EP2670969B1 - Fuel injection system comprising an overflow valve - Google Patents

Fuel injection system comprising an overflow valve Download PDF

Info

Publication number
EP2670969B1
EP2670969B1 EP11802968.5A EP11802968A EP2670969B1 EP 2670969 B1 EP2670969 B1 EP 2670969B1 EP 11802968 A EP11802968 A EP 11802968A EP 2670969 B1 EP2670969 B1 EP 2670969B1
Authority
EP
European Patent Office
Prior art keywords
valve piston
injection system
fuel injection
bore
fuel
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.)
Active
Application number
EP11802968.5A
Other languages
German (de)
French (fr)
Other versions
EP2670969A1 (en
Inventor
Armin Merz
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 EP2670969A1 publication Critical patent/EP2670969A1/en
Application granted granted Critical
Publication of EP2670969B1 publication Critical patent/EP2670969B1/en
Active 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
    • 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
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0023—Valves in the fuel supply and return system
    • F02M37/0029—Pressure regulator in the low pressure fuel system
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0047—Layout or arrangement of systems for feeding fuel
    • F02M37/0052—Details on the fuel return circuit; Arrangement of pressure regulators
    • 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
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • 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

Definitions

  • the invention relates to a fuel injection system for an internal combustion engine having the features of the preamble of claim 1.
  • Such a fuel injection system is characterized by DE 10 2008 044 361 A1 known.
  • This fuel injection system has a prefeed pump and a high-pressure pump, which is supplied by means of the prefeed pump fuel from a fuel tank.
  • the fuel injection system comprises a metering unit for controlling the amount of fuel to be supplied via an inlet to at least one pump element of the high-pressure pump.
  • an overflow valve is arranged which has an axially displaceable valve piston, via the axial displacement of which at least one outflow opening can be opened or closed. From the inlet downstream of the metering unit discharges a leakage amount of the metering unit from.
  • an axially extending flow channel is formed with a cross-sectional constriction and in the region of the cross-sectional constriction opens a substantially radially extending bore in the valve piston in the flow channel.
  • the overflow valve is used to control fuel from the inlet between the prefeed pump and the metering unit.
  • a throttle is arranged and the drain opens into an inlet between the fuel tank and the prefeed pump. Due to the outflow with the throttle, which is also referred to as a zero feed throttle, it is ensured that when the zero delivery of the high pressure pump, the leakage amount of the metering unit is not promoted by the high pressure pump.
  • the drain with the throttle are provided in this fuel injection system in addition to the overflow valve whereby the structure of the fuel injection system is expensive.
  • a fuel injection system which has a prefeed pump and a high-pressure pump, which is supplied by means of the prefeed pump fuel from a fuel tank.
  • the fuel injection system comprises a metering unit for controlling the intake via at least one Pump element of the high-pressure pump to be supplied amount of fuel.
  • an overflow valve is arranged which has an axially displaceable valve piston, via the axial displacement of which at least one outflow opening can be opened or closed.
  • an axially extending flow channel is formed with a cross-sectional constriction and in the region of the cross-sectional constriction opens a substantially radially extending bore in the valve piston in the flow channel.
  • the overflow valve is used to control fuel from the inlet between the prefeed pump and the metering unit. In this fuel injection system, there is no drain for a leakage amount of the metering unit.
  • a fuel injection system which has a prefeed pump and a high-pressure pump, which is supplied by means of the prefeed pump fuel from a fuel tank.
  • the fuel injection system has a volume-flow-controlled bypass valve with an axially displaceable valve piston, via the axial displacement of which an outflow opening can be opened or closed.
  • an axially extending flow channel is formed with a cross-sectional constriction and in the region of the cross-sectional constriction opens a substantially radially extending bore in the valve piston in the flow channel.
  • the axial flow channel of the bypass valve is traversed by fuel, which is deactivated at the high-pressure pump or from the high-pressure region of the fuel injection system.
  • valve piston As the volume flow through the flow channel increases, the valve piston is moved axially so that it releases an outflow opening through which fuel can flow into the fuel tank.
  • no metering unit is provided for controlling the amount of fuel to be supplied to the high-pressure pump, and thus no outflow of a leakage amount of a metering unit is provided.
  • the fuel injection system according to the invention with the features of claim 1 has the advantage that its structure is simplified, since the outflow of the leakage amount of the metering unit via the substantially radially extending bore into the flow channel of the valve piston of the spill valve and thus no separate throttle in the outflow required is.
  • the cross-sectional constriction of the flow channel may be formed in the manner of a Venturi nozzle whereby a leakage of the leakage amount of the metering unit is ensured at zero promotion.
  • the flow channel can have two oppositely conical sections, which are juxtaposed with their smaller diameters directly or via an intermediate cylindrical section.
  • the inner contour of the flow channel may also be spherical, with the inner contour preferably bulging convexly inwards.
  • the radius of the spherically formed inner contour can be chosen differently in the flow direction before and behind the cross-sectional constriction. The same applies with respect to the respective cone angle, provided that the cross-sectional constriction is formed by means of two opposite cone-shaped sections.
  • the valve piston is designed in several parts and comprises at least one sleeve-shaped component for forming the flow channel.
  • the sleeve-shaped component can be processed separately before joining the parts of the valve piston, which facilitates the formation of the flow channel. As a result, the production costs and the production costs are further reduced.
  • the sleeve-shaped component is pressed to form the flow channel in a central bore of the valve piston.
  • the central bore for receiving the sleeve-shaped component may for example be formed in a further sleeve-shaped component.
  • the central bore is at least partially formed as a flow channel and designed as a through hole.
  • the through-bore is preferably flowed through by fuel permanently and thus allows a constant lubrication and / or cooling of the high-pressure pump.
  • the fuel flowing through the valve piston is supplied to a return via an outflow opening.
  • the discharge opening is preferably independent of the respective axial position of the valve piston released, so that a continuous flow is guaranteed.
  • An axial displacement of the valve piston and consequently the complete opening of the overflow valve is effected only when a predetermined limit pressure is exceeded (one-stage design of the overflow valve).
  • the overflow valve can also be designed as a two-stage valve.
  • the release of the discharge opening for returning the lubricating and / or cooling amount first stage
  • the release of at least one further outflow opening takes place.
  • the central bore of the valve piston is at least partially formed as a flow channel and designed as a blind hole.
  • the blind hole is preferably hydraulically connected via a transverse bore with at least one outlet opening.
  • a permanent or, depending on the axial position of the valve piston a temporary hydraulic connection can be made via the transverse bore, so that a one- or two-stage concept can be realized.
  • the central bore itself can serve as a flow channel.
  • the central bore or the flow channel can be formed as a through hole or blind hole.
  • single-stage, as well as two-stage valves can be realized.
  • valve piston is received in a housing part which has at least one substantially radially extending bore.
  • the essentially radially extending bore is preferably arranged in the housing part in such a way that, optionally in dependence on the axial position of the valve piston, it permits a hydraulic connection of the flow passage with a supply or return.
  • the housing part may for example be sleeve-shaped and insertable into a bore of the housing of the high-pressure pump.
  • the housing of the high pressure pump can form the housing part.
  • the at least one substantially radially extending bore serves as a discharge opening, via which the flow channel of the valve piston is hydraulically connectable to a return.
  • the hydraulic connection may require an axial displacement of the valve piston to release the discharge port.
  • the hydraulic connection can also be permanent, for example, to ensure a constant lubrication and / or cooling of the high-pressure pump.
  • the design as a two-stage valve requires the formation of at least two substantially radially extending bores through which fuel can flow.
  • At least one further substantially radially extending bore may be formed, which is hydraulically connectable to the substantially radially extending bore of the valve piston in order to first supply the leakage quantity of the metering unit to the flow channel and via the flow channel to a return line.
  • a circumferential groove for forming an annular space between the valve piston and the housing part is preferably formed on the valve piston and / or in the housing part.
  • the hydraulic connection of the holes is thus independent of the rotational position of the valve piston relative to the housing part.
  • a circumferential groove can also be formed on the sleeve-shaped component of a two-part valve piston.
  • valve piston is acted upon in the closing direction by the spring force of a spring. While the opening of the overflow valve is effected solely by the hydraulic pressure, the return of the valve piston to its initial position via the spring force is a spring.
  • the spring is preferably on the one hand on the valve piston, on the other hand-at least indirectly-supported on the housing part, which surrounds the valve piston.
  • a low pressure circuit that in the Fig. 1 illustrated fuel injection system includes a low pressure circuit.
  • Components of the low pressure circuit are a prefeed pump 1, which sucks fuel from a fuel tank 2 and a high-pressure pump 3, a arranged between the prefeed pump 1 and the high-pressure pump 3 metering unit 4 for flow control and a spill valve 7, whose task is the pressure in front of the metering unit 4 as constant as possible.
  • the overflow valve 7 opens, so that fuel can flow off via a return 17.
  • the fuel was already passed as a lubricant and / or coolant through the low pressure region of the high pressure pump.
  • the overflow valve shown has a further connection to a return line 17, via which fuel can flow off continuously.
  • the drainage is throttled.
  • the metered via the metering unit amount of fuel is fed via an inlet 5 at least one pump element 6 of the high-pressure pump 3. In the present case two pump elements 6 are shown.
  • the fuel is conveyed to high pressure and then fed to a high-pressure accumulator 22.
  • the high-pressure accumulator 22 has a plurality of connections 23 for fuel injectors (not shown), by means of which the fuel in the combustion chamber of an internal combustion engine (not shown) can be injected.
  • prefeed pump 1, metering unit 4 and overflow valve 7 can be integrated into the high-pressure pump 3 or attached thereto.
  • a common housing 24 is indicated schematically by the dot-dash-dot line.
  • Fig. 2 shows the spill valve 7 of the low-pressure circuit of Fig. 1 , It comprises a housing part 15, with which it is inserted in a bore (not shown) of the housing 24 of the high-pressure pump 3.
  • a housing part 15 In the housing part 15, an axially displaceable valve piston 8 is accommodated, in which a continuous flow channel 10 is formed (see Fig. 3 ).
  • the flow channel 10 has a spherically shaped inner contour, so that a cross-sectional constriction 11 is formed in the manner of a Venturi nozzle.
  • a radially extending bore 12 is guided by the valve piston 8, which connects the flow channel 10 with an annular space 19 which is formed between the housing part 15 and the valve piston 8.
  • the annular space 19 is formed by a provided in the housing part 15 circumferential groove 18.
  • a further circumferential groove 18 is also provided on the outer circumference of the valve piston 8, which also communicates with the annular space 19.
  • a trained in the housing part 15 radially extending bore 16 opens into the annular space 19 and is also in hydraulic communication with the inlet 5 of the high-pressure pump 3.
  • the entering into the inlet 5 leakage amount of the metering unit 4 can therefore via the bore 16, the annular space 19, the Bore 12 and the flow channel 10 of a discharge opening 9 and here a return 17 are supplied.
  • the discharge opening 9 is also designed as a radially extending bore in the housing part 15. Due to the hydraulic connection of the flow channel 10 with the inlet 5 of the high-pressure pump 3, a separately designed zero-delivery throttle is dispensable.
  • the flow channel 10 is designed in the manner of a Venturi nozzle, that is to say that it has a cross-sectional constriction 11.
  • the bore 12 opens into the flow channel 10. If now flows through the flow channel 10 of fuel, this has the consequence that in the bore 12, a negative pressure is created, which is the outflow supports the leakage quantity.
  • the amount of leakage is fed together with the fuel to a discharge opening 9 and here a return 17.
  • the discharge opening 9 is permanently in hydraulic communication with the flow channel 10, so that continuous flow of fuel through the valve piston 8. As a result, a constant lubrication and / or cooling of the high-pressure pump 3 is ensured.
  • FIG. 5 An alternative embodiment of an overflow valve 7 according to the invention for a low-pressure circuit is in the Fig. 5 shown.
  • the valve piston 8 in this case made in two parts.
  • the flow channel 10 is formed by a sleeve-shaped component 13 which is pressed into a central bore 14 of the valve piston 8.
  • the central bore 14 is designed as a blind hole, so that the valve piston 8 is not continuously flowed through by a lubricating and / or cooling amount.
  • a progressive axial displacement of the valve piston 8 then causes the release of at least one further outflow opening 9 and thus the complete opening of the overflow valve 7 (second stage).
  • the overflow valve of the Fig. 5 designed as a two-stage valve.
  • At least one further radially extending bore 16 in the housing part 15 is formed, which serves as an inlet or is hydraulically connected to the inlet 5 of the high-pressure pump 3.
  • the bore 16 is hydraulically connectable to the radial bore 12 of the valve piston 8, which opens in the region of the cross-sectional constriction 11 in the flow channel 10. Due to the two-part design of the valve piston 8 and the bore 12 is made in two parts.
  • the sleeve-shaped component 13 has on its outer circumference a circumferential groove 18 for forming an annular space 19.
  • a hydraulic connection of the bore 12 with the bore 16 initially requires an axial displacement of the valve piston 8.
  • valve piston 8 The axial displacement of the valve piston 8 is effected in the opening direction of the valve via the hydraulic pressure p (see arrow in FIG Fig. 5 ).
  • the valve piston 8 In the closing direction the valve piston 8 is acted upon by the spring force of a spring 20, which is supported on the one hand on the valve piston 8, on the other hand on a closure plug 21 which is pressed into the housing part 15.
  • the spring 20 thus causes the return of the valve piston.
  • the presentation of the Fig. 4 shows the overflow 7 of the Fig. 5 as part of a Kraftstoffeinspitzsystems or a low pressure circuit of a fuel injection system. This is different from the one of Fig. 1 only in that the overflow valve 7 is designed as a two-stage valve.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Kraftstoffeinspritzsystem für eine Brennkraftmaschine mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a fuel injection system for an internal combustion engine having the features of the preamble of claim 1.

Ein solches Kraftstoffeinspritzsystem ist durch die DE 10 2008 044 361 A1 bekannt. Dieses Kraftstoffeinspritzsystem weist eine Vorförderpumpe und eine Hochdruckpumpe auf, der mittels der Vorförderpumpe Kraftstoff aus einem Kraftstofftank zugeführt wird. Das Kraftstoffeinspritzsystem umfasst eine Zumesseinheit zur Regelung der über einen Zulauf wenigstens einem Pumpenelement der Hochdruckpumpe zuzuführenden Kraftstoffmenge. Zwischen der Vorförderpumpe und der Zumesseinheit ist ein Überströmventil angeordnet, das einen axial verschiebbaren Ventilkolben aufweist, über dessen axiale Verschiebung wenigstens eine Abströmöffnung freigebbar oder verschließbar ist. Vom Zulauf führt stromabwärts der Zumesseinheit ein Abfluss für eine Leckagemenge der Zumesseinheit ab. Im Ventilkolben des Überströmventils ist ein axial verlaufender Strömungskanal mit einer Querschnittsverengung ausgebildet ist und im Bereich der Querschnittsverengung mündet eine im wesentlichen radial verlaufende Bohrung im Ventilkolben in den Strömungskanal. Das Überströmventil dient dazu Kraftstoff aus dem Zulauf zwischen der Vorförderpumpe und der Zumesseinheit abzusteuern. Im Abfluss für die Leckagemenge der Zumesseinheit ist eine Drossel angeordnet und der Abfluss mündet in einen Zulauf zwischen dem Kraftstofftank und der Vorförderpumpe. Durch den Abfluss mit der Drossel, die auch als Nullförderdrossel bezeichnet wird, ist sichergestellt dass bei erforderlicher Nullförderung der Hochdruckpumpe die Leckagemenge der Zumesseinheit nicht durch die Hochdruckpumpe gefördert wird. Der Abfluss mit der Drossel sind bei diesem Kraftstoffeinspritzsystem zusätzlich zum Überströmventil vorgesehen wodurch der Aufbau des Kraftstoffeinspritzsystems aufwendig ist.Such a fuel injection system is characterized by DE 10 2008 044 361 A1 known. This fuel injection system has a prefeed pump and a high-pressure pump, which is supplied by means of the prefeed pump fuel from a fuel tank. The fuel injection system comprises a metering unit for controlling the amount of fuel to be supplied via an inlet to at least one pump element of the high-pressure pump. Between the prefeed pump and the metering unit, an overflow valve is arranged which has an axially displaceable valve piston, via the axial displacement of which at least one outflow opening can be opened or closed. From the inlet downstream of the metering unit discharges a leakage amount of the metering unit from. In the valve piston of the overflow valve, an axially extending flow channel is formed with a cross-sectional constriction and in the region of the cross-sectional constriction opens a substantially radially extending bore in the valve piston in the flow channel. The overflow valve is used to control fuel from the inlet between the prefeed pump and the metering unit. In the drain for the leakage amount of the metering unit, a throttle is arranged and the drain opens into an inlet between the fuel tank and the prefeed pump. Due to the outflow with the throttle, which is also referred to as a zero feed throttle, it is ensured that when the zero delivery of the high pressure pump, the leakage amount of the metering unit is not promoted by the high pressure pump. The drain with the throttle are provided in this fuel injection system in addition to the overflow valve whereby the structure of the fuel injection system is expensive.

Durch die WO 99/56016 A1 ist ein Kraftstoffeinspritzsystem bekannt, das eine Vorförderpumpe und eine Hochdruckpumpe aufweist, der mittels der Vorförderpumpe Kraftstoff aus einem Kraftstofftank zugeführt wird. Das Kraftstoffeinspritzsystem umfasst eine Zumesseinheit zur Regelung der über einen Zulauf wenigstens einem Pumpenelement der Hochdruckpumpe zuzuführenden Kraftstoffmenge. Zwischen der Vorförderpumpe und der Zumesseinheit ist ein Überströmventil angeordnet, das einen axial verschiebbaren Ventilkolben aufweist, über dessen axiale Verschiebung wenigstens eine Abströmöffnung freigebbar oder verschließbar ist. Im Ventilkolben des Überströmventils ist ein axial verlaufender Strömungskanal mit einer Querschnittsverengung ausgebildet und im Bereich der Querschnittsverengung mündet eine im wesentlichen radial verlaufende Bohrung im Ventilkolben in den Strömungskanal. Das Überströmventil dient dazu Kraftstoff aus dem Zulauf zwischen der Vorförderpumpe und der Zumesseinheit abzusteuern. Bei diesem Kraftstoffeinspritzsystem ist kein Abfluss für eine Leckagemenge der Zumesseinheit vorgesehen.By the WO 99/56016 A1 a fuel injection system is known, which has a prefeed pump and a high-pressure pump, which is supplied by means of the prefeed pump fuel from a fuel tank. The fuel injection system comprises a metering unit for controlling the intake via at least one Pump element of the high-pressure pump to be supplied amount of fuel. Between the prefeed pump and the metering unit, an overflow valve is arranged which has an axially displaceable valve piston, via the axial displacement of which at least one outflow opening can be opened or closed. In the valve piston of the overflow valve, an axially extending flow channel is formed with a cross-sectional constriction and in the region of the cross-sectional constriction opens a substantially radially extending bore in the valve piston in the flow channel. The overflow valve is used to control fuel from the inlet between the prefeed pump and the metering unit. In this fuel injection system, there is no drain for a leakage amount of the metering unit.

Durch die DE 10 2009 005 595 A1 ist ein Kraftstoffeinspritzsystem bekannt, das eine Vorförderpumpe und eine Hochdruckpumpe aufweist, der mittels der Vorförderpumpe Kraftstoff aus einem Kraftstofftank zugeführt wird. Das Kraftstoffeinspritzsystem weist ein volumenstromgeregeltes Umgehungsventil mit einem axial verschiebbaren Ventilkolben auf, über dessen axiale Verschiebung eine Abströmöffnung freigebbar oder verschließbar ist. Im Ventilkolben ist ein axial verlaufender Strömungskanal mit einer Querschnittsverengung ausgebildet und im Bereich der Querschnittsverengung mündet eine im wesentlichen radial verlaufende Bohrung im Ventilkolben in den Strömungskanal. Der axiale Strömungskanal des Umgehungsventils wird von Kraftstoff durchströmt, der an der Hochdruckpumpe oder aus dem Hochdruckbereich des Kraftstoffeinspritzsystems abgesteuert wird. Mit zunehmendem Volumenstrom durch den Strömungskanal wird der Ventilkolben axial so bewegt, dass dieser eine Abströmöffnung freigibt, durch die Kraftstoff in den Kraftstofftank abfließen kann. Bei diesem Kraftstoffeinspritzsystem ist keine Zumesseinheit zur Regelung der der Hochdruckpumpe zuzuführenden Kraftstoffmenge und somit auch kein Abfluss einer Leckagemenge einer Zumesseinheit vorgesehen.By the DE 10 2009 005 595 A1 a fuel injection system is known, which has a prefeed pump and a high-pressure pump, which is supplied by means of the prefeed pump fuel from a fuel tank. The fuel injection system has a volume-flow-controlled bypass valve with an axially displaceable valve piston, via the axial displacement of which an outflow opening can be opened or closed. In the valve piston an axially extending flow channel is formed with a cross-sectional constriction and in the region of the cross-sectional constriction opens a substantially radially extending bore in the valve piston in the flow channel. The axial flow channel of the bypass valve is traversed by fuel, which is deactivated at the high-pressure pump or from the high-pressure region of the fuel injection system. As the volume flow through the flow channel increases, the valve piston is moved axially so that it releases an outflow opening through which fuel can flow into the fuel tank. In this fuel injection system, no metering unit is provided for controlling the amount of fuel to be supplied to the high-pressure pump, and thus no outflow of a leakage amount of a metering unit is provided.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzsystem mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass dessen Aufbau vereinfacht ist, da der Abfluss der Leckagemenge der Zumesseinheit über die im wesentlichen radial verlaufende Bohrung in den Strömungskanal des Ventilkolbens des Überströmventils mündet und somit keine separate Drossel im Abfluss erforderlich ist. Die Querschnittsverengung des Strömungskanals kann nach Art einer Venturi-Düse ausgebildet sein wodurch ein Abfließen der Leckagemenge der Zumesseinheit bei Nullförderung sichergestellt ist.The fuel injection system according to the invention with the features of claim 1 has the advantage that its structure is simplified, since the outflow of the leakage amount of the metering unit via the substantially radially extending bore into the flow channel of the valve piston of the spill valve and thus no separate throttle in the outflow required is. The cross-sectional constriction of the flow channel may be formed in the manner of a Venturi nozzle whereby a leakage of the leakage amount of the metering unit is ensured at zero promotion.

Zur Ausbildung der Querschnittsverengung kann der Strömungskanal zwei gegenläufig konusförmige Abschnitte aufweisen, die mit ihren kleineren Durchmessern direkt oder über einen zwischenliegenden zylinderförmigen Abschnitt aneinandergesetzt sind. Alternativ kann die Innenkontur des Strömungskanals auch sphärisch ausgebildet sein, wobei sich die Innenkontur vorzugsweise konvex nach innen wölbt. Der Radius der sphärisch ausgebildeten Innenkontur kann in Strömungsrichtung vor und hinter der Querschnittsverengung unterschiedlich gewählt sein. Gleiches gilt in Bezug auf den jeweiligen Konuswinkel, sofern die Querschnittsverengung mittels zweier gegenläufig konusförmiger Abschnitte ausgebildet wird.To form the cross-sectional constriction, the flow channel can have two oppositely conical sections, which are juxtaposed with their smaller diameters directly or via an intermediate cylindrical section. Alternatively, the inner contour of the flow channel may also be spherical, with the inner contour preferably bulging convexly inwards. The radius of the spherically formed inner contour can be chosen differently in the flow direction before and behind the cross-sectional constriction. The same applies with respect to the respective cone angle, provided that the cross-sectional constriction is formed by means of two opposite cone-shaped sections.

Gemäß einer bevorzugten Ausführungsform der Erfindung ist der Ventilkolben mehrteilig ausgebildet und umfasst wenigstens ein hülsenförmiges Bauteil zur Ausbildung des Strömungskanals. Das hülsenförmige Bauteil kann vor dem Fügen der Teile des Ventilkolbens getrennt bearbeitet werden, was die Ausbildung des Strömungskanals erleichtert. Dadurch werden der Fertigungsaufwand sowie die Herstellungskosten weiter reduziert.According to a preferred embodiment of the invention, the valve piston is designed in several parts and comprises at least one sleeve-shaped component for forming the flow channel. The sleeve-shaped component can be processed separately before joining the parts of the valve piston, which facilitates the formation of the flow channel. As a result, the production costs and the production costs are further reduced.

Vorzugsweise ist das hülsenförmige Bauteil zur Ausbildung des Strömungskanals in eine zentrale Bohrung des Ventilkolbens eingepresst. Auf diese Weise wird eine kraftschlüssige Verbindung der Teile des Ventilkolbens erreicht. Die zentrale Bohrung zur Aufnahme des hülsenförmigen Bauteils kann beispielsweise in einem weiteren hülsenförmigen Bauteil ausgebildet sein.Preferably, the sleeve-shaped component is pressed to form the flow channel in a central bore of the valve piston. In this way, a frictional connection of the parts of the valve piston is achieved. The central bore for receiving the sleeve-shaped component may for example be formed in a further sleeve-shaped component.

Gemäß einer Weiterbildung der Erfindung ist die zentrale Bohrung zumindest teilweise als Strömungskanal ausgebildet und als Durchgangsbohrung ausgeführt. Die Durchgangsbohrung wird vorzugsweise dauerhaft von Kraftstoff durchströmt und ermöglicht somit eine konstante Schmierung und/oder Kühlung der Hochdruckpumpe. Der den Ventilkolben durchströmende Kraftstoff wird über eine Abströmöffnung einem Rücklauf zugeführt. Vorzugsweise ist hierzu die Abströmöffnung unabhängig von der jeweiligen axialen Lage des Ventilkolbens freigegeben, so dass ein kontinuierliches Abfließen gewährleistet ist. Eine axiale Verschiebung des Ventilkolbens und demzufolge das vollständige Öffnen des Überströmventils wird erst bei Überschreiten eines vorgegebenen Grenzdrucks bewirkt (einstufige Ausführung des Überströmventils). Sofern keine konstante Schmierung und/oder Kühlung erwünscht ist, kann das Überströmventil auch als zweistufiges Ventil ausgeführt sein. Die Freigabe der Abströmöffnung zur Rückführung der Schmier- und/oder Kühlmenge (erste Stufe) setzt dann eine axiale Verschiebung des Ventilkolbens voraus. Mit fortschreitender axialer Verschiebung des Ventilkolbens erfolgt die Freigabe wenigstens einer weiteren Abströmöffnung (zweite Stufe).According to one embodiment of the invention, the central bore is at least partially formed as a flow channel and designed as a through hole. The through-bore is preferably flowed through by fuel permanently and thus allows a constant lubrication and / or cooling of the high-pressure pump. The fuel flowing through the valve piston is supplied to a return via an outflow opening. For this purpose, the discharge opening is preferably independent of the respective axial position of the valve piston released, so that a continuous flow is guaranteed. An axial displacement of the valve piston and consequently the complete opening of the overflow valve is effected only when a predetermined limit pressure is exceeded (one-stage design of the overflow valve). If no constant lubrication and / or cooling is desired, the overflow valve can also be designed as a two-stage valve. The release of the discharge opening for returning the lubricating and / or cooling amount (first stage) then requires an axial displacement of the valve piston. With progressive axial displacement of the valve piston, the release of at least one further outflow opening (second stage) takes place.

Gemäß einer alternativen Ausführungsform ist die zentrale Bohrung des Ventilkolbens zumindest teilweise als Strömungskanal ausgebildet und als Sacklochbohrung ausgeführt. Die Sacklochbohrung ist vorzugsweise über eine Querbohrung mit wenigstens einer Abströmöffnung hydraulisch verbindbar. Dabei kann über die Querbohrung eine dauerhafte oder, in Abhängigkeit von der axialen Lage des Ventilkolbens, eine zeitweise hydraulische Verbindung hergestellt werden, so dass ein ein- oder zweistufiges Konzept realisierbar ist.According to an alternative embodiment, the central bore of the valve piston is at least partially formed as a flow channel and designed as a blind hole. The blind hole is preferably hydraulically connected via a transverse bore with at least one outlet opening. In this case, a permanent or, depending on the axial position of the valve piston, a temporary hydraulic connection can be made via the transverse bore, so that a one- or two-stage concept can be realized.

Sofern der Ventilkolben einteilig ausgebildet ist, kann die zentrale Bohrung selbst als Strömungskanal dienen. Wie zuvor beschrieben kann die zentrale Bohrung bzw. der Strömungskanal als Durchgangsbohrung oder Sacklochbohrung ausgebildet sein. Ferner sind einstufige, als auch zweistufige Ventile realisierbar.If the valve piston is formed in one piece, the central bore itself can serve as a flow channel. As described above, the central bore or the flow channel can be formed as a through hole or blind hole. Furthermore, single-stage, as well as two-stage valves can be realized.

Weiterhin wird vorgeschlagen, dass der Ventilkolben in einem Gehäuseteil aufgenommen ist, das wenigstens eine im Wesentlichen radial verlaufende Bohrung besitzt. Die im Wesentlichen radial verlaufende Bohrung ist bevorzugt derart im Gehäuseteil angeordnet, dass sie, ggf. in Abhängigkeit von der axialen Lage des Ventilkolbens, eine hydraulische Verbindung des Strömungskanals mit einem Zu- oder Rücklauf ermöglicht. Das Gehäuseteil kann beispielsweise hülsenförmig ausgebildet und in eine Bohrung des Gehäuses der Hochdruckpumpe einsetzbar sein. Alternativ kann auch das Gehäuse der Hochdruckpumpe das Gehäuseteil bilden.Furthermore, it is proposed that the valve piston is received in a housing part which has at least one substantially radially extending bore. The essentially radially extending bore is preferably arranged in the housing part in such a way that, optionally in dependence on the axial position of the valve piston, it permits a hydraulic connection of the flow passage with a supply or return. The housing part may for example be sleeve-shaped and insertable into a bore of the housing of the high-pressure pump. Alternatively, the housing of the high pressure pump can form the housing part.

Gemäß einer bevorzugten Ausführungsform der Erfindung dient die wenigstens eine im Wesentlichen radial verlaufende Bohrung als Abströmöffnung, über welche der Strömungskanal des Ventilkolbens mit einem Rücklauf hydraulisch verbindbar ist. Die hydraulische Verbindung kann eine axiale Verschiebung des Ventilkolbens erfordern, um die Abströmöffnung freizugeben. Die hydraulische Verbindung kann aber auch dauerhaft bestehen, um beispielsweise eine konstante Schmierung und/oder Kühlung der Hochdruckpumpe zu gewährleisten. Die Ausführung als zweistufiges Ventil erfordert die Ausbildung von wenigstens zwei im Wesentlichen radial verlaufenden Bohrungen, über welche Kraftstoff abströmen kann. Darüber hinaus kann wenigstens eine weitere im Wesentlichen radial verlaufende Bohrung ausgebildet sein, welche mit der im Wesentlichen radial verlaufenden Bohrung des Ventilkolbens hydraulisch verbindbar ist, um die Leckagemenge der Zumesseinheit zunächst dem Strömungskanal und über den Strömungskanal einem Rücklauf zuzuführen.According to a preferred embodiment of the invention, the at least one substantially radially extending bore serves as a discharge opening, via which the flow channel of the valve piston is hydraulically connectable to a return. The hydraulic connection may require an axial displacement of the valve piston to release the discharge port. The hydraulic connection can also be permanent, for example, to ensure a constant lubrication and / or cooling of the high-pressure pump. The design as a two-stage valve requires the formation of at least two substantially radially extending bores through which fuel can flow. In addition, at least one further substantially radially extending bore may be formed, which is hydraulically connectable to the substantially radially extending bore of the valve piston in order to first supply the leakage quantity of the metering unit to the flow channel and via the flow channel to a return line.

Um die hydraulische Verbindung einer im Wesentlichen radial verlaufender Bohrungen des Gehäuseteils mit einer entsprechenden Bohrung des Ventilkolbens zu erleichtern, ist vorzugsweise am Ventilkolben und/oder im Gehäuseteil eine Umfangsnut zur Ausbildung eines Ringraums zwischen dem Ventilkolben und dem Gehäuseteil ausgebildet. Die hydraulische Verbindung der Bohrungen ist somit unabhängig von der Rotationslage des Ventilkolbens gegenüber dem Gehäuseteil. Alternativ oder ergänzend kann auch am hülsenförmigen Bauteil eines zweiteilig ausgeführten Ventilkolbens eine Umfangsnut ausgebildet sein.In order to facilitate the hydraulic connection of a substantially radially extending bores of the housing part with a corresponding bore of the valve piston, a circumferential groove for forming an annular space between the valve piston and the housing part is preferably formed on the valve piston and / or in the housing part. The hydraulic connection of the holes is thus independent of the rotational position of the valve piston relative to the housing part. Alternatively or additionally, a circumferential groove can also be formed on the sleeve-shaped component of a two-part valve piston.

Weiterhin bevorzugt wird der Ventilkolben in Schließrichtung von der Federkraft einer Feder beaufschlagt. Während das Öffnen des Überströmventils allein über den hydraulischen Druck bewirkt wird, erfolgt die Rückstellung des Ventilkolbens in seine Ausgangslage über die Federkraft eine Feder. Die Feder ist hierzu vorzugsweise einerseits am Ventilkolben, andererseits -zumindest mittelbar- am Gehäuseteil abgestützt, das den Ventilkolben umgibt.Further preferably, the valve piston is acted upon in the closing direction by the spring force of a spring. While the opening of the overflow valve is effected solely by the hydraulic pressure, the return of the valve piston to its initial position via the spring force is a spring. For this purpose, the spring is preferably on the one hand on the valve piston, on the other hand-at least indirectly-supported on the housing part, which surrounds the valve piston.

Bevorzugte Ausführungsformen der Erfindung werden nachfolgend anhand der beigefügten Zeichnungen näher erläutert. Diese zeigen:

Fig. 1
eine schematische Darstellung eines Kraftstoffeinspritzsystems mit einem Überströmventil,
Fig. 2
einen Längsschnitt durch das Überströmventil der Fig. 1, welcher den Ventilkolben in einer Ansicht zeigt,
Fig. 3
eine Schnittansicht durch den Ventilkolben des Überströmventils der Fig. 2,
Fig. 4
eine schematische Darstellung eines Kraftstoffeinspritzsystems mit einem alternativen erfindungsgemäßen Niederdruckkreis und
Fig. 5
einen Längsschnitt durch das Überströmventil der Fig. 4, welcher ein hülsenförmiges Bauteil des Ventilkolbens in einer Schnittansicht zeigt.
Preferred embodiments of the invention are explained below with reference to the accompanying drawings. These show:
Fig. 1
a schematic representation of a fuel injection system with a spill valve,
Fig. 2
a longitudinal section through the overflow of the Fig. 1 showing the valve piston in a view
Fig. 3
a sectional view through the valve piston of the overflow valve of Fig. 2 .
Fig. 4
a schematic representation of a fuel injection system with an alternative low-pressure circuit according to the invention and
Fig. 5
a longitudinal section through the overflow of the Fig. 4 which shows a sleeve-shaped component of the valve piston in a sectional view.

Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings

Das in der Fig. 1 dargestellte Kraftstoffeinspritzsystem umfasst einen Niederdruckkreis. Bestandteile des Niederdruckkreises sind eine Vorförderpumpe 1, welche Kraftstoff aus einem Kraftstofftank 2 ansaugt und einer Hochdruckpumpe 3 zuführt, eine zwischen der Vorförderpumpe 1 und der Hochdruckpumpe 3 angeordnete Zumesseinheit 4 zur Mengenregelung sowie ein Überströmventil 7, dessen Aufgabe es ist, den Druck vor der Zumesseinheit 4 möglichst konstant zu halten. Übersteigt der Druck einen bestimmten Grenzdruck, öffnet das Überströmventil 7, so dass Kraftstoff über einen Rücklauf 17 abfließen kann. Zuvor wurde der Kraftstoff bereits als Schmier- und/oder Kühlmittel durch den Niederdruckbereich der Hochdruckpumpe geführt. Um eine konstante Schmierung und/oder Kühlung zu ermöglichen, weist das dargestellte Überströmventil eine weitere Anbindung an einen Rücklauf 17 auf, über welchen Kraftstoff kontinuierlich abfließen kann. Vorzugsweise erfolgt das Abfließen gedrosselt.That in the Fig. 1 illustrated fuel injection system includes a low pressure circuit. Components of the low pressure circuit are a prefeed pump 1, which sucks fuel from a fuel tank 2 and a high-pressure pump 3, a arranged between the prefeed pump 1 and the high-pressure pump 3 metering unit 4 for flow control and a spill valve 7, whose task is the pressure in front of the metering unit 4 as constant as possible. If the pressure exceeds a certain limit pressure, the overflow valve 7 opens, so that fuel can flow off via a return 17. Previously, the fuel was already passed as a lubricant and / or coolant through the low pressure region of the high pressure pump. In order to allow a constant lubrication and / or cooling, the overflow valve shown has a further connection to a return line 17, via which fuel can flow off continuously. Preferably, the drainage is throttled.

Die über die Zumesseinheit zugemessene Menge Kraftstoff wird über einen Zulauf 5 wenigstens einem Pumpenelement 6 der Hochdruckpumpe 3 zugeführt. Vorliegend sind zwei Pumpenelemente 6 dargestellt. In den Pumpenelementen 6 der Hochdruckpumpe 3 wird der Kraftstoff auf Hochdruck gefördert und anschließend einem Hochdruckspeicher 22 zugeführt. Der Hochdruckspeicher 22 weist mehrere Anschlüsse 23 für Kraftstoffinjektoren (nicht dargestellt) auf, mittels welcher der Kraftstoff in den Brennraum einer Brennkraftmaschine (nicht dargestellt) einspritzbar ist.The metered via the metering unit amount of fuel is fed via an inlet 5 at least one pump element 6 of the high-pressure pump 3. In the present case two pump elements 6 are shown. In the pump elements 6 of the high-pressure pump 3, the fuel is conveyed to high pressure and then fed to a high-pressure accumulator 22. The high-pressure accumulator 22 has a plurality of connections 23 for fuel injectors (not shown), by means of which the fuel in the combustion chamber of an internal combustion engine (not shown) can be injected.

Die Komponenten Vorförderpumpe 1, Zumesseinheit 4 und Überströmventil 7 können in die Hochdruckpumpe 3 integriert bzw. hieran angebaut sein. Ein gemeinsames Gehäuse 24 ist schematisch über die Punkt-Strich-Punkt Linie angedeutet.The components prefeed pump 1, metering unit 4 and overflow valve 7 can be integrated into the high-pressure pump 3 or attached thereto. A common housing 24 is indicated schematically by the dot-dash-dot line.

Fig. 2 zeigt das Überströmventil 7 des Niederdruckkreises der Fig. 1. Es umfasst ein Gehäuseteil 15, mit welchem es in einer Bohrung (nicht dargestellt) des Gehäuses 24 der Hochdruckpumpe 3 eingesetzt ist. Im Gehäuseteil 15 ist ein axial verschiebbarer Ventilkolben 8 aufgenommen, in welchem ein durchgehender Strömungskanal 10 ausgebildet ist (siehe Fig. 3). Der Strömungskanal 10 weist eine sphärisch geformte Innenkontur auf, so dass eine Querschnittsverengung 11 nach Art einer Venturi-Düse ausgebildet wird. Im Bereich der Querschnittsverengung 11 ist zudem eine radial verlaufende Bohrung 12 durch den Ventilkolben 8 geführt, welche den Strömungskanal 10 mit einem Ringraum 19 verbindet, der zwischen dem Gehäuseteil 15 und dem Ventilkolben 8 ausgebildet ist. Der Ringraum 19 wird durch eine im Gehäuseteil 15 vorgesehene Umfangsnut 18 gebildet. Eine weitere Umfangsnut 18 ist ferner außenumfangseitig am Ventilkolben 8 vorgesehen, welche ebenfalls mit dem Ringraum 19 kommuniziert. Eine im Gehäuseteil 15 ausgebildete radial verlaufende Bohrung 16 mündet in den Ringraum 19 und steht ferner in hydraulischer Verbindung mit dem Zulauf 5 der Hochdruckpumpe 3. Die in den Zulauf 5 gelangende Leckagemenge der Zumesseinheit 4 kann demnach über die Bohrung 16, den Ringraum 19, die Bohrung 12 sowie den Strömungskanal 10 einer Abströmöffnung 9 und hierüber einem Rücklauf 17 zugeführt werden. Die Abströmöffnung 9 ist ebenfalls als radial verlaufende Bohrung im Gehäuseteil 15 ausgeführt. Aufgrund der hydraulischen Verbindung des Strömungskanals 10 mit dem Zulauf 5 der Hochdruckpumpe 3 ist eine separat ausgebildete Nullförderdrossel entbehrlich. Fig. 2 shows the spill valve 7 of the low-pressure circuit of Fig. 1 , It comprises a housing part 15, with which it is inserted in a bore (not shown) of the housing 24 of the high-pressure pump 3. In the housing part 15, an axially displaceable valve piston 8 is accommodated, in which a continuous flow channel 10 is formed (see Fig. 3 ). The flow channel 10 has a spherically shaped inner contour, so that a cross-sectional constriction 11 is formed in the manner of a Venturi nozzle. In the region of the cross-sectional constriction 11 also a radially extending bore 12 is guided by the valve piston 8, which connects the flow channel 10 with an annular space 19 which is formed between the housing part 15 and the valve piston 8. The annular space 19 is formed by a provided in the housing part 15 circumferential groove 18. A further circumferential groove 18 is also provided on the outer circumference of the valve piston 8, which also communicates with the annular space 19. A trained in the housing part 15 radially extending bore 16 opens into the annular space 19 and is also in hydraulic communication with the inlet 5 of the high-pressure pump 3. The entering into the inlet 5 leakage amount of the metering unit 4 can therefore via the bore 16, the annular space 19, the Bore 12 and the flow channel 10 of a discharge opening 9 and here a return 17 are supplied. The discharge opening 9 is also designed as a radially extending bore in the housing part 15. Due to the hydraulic connection of the flow channel 10 with the inlet 5 of the high-pressure pump 3, a separately designed zero-delivery throttle is dispensable.

Vorteilhafterweise ist der Strömungskanal 10 nach Art einer Venturi-Düse ausgebildet, das heißt, dass er eine Querschnittsverengung 11 aufweist. Im Bereich der Querschnittsverengung 11 mündet die Bohrung 12 in den Strömungskanal 10. Wird nun der Strömungskanal 10 von Kraftstoff durchströmt hat dies zur Folge, dass in der Bohrung 12 ein Unterdruck entsteht, welcher das Abfließen der Leckagemenge unterstützt. Die Leckagemenge wird zusammen mit dem Kraftstoff einer Abströmöffnung 9 und hierüber einem Rücklauf 17 zugeführt. Die Abströmöffnung 9 steht dauerhaft in hydraulischer Verbindung mit dem Strömungskanal 10, so dass kontinuierlich Kraftstoff den Ventilkolben 8 durchströmt. Dadurch ist eine konstante Schmierung und/oder Kühlung der Hochdruckpumpe 3 gewährleistet.Advantageously, the flow channel 10 is designed in the manner of a Venturi nozzle, that is to say that it has a cross-sectional constriction 11. In the region of the cross-sectional constriction 11, the bore 12 opens into the flow channel 10. If now flows through the flow channel 10 of fuel, this has the consequence that in the bore 12, a negative pressure is created, which is the outflow supports the leakage quantity. The amount of leakage is fed together with the fuel to a discharge opening 9 and here a return 17. The discharge opening 9 is permanently in hydraulic communication with the flow channel 10, so that continuous flow of fuel through the valve piston 8. As a result, a constant lubrication and / or cooling of the high-pressure pump 3 is ensured.

Eine alternative Ausführungsform eines erfindungsgemäßen Überströmventils 7 für einen Niederdruckkreis ist in der Fig. 5 dargestellt. Im Unterschied zum Ventil der Fig. 2 und 3 ist der Ventilkolben 8 vorliegend zweiteilig ausgeführt. Der Strömungskanal 10 wird durch ein hülsenförmiges Bauteil 13 ausgebildet, das in eine zentrale Bohrung 14 des Ventilkolbens 8 eingepresst ist. Die zentrale Bohrung 14 ist als Sacklochbohrung ausgeführt, so dass der Ventilkolben 8 nicht kontinuierlich von einer Schmier- und/oder Kühlmenge durchströmt wird. Um den Anschluss des Strömungskanals 10 an eine Abströmöffnung 9 zu ermöglichen, bedarf es einer axialen Verschiebung des Ventilkolbens 8 (erste Stufe). Ein fortschreitende axiale Verschiebung des Ventilkolbens 8 bewirkt dann die Freigabe wenigstens einer weiteren Abströmöffnung 9 und damit das vollständige Öffnen des Überströmventils 7 (zweite Stufe). Im Unterschied zum Ventil der Fig. 2 und 3 ist demnach das Überströmventil der Fig. 5 als zweistufiges Ventil ausgeführt.An alternative embodiment of an overflow valve 7 according to the invention for a low-pressure circuit is in the Fig. 5 shown. Unlike the valve of FIGS. 2 and 3 is the valve piston 8 in this case made in two parts. The flow channel 10 is formed by a sleeve-shaped component 13 which is pressed into a central bore 14 of the valve piston 8. The central bore 14 is designed as a blind hole, so that the valve piston 8 is not continuously flowed through by a lubricating and / or cooling amount. To allow the connection of the flow channel 10 to a discharge opening 9, it requires an axial displacement of the valve piston 8 (first stage). A progressive axial displacement of the valve piston 8 then causes the release of at least one further outflow opening 9 and thus the complete opening of the overflow valve 7 (second stage). Unlike the valve of FIGS. 2 and 3 is therefore the overflow valve of the Fig. 5 designed as a two-stage valve.

Neben den als Abströmöffnungen 9 dienenden radial verlaufenden Bohrungen 9 im Gehäuseteil 15 ist wenigstens eine weitere radial verlaufende Bohrung 16 im Gehäuseteil 15 ausgebildet, welche als Zulauf dient bzw. mit dem Zulauf 5 der Hochdruckpumpe 3 hydraulisch in Verbindung steht. Die Bohrung 16 ist mit der radialen Bohrung 12 des Ventilkolbens 8 hydraulisch verbindbar, welche im Bereich der Querschnittsverengung 11 in den Strömungskanal 10 mündet. Aufgrund der zweiteiligen Ausführung des Ventilkolbens 8 ist auch die Bohrung 12 zweiteilig ausgeführt. Um die hydraulische Verbindung beider Teile der Bohrung 12 sicherzustellen, weist das hülsenförmige Bauteil 13 außenumfangseitig eine Umfangsnut 18 zur Ausbildung eines Ringraums 19 auf. Eine hydraulische Verbindung der Bohrung 12 mit der Bohrung 16 setzt jedoch zunächst eine axiale Verschiebung des Ventilkolbens 8 voraus.In addition to serving as outflow openings 9 radially extending holes 9 in the housing part 15 at least one further radially extending bore 16 in the housing part 15 is formed, which serves as an inlet or is hydraulically connected to the inlet 5 of the high-pressure pump 3. The bore 16 is hydraulically connectable to the radial bore 12 of the valve piston 8, which opens in the region of the cross-sectional constriction 11 in the flow channel 10. Due to the two-part design of the valve piston 8 and the bore 12 is made in two parts. In order to ensure the hydraulic connection of both parts of the bore 12, the sleeve-shaped component 13 has on its outer circumference a circumferential groove 18 for forming an annular space 19. However, a hydraulic connection of the bore 12 with the bore 16 initially requires an axial displacement of the valve piston 8.

Die axiale Verschiebung des Ventilkolbens 8 wird in Öffnungsrichtung des Ventils über den hydraulischen Druck p bewirkt (siehe Pfeil in Fig. 5). In Schließrichtung wird der Ventilkolben 8 von der Federkraft einer Feder 20 beaufschlagt, welche einerseits am Ventilkolben 8, andererseits an einem Verschlussstopfen 21 abgestützt ist, der in das Gehäuseteil 15 eingepresst ist. Die Feder 20 bewirkt somit die Rückstellung des Ventilkolbens 8.The axial displacement of the valve piston 8 is effected in the opening direction of the valve via the hydraulic pressure p (see arrow in FIG Fig. 5 ). In the closing direction the valve piston 8 is acted upon by the spring force of a spring 20, which is supported on the one hand on the valve piston 8, on the other hand on a closure plug 21 which is pressed into the housing part 15. The spring 20 thus causes the return of the valve piston. 8

Die Darstellung der Fig. 4 zeigt das Überströmventil 7 der Fig. 5 als Bestandteil eines Kraftstoffeinspitzsystems bzw. eines Niederdruckkreises eines Kraftstoffeinspritzsystems. Dieses unterscheidet sich von dem der Fig. 1 lediglich dadurch, dass das Überströmventil 7 als zweistufiges Ventil ausgeführt ist.The presentation of the Fig. 4 shows the overflow 7 of the Fig. 5 as part of a Kraftstoffeinspitzsystems or a low pressure circuit of a fuel injection system. This is different from the one of Fig. 1 only in that the overflow valve 7 is designed as a two-stage valve.

Claims (9)

  1. Fuel injection system for an internal combustion engine, wherein the fuel injection system has a pre-delivery pump (1) and a high-pressure pump (3) to which fuel is supplied from a fuel tank (2) by means of the pre-delivery pump (1), having a metering unit (4) for regulating the fuel quantity to be supplied via a feed line (5) to at least one pump element (6) of the high-pressure pump (3), having a flow transfer valve (7) which is arranged between the pre-delivery pump (1) and the metering unit (4) and which has an axially displaceable valve piston (8), by means of the axial displacement of which at least one outflow opening (9) can be opened up or closed off, wherein an outlet for a leakage quantity from the metering unit (4) leads away from the feed line (5) downstream of the metering unit (4), wherein, in the valve piston (8) of the flow transfer valve (7), there is formed an axially running flow duct (10) with a cross-sectional constriction (11), and a substantially radially running bore (12) in the valve piston (8) opens into the flow duct (10) in the region of the cross-sectional constriction (11), characterized in that the flow duct (10) is connected via the bore (12) to the outlet for the leakage quantity from the metering unit (4).
  2. Fuel injection system according to Claim 1,
    characterized in that the valve piston (8) is of multipart form and comprises at least one sleeve-shaped component (13) for forming the flow duct (10).
  3. Fuel injection system according to Claim 2,
    characterized in that the sleeve-shaped component (13) is pressed into a central bore (14) of the valve piston (8).
  4. Fuel injection system according to Claim 3,
    characterized in that the central bore (14) is at least partially in the form of a flow duct (10), and is configured as a through bore.
  5. Fuel injection system according to Claim 3,
    characterized in that the central bore (14) is at least partially in the form of a flow duct (10), and is configured as a blind bore.
  6. Fuel injection system according to one of the preceding claims,
    characterized in that the valve piston (8) is accommodated in a housing part (15) which has at least one substantially radially running bore (16).
  7. Fuel injection system according to Claim 6,
    characterized in that the at least one substantially radially running bore (16) serves as an outflow opening (9) via which the flow duct (10) is hydraulically connectable to a return line (17).
  8. Fuel injection system according to Claim 6 or 7,
    characterized in that, on the valve piston (8) and/or in the housing part (15), there is formed a circumferential groove (18) for forming an annular chamber (19) between the valve piston (8) and the housing part (15).
  9. Fuel injection system according to one of the preceding claims,
    characterized in that the valve piston (8) is forced in a closing direction by the spring force of a spring (20).
EP11802968.5A 2011-01-31 2011-12-30 Fuel injection system comprising an overflow valve Active EP2670969B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110003362 DE102011003362A1 (en) 2011-01-31 2011-01-31 Overflow valve for a fuel injection system and fuel injection system with overflow valve
PCT/EP2011/074320 WO2012103998A1 (en) 2011-01-31 2011-12-30 Overflow valve for a fuel injection system and fuel injection system comprising an overflow valve

Publications (2)

Publication Number Publication Date
EP2670969A1 EP2670969A1 (en) 2013-12-11
EP2670969B1 true EP2670969B1 (en) 2015-10-07

Family

ID=45440556

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11802968.5A Active EP2670969B1 (en) 2011-01-31 2011-12-30 Fuel injection system comprising an overflow valve

Country Status (4)

Country Link
EP (1) EP2670969B1 (en)
CN (1) CN103339364B (en)
DE (1) DE102011003362A1 (en)
WO (1) WO2012103998A1 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013216889B4 (en) * 2013-08-26 2016-08-11 Robert Bosch Gmbh Overflow valve for a fuel injection system and fuel injection system
CN105637211B (en) * 2013-10-14 2019-06-04 沃尔沃卡车集团 Fuel system for internal combustion engine
DE102013224387B4 (en) * 2013-11-28 2019-11-28 Robert Bosch Gmbh Fuel injection system and method for operating a fuel injection system
CN104500294A (en) * 2014-12-29 2015-04-08 江铃汽车股份有限公司 Exhaust structure of high-pressure oil pump
DE102015217850A1 (en) * 2015-09-17 2017-03-23 Continental Automotive Gmbh Fuel injection system and lubrication method
CN105673283A (en) * 2016-01-28 2016-06-15 山东康达精密机械制造有限公司 Low-pressure oil cavity pressurizing device for inline distribution type electronic control injection pump
DE102017203988A1 (en) * 2017-03-10 2018-09-13 Robert Bosch Gmbh Overflow valve for pressure control in a low-pressure circuit of a fuel injection system, fuel injection system
DE102019209687A1 (en) * 2019-07-02 2021-01-07 Robert Bosch Gmbh Method of operating a fuel supply system
CN113898511B (en) * 2021-09-18 2022-11-29 襄阳航宇机电液压应用技术有限公司 Fuel flow valve

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19818385A1 (en) * 1998-04-24 1999-10-28 Bosch Gmbh Robert Connecting valve for fuel injection system of internal combustion engine
JP2002322968A (en) * 2001-04-26 2002-11-08 Denso Corp Fuel feeding device
JP4433043B2 (en) * 2007-12-05 2010-03-17 株式会社デンソー Fuel supply device
DE102009005595A1 (en) * 2009-01-21 2010-07-29 Mann + Hummel Gmbh Valve for fuel systems

Also Published As

Publication number Publication date
WO2012103998A1 (en) 2012-08-09
CN103339364B (en) 2016-10-05
CN103339364A (en) 2013-10-02
DE102011003362A1 (en) 2012-08-02
EP2670969A1 (en) 2013-12-11

Similar Documents

Publication Publication Date Title
EP2670969B1 (en) Fuel injection system comprising an overflow valve
DE102005003663B4 (en) Fuel injectors with reduced wear
EP2635791B1 (en) Fuel injection system of an internal combustion engine
DE102009032850B4 (en) Pressure relief valve, in particular for a common rail injection system
EP2836698B1 (en) Flow restrictor with ball and throttle
DE102011083475A1 (en) Hydraulic valve for fuel injection system such as common rail injection system, has valve housing whose output port is comprised of axial bore and/or axially spaced radial bores, for relieving spring chamber mounted with spring element
WO2012052225A1 (en) Fuel pump for a fuel pump injection system of an internal combustion engine
DE102012203724A1 (en) Fuel conveying device for common-rail injection system in combustion engine, has flow path arranged in valve for hydraulic connection of shaft bearing of high pressure pump with return-flow pipe, where throttle is integrated into flow path
EP2511514B1 (en) Fuel injector valve
EP3470714A1 (en) Valve for adjusting a cooling fluid flow for cooling pistons
WO2018069020A1 (en) Overflow valve, in particular for a high-pressure pump, high-pressure pump, and fuel injection system
EP3054150B1 (en) Relief valve for a high-pressure pump and high-pressure pump
DE102006050033A1 (en) Injector, in particular common rail injector
DE102016219486A1 (en) Throttling element, in particular for a high pressure pump, in particular a low pressure circuit of a fuel injection system
DE102018200565A1 (en) Injector for metering gaseous fuel, Gaseinblassystem with such an injector and method for operating this injector
EP3034858B1 (en) Relief valve for a fuel pump
DE102011089626A1 (en) Pressure relief valve for fuel delivery device of fuel injection system for injecting fuel in combustion chamber of internal combustion engine, has valve housing with input and output, where input and output are connected over valve element
DE102018117111A1 (en) Connecting rod for a variable compression internal combustion engine
DE102017206607A1 (en) overflow
DE10218025B4 (en) Throttling device, in particular for a high-pressure force injection device for an internal combustion engine
DE102015218284A1 (en) Electromagnetically actuated inlet valve and high-pressure pump with inlet valve
DE102018212414A1 (en) Venturi throat pipe
DE102018212413A1 (en) fastening device
DE102022211470A1 (en) Fuel injection system of an internal combustion engine
WO2013037544A1 (en) Non-return valve, in particular for a high-pressure fuel pump, and pump comprising a non-return valve

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: 20130902

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

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150609

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): 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: AT

Ref legal event code: REF

Ref document number: 753915

Country of ref document: AT

Kind code of ref document: T

Effective date: 20151015

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

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: DE

Ref legal event code: R096

Ref document number: 502011008038

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20151007

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: ES

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: 20151007

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: 20151007

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: 20151007

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: 20160207

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: 20151007

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: 20160107

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

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: 20151007

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: 20151007

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: 20160108

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: 20151007

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: 20151007

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: 20151007

Ref country code: BE

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

Effective date: 20151231

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: 20160208

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011008038

Country of ref document: DE

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

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: 20151007

Ref country code: LU

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: 20151230

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: 20151007

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: 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: 20151007

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: 20151007

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: 20151007

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: 20151007

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: 20151007

26N No opposition filed

Effective date: 20160708

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Effective date: 20160107

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: 20151230

Ref country code: LI

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

Effective date: 20151231

Ref country code: CH

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

Effective date: 20151231

Ref country code: GB

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

Effective date: 20160107

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

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: 20151007

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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: 20111230

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: 20151007

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: 20151007

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

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: 20151007

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 753915

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161230

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: 20161230

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: 20151007

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: 20151007

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: 20151007

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

Ref country code: FR

Payment date: 20211220

Year of fee payment: 11

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

Ref country code: IT

Payment date: 20211230

Year of fee payment: 11

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

Ref country code: FR

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

Effective date: 20221231

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

Ref country code: IT

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

Effective date: 20221230

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

Ref country code: DE

Payment date: 20240227

Year of fee payment: 13