32, so that the incorporation of further channels or bores is unnecessary.
  • FIGS. 9 and 10 show an embodiment in which, in turn, a locking member 36 designed as a spherical segment is used, which in the region of its central plane 15 parallel to the seat contact zone 10 adjoins the wall of the bore 38, which as Guidance for the locking member 36 is used and compared to and the subsequent valve seat 6, the locking member 36 delimits the throttle space 37.
  • Outflow cross-sections opening toward the low-pressure side are assigned to this, which, as throttle cross-sections, are dependent on the stroke position of the blocking member 36 in the size of their cross-sectional area.
  • These variable throttle cross sections are formed by recesses 40 in the circumference of the throttle bore 39, which can be designed according to the desired throttle behavior.
  • FIGS. 9 and 10 an embodiment is illustrated in which, in the closed position of the locking member 36, the recesses 40 are at least largely deactivated via the locking member 36 and are only released with an increasing opening stroke.

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)
  • Lift Valve (AREA)
  • Electrically Operated Instructional Devices (AREA)
  • Check Valves (AREA)
  • Details Of Valves (AREA)

Abstract

L'invention concerne une configuration de soupapes de distribution, selon laquelle l'étranglement étagé au niveau de points d'étranglement (5) disposés dans l'alimentation côté haute pression (2) dans l'écoulement côté basse pression (17) est réalisé par un élément obturant (7, 32, 36) pour éviter l'érosion par cavitation.
PCT/EP2001/010685 2000-09-18 2001-09-15 Configuration de soupapes de distribution Ceased WO2002023036A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP01978375A EP1319127B1 (fr) 2000-09-18 2001-09-15 Configuration de soupapes de distribution
DE50109103T DE50109103D1 (de) 2000-09-18 2001-09-15 Ventilausbildung für steuerventile

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10046416A DE10046416C2 (de) 2000-09-18 2000-09-18 Ventilausbildung für Steuerventile
DE10046416.5 2000-09-18

Publications (1)

Publication Number Publication Date
WO2002023036A1 true WO2002023036A1 (fr) 2002-03-21

Family

ID=7656842

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2001/010685 Ceased WO2002023036A1 (fr) 2000-09-18 2001-09-15 Configuration de soupapes de distribution

Country Status (4)

Country Link
EP (1) EP1319127B1 (fr)
AT (1) ATE319003T1 (fr)
DE (2) DE10046416C2 (fr)
WO (1) WO2002023036A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007065746A1 (fr) * 2005-12-05 2007-06-14 Robert Bosch Gmbh Soupape d'injection de carburant
KR100822955B1 (ko) * 2004-08-06 2008-04-16 로베르트 보쉬 게엠베하 내연기관의 연소 챔버 내부로 연료를 분사하는 장치
WO2008092711A1 (fr) * 2007-01-30 2008-08-07 Robert Bosch Gmbh Siège de soupape sphérique à comportement d'érosion réduit
EP1916410A3 (fr) * 2006-10-20 2008-12-17 Robert Bosch Gmbh Soupape de distribution pour un injecteur et injecteur
EP2290272A3 (fr) * 2009-08-27 2013-08-21 Robert Bosch GmbH Siège de soupape sphérique à érosion par cavitation optimisée
WO2014102028A1 (fr) * 2012-12-27 2014-07-03 Robert Bosch Gmbh Soupape de réglage de pression pour un système d'injection de carburant
CN104169019B (zh) * 2012-03-15 2016-08-24 罗伯特·博世有限公司 制造阀的方法和冲压阀的衔铁销中球形顶的工具
EP3115592A3 (fr) * 2015-07-08 2017-01-25 Robert Bosch Gmbh Soupape de commande pour injecteur de carburant et injecteur de carburant

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3884252B2 (ja) * 2001-09-27 2007-02-21 三菱電機株式会社 高圧燃料供給装置用電磁弁
DE102005024045A1 (de) * 2005-05-25 2006-11-30 Robert Bosch Gmbh Injektor für ein Kraftstoffeinspritzsystem

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DE4238727A1 (de) * 1992-11-17 1994-05-19 Bosch Gmbh Robert Magnetventil
US5664545A (en) * 1994-12-02 1997-09-09 Nippondenso Co., Ltd. Fuel injection apparatus

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DE3930757A1 (de) * 1989-09-14 1991-03-28 Teves Gmbh Alfred Ventil, insbesondere fuer schlupfgeregelte hydraulische bremsanlagen
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DE4402752A1 (de) * 1994-01-31 1995-08-03 Danfoss As Heizkörperventil
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DE19624001A1 (de) * 1996-06-15 1997-12-18 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
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US6079641A (en) * 1998-10-13 2000-06-27 Caterpillar Inc. Fuel injector with rate shaping control through piezoelectric nozzle lift
DE19946833C2 (de) * 1999-09-30 2002-02-21 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten

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DE4238727A1 (de) * 1992-11-17 1994-05-19 Bosch Gmbh Robert Magnetventil
US5664545A (en) * 1994-12-02 1997-09-09 Nippondenso Co., Ltd. Fuel injection apparatus

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100822955B1 (ko) * 2004-08-06 2008-04-16 로베르트 보쉬 게엠베하 내연기관의 연소 챔버 내부로 연료를 분사하는 장치
WO2007065746A1 (fr) * 2005-12-05 2007-06-14 Robert Bosch Gmbh Soupape d'injection de carburant
EP1916410A3 (fr) * 2006-10-20 2008-12-17 Robert Bosch Gmbh Soupape de distribution pour un injecteur et injecteur
US8602321B2 (en) 2007-01-30 2013-12-10 Robert Bosch Gmbh Ball valve with reduced erosion behavior
CN101595297B (zh) * 2007-01-30 2013-10-30 罗伯特·博世有限公司 具有降低的腐蚀特性的球座阀
WO2008092711A1 (fr) * 2007-01-30 2008-08-07 Robert Bosch Gmbh Siège de soupape sphérique à comportement d'érosion réduit
EP2290272A3 (fr) * 2009-08-27 2013-08-21 Robert Bosch GmbH Siège de soupape sphérique à érosion par cavitation optimisée
CN104169019B (zh) * 2012-03-15 2016-08-24 罗伯特·博世有限公司 制造阀的方法和冲压阀的衔铁销中球形顶的工具
WO2014102028A1 (fr) * 2012-12-27 2014-07-03 Robert Bosch Gmbh Soupape de réglage de pression pour un système d'injection de carburant
CN105102807A (zh) * 2012-12-27 2015-11-25 罗伯特·博世有限公司 用于燃料喷射系统的压力调节阀
JP2016502031A (ja) * 2012-12-27 2016-01-21 ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング 燃料噴射システム用圧力制御弁
CN105102807B (zh) * 2012-12-27 2018-02-06 罗伯特·博世有限公司 用于燃料喷射系统的压力调节阀
US10041459B2 (en) 2012-12-27 2018-08-07 Robert Bosch Gmbh Pressure control valve for a fuel injection system
EP3115592A3 (fr) * 2015-07-08 2017-01-25 Robert Bosch Gmbh Soupape de commande pour injecteur de carburant et injecteur de carburant

Also Published As

Publication number Publication date
EP1319127A1 (fr) 2003-06-18
DE10046416C2 (de) 2002-11-07
DE50109103D1 (de) 2006-04-27
ATE319003T1 (de) 2006-03-15
EP1319127B1 (fr) 2006-03-01
DE10046416A1 (de) 2002-04-11

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