EP2888469B1 - Common rail system - Google Patents

Common rail system Download PDF

Info

Publication number
EP2888469B1
EP2888469B1 EP13750553.3A EP13750553A EP2888469B1 EP 2888469 B1 EP2888469 B1 EP 2888469B1 EP 13750553 A EP13750553 A EP 13750553A EP 2888469 B1 EP2888469 B1 EP 2888469B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure pump
ball
pressure
vno
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.)
Not-in-force
Application number
EP13750553.3A
Other languages
German (de)
French (fr)
Other versions
EP2888469A1 (en
Inventor
Florian Schulz
Gerd Strobel
Wolfgang Knöbel
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.)
Kendrion Villingen GmbH
Original Assignee
Kendrion Villingen 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 Kendrion Villingen GmbH filed Critical Kendrion Villingen GmbH
Publication of EP2888469A1 publication Critical patent/EP2888469A1/en
Application granted granted Critical
Publication of EP2888469B1 publication Critical patent/EP2888469B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F02M63/02—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
    • F02M63/0265—Pumps feeding 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F02M59/368—Pump inlet valves being closed when actuated
    • 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

Definitions

  • the invention relates to a common rail system for an internal combustion engine of a vehicle according to the preamble of patent claim 1.
  • Common rail systems as fuel injection systems which have a high-pressure pump for providing high-pressure fuel for a high-pressure accumulator (common rail) and a low-pressure pump as a prefeed pump, which promotes the fuel from a fuel tank via a delivery line to the high-pressure pump, wherein the controlled by the high-pressure pump the high-pressure accumulator amount of fuel through a flow control valve arranged in the feed line and the measured by the flow control valve amount of fuel is acted upon by the high-pressure pump with the appropriate high pressure.
  • a high-pressure pump for providing high-pressure fuel for a high-pressure accumulator (common rail) and a low-pressure pump as a prefeed pump, which promotes the fuel from a fuel tank via a delivery line to the high-pressure pump, wherein the controlled by the high-pressure pump the high-pressure accumulator amount of fuel through a flow control valve arranged in the feed line and the measured by the flow control valve amount of fuel is acted upon by the high-pressure pump with the appropriate high pressure.
  • Such a common-rail system CRS is schematically shown in FIG FIG. 4 shown. Thereafter, this common rail system CRS consists of a high-pressure accumulator R, from which injectors Inj an internal combustion engine (not shown), for example. A diesel engine are supplied with fuel.
  • the high-pressure accumulator R is connected via a high-pressure line L1 to a high-pressure pump HP, which is driven by an electric motor M1.
  • Fuel is conveyed from a fuel tank KB by means of a low-pressure pump NP driven by an electric motor M2 via a delivery line L2 for a flow control valve VNC, which is designed as an electromagnetic switching valve of the type slide valve and closed in the de-energized state ("normally closed").
  • this slide valve VNC is connected to the high-pressure pump HP.
  • a high-pressure control valve HPV connects the high-pressure accumulator R via a pressure relief line L3 to the output side of the low-pressure pump NP.
  • This designed as an electromagnetic switching valve high pressure control valve HPV is used for rapid pressure reduction of the high-pressure accumulator R.
  • This high-pressure control valve HPV is necessary because disadvantageously, the slide valve VNC has no 100% leakage. This leakage has its cause in the required for the displacement of the slide element game between this slide element and the valve body.
  • fuel enters and is compressed in the high-pressure pump HP, with the result that the pressure in the high-pressure accumulator R increases when the injectors Inj do not deliver fuel to the internal combustion engine, ie no consumer is connected to the high-pressure accumulator R.
  • the HPV high-pressure control valve the pressure is released in such operating states.
  • Both the flow control valve VNC, the high and low pressure pumps HP and NP, the high pressure control valve HPV and the injectors Inj are controlled by a controller (not shown).
  • One of the FIG. 4 appropriate common rail system is, for example, from the DE 60 2005 003 427 T2 known, in which a slide valve is used as a flow control valve, which is closed in the de-energized state.
  • a slide valve is used as a flow control valve, which is closed in the de-energized state.
  • an improved construction of a slide valve is proposed. This improved construction relates to the design of the slider element.
  • the invention has the object of developing a common rail system of the type mentioned in such a way that the disadvantages known from the prior art are avoided, in particular a simple structure with few components is made possible.
  • This common rail system for an internal combustion engine of a vehicle comprises a high-pressure pump which supplies high-pressure fuel to a high-pressure accumulator, from which the fuel is supplied to at least one injection valve of the internal combustion engine, and a low-pressure pump for conveying fuel from a fuel tank via a delivery line to the high-pressure pump and finally a flow control valve as an electromagnetic switching valve, which is arranged in the delivery line for controlling the amount of fuel supplied from the high-pressure pump to the high-pressure accumulator.
  • the flow control valve is formed as a ball seat valve with an inlet port connected to the low pressure pump and an outlet port connected to the high pressure pump, which is open in the de-energized state.
  • Such ball seat valves as electromagnetic switching valves, which are open in the de-energized state, are, for example, from the DE 40 41 377 A1 or the EP 1 241 338 A1 known.
  • DE 102 51 014 A1 discloses an electromagnetic control valve for fuel injection liners of internal combustion engines, which is designed as a slide valve.
  • the valve is controlled by an adjustable valve piston with side openings that interact with the outlet openings of the valve.
  • the sealing of the valve via a sealing ball, which can be pressed by a plunger on the valve piston against a sealing ball seat.
  • the common rail system according to the invention is characterized in that the ball seat valve is formed with a valve seat and a valve ball, such that in the energized state of the ball seat valve by pressurization by the low pressure pump, the valve ball rests against the valve seat under closure of the inlet opening. In addition, pressed in the de-energized state, a valve lifter to the valve ball and lifts it from the valve seat.
  • valve ball Since the valve ball is located on the pressure side and is pressed against the valve seat exclusively by the fluid pressure of the low-pressure pump in the energized state of the ball seat valve, eliminates spring elements on the pressure side and therefore no spring tolerances must be respected or adjusted. It is achieved a high tightness and thus ensures complete freedom from leaks.
  • the ball seat valve is formed with a spring-biased valve tappet, such that for opening the inlet opening of the valve tappet in the de-energized state of the ball seat valve in a valve ball stands by the valve seat lifting operative connection.
  • the ball seat valve has a relative to a pole core displaceable armature, which receives the valve stem centrally.
  • the armature which receives the valve stem, working against a compression spring, which is located on the non-pressurized side.
  • the pole core has a central bore for receiving a compression spring, at one end the compression spring is supported against the armature and the other end against a bore on the armature facing away from the pole core occlusive closure part of the pole core is supported.
  • the spring force of the compression spring acting on the valve tappet can be adjusted depending on the penetration depth of the closure part into the pole core.
  • the armature is formed with a decentralized bore which connects the bore of the pole core with a valve ball-side valve chamber.
  • the common-rail system CRS after FIG. 1 consists of a high-pressure accumulator R with high-pressure fuel, which is supplied by means of injectors Inj an internal combustion engine (not shown).
  • the high-pressure accumulator R is connected via a high-pressure line L1 to a high-pressure pump HP, which is driven by an electric motor M1.
  • a driven by an electric motor M2 low pressure pump NP delivers fuel from a fuel tank KB, which is supplied via a delivery line L2 of the high-pressure pump HP, wherein in this delivery line L2 a ball seat valve VNO is arranged as a flow control valve, which is open as an electromagnetic switching valve in the de-energized state.
  • the high-pressure accumulator R is connected via a mechanical overpressure valve VÜ and a pressure relief line L3 to the delivery line L2 between the low-pressure pump NP and the ball seat valve VNO.
  • This pressure relief valve VÜ is required only for safety reasons in order to be able to discharge an overpressure in the high-pressure accumulator R in the event of a "worst case".
  • this common rail system comprises CRS according to FIG. 1 also a control unit (not shown), which controls the low pressure pump NP, the high pressure pump HP, the ball seat valve VNO and the injectors Inj via control lines (not shown) in response to sensor signals and operating condition of the internal combustion engine.
  • This common rail system CRS is characterized by the use of a ball seat valve VNO as a flow control valve, which is open in the de-energized state and controls the high-pressure pump HP supplied fuel flow.
  • the ball seat valve VNO In the idle state, ie in the de-energized state, the ball seat valve VNO is open, so that in case of failure or failure of this ball seat valve VNO funded by the low-pressure pump NP fuel can be delivered to the high-pressure pump, so that at least malfunctions are excluded with respect to the internal combustion engine.
  • Such a ball seat valve VNO shows FIG. 2 which accommodates in a valve housing 20 a centrally mounted pole core 8, which is partially enclosed by a toroidal coil, consisting of a arranged on a bobbin 15 coil winding 16.
  • a valve body 1 Connected to the pole core 8 via a connecting ring 13 is a valve body 1 with a central bore 1a, which forms a central receiving space 1b for an armature 5 on the pole core side.
  • the armature 5 carries centrally a valve stem 6, the pole core side, the end face of the armature 5 projects beyond and projects into a central bore 8 a of the pole core 8.
  • This bore 8a is closed at the end by a closure 11, wherein a disposed in the bore 8a of the pole core 8 compression spring 9 is supported on the one hand against this closure 11 and on the other hand against the adjacent end face of the armature 5 via a spring plate 7 present there.
  • the bore 8a of the pole core 8 goes on the anchor side in a stepped cylindrical bore 8b, whose diameter corresponds to the diameter of the armature 5, so that the armature 5 in energizing the coil winding 16 in this bore 8b of Polkerns 8 is pulled against the spring force of the prestressed compression spring 9 to the pole face of the pole core 8.
  • the surrounding this cylindrical bore ring 8c is formed as a control cone with an outer cone, which serves to adjust the magnetic force-stroke curve when the armature 5 from its rest position corresponding to the in FIG. 2 shown position is drawn by energizing the coil winding 16 in the direction of the pole face of the pole core 8.
  • the armature 5 is received by a sleeve 10 which extends over the region of the bore 1 b and the connecting ring 13.
  • the bore 1a of the valve body 1 extends into a valve chamber 1c and ends at an inlet port 1d, which is connected to the low-pressure pump NP.
  • valve chamber 1c takes a ball cage 3 for receiving a valve ball 4 and an adjoining valve seat 2 for the valve ball 4.
  • At least two diametrically opposite radial holes 1e are provided as an outlet opening 1e, which are guided on the high-pressure pump HP.
  • valve stem 6 starting from the pole core facing away from the end face of the armature 5 to such a length that in the in FIG. 2 illustrated rest position of the ball seat valve VNO, so in the de-energized state, the compression spring 9 the armature. 5 pushes completely into the bore 1b of the valve body 1 in the direction of the inlet opening 1d, while the valve stem 6 with a needle tip 6a lifts the valve ball 4 from the valve seat 2, so that the passage between the inlet port 1d and the outlet port 1e is released.
  • the armature 5 has a non-centered, parallel to the longitudinal axis extending bore 5a, which connects the two end faces.
  • the valve chamber 1c and the outlet openings 1e are connected to the bore 8a of the pole core 8, so that a pressure equalization between these spaces can take place during operation of the ball seat valve VNO, or builds up no pressure difference between these spaces.
  • a flange 12 is provided on the high pressure pump HP.
  • O-rings 14 and 21 of the valve body 1 are provided as sealing rings.
  • the bobbin 16 is encapsulated to form a connector 18 receiving plastic body 17, wherein a sealing disc 19 makes the seal against the environment.
  • FIG. 3 A schematic characteristic of the ball seat valve VNO according to Figure 2 shows FIG. 3 , which indicates the volume flow Q as a function of the current intensity I.
  • a high flow or volume flow of fluid, ie fuel is achieved, which decreases with increasing current, so with increasing current up to the value zero, ie until the ball seat valve VNO is closed. Because of the hysteresis properties of the electromagnet, the characteristic doubles in the middle range.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Magnetically Actuated Valves (AREA)

Description

Die Erfindung betrifft ein Common-Rail-System für eine Brennkraftmaschine eines Fahrzeugs gemäß Oberbegriff des Patentanspruchs 1.The invention relates to a common rail system for an internal combustion engine of a vehicle according to the preamble of patent claim 1.

Common-Rail-Systeme als Kraftstoffeinspritzsysteme sind bekannt, die eine Hochdruckpumpe zum Bereitstellen von unter Hochdruck stehendem Kraftstoff für einen Hochdruckspeicher (Common Rail) und eine Niederdruckpumpe als Vorförderpumpe aufweisen, welche den Kraftstoff von einem Kraftstofftank über eine Förderleitung an die Hochdruckpumpe fördert, wobei die von der Hochdruckpumpe dem Hochdruckspeicher zugeführte Kraftstoffmenge durch ein in der Förderleitung angeordnetes Durchflussregelventil gesteuert und die von dem Durchflussregelventil bemessene Kraftstoffmenge von der Hochdruckpumpe mit dem entsprechenden Hochdruck beaufschlagt wird.Common rail systems as fuel injection systems are known which have a high-pressure pump for providing high-pressure fuel for a high-pressure accumulator (common rail) and a low-pressure pump as a prefeed pump, which promotes the fuel from a fuel tank via a delivery line to the high-pressure pump, wherein the controlled by the high-pressure pump the high-pressure accumulator amount of fuel through a flow control valve arranged in the feed line and the measured by the flow control valve amount of fuel is acted upon by the high-pressure pump with the appropriate high pressure.

Ein solches Common-Rail-System CRS ist schematisch in Figur 4 dargestellt. Hiernach besteht dieses Common-Rail-System CRS aus einem Hochdruckspeicher R, aus welchem Einspritzventile Inj einer Brennkraftmaschine (nicht dargestellt), bspw. eines Dieselmotors mit Kraftstoff versorgt werden.Such a common-rail system CRS is schematically shown in FIG FIG. 4 shown. Thereafter, this common rail system CRS consists of a high-pressure accumulator R, from which injectors Inj an internal combustion engine (not shown), for example. A diesel engine are supplied with fuel.

Der Hochdruckspeicher R ist über eine Hochdruckleitung L1 mit einer Hochdruckpumpe HP verbunden, welche von einem Elektromotor M1 angetrieben wird. Aus einem Kraftstoffbehälter KB wird mittels einer von einem Elektromotor M2 angetriebenen Niederdruckpumpe NP über eine Förderleitung L2 Kraftstoff für ein Durchflussregelventil VNC gefördert, welches als elektromagnetisches Schaltventil in der Bauart Schieberventil ausgebildet und im unbestromten Zustand geschlossen ist ("Normally Closed"). Ausgangsseitig ist dieses Schieberventil VNC mit der Hochdruckpumpe HP verbunden.The high-pressure accumulator R is connected via a high-pressure line L1 to a high-pressure pump HP, which is driven by an electric motor M1. Fuel is conveyed from a fuel tank KB by means of a low-pressure pump NP driven by an electric motor M2 via a delivery line L2 for a flow control valve VNC, which is designed as an electromagnetic switching valve of the type slide valve and closed in the de-energized state ("normally closed"). On the output side, this slide valve VNC is connected to the high-pressure pump HP.

Schließlich verbindet ein Hochdruckregelventil HPV den Hochdruckspeicher R über eine Druckablassleitung L3 mit der Ausgangsseite der Niederdruckpumpe NP. Dieses als elektromagnetisches Schaltventil ausgebildete Hochdruckregelventil HPV dient zur schnellen Druckverminderung des Hochdruckspeichers R.Finally, a high-pressure control valve HPV connects the high-pressure accumulator R via a pressure relief line L3 to the output side of the low-pressure pump NP. This designed as an electromagnetic switching valve high pressure control valve HPV is used for rapid pressure reduction of the high-pressure accumulator R.

Dieses Hochdruckregelventil HPV ist deshalb erforderlich, da in nachteiliger Weise das Schieberventil VNC keine 100%ige Leckagefreiheit aufweist. Diese Leckage hat ihre Ursache in dem für die Verschiebbarkeit des Schieberelementes erforderlichen Spiel zwischen diesem Schieberelement und dem Ventilkörper. Das führt dazu, dass im Schiebebetrieb Kraftstoff in die Hochdruckpumpe HP gelangt und dort verdichtet wird, mit der Folge dass im Hochdruckspeicher R der Druck ansteigt, wenn die Injektoren Inj keinen Kraftstoff an die Brennkraftmaschine liefern, also kein Verbraucher mit dem Hochdruckspeicher R verbunden ist. Mit dem Hochdruckregelventil HPV wird in solchen Betriebszuständen der Druck abgelassen.This high-pressure control valve HPV is necessary because disadvantageously, the slide valve VNC has no 100% leakage. This leakage has its cause in the required for the displacement of the slide element game between this slide element and the valve body. As a result, in the coasting mode, fuel enters and is compressed in the high-pressure pump HP, with the result that the pressure in the high-pressure accumulator R increases when the injectors Inj do not deliver fuel to the internal combustion engine, ie no consumer is connected to the high-pressure accumulator R. With the HPV high-pressure control valve, the pressure is released in such operating states.

Sowohl das Durchflussregelventil VNC, die Hoch- und Niederdruckpumpe HP bzw. NP, das Hochdruckregelventil HPV als auch die Einspritzventile Inj werden von einem Steuergerät (nicht dargestellt) gesteuert bzw. geregelt.Both the flow control valve VNC, the high and low pressure pumps HP and NP, the high pressure control valve HPV and the injectors Inj are controlled by a controller (not shown).

Ein der Figur 4 entsprechendes Common-Rail-System ist bspw. aus der DE 60 2005 003 427 T2 bekannt, bei dem als Durchflussregelventil ein Schieberventil verwendet wird, welches im unbestromten Zustand geschlossen ist. Um den bei Verwendung von üblichen Schieberventilen neben der mangelnden Leckagefreiheit auftretenden Nachteilen, nämlich mangelnde Zentrierung des Schieberelementes im Ventilraum und die dadurch bedingte mangelnde Gleitfähigkeit, welche zu einer höheren Abnutzung mit hohem Abrieb führt, entgegenzuwirken, wird eine verbesserte Konstruktion eines Schieberventils vorgeschlagen. Diese verbesserte Konstruktion betrifft die Ausgestaltung des Schieberelementes.One of the FIG. 4 appropriate common rail system is, for example, from the DE 60 2005 003 427 T2 known, in which a slide valve is used as a flow control valve, which is closed in the de-energized state. To the occurring when using conventional slide valves in addition to the lack of freedom from leaks, namely lack of centering of the Slider element in the valve chamber and the consequent lack of lubricity, which leads to a higher wear with high abrasion counteract, an improved construction of a slide valve is proposed. This improved construction relates to the design of the slider element.

Der Nachteil der mangelnden Leckagefreiheit bei der Verwendung eines Schieberventils in einem Common-Rail-System wird gemäß der DE 198 46 157 A1 dadurch beseitigt, dass ausgangsseitig des Durchflussregelventils sowohl eine auf den Kraftstoffbehälter zurückgeführte Rücklaufleitung vorgesehen ist als auch ein Differenzdruckventil angeschlossen ist, welches mit den Saugventilen einer Hochdruckpumpe verbunden ist. Damit wird erreicht, dass die Hochdruckpumpe im Betriebszustand "Null-Förderung" keinen Kraftstoff fördert, da das Differenzdruckventil vom Leckstrom des Durchflussregelventils nicht überwunden werden kann.The disadvantage of the lack of freedom from leakage when using a slide valve in a common rail system is according to the DE 198 46 157 A1 eliminated in that the output side of the flow control valve is provided both a returned to the fuel tank return line and a differential pressure valve is connected, which is connected to the suction valves of a high-pressure pump. This ensures that the high-pressure pump in the operating state "zero delivery" does not deliver fuel, since the differential pressure valve can not be overcome by the leakage flow of the flow control valve.

Ein weiterer Nachteil der Verwendung von "Normally Closed"-Schieberventilen in Common-Rail-Systemen liegt darin, dass im Falle eines Defektes oder des Ausfalls eines solchen Schieberventils kein Kraftstoff mehr in das Rail, also in den Hochdruckspeicher gefördert werden kann und damit ein weiterer Betrieb der Brennkraftmaschine nicht mehr möglich ist.Another disadvantage of the use of "normally closed" slide valves in common rail systems is that in the event of a defect or failure of such a slide valve no more fuel in the rail, so in the high-pressure accumulator can be promoted and thus another Operation of the internal combustion engine is no longer possible.

Der Erfindung liegt die Aufgabe zugrunde Common-Rail-System der eingangs genannten Art derart weiterzubilden, dass die aus dem Stand der Technik bekannten Nachteile vermieden werden, insbesondere ein einfacher Aufbau mit wenigen Bauteilen ermöglicht wird.The invention has the object of developing a common rail system of the type mentioned in such a way that the disadvantages known from the prior art are avoided, in particular a simple structure with few components is made possible.

Diese Aufgabe wird gelöst durch ein Common-Rail-System mit den Merkmalen des Patentanspruchs 1.This object is achieved by a common rail system having the features of patent claim 1.

Dieses Common-Rail-System für eine Brennkraftmaschine eines Fahrzeug umfasst eine Hochdruckpumpe, welche mit Hochdruck beaufschlagten Kraftstoff an einen Hochdruckspeicher liefert, von welchem der Kraftstoff mindestens einem Einspritzventil der Brennkraftmaschine zugeführt wird, ferner eine Niederdruckpumpe zur Förderung von Kraftstoff aus einem Kraftstoffbehälter über eine Förderleitung an die Hochdruckpumpe und schließlich ein Durchflussregelventil als elektromagnetisches Schaltventil, welches in der Förderleitung zur Steuerung der von der Hochdruckpumpe dem Hochdruckspeicher zugeführten Kraftstoffmenge angeordnet ist. Außerdem ist das Durchflussregelventil als Kugelsitzventil mit einer mit der Niederdruckpumpe verbundenen Einlassöffnung und einer mit der Hochdruckpumpe verbundenen Auslassöffnung ausgebildet, welches im unbestromten Zustand geöffnet ist.This common rail system for an internal combustion engine of a vehicle comprises a high-pressure pump which supplies high-pressure fuel to a high-pressure accumulator, from which the fuel is supplied to at least one injection valve of the internal combustion engine, and a low-pressure pump for conveying fuel from a fuel tank via a delivery line to the high-pressure pump and finally a flow control valve as an electromagnetic switching valve, which is arranged in the delivery line for controlling the amount of fuel supplied from the high-pressure pump to the high-pressure accumulator. In addition, the flow control valve is formed as a ball seat valve with an inlet port connected to the low pressure pump and an outlet port connected to the high pressure pump, which is open in the de-energized state.

Ein solches erfindungsgemäßes Common-Rail-System mit einem Kugelsitzventil, welches im unbestromten Zustand offen ist ("Normally Open"), führt im Betrieb der Brennkraftmaschine zumindest zu keiner Fehlfunktion des Brennkraftmaschine, wenn dieses Kugelsitzventil defekt wird oder ausfällt.Such a common rail system according to the invention with a ball seat valve, which is open in the de-energized state ("normally open"), during operation of the internal combustion engine leads at least to no malfunction of the internal combustion engine when this ball seat valve becomes defective or fails.

Ein weiterer Vorteil besteht darin, dass ein solches Kugelsitzventil als elektromagnetisches Schaltventil keine Leckage aufweist, so dass im Betriebszustand "Null-Förderung" kein Kraftstoff über die Hochdruckpumpe in den Hochdruckspeicher gefördert wird. Dies führt dazu, dass auf das bei dem bekannten Common-Rail-System gemäß Figur 4 erforderliche Hochdruckregelventil HPV entfallen kann. Aus sicherheitstechnischen Gründen ist es ausreichend, anstelle dieses Hochdruckregelventils HPV nur ein mechanisches Überdruckventil vorzusehen. Dieses mechanische Überdruckventil öffnet nur im "worst case", bspw. wenn das Kugelsitzventil klemmen würde.Another advantage is that such a ball seat valve as an electromagnetic switching valve has no leakage, so that in the operating state "zero delivery" no fuel is conveyed through the high-pressure pump in the high-pressure accumulator. This leads to that in the known common rail system according to FIG. 4 required high-pressure control valve HPV can be omitted. For safety reasons, it is sufficient instead of this high pressure control valve HPV only provide a mechanical pressure relief valve. This mechanical pressure relief valve opens only in the "worst case", for example, if the ball seat valve would jam.

Damit reduziert sich gegenüber bekannten Common-Rail-Systemen gemäß Stand der Technik die Anzahl der erforderlichen Bauteile, zumindest aber wird mit dem erfindungsgemäßen Common-Rail-System ein einfacherer Aufbau realisiert, da ein aufwendiges Hochdruckregelventil entfällt.This reduces the number of required components compared to known common rail systems according to the prior art, but at least a simpler design is realized with the common rail system according to the invention, since a complex high-pressure control valve is eliminated.

Solche Kugelsitzventile als elektromagnetische Schaltventile, die im stromlosen Zustand offen sind, sind bspw. aus der DE 40 41 377 A1 oder der EP 1 241 338 A1 bekannt.Such ball seat valves as electromagnetic switching valves, which are open in the de-energized state, are, for example, from the DE 40 41 377 A1 or the EP 1 241 338 A1 known.

DE 102 51 014 A1 offenbart ein elektromagnetisches Regelventil für Kraftstoffeinspritzeinlagen von Brennkraftmaschinen, das als Schieberventil ausgebildet ist. Die Ventilregelung erfolgt durch einen einstellbaren Ventilkolben mit Seitenöffnungen, die mit den Austrittöffnungen des Ventils zusammenwirken. Die Abdichtung des Ventils erfolgt über eine Dichtkugel, die durch einen Stößel über den Ventilkolben gegen einen Dichtkugelsitz gepresst werden kann. DE 102 51 014 A1 discloses an electromagnetic control valve for fuel injection liners of internal combustion engines, which is designed as a slide valve. The valve is controlled by an adjustable valve piston with side openings that interact with the outlet openings of the valve. The sealing of the valve via a sealing ball, which can be pressed by a plunger on the valve piston against a sealing ball seat.

Das erfindungsgemäße Common-Rail-System zeichnet sich dadurch aus, dass das Kugelsitzventil mit einem Ventilsitz und einer Ventilkugel ausgebildet ist, derart, dass im bestromten Zustand des Kugelsitzventils durch Druckbeaufschlagung seitens der Niederdruckpumpe die Ventilkugel am Ventilsitz unter Verschluss der Einlassöffnung anliegt. Außerdem drückt im unbestromten Zustand ein Ventilstößel an die Ventilkugel und hebt diese vom Ventilsitz ab.The common rail system according to the invention is characterized in that the ball seat valve is formed with a valve seat and a valve ball, such that in the energized state of the ball seat valve by pressurization by the low pressure pump, the valve ball rests against the valve seat under closure of the inlet opening. In addition, pressed in the de-energized state, a valve lifter to the valve ball and lifts it from the valve seat.

Da die Ventilkugel auf der Druckseite liegt und ausschließlich vom Fluiddruck der Niederdruckpumpe im bestromten Zustand des Kugelsitzventils gegen den Ventilsitz gedrückt wird, entfallen Federelemente auf der Druckseite und es müssen deshalb keine Federtoleranzen beachtet bzw. eingestellt werden. Es wird eine hohe Dichtheit erreicht und damit auch eine vollständige Leckagefreiheit sichergestellt.Since the valve ball is located on the pressure side and is pressed against the valve seat exclusively by the fluid pressure of the low-pressure pump in the energized state of the ball seat valve, eliminates spring elements on the pressure side and therefore no spring tolerances must be respected or adjusted. It is achieved a high tightness and thus ensures complete freedom from leaks.

In einer Ausgestaltung der Erfindung ist das Kugelsitzventil mit einem federvorgespannten Ventilstößel ausgebildet, derart dass zum Öffnen der Einlassöffnung der Ventilstößel im unbestromten Zustand des Kugelsitzventils in einer die Ventilkugel von dessen Ventilsitz abhebenden Wirkverbindung steht. Erfindungsgemäß weist das Kugelsitzventil einen gegenüber einem Polkern verschiebbaren Anker auf, der den Ventilstößel zentrisch aufnimmt. Damit arbeitet der Anker, der den Ventilstößel aufnimmt, gegen eine Druckfeder, die sich auf der drucklosen Seite befindet.In one embodiment of the invention, the ball seat valve is formed with a spring-biased valve tappet, such that for opening the inlet opening of the valve tappet in the de-energized state of the ball seat valve in a valve ball stands by the valve seat lifting operative connection. According to the invention, the ball seat valve has a relative to a pole core displaceable armature, which receives the valve stem centrally. Thus, the armature, which receives the valve stem, working against a compression spring, which is located on the non-pressurized side.

Dies führt zu einer mechanischen Entkopplung von Anker bzw. Ventilstößel und Ventilkugel, wodurch die Belastungen des Ankers und des Ventilstößels unter Vibrationen reduziert werden.This leads to a mechanical decoupling of armature or valve tappet and valve ball, whereby the loads of the armature and of the valve tappet are reduced under vibrations.

Gemäß einer weiteren Ausgestaltung der Erfindung weist der Polkern eine zentrische Bohrung zur Aufnahme einer Druckfeder auf, wobei einenends die Druckfeder sich gegen den Anker abstützt und andernends gegen ein die Bohrung an der ankerabgewandten Seite des Polkerns verschließendes Verschlussteil des Polkerns abstützt.According to a further embodiment of the invention, the pole core has a central bore for receiving a compression spring, at one end the compression spring is supported against the armature and the other end against a bore on the armature facing away from the pole core occlusive closure part of the pole core is supported.

Mit einem solchen Verschlussteil, das entweder mittels einer Presspassung oder einer Schraubverbindung in die Bohrung des Polkerns eingeführt wird, lässt sich in Abhängigkeit der Eindringtiefe des Verschlussteils in den Polkern die Federkraft der auf den Ventilstößel wirkenden Druckfeder einstellen.With such a closure part, which is introduced into the bore of the pole core either by means of a press fit or a screw connection, the spring force of the compression spring acting on the valve tappet can be adjusted depending on the penetration depth of the closure part into the pole core.

Schließlich ist es gemäß einer letzten Ausgestaltung der Erfindung vorgesehen, dass der Anker mit einer dezentralen Bohrung ausgebildet ist, welche die Bohrung des Polkerns mit einem ventilkugelseitigen Ventilraum verbindet. Damit wird ein Druckausgleich der beiden Räume über diese dezentrale Bohrung des Ankers erreicht und dadurch Druckpulsationen verhindert und eine gleichmäßige Füllung der Arbeitsräume der Hochdruckpumpe ermöglicht.Finally, it is provided according to a last embodiment of the invention that the armature is formed with a decentralized bore which connects the bore of the pole core with a valve ball-side valve chamber. Thus, a pressure equalization of the two rooms is achieved via this decentralized bore of the armature and thereby prevents pressure pulsations and allows uniform filling of the working spaces of the high-pressure pump.

Die Erfindung wird nachfolgend anhand eines Ausführungsbeispiels unter Bezugnahme auf die beigefügten Figuren ausführlich beschrieben. Es zeigen:

Figur 1
eine schematische Darstellung eines Common-Rail-Systems mit einem Kugelsitzventil als Durchflussregelventil gemäß einer Ausführungsform der Erfindung,
Figur 2
einen axialen Längsschnitt des Kugelsitzventils des Common-Rail-Systems nach Figur 1,
Figur 3
eine Kennlinie des Kugelsitzventils nach Figur 2, und
Figur 4
eine schematische Darstellung eines Common-Rail-Systems mit einem Schieberventil als Durchflussregelventil gemäß Stand der Technik.
The invention will now be described in detail by means of an embodiment with reference to the accompanying figures. Show it:
FIG. 1
a schematic representation of a common rail system with a ball seat valve as a flow control valve according to an embodiment of the invention,
FIG. 2
an axial longitudinal section of the ball seat valve of the common rail system according to FIG. 1 .
FIG. 3
a characteristic of the ball seat valve after FIG. 2 , and
FIG. 4
a schematic representation of a common rail system with a slide valve as a flow control valve according to the prior art.

Das Common-Rail-System CRS nach Figur 1 besteht aus einem Hochdruckspeicher R mit Hochdruck beaufschlagten Kraftstoff, welcher mittels Injektoren Inj einer Brennkraftmaschine (nicht dargestellt) zugeführt wird.The common-rail system CRS after FIG. 1 consists of a high-pressure accumulator R with high-pressure fuel, which is supplied by means of injectors Inj an internal combustion engine (not shown).

Der Hochdruckspeicher R ist über eine Hochdruckleitung L1 mit einer Hochdruckpumpe HP verbunden, die von einem Elektromotor M1 angetrieben wird.The high-pressure accumulator R is connected via a high-pressure line L1 to a high-pressure pump HP, which is driven by an electric motor M1.

Eine von einem Elektromotor M2 angetriebene Niederdruckpumpe NP fördert Kraftstoff aus einem Kraftstoffbehälter KB, der über eine Förderleitung L2 der Hochdruckpumpe HP zugeführt wird, wobei in dieser Förderleitung L2 ein Kugelsitzventil VNO als Durchflussregelventil angeordnet ist, welches als elektromagnetisches Schaltventil im unbestromten Zustand offen ist.A driven by an electric motor M2 low pressure pump NP delivers fuel from a fuel tank KB, which is supplied via a delivery line L2 of the high-pressure pump HP, wherein in this delivery line L2 a ball seat valve VNO is arranged as a flow control valve, which is open as an electromagnetic switching valve in the de-energized state.

Mit diesem Kugelsitzventil VNO wird die Kraftstoffmenge gesteuert, die die Hochdruckpumpe HP dem Hochdruckspeicher R zuführt.With this ball seat valve VNO, the amount of fuel that supplies the high pressure pump HP to the high pressure accumulator R is controlled.

Schließlich ist der Hochdruckspeicher R über ein mechanisches Überdruckventil VÜ und einer Druckablassleitung L3 mit der Förderleitung L2 zwischen der Niederdruckpumpe NP und dem Kugelsitzventil VNO verbunden. Dieses Überdruckventil VÜ ist lediglich aus sicherheitstechnischen Gründen erforderlich, um im Falle eines "worst case" einen Überdruck im Hochdruckspeicher R ablassen zu können.Finally, the high-pressure accumulator R is connected via a mechanical overpressure valve VÜ and a pressure relief line L3 to the delivery line L2 between the low-pressure pump NP and the ball seat valve VNO. This pressure relief valve VÜ is required only for safety reasons in order to be able to discharge an overpressure in the high-pressure accumulator R in the event of a "worst case".

Schließlich umfasst dieses Common-Rail-System CRS gemäß Figur 1 auch ein Steuergerät (nicht dargestellt), welches die Niederdruckpumpe NP, die Hochdruckpumpe HP, das Kugelsitzventil VNO und die Injektoren Inj über Steuerleitungen (nicht dargestellt) in Abhängigkeit von Sensorsignalen und Betriebszustand der Brennkraftmaschine steuert.Finally, this common rail system comprises CRS according to FIG. 1 also a control unit (not shown), which controls the low pressure pump NP, the high pressure pump HP, the ball seat valve VNO and the injectors Inj via control lines (not shown) in response to sensor signals and operating condition of the internal combustion engine.

Dieses erfindungsgemäße Common-Rail-System CRS zeichnet sich durch die Verwendung eines Kugelsitzventils VNO als Durchflussregelventil aus, welches im unbestromten Zustand offen ist und den der Hochdruckpumpe HP zugeführten Kraftstoff-Volumenstrom steuert.This common rail system CRS according to the invention is characterized by the use of a ball seat valve VNO as a flow control valve, which is open in the de-energized state and controls the high-pressure pump HP supplied fuel flow.

Dadurch dass ein solches Kugelsitzventil VNO leckagefrei ist, wird im Betriebszustand "Null-Förderung" kein Kraftstoff von dem Kugelsitzventil VNO an die Hochdruckpumpe HP geliefert. Deshalb kann auf ein Hochdruckregelventil HPV, wie im Stand der Technik nach Figur 4 erforderlich ist, bei dem erfindungsgemäßen Common-Rail-System CRS gemäß Figur 1 verzichtet werden. Aus sicherheitstechnischen Gründen ist lediglich ein mechanisches Überdruckventil VÜ vorgesehen, welches eine Verbindung zwischen dem Hochdruckspeicher R und der Förderleitung L2 zwischen der Niederdruckpumpe NP und dem Kugelsitzventil VNO herstellen kann.As a result of such a ball seat valve VNO being leak-free, no fuel is supplied from the ball seat valve VNO to the high-pressure pump HP in the operating state "zero delivery". Therefore, it can be applied to a high pressure control valve HPV, as in the prior art FIG. 4 is required, according to the invention in the common rail system CRS FIG. 1 be waived. For safety reasons, only a mechanical pressure relief valve VÜ is provided, which is a connection between the high pressure accumulator R and the delivery line L2 between the low pressure pump NP and the ball seat valve VNO can produce.

Im Ruhezustand, also im unbestromten Zustand ist das Kugelsitzventil VNO offen, so dass bei einem Defekt oder bei einem Ausfall dieses Kugelsitzventils VNO trotzdem der von der Niederdruckpumpe NP geförderte Kraftstoff an die Hochdruckpumpe geliefert werden kann, so dass zumindest Fehlfunktionen betreffend die Brennkraftmaschine ausgeschlossen sind.In the idle state, ie in the de-energized state, the ball seat valve VNO is open, so that in case of failure or failure of this ball seat valve VNO funded by the low-pressure pump NP fuel can be delivered to the high-pressure pump, so that at least malfunctions are excluded with respect to the internal combustion engine.

Ein solches Kugelsitzventil VNO zeigt Figur 2, welches in einem Ventilgehäuse 20 einen zentrisch gelagerten Polkern 8 aufnimmt, der teilweise von einer Ringspule, bestehend aus einer auf einem Spulenkörper 15 angeordneten Spulenwicklung 16 umschlossen wird.Such a ball seat valve VNO shows FIG. 2 which accommodates in a valve housing 20 a centrally mounted pole core 8, which is partially enclosed by a toroidal coil, consisting of a arranged on a bobbin 15 coil winding 16.

An den Polkern 8 schließt sich über einen Verbindungsring 13 ein Ventilkörper 1 mit einer zentrischen Bohrung 1a an, der polkernseitig einen zentrischen Aufnahmeraum 1b für einen Anker 5 bildet. Der Anker 5 trägt zentrisch einen Ventilstößel 6, der polkernseitig die Stirnfläche des Ankers 5 überragt und in eine zentrische Bohrung 8a des Polkerns 8 hineinragt. Diese Bohrung 8a wird endseitig durch einen Verschluss 11 verschlossen, wobei eine in der Bohrung 8a des Polkerns 8 angeordnete Druckfeder 9 sich einerseits gegen diesen Verschluss 11 und andererseits gegen die benachbarte Stirnseite des Ankers 5 über einen dort anliegenden Federteller 7 abstützt.Connected to the pole core 8 via a connecting ring 13 is a valve body 1 with a central bore 1a, which forms a central receiving space 1b for an armature 5 on the pole core side. The armature 5 carries centrally a valve stem 6, the pole core side, the end face of the armature 5 projects beyond and projects into a central bore 8 a of the pole core 8. This bore 8a is closed at the end by a closure 11, wherein a disposed in the bore 8a of the pole core 8 compression spring 9 is supported on the one hand against this closure 11 and on the other hand against the adjacent end face of the armature 5 via a spring plate 7 present there.

Die Bohrung 8a des Polkerns 8 geht ankerseitig in eine abgesetzte zylindrische Bohrung 8b über, deren Durchmesser dem Durchmesser des Ankers 5 entspricht, so dass der Anker 5 bei einer Bestromung der Spulenwicklung 16 in diese Bohrung 8b des Polkerns 8 gegen die Federkraft der vorgespannten Druckfeder 9 an die Polfläche des Polkerns 8 gezogen wird. Der diese zylindrische Bohrung umgebende Ring 8c ist als Steuerkonus mit einem Außenkonus ausgebildet, der dazu dient, die Magnetkraft-Hub-Kennlinie einzustellen, wenn der Anker 5 aus seiner Ruhestellung entsprechend der in Figur 2 dargestellten Position durch Bestromung der Spulenwicklung 16 in Richtung der Polfläche des Polkerns 8 gezogen wird.The bore 8a of the pole core 8 goes on the anchor side in a stepped cylindrical bore 8b, whose diameter corresponds to the diameter of the armature 5, so that the armature 5 in energizing the coil winding 16 in this bore 8b of Polkerns 8 is pulled against the spring force of the prestressed compression spring 9 to the pole face of the pole core 8. The surrounding this cylindrical bore ring 8c is formed as a control cone with an outer cone, which serves to adjust the magnetic force-stroke curve when the armature 5 from its rest position corresponding to the in FIG. 2 shown position is drawn by energizing the coil winding 16 in the direction of the pole face of the pole core 8.

Der Anker 5 wird von einer Hülse 10 aufgenommen, die sich über den Bereich der Bohrung 1b und des Verbindungsringes 13 erstreckt.The armature 5 is received by a sleeve 10 which extends over the region of the bore 1 b and the connecting ring 13.

Auf der polkernabgewandten Seite des Ankers 5 erstreckt sich die Bohrung 1a des Ventilkörpers 1 bis in einen Ventilraum 1c und geht endseitig in eine Einlassöffnung 1d über, die an die Niederdruckpumpe NP angeschlossen ist.On the pole core side facing away from the armature 5, the bore 1a of the valve body 1 extends into a valve chamber 1c and ends at an inlet port 1d, which is connected to the low-pressure pump NP.

Der sich an diese Einlassöffnung 1d anschließende Ventilraum 1c nimmt einen Kugelkäfig 3 zu Aufnahme einer Ventilkugel 4 und einen sich daran anschließenden Ventilsitz 2 für die Ventilkugel 4 auf.The adjoining this inlet opening 1d valve chamber 1c takes a ball cage 3 for receiving a valve ball 4 and an adjoining valve seat 2 for the valve ball 4.

In einem an den Ventilraum 1c anschließenden Bereich der zentralen Bohrung 1a des Ventilkörpers 1 sind wenigstens zwei diametral gegenüberliegende radiale Bohrungen 1e als Auslassöffnung 1e vorgesehen, die auf die Hochdruckpumpe HP geführt werden.In a subsequent to the valve chamber 1c region of the central bore 1a of the valve body 1, at least two diametrically opposite radial holes 1e are provided as an outlet opening 1e, which are guided on the high-pressure pump HP.

Der Ventilstößel 6 weist ausgehend von der polkernabgewandten Stirnseite des Ankers 5 eine solche Länge auf, dass in der in Figur 2 dargestellten Ruhestellung des Kugelsitzventils VNO, also im unbestromten Zustand die Druckfeder 9 den Anker 5 vollständig in die Bohrung 1b des Ventilkörpers 1 in Richtung der Einlassöffnung 1d drückt und dabei der Ventilstößel 6 mit einer Nadelspitze 6a die Ventilkugel 4 von dem Ventilsitz 2 abhebt, so dass der Durchgang zwischen der Einlassöffnung 1d und der Auslassöffnung 1e freigegeben wird.The valve stem 6, starting from the pole core facing away from the end face of the armature 5 to such a length that in the in FIG. 2 illustrated rest position of the ball seat valve VNO, so in the de-energized state, the compression spring 9 the armature. 5 pushes completely into the bore 1b of the valve body 1 in the direction of the inlet opening 1d, while the valve stem 6 with a needle tip 6a lifts the valve ball 4 from the valve seat 2, so that the passage between the inlet port 1d and the outlet port 1e is released.

Der Anker 5 weist eine nichtzentrische, parallel zur Längsachse verlaufende Bohrung 5a auf, die dessen beiden Stirnflächen verbindet. Damit werden der Ventilraum 1c und die Auslassöffnungen 1e mit der Bohrung 8a des Polkerns 8 verbunden, so dass ein Druckausgleich zwischen diesen Räumen während des Betriebes des Kugelsitzventils VNO erfolgen kann, bzw. sich keine Druckdifferenz zwischen diesen Räumen aufbaut.The armature 5 has a non-centered, parallel to the longitudinal axis extending bore 5a, which connects the two end faces. Thus, the valve chamber 1c and the outlet openings 1e are connected to the bore 8a of the pole core 8, so that a pressure equalization between these spaces can take place during operation of the ball seat valve VNO, or builds up no pressure difference between these spaces.

Zur Montage des Kugelsitzventils VNO, bspw. an der Hochdruckpumpe HP ist ein Flansch 12 vorgesehen. Bei einem entsprechenden Anschluss sind O-Ringe 14 und 21 des Ventilkörpers 1 als Dichtringe vorgesehen. Der Spulenkörper 16 ist zur Bildung eines einen Anschlussstecker 18 aufnehmenden Kunststoffkörpers 17 umspritzt, wobei eine Dichtscheibe 19 die Dichtheit gegenüber der Umgebung herstellt.For mounting the ball seat valve VNO, for example. On the high pressure pump HP, a flange 12 is provided. In a corresponding connection O-rings 14 and 21 of the valve body 1 are provided as sealing rings. The bobbin 16 is encapsulated to form a connector 18 receiving plastic body 17, wherein a sealing disc 19 makes the seal against the environment.

Wird ausgehend der Ruhelage des Kugelsitzventils VCO gemäß Figur 2 die Spulenwicklung 16 bestromt, wird der Anker 5 zusammen mit dem Ventilstößel 6 in Richtung des Polkerns 8 gegen die Federkraft der Druckfeder 9 gezogen, so dass aufgrund des einlassseitigen Druckes die Ventilkugel 4 in den Ventilsitz 2 gedrückt und dadurch das Kugelsitzventil VNO geschlossen wird.If the coil winding 16 is energized starting from the rest position of the ball seat valve VCO according to FIG. 2, the armature 5 is pulled together with the valve lifter 6 in the direction of the pole core 8 against the spring force of the compression spring 9, so that the valve ball 4 enters the valve seat 2 due to the inlet-side pressure pressed and thereby the ball seat valve VNO is closed.

Bei der Montage des Kugelsitzventils VNO kann eine Federkrafteinstellung der Druckfeder 9, mit welcher der Anker 5 vorgespannt wird, durchgeführt werden. Hierzu kann der die Bohrung 8a des Polkerns 8 endseitig verschließende Verschluss 11 unterschiedlich tief in die Bohrung 8a eingeführt werden oder mit unterschiedlichen Längen ausgebildet werden, so dass hierdurch unterschiedliche Einbaulängen für die Druckfeder 9 entstehen. Zum Einbringen des Verschlusses 11 in die Bohrung 8a kann ein Presspassung oder auch eine Gewindeverbindung vorgesehen werden.When mounting the ball seat valve VNO a spring force adjustment of the compression spring 9, with which the armature 5 is biased, are performed. For this purpose, the bore 8a of the pole core 8 end closing closure 11 different be introduced deeply into the bore 8a or formed with different lengths, so that in this way different installation lengths for the compression spring 9 arise. For introducing the closure 11 in the bore 8a, a press fit or a threaded connection can be provided.

Durch unterschiedliche Tellerfedern 7 kann auch leicht eine Hubeinstellung des Ankers 5 vorgenommen werden.By different disc springs 7 can also be easily a stroke adjustment of the armature 5 are made.

Eine schematische Kennlinie des Kugelsitzventils VNO gemäß Figur 2 zeigt Figur 3, die in Abhängigkeit der Stromstärke I den Volumenstrom Q angibt. Im unbestromten Zustand bzw. bei geringen Stromstärken wird ein hoher Durchfluss bzw. Volumenstrom an Fluid, also an Kraftstoff erzielt, der mit zunehmender Bestromung, also mit zunehmender Stromstärke bis auf den Wert Null abnimmt, d. h. bis das Kugelsitzventil VNO geschlossen ist. Wegen Hystereseeigenschaften des Elektromagneten verdoppelt sich die Kennlinie im mittleren Bereich.A schematic characteristic of the ball seat valve VNO according to Figure 2 shows FIG. 3 , which indicates the volume flow Q as a function of the current intensity I. In the de-energized state or at low currents, a high flow or volume flow of fluid, ie fuel is achieved, which decreases with increasing current, so with increasing current up to the value zero, ie until the ball seat valve VNO is closed. Because of the hysteresis properties of the electromagnet, the characteristic doubles in the middle range.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Ventilkörpervalve body
1a1a
zentrische Bohrung des Ventilkörpers 1Centric bore of the valve body. 1
1b1b
Aufnahmeraum des Ventilkörpers 1Receiving space of the valve body 1
1c1c
Ventilraumvalve chamber
1d1d
Einlassöffnunginlet port
1e1e
Auslassöffnungoutlet
22
Ventilsitzvalve seat
33
Kugelkäfigball cage
44
Ventilkugelvalve ball
55
Ankeranchor
5a5a
dezentrale Bohrung des Ankers 5decentralized bore of the armature 5
66
Ventilstößeltappet
77
Federtellerspring plate
88th
Polkernpole core
8a8a
Bohrung des Polkerns 8Bore of the pole core 8
8b8b
Bohrung des Polkerns 8Bore of the pole core 8
8c8c
Steuerkonus des Polkerns 8Control cone of the pole core 8
99
Druckfedercompression spring
1010
Hülseshell
1111
Verschluss des Polkerns 8Closure of the pole core 8
1212
Flanschflange
1313
Verbindungsringconnecting ring
1414
O-RingO-ring
1515
Spulenkörperbobbins
1616
Spulenwicklungcoil winding
1717
KunststoffkörperPlastic body
1818
Anschlusssteckerconnector
1919
Dichtscheibesealing washer
2020
Ventilgehäusevalve housing
2121
O-RingO-ring
CRSCRS
Common-Rail-SystemCommon Rail System
HPHP
Hochdruckpumpehigh pressure pump
HPVHPV
HochdruckregelventilHigh-pressure control valve
Injinj
Injektorinjector
KBKB
KraftstoffbehälterFuel tank
M1M1
Elektromotor der Hochdruckpumpe HPElectric motor of HP high pressure pump
M2M2
Elektromotor der Niederdruckpumpe NPElectric motor of low pressure pump NP
NPNP
NiederdruckpumpeLow pressure pump
L1L1
HochdruckleitungHigh-pressure line
L2L2
Förderleitungdelivery line
L3L3
DruckablassleitungDepressurization line
RR
HochdruckspeicherHigh-pressure accumulator
VNCVNC
Schieberventilspool valve
VNOVNO
KugelsitzventilBall seat valve
VÜVÜ
mechanisches Überdruckventilmechanical pressure relief valve

Claims (4)

  1. A common rail system (CRS) for an internal combustion engine of a vehicle, comprising:
    - a high-pressure pump (HP), which supplies fuel impinged with high pressure to a high-pressure accumulator (R), from which the fuel is fed to at least one injection valve (Inj) of the internal combustion engine,
    - a low-pressure pump (NP) to convey fuel from the fuel tank (KB) via a conveyor line (L2) to the high-pressure pump (HP),
    - a flow control valve as an electromagnetic switching valve, which is arranged in the conveyor line (L2) to control the quantity of fuel fed from the high-pressure pump (HP) to the high-pressure accumulator (R), wherein the flow control valve is embodied as a ball seat valve (VNO) with an inlet opening (1d) connected to the low-pressure pump (NP) and an outlet opening (1e) connected to the high-pressure pump (HP), which valve is open in the de-energized state, wherein the ball seat valve (VNO) comprises an anchor (5), which can be displaced in reference to a pole core (8) and centrically receives the valve tappet (6),
    wherein the pole core (8) comprises a centric, cylindrical bore (8b) with a surrounding ring (8c), which is embodied as a control cone for adjusting a magnetic force-stroke characteristic,
    characterized in that
    the ball seat valve (VNO) is embodied with a valve seat (2) and a valve ball (4) such that in the energized state of the ball seat valve (VNO), by applying pressure on the part of the low-pressure pump (NP), the valve ball (4) abuts on the valve seat (2), hereby closing the inlet opening (1d), wherein in the de-energized state a valve tappet (6) presses against the valve ball (4) and lifts it off the valve seat (2).
  2. Common rail system (CRS) according to claim 1,
    characterized in that
    the ball seat valve (VNO) is embodied with a spring preloaded valve tappet (6) such that in order to open the inlet opening (1d) the valve tappet (6), in the de-energized state of the ball seat valve (VNO), is in an operative connection lifting the valve ball (4) off its valve seat (2).
  3. Common rail system (CRS) according to claim 2,
    characterized in that
    the pole core (8) comprises a central bore (8a) to receive a compression spring (9), wherein at one end the compression spring (9) is supported by the anchor (5) and at the other end is supported by a closure part (11) of the pole core (8), closing the bore (8a) at a side of the pole core (8) pointing away from the anchor.
  4. Common rail system (CRS) according to claim 2,
    characterized in that
    the anchor (5) is embodied with a decentralized bore (5a), which connects the bore (8a) of the pole core (8) with a valve chamber (1c) at the side of the valve ball.
EP13750553.3A 2012-08-23 2013-08-14 Common rail system Not-in-force EP2888469B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012107764.9A DE102012107764A1 (en) 2012-08-23 2012-08-23 Common Rail System
PCT/EP2013/067020 WO2014029676A1 (en) 2012-08-23 2013-08-14 Common rail system

Publications (2)

Publication Number Publication Date
EP2888469A1 EP2888469A1 (en) 2015-07-01
EP2888469B1 true EP2888469B1 (en) 2019-04-24

Family

ID=49000474

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13750553.3A Not-in-force EP2888469B1 (en) 2012-08-23 2013-08-14 Common rail system

Country Status (6)

Country Link
US (1) US9765741B2 (en)
EP (1) EP2888469B1 (en)
CN (1) CN104583577B (en)
DE (1) DE102012107764A1 (en)
ES (1) ES2734990T3 (en)
WO (1) WO2014029676A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015212387A1 (en) * 2015-07-02 2017-01-05 Robert Bosch Gmbh Electromagnetically actuated suction valve for a high-pressure pump and method for producing such a suction valve
DE102015116240A1 (en) 2015-09-25 2017-03-30 Kendrion (Villingen) Gmbh Electric actuator of a valve device
DE102015119462A1 (en) 2015-11-11 2017-05-11 Kendrion (Villingen) Gmbh Electromagnetic actuator for a valve device
JP6806246B2 (en) * 2017-05-19 2021-01-06 アイシン・エィ・ダブリュ株式会社 Relief valve
DE102017222559B4 (en) * 2017-12-13 2021-03-11 Vitesco Technologies GmbH Method and device for predicting the point in time of failure of the pressure relief valve of a high-pressure fuel pump of a motor vehicle
CN111219279B (en) * 2020-01-08 2021-07-09 一汽解放汽车有限公司 Fuel injection system with self-protection function and pressure control method
CN112138460B (en) * 2020-10-02 2022-06-28 台州半城暖通科技有限公司 Cover-lifting demagnetizing filter

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4041377A1 (en) * 1989-12-28 1991-07-04 Aisin Aw Co 2-WAY ELECTROMAGNETIC VALVE
DE10251014A1 (en) * 2002-11-02 2004-05-19 Robert Bosch Gmbh Fuel dispensing unit for fuel injection system for internal combustion engine has shutoff sleeve in interior of valve piston and valve piston and shutoff sleeve form shutoff device
DE69917552T2 (en) * 1998-09-29 2005-06-16 Eaton Electromagnetic pressure control valve

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03157576A (en) * 1989-11-15 1991-07-05 Aisin Aw Co Ltd Three-way solenoid valve and manufacture thereof
DE19727785B4 (en) * 1997-06-30 2006-04-13 Robert Bosch Gmbh Flow control valve for controlling liquids
DE19846157A1 (en) 1998-10-07 2000-04-13 Bosch Gmbh Robert Pump arrangement for high-pressure fuel generation
JPWO2002055870A1 (en) * 2001-01-05 2004-05-20 株式会社日立製作所 High pressure fuel supply pump
JP4627603B2 (en) * 2001-03-15 2011-02-09 日立オートモティブシステムズ株式会社 Fuel supply device
EP1852603B1 (en) 2004-09-24 2009-04-29 Denso Corporation Flow control valve
DE102005027779A1 (en) * 2005-06-15 2006-12-28 Schultz, Wolfgang E., Dipl.-Ing. Electromagnet with control cone
DE102006054316A1 (en) * 2006-07-18 2008-01-24 Robert Bosch Gmbh Method for determining a fault in a fuel metering unit of an injection system
DE102007028960A1 (en) 2007-06-22 2008-12-24 Robert Bosch Gmbh High-pressure pump for fuel system of internal combustion engine, has intake valve device, which is brought by actuation device to certain position or held in certain position
DE102008029979B4 (en) * 2008-06-24 2024-02-29 Robert Bosch Gmbh Actuating magnet with anti-adhesive disc

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4041377A1 (en) * 1989-12-28 1991-07-04 Aisin Aw Co 2-WAY ELECTROMAGNETIC VALVE
DE69917552T2 (en) * 1998-09-29 2005-06-16 Eaton Electromagnetic pressure control valve
DE10251014A1 (en) * 2002-11-02 2004-05-19 Robert Bosch Gmbh Fuel dispensing unit for fuel injection system for internal combustion engine has shutoff sleeve in interior of valve piston and valve piston and shutoff sleeve form shutoff device

Also Published As

Publication number Publication date
WO2014029676A1 (en) 2014-02-27
ES2734990T3 (en) 2019-12-13
US20150167611A1 (en) 2015-06-18
EP2888469A1 (en) 2015-07-01
CN104583577B (en) 2018-11-20
DE102012107764A1 (en) 2014-04-10
CN104583577A (en) 2015-04-29
US9765741B2 (en) 2017-09-19

Similar Documents

Publication Publication Date Title
EP2888469B1 (en) Common rail system
EP2238338B1 (en) Fuel injection system for an internal combustion engine
EP2684200B1 (en) Electromagnetic actuator
EP1509694B1 (en) High-pressure accumulator for fuel injection systems with integrated pressure control valve
EP1865192B1 (en) Fuel injector with servo assistance
EP1402170B1 (en) Control module for an injector of an accumulator injection system
WO1999031383A1 (en) High pressure pump for supplying fuel in fuel injection systems of internal combustion engines
EP2310662A1 (en) Fuel injector
EP1799999B1 (en) Fuel system for an internal combustion engine
EP1379779A2 (en) Seat/sliding valve comprising a pressure compensation pin
WO2018001626A1 (en) Electromagnetically actuatable inlet valve and high-pressure pump comprising an inlet valve
EP2981702A1 (en) Fuel piston plug-in pump having a housing, at least one axially movable piston disposed in the housing, and a coupling section
EP2733345A1 (en) Pressure control valve for a high pressure storage tank of a combustion engine
DE102005061362B3 (en) Pressure control valve for injection system of multi-cylinder internal combustion engine, has closing body provided in non-controlled condition of actuator in closing position, where force acting on body is changed by controlling actuator
EP1911966A2 (en) Fuel injector for a combustion engine
EP3032090B1 (en) Switching or pressure control valve for a fuel injection system
EP3390807A1 (en) Valve, in particular a suction valve, in a high-pressure pump of a fuel injection system
WO2017050463A1 (en) Electromagnetically actuable inlet valve and high-pressure pump having an inlet valve
EP3365551A1 (en) Electromagnetically operable inlet valve and high-pressure pump having an inlet valve
DE102022205162A1 (en) Piston pump, especially high-pressure fuel pump, and inlet valve for a piston pump
DE102020206035A1 (en) High pressure fuel pump
DE102022209219A1 (en) Fuel pump
EP1636487B1 (en) Pressure control valve for a fuel injection system provided with an accumulator
WO2014202260A1 (en) Injection device
WO2024022668A1 (en) Fuel pump

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: 20141113

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

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20170217

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20190103

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

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

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502013012703

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1124456

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190515

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190424

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

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: 20190424

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

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: 20190424

Ref country code: LT

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: 20190424

Ref country code: FI

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: 20190424

Ref country code: SE

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: 20190424

Ref country code: AL

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: 20190424

Ref country code: PT

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: 20190824

Ref country code: NO

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: 20190724

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20190822

Year of fee payment: 7

Ref country code: IT

Payment date: 20190821

Year of fee payment: 7

Ref country code: ES

Payment date: 20190919

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

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: 20190424

Ref country code: PL

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: 20190424

Ref country code: BG

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: 20190724

Ref country code: GR

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: 20190725

Ref country code: RS

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: 20190424

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2734990

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20191213

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

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: 20190824

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013012703

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

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: 20190424

Ref country code: CZ

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: 20190424

Ref country code: EE

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: 20190424

Ref country code: SK

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: 20190424

Ref country code: DK

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: 20190424

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

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: 20190424

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: TR

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: 20190424

26N No opposition filed

Effective date: 20200127

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190814

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

Ref country code: SI

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: 20190424

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190814

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

Ref country code: MC

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: 20190424

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190814

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 NON-PAYMENT OF DUE FEES

Effective date: 20190814

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1124456

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190814

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20200928

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190814

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

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: 20190424

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20130814

Ref country code: MT

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: 20190424

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200814

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200831

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20220110

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502013012703

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200815

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

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: 20190424

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: 20220301