EP2647823A1 - Soupape de réglage de pression - Google Patents

Soupape de réglage de pression Download PDF

Info

Publication number
EP2647823A1
EP2647823A1 EP13154525.3A EP13154525A EP2647823A1 EP 2647823 A1 EP2647823 A1 EP 2647823A1 EP 13154525 A EP13154525 A EP 13154525A EP 2647823 A1 EP2647823 A1 EP 2647823A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
stage
pressure control
control 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.)
Withdrawn
Application number
EP13154525.3A
Other languages
German (de)
English (en)
Inventor
Helmar Gruhl
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.)
Robert Bosch GmbH
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 EP2647823A1 publication Critical patent/EP2647823A1/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F02M63/0049—Combined valve units, e.g. for controlling pumping chamber and injection valve
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • 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
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • 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
    • F02M63/0043—Two-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
    • 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
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0061—Single actuator acting on two or more valve bodies
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/025—Means for varying pressure in common rails by bleeding fuel pressure from the common rail
    • 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

  • DE 102 31 135 A1 refers to a pressure relief valve.
  • the pressure relief valve comprises a closing element, which is displaceable axially in the opening direction against the force acting in the closing direction of a closing spring in a bore.
  • the closing element rests against a valve seat when the pressure relief valve is closed and closes off an inlet.
  • a piston is integrated, which is connected via a connecting element with the closing element and within the inlet in the axial direction is displaceable.
  • pressure control valves are frequently used in fuel injection systems, for example in the common rail system.
  • the said pressure control valves have to work in a very large working range of very small flow rates at very high pressures to very high flow rates at low pressures and ensure high dynamics. This makes it increasingly difficult to find an optimal valve design for the entire operating range with increasing nominal pressures of the high-pressure reservoirs.
  • a pressure regulating valve which is used for regulating the pressure in a high-pressure accumulator, for example in a high-pressure accumulator for a fuel injection system (common rail).
  • the pressure control valve is designed in two stages and has a first valve stage, which is designed for a smaller flow within a first operating range of the pressure control valve and also a second valve stage, which is designed for a larger flow within a second operating range of the present invention proposed pressure control valve.
  • the first valve stage is a solenoid valve and the second valve stage is a hydraulic valve.
  • the first valve stage and the second valve stage are formed in a common valve insert which can be received on an end face of a tubular high-pressure accumulator of a fuel injection system for vehicles.
  • the common valve insert is, for example, a solid metal body provided with an external thread.
  • the pressure regulating valve proposed according to the invention operates in two stages, whereby it can cover different operating ranges, which are characterized by different operating parameters, through the two valve stages realized in these. While the first valve stage, which is a solenoid valve, is optimized for a first operating range that can be characterized by very small required valve flows, the second valve stage, which is designed as a hydraulic valve, is optimized for use at high flow rates. In this way, the operating range of the present invention proposed pressure control valve is divided with respect to the flow in two zones, for which the zones respectively associated valve stage can be optimized separately and independently.
  • both valve stages can be formed in one and the same externally threaded valve insert, in which a control chamber is formed, which can be filled via an inlet throttle passage extending through the common valve insert.
  • This control chamber in the common valve insert is pressure-relieved by a first closing element, which may be spherical, for example.
  • the belonging to the first valve stage, in particular spherical-shaped closing element is actuated by a rod-shaped valve member which is actuated by a magnetic coil, which executes the advantageously as a solenoid valve first Includes valve stage.
  • Said first valve stage realizes a direct control of the pressure in the pressure accumulator, in particular a high-pressure accumulation chamber of a fuel injection system for vehicles at low flow rates and a very high pressure level.
  • the first valve stage ie the solenoid valve of the present invention proposed pressure valve actuated at a corresponding pressure reduction in the control chamber
  • the second valve stage which is designed as a hydraulic valve, and is activated in a second operating range of the inventively proposed pressure control valve, if at a lower pressure level in the high-pressure accumulator larger flow rates must be realized.
  • the operation of the present invention proposed pressure control valve is such that the first valve stage is actuated by means of the electromechanical actuator, i. is designed as a solenoid valve, at the opening of which the pressure in the control chamber is reduced.
  • the control chamber which can be relieved of pressure by the first valve stage, is refilled with fuel via the aforementioned inlet throttle channel, which extends through the common valve insert.
  • the system pressure i. the pressure prevailing in the high pressure accumulator pressure are controlled directly, as long as the pressure in the control chamber does not fall below an opening pressure for an actuator for the second valve stage, which is designed as a hydraulic valve. In normal operation, it is desirable to set as little flow as possible so as not to unnecessarily waste energy.
  • a pressure booster which is formed substantially piston-shaped.
  • One end of the piston-shaped pressure booster projects into the pressure chamber which can be relieved of pressure via the first valve stage, while the opposite end of the piston-shaped pressure booster acts on a closing element of the second valve stage, which is likewise spherical.
  • the transition from the small flow rates required for pressure control to larger flow rates, ie the flow limit or a Flow transition range is dependent on the design of the inlet throttle channel for the control chamber and the pressurizable surface of the piston-shaped pressure booster, which projects into the control chamber and a closing spring and the seat diameter of the piston-shaped pressure booster actuated hydraulic valve.
  • the second valve stage i. the hydraulically operated valve is used in addition to the first valve stage.
  • the pressure in the control chamber by opening the first valve stage must be reduced so far that the pressure booster enters the control chamber and consequently releases the second closing element from the second valve seat of the second valve stage, so that larger flows can be achieved.
  • the inventively proposed solution of a two-stage pressure control valve allows optimization of each of the two valve stages for the respective work areas.
  • the two valve stages one of which is designed as a solenoid valve and the other as a hydraulic valve, can be optimized for each different operating ranges separately and independently.
  • High flexibility in terms of the design of the individual valve stages and the use of a servo mechanism ensures high scalability, ie the pressure control valve proposed according to the invention can also be adapted to other operating ranges by appropriate parameter selection, for example, with increasing nominal operating system pressure.
  • Another salient advantage of the present invention's proposed pressure control valve is the automatic actuation of the second valve, i. of the hydraulic valve after actuation of the first valve stage, i. the solenoid valve as soon as the latter reaches a certain pressure level in the control chamber.
  • the proposed solution according to the invention further enables a very simple scalability for changing requirements or operating range by respectively adjusting the hydraulically effective diameter of the servo mechanism and the inlet throttles.
  • the electromechanically actuated valve stage i. the first valve stage remains unchanged.
  • a larger usable operating range by optimizing the first valve stage to flows below 50 l / h at pressures up to> 3000 bar and the second valve stage at high flow rates up to 400 l / h and low pressures of 150 bar up to 500 bar.
  • a proportionality of the drive current with respect to the pressure shown in each case can be used to control the pressure (control principle open loop) with known flow.
  • a pressure regulating valve 10 proposed according to the invention is accommodated on a high-pressure accumulator 12.
  • the high-pressure accumulator 12 is, for example, a high-pressure accumulator (common rail), as used in fuel injection systems on internal combustion engines of passenger cars or trucks use.
  • the inventively proposed pressure control valve 10 is accommodated on an end face of the tubular high-pressure accumulator 12.
  • the high pressure accumulator 12 includes a cavity 14 in which the fuel under very high pressure is stored.
  • the pressure level in the cavity 14 of the high pressure accumulator 12 is maintained by a non-illustrated high-pressure pumping unit, in particular a high-pressure pump continuously.
  • the pressure level in the cavity 14 of the high pressure accumulator 12 is in the order of 1,800 bar to 2,000 bar or more.
  • the prevailing in the cavity 14 of the high-pressure accumulator 12 pressure level is also referred to as Railsystemdruck.
  • FIG. 1 further shows, in the material of the high-pressure accumulator 12, a valve core 16 is inserted.
  • the valve insert 16 has on its lateral surface, for example, a screw thread 18, with which the valve insert 16 is screwed into the solid material of the high-pressure accumulator 12.
  • the valve insert 16 receives a first valve stage 20, which may be formed in an advantageous manner as a solenoid valve, further comprises a second valve stage 42, which is designed as a hydraulic valve.
  • the first valve stage 20, which is a solenoid valve comprises a magnetic coil 22.
  • a first closing element 26 opening or closing a first valve seat 20 of the first valve stage 20 is actuated by means of an actuating element.
  • the ball-shaped, for example, first closing element 26 closes or opens an outlet throttle 28 in the first valve seat 24, so that a control chamber 30, which is accommodated in the common valve insert 16, is pressure-relieved.
  • the control chamber 30 in the common valve insert 16 is pressurized via an inlet throttle passage 44 extending through the solid material of the common valve insert 16.
  • the first valve stage is associated with a first return channel 32, which opens into a common return region 34.
  • a piston-shaped pressure booster 38 projects into it.
  • the piston-shaped pressure booster 38 can be acted upon by a closing spring 40 in the closing direction.
  • the closing spring 40 may be accommodated, for example, on a region of the piston-shaped pressure booster which is tapered in terms of its diameter and is supported on the underside of the first valve seat 24 in an advantageous manner.
  • the piston-shaped pressure intensifier 38 acts on a second closing element 48, which is in particular spherical and is part of the second valve stage 42, which is designed as a hydraulic valve.
  • the second closing element 48 is pressed by the piston-shaped pressure booster 38 in a second valve seat 42 having a valve funnel 70.
  • the second valve seat 52 comprises a tubular preform 50 and a throttle bore 56, through which the cavity 14 of the high pressure accumulator 12 is connected to the inlet throttle passage 44 for filling the control chamber 30. How out FIG. 1 Furthermore, the second valve seat 52 is centered on B fabricatkanten 54 on the plan side of the solid material of the high-pressure accumulator 12.
  • a valve chamber 66 is formed, from which a second return passage 46 extends to the common return 34 on the low pressure side of the pressure regulating valve 10.
  • a production-related guide gap 64 is formed along the pressure booster 38, which extends between the control chamber 30 and the second closing element 48, there is a production-related guide gap 64, via which a leakage flow 58 flows (cf. FIG. 2 ).
  • FIG. 2 is the inventively proposed pressure control valve according to FIG. 1 shown in the closed state.
  • a leakage current identified by reference numeral 58 sets. Due to the stored in the cavity 14 of the high-pressure accumulator 12 at high pressure fuel, a leakage, starting from the cavity 14 through the throttle bore 56 of the second valve seat 52 is the Inlet throttle channel 44 flows. About the inlet throttle passage 44 of the control chamber 30 is acted upon in the common valve core 16. Along the production-related adjusting guide gap 64 between the receiving bore for the pressure booster 38 in the common valve core 16, the leakage flow 58 flows into the valve chamber 66 and from there via the second return passage 46 to the common return 34 on the low pressure side of the present invention proposed pressure control valve 10. The size of the leakage current is negligible. The leakage flow 58 flows on the low pressure side back to the fuel tank of the vehicle.
  • FIG. 3 shows the inventively proposed two-stage pressure control valve in a state in which the realization of small flows, the first valve stage is activated.
  • the first valve stage 20 that is, the solenoid valve is activated.
  • the valve member 36 moves on, so that the first spherical-shaped closure member 26 releases the first valve seat 24 and the control chamber 30 is consequently relieved of pressure via the outlet throttle 28.
  • the first leakage flow 60 also flows via the throttle bore 36 of the second valve seat 52, the inlet throttle passage 44 in the common valve core 16 to the control chamber 30 and flows through the opened outlet throttle 28 and the first return passage 32 to the common return 34 on the low pressure side of the pressure control valve 10.
  • FIG. 3 shows that in the operating state shown there, the pressure in the control chamber 30 has not fallen so far that the piston-shaped pressure booster 38 aufirrifact, ie the second closing element 78, the second valve seat 52 is not yet released. Accordingly, in the in FIG. 3 shown state only the first leakage flow 60 a, which - as outlined above - flows through the control chamber 30 and the first return passage 32. At the same time, the leakage flow 58, starting from the cavity 14 of the high-pressure accumulator 12, likewise flows via the throttle bore 56, the inlet throttle passage 44 in the common valve insert 16, the control chamber 30, the first return passage 32, the common return 34 of the high-pressure accumulator 12.
  • FIG. 4 shows the inventively proposed two-stage pressure control valve in a state in which both the first valve stage and the second valve stage of the pressure regulating valve is activated.
  • the leakage flow 58 the leakage flow 60, which flows off when the first valve stage 20 is activated, and the second leakage flow 62, which flows out when the second valve stage 42 is open, to a common leakage flow, which is fed back to the fuel tank of the vehicle.
  • the first valve stage 20 As soon as the first valve stage 20 is activated again, ie the first valve stage 20 - designed as a solenoid valve - the first closing element 26 again in the first valve seat 24, there is a pressure build-up in the control chamber 30, since this continuously by the operating pressure level, which in the cavity 14th of the high-pressure accumulator 12 is maintained, is acted upon.
  • the pressure in the cavity 14 of the high pressure accumulator 12 is always on the throttle bore 56 and adjoining this inlet throttle passage 44 at the control chamber 30, so that in this closed outlet throttle 28, the pressure level increases.
  • the inventively proposed pressure control valve 10 can be achieved in a compact design that the first valve stage 20 and the second valve stage 42 can be integrated into one and the same valve insert 16.
  • the first valve stage 20 preferably designed as a solenoid valve, to be optimally designed with respect to the required flow rates to be realized at the first operating range of the pressure control valve, wherein the second valve stage 42 of the present invention proposed pressure control valve 10, designed as a hydraulic valve, in optimal Be adapted to the displayed larger flow rates and the corresponding pressure level.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Magnetically Actuated Valves (AREA)
EP13154525.3A 2012-04-02 2013-02-08 Soupape de réglage de pression Withdrawn EP2647823A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201210205329 DE102012205329A1 (de) 2012-04-02 2012-04-02 Druckregelventil

Publications (1)

Publication Number Publication Date
EP2647823A1 true EP2647823A1 (fr) 2013-10-09

Family

ID=47722058

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13154525.3A Withdrawn EP2647823A1 (fr) 2012-04-02 2013-02-08 Soupape de réglage de pression

Country Status (2)

Country Link
EP (1) EP2647823A1 (fr)
DE (1) DE102012205329A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2421418A1 (fr) * 1978-03-30 1979-10-26 Bosch Gmbh Robert Regulateur electromagnetique de pression
EP0226774A2 (fr) * 1985-12-14 1987-07-01 Robert Bosch Gmbh Limiteur de pression servocommandé
EP0964153A2 (fr) * 1998-06-08 1999-12-15 Wärtsilä NSD Oy Ab Dispositif d'une soupape de sécurité et de régulation dans un système d'alimentation en carburant
WO2003023266A1 (fr) * 2001-09-06 2003-03-20 Invensys Sensor Systems Vanne de regulation de pression presentant des fonctions de reglage
DE10231135A1 (de) 2002-07-10 2004-01-29 Robert Bosch Gmbh Druckentlastungsventil

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2421418A1 (fr) * 1978-03-30 1979-10-26 Bosch Gmbh Robert Regulateur electromagnetique de pression
EP0226774A2 (fr) * 1985-12-14 1987-07-01 Robert Bosch Gmbh Limiteur de pression servocommandé
EP0964153A2 (fr) * 1998-06-08 1999-12-15 Wärtsilä NSD Oy Ab Dispositif d'une soupape de sécurité et de régulation dans un système d'alimentation en carburant
WO2003023266A1 (fr) * 2001-09-06 2003-03-20 Invensys Sensor Systems Vanne de regulation de pression presentant des fonctions de reglage
DE10231135A1 (de) 2002-07-10 2004-01-29 Robert Bosch Gmbh Druckentlastungsventil

Also Published As

Publication number Publication date
DE102012205329A1 (de) 2013-10-02

Similar Documents

Publication Publication Date Title
EP1598551B1 (fr) Dispositif d'injection de carburant
EP2016278B1 (fr) Régulateur de pression avec fonction de circulation de secours et de purge
EP2536942B1 (fr) Soupape d'injection de carburant haute pression pour un moteur à combustion interne
DE102007000389B4 (de) Kraftstoffeinspritzsystem
EP1373718A1 (fr) Soupape de limitation de pression pour systemes d'injection de carburant
AT501914A4 (de) Vorrichtung zum einspritzen von kraftstoff in den brennraum einer brennkraftmaschine
EP1373706A1 (fr) Soupape d'injection
EP2659125B1 (fr) Dispositif de regulation de pression d'un système d'injection de carburant ayant une soupape arrange du côté pression de la pompe
DE102008001602B4 (de) Verfahren zum Ansteuern eines Steuerventils eines Kraftstoff-Injektors sowie Kraftstoff-Einspritzsystem
DE10334615A1 (de) Druckregelventil für Speicherkraftstoffeinspritzsystem
EP2733345A1 (fr) Soupape de régulation de pression pour un accumulateur haute pression d'un moteur à combustion
WO2006058604A1 (fr) Injecteur de carburant
EP2647823A1 (fr) Soupape de réglage de pression
EP2138709B1 (fr) Injecteur de carburant actionné directement
DE10334616A1 (de) Druckregelventil für Speicherkraftstoffeinspritzsystem
DE102007016625A1 (de) Ventil und Einspritzanlage für eine Brennkraftmaschine mit Ventil
DE102007001365A1 (de) Injektor mit Steuer- und Schaltkammer
DE10351881A1 (de) Injektor mit Strukturen zur Begrenzung verschleißbedingter Änderungen eines Öffnungsverlaufs
WO2009130063A1 (fr) Injecteur
DE19939449A1 (de) Verfahren zum Steuern von Flüssigkeiten
DE19939454A1 (de) Verfahren und Vorrichtung zum Steuern von Flüssigkeiten
DE102015008135A1 (de) Sicherheitsventil und Kraftstoffeinspritzsystem mit einem solchen
DE102019220172A1 (de) Kraftstoffinjektor für eine Brennkraftmaschine
EP1636487B1 (fr) Soupape de reglage de pression pour systeme d'injection de carburant a accumulateur
DE102012004471B4 (de) Injektor

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

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20140409

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

17Q First examination report despatched

Effective date: 20141113

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20150324