EP3039282B1 - Pump, in particular a high-pressure fuel pump - Google Patents

Pump, in particular a high-pressure fuel pump Download PDF

Info

Publication number
EP3039282B1
EP3039282B1 EP14742485.7A EP14742485A EP3039282B1 EP 3039282 B1 EP3039282 B1 EP 3039282B1 EP 14742485 A EP14742485 A EP 14742485A EP 3039282 B1 EP3039282 B1 EP 3039282B1
Authority
EP
European Patent Office
Prior art keywords
pump
low
pressure module
metering device
hollow cylindrical
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
EP14742485.7A
Other languages
German (de)
French (fr)
Other versions
EP3039282A1 (en
Inventor
Jochen Aleker
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 EP3039282A1 publication Critical patent/EP3039282A1/en
Application granted granted Critical
Publication of EP3039282B1 publication Critical patent/EP3039282B1/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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/48—Assembling; Disassembling; Replacing
    • F02M59/485—Means for fixing delivery valve casing and barrel to each other or to pump casing

Definitions

  • the invention relates to a pump, in particular high-pressure fuel pump, according to the preamble of claim 1.
  • Such a pump in the form of a high-pressure fuel pump is through DE 10 2009 000 835 A1 known.
  • This pump has a housing part in which a pump piston is movably arranged in a cylinder bore, which delimits a pump working chamber in the cylinder bore.
  • the pump has an inlet valve which is arranged in the housing part and through which the pump working space can be connected to an inlet for conveying medium.
  • a metering device is provided, through which the pump working space supplied amount of conveying medium is variably adjustable.
  • the inlet partially runs through a low-pressure module, in which the metering device is arranged and which is connected to the housing part of the pump.
  • a connection for the inlet is arranged, which can lead, for example, from a feed pump to the low pressure module.
  • the inlet runs from the metering device in the low-pressure module through the housing part of the pump to the inlet valve arranged in the housing part.
  • the housing part of the pump has a subsequent to the cylinder bore hollow cylindrical projection, in which the inlet valve is arranged with the valve housing.
  • the low-pressure module has a recess into which protrudes the projection of the housing part, wherein the inlet from the metering device to the inlet valve in the hollow-cylindrical projection extends.
  • the valve housing of the inlet valve is pressed by a provided with a central opening screw ring into the hollow cylindrical projection of the housing part, so that the pump working space is sealed to the approach.
  • a space adjoining the projection is delimited, from which fuel can pass from the space to the inlet valve through bores extending from the central opening in the screw ring.
  • the pump according to the invention with the features of claim 1 has the advantage that it is simple, inexpensive and compact in size to produce, since the inlet to the inlet valve from the outer shell of the hollow cylindrical projection of the housing part arranged annulus takes place and the hollow cylindrical approach to the outside the screw plug is closed.
  • FIG. 1 a simplified representation of a pump in a longitudinal section with one of these associated low-pressure module according to a first embodiment
  • FIG. 2 the pump in a view in the direction of arrow II in FIG. 1
  • FIG. 3 the pump with the low pressure module according to a second embodiment.
  • a pump which is in particular a high-pressure fuel pump for a fuel injection device of an internal combustion engine.
  • the pump has a housing part 10, which is referred to below as the cylinder head.
  • the cylinder head 10 has a cylinder bore 12 in which a pump piston 14 is displaceably guided.
  • the pump piston 14 defines with its protruding into the cylinder bore 12 end of a pump working chamber 16.
  • the protruding from the cylinder bore 12 end of the pump piston 14 is connected to a transmission device, for example in the form of a roller tappet 20.
  • the roller tappet 20 is supported on a cam 22 of a drive shaft 24, through which a rotational movement of the pump piston 14 in the cylinder bore 12 is effected during the rotational movement of the drive shaft 24.
  • the drive shaft 24 may be part of the pump or part of the internal combustion engine, such as the camshaft or another shaft.
  • the pump working chamber 16 can be connected via an inlet valve 26 to a low-pressure inlet 27 to the pump and via an outlet valve 28 to a high-pressure outlet which leads, for example, to a high-pressure accumulator 30.
  • the low-pressure inlet 27 can be fed, for example, from a feed pump, which sucks fuel from a reservoir.
  • the inlet valve 26 has a valve housing 32 and is designed as a check valve.
  • the inlet valve 26 has a piston-shaped valve member 34, which is guided via its shaft 36 in the valve housing 32 and which cooperates with a formed at its diameter in relation to the shaft 36 enlarged head 38 sealing surface with a valve housing 32 formed on the valve seat.
  • the valve member 34 is acted upon by a closing spring 40 in the closing direction.
  • the cylinder head 10 is inserted in a receptacle 44 of a basic housing of the pump or a housing of the internal combustion engine, for example, the cylinder head or engine block, wherein the receptacle 44 is formed for example as a bore.
  • the cylinder head 10 in this case has a flange-like region 46, which has a larger cross section than the receptacle 44 and on which the receptacle 44 surrounding outside rests.
  • a projecting through the receptacle 44 extension 48 connects, in which the cylinder bore 12 extends and from which the connected to the roller tappet 20 end of the pump piston 14 protrudes.
  • a hollow cylindrical projection 50 connects to the cylinder head 10, which extends at least approximately coaxial with the cylinder bore 12.
  • valve housing 32 of the inlet valve 26 is inserted from the cylinder bore 12 facing away from the outside in the hollow cylindrical projection 50, wherein the valve housing 32 rests against an annular shoulder 52 of the cylinder head 10 formed at the transition from the cylinder bore 12 to the projection 50.
  • a closure screw 56 is inserted into the projection 50, which has an external thread which cooperates with an internal thread of the projection 50.
  • the valve housing 32 is pressed against the annular shoulder 52 to seal the pump working chamber 16 to the approach 50 out.
  • 52 may be disposed between the valve housing 32 and the annular shoulder a sealing ring.
  • the closure screw 56 has, on its inner side facing the valve housing 32, a central recess 58 in which the end of the shaft 36 of the valve member 34 projecting from the valve housing 32 and the closing spring 40 are arranged.
  • valve housing 32 Provided in the circumference of the valve housing 32 are at least one or preferably a plurality of inlet bores 60 distributed over the circumference, through which fuel enters the inlet valve 26.
  • the valve housing 32 is surrounded in the projection 50 by an annular groove 62, into which the inlet bores 60 open.
  • the annular groove 62 is connected to the outer periphery of the lug 50 via at least one bore 64 extending through the lug 50.
  • a nozzle 66 is formed, in which the outlet valve 28 is arranged. At the nozzle 66 to the memory 30 leading hydraulic line can be connected.
  • a low pressure module 70 is provided, through which the inlet 27 extends to the inlet valve 26.
  • the low-pressure module 70 has a module housing 72, which is connected to the cylinder head 10 and which is placed on the hollow cylindrical projection 50 of the cylinder head 10.
  • the module housing 72 is made of a lightweight material such as light metal such as aluminum or an aluminum alloy or plastic.
  • the module housing 72 has an approximately cylindrical shape, which is placed on the projection 50 of the cylinder head 10 and has a projection 50 receiving recess 74.
  • the module housing 72 bears against the flange-like region 46 of the cylinder head 10 and between the module housing 72 and the region 46 a sealing element 76, for example in the form of a sealing ring, is clamped.
  • the module housing 72 may, for example, be pressed onto the cylinder head 10 or fastened to the cylinder head 10 by means of a latching connection or via at least one or more screws.
  • Adjoining the recess 74 in the module housing 72 is an opening 78 into which a metering device 80 is inserted which serves to be able to variably set the amount of fuel supplied to the inlet valve 26.
  • the metering device 80 is designed, for example, as a proportional valve, by means of which flow cross sections of different sizes can be set.
  • the metering device 80 has a housing in which a piston 82 is arranged, through which the flow cross-section is set between an inlet opening into the metering device 80 and a drain discharging therefrom.
  • the piston 82 is displaceable against a spring 85 by means of an electrical actuator 84, for example an electromagnet. Depending on the position of the piston 82 are set by this differently sized flow cross sections.
  • the feed into the metering device 80 takes place at least approximately radially to the longitudinal axis 83 of the piston 82 and the drain at least approximately coaxial with the longitudinal axis 83 of the piston 82 of the metering device 80 and opens into the recess 74 of the module housing 72.
  • an annular space is formed between the outer periphery of the neck 50 of the cylinder head 10 and the recess 74 so that fuel from the recess 74 on the Bore 64 in approach 50 can reach the inlet valve 26.
  • an electrical terminal 81 is arranged for connection to an electronic control device, by which the actuator 84 is driven.
  • the metering device 80 When connected to the cylinder head 10 low-pressure module 70, the metering device 80 is arranged so that the longitudinal axis 83 of the piston 82 at least approximately coaxial with the cylinder bore 12 extends.
  • the module housing 72 has an at least approximately radially to the recess 74 outwardly projecting projection 86 with a bore 87.
  • a connecting piece 88 is inserted, for example, pressed.
  • a hydraulic line can be connected, which leads, for example, from a feed pump to the low-pressure module 70.
  • the bore 87 in the module housing 72 is connected via a further bore 89 with the metering device 80, wherein the further bore 89 opens in a surrounding the piston 82 of the metering device 80 annular space 90 in the module housing 72.
  • the annular space 90 and the bore 87 can be arranged offset to one another in the direction of the longitudinal axis 83 of the piston 82, so that the further bore 89 extends correspondingly obliquely in the module housing 72.
  • the pump fuel passes, for example, from a supply pump from a reservoir via the connecting piece 88 into the bore 87 in the module housing 72 and from there via the further bore 89 in the annular space 90. From the annular space 90 of the fuel passes through the piston 82 of the The coaxial arrangement of the piston 82 of the metering device 80 to the inlet valve 26, which in turn is coaxial with the cylinder bore 12 is arranged, a favorable inflow of the fuel is achieved. During the suction stroke of the pump piston 14, the inlet valve 26 opens, so that fuel flows into the pump working chamber 16.
  • the amount of fuel flowing into the pump working chamber 16 depends on the flow cross section set by the piston 82 of the metering device 80. If no fuel is to be delivered by the pump, the metering device 80 is closed so that it blocks the flow cross-section. If, due to leakage of the metering device, fuel still reaches the pump and is pumped through it, the excess fuel delivered can be discharged by suitable measures in the fuel injector.
  • an overflow valve are discharged by the pump from the pump too much subsidized fuel that is not supplied by the metering device 80 of the pump can.
  • the overflow valve is not arranged on the low pressure module 70, but for example on the feed pump.
  • the connecting piece 88 is arranged as the only hydraulic connection and the electrical connection 81 for the metering device 80 is provided. Other hydraulic connections, such as a return, are not provided.
  • the low-pressure module 70 can be placed in any rotational positions on the cylinder head 10 due to the circular cylindrical design of the projection 50 of the cylinder head 10, via the recess 74 and existing between this and the neck 50 of the cylinder head 10 annulus always a connection between the flow of the metering device 80 and the inlet valve 26 is present.
  • the pump is shown with the low pressure module 170 according to a second embodiment.
  • the cylinder head 10 of the pump is the same as in the first embodiment, but the low-pressure module 170 is formed differently and the metering device 180 is arranged differently.
  • the module housing 172 according to the second embodiment is flatter than in the first embodiment and has a flange 173 with an opening 174, wherein the module housing 172 is placed on the cylinder head 10 so that its opening 174 surrounds the projection 50 of the cylinder head 10. Laterally to the flange 173 then the module housing 172 has a projection 186, at the end in a bore 187 of the connecting piece 88 is used.
  • a further opening 178 is provided in the module housing 172, into which the metering device 80 is inserted.
  • the opening 178 is aligned with its longitudinal axis at least approximately parallel to the longitudinal axis of the opening 174.
  • the bore 187 is followed in the module housing 172 by a further bore 189, which opens into a piston 82 of the metering device 80 radially surrounding annular space 190.
  • a space 191 is formed, into which the outlet of the metering device 80 opens and which is connected to a bore 192 opening into the opening 174.
  • an annular space is formed between the projection 50 and the opening 174 in the flange 173 of the module housing 172.
  • a sealing element 76 is arranged between the flange 173 of the module housing 172 and the flange-like region 46 of the cylinder head 10.
  • a sealing element 193 for example in the form of a sealing ring arranged above the bore 64 in the projection 50 of the cylinder head 10 between the projection 50 and the opening 174 of the flange 173, a sealing element 193, for example in the form of a sealing ring arranged above the bore 64 in the projection 50 of the cylinder head 10 between the projection 50 and the opening 174 of the flange 173, a sealing element 193, for example in the form of a sealing ring arranged.
  • a sealing element 194 for example in the form of a sealing ring, is arranged between the closure screw 56 and the inner jacket of the extension 50.
  • the low-pressure module 170 can be connected as a result of the circular cylindrical design of the projection 50 of the cylinder head 10 in any rotational positions with the cylinder head 10. Irrespective of the rotational position of the low-pressure module 70, a connection between the bore 192 of the module housing 172 with the bore 64 of the projection 50 and thus with the inlet valve 26 is always present via the annular space present between the projection 50 and the opening 174 of the flange 173.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Pumpe, insbesondere Kraftstoffhochdruckpumpe, nach der Gattung des Anspruchs 1.The invention relates to a pump, in particular high-pressure fuel pump, according to the preamble of claim 1.

Eine solche Pumpe in Form einer Kraftstoffhochdruckpumpe ist durch die DE 10 2009 000 835 A1 bekannt. Diese Pumpe weist ein Gehäuseteil auf, in dem in einer Zylinderbohrung ein Pumpenkolben beweglich angeordnet ist, der in der Zylinderbohrung einen Pumpenarbeitsraum begrenzt. Die Pumpe weist ein Einlassventil auf, das im Gehäuseteil angeordnet ist und durch das der Pumpenarbeitsraum mit einem Zulauf für Fördermedium verbindbar ist. Im Zulauf ist eine Zumesseinrichtung vorgesehen, durch die die dem Pumpenarbeitsraum zugeführte Menge an Fördermedium variabel einstellbar ist. Der Zulauf verläuft teilweise durch ein Niederdruckmodul, in dem die Zumesseinrichtung angeordnet ist und das mit dem Gehäuseteil der Pumpe verbunden ist. Am Niederdruckmodul ist ein Anschluss für den Zulauf angeordnet, der beispielsweise von einer Förderpumpe zum Niederdruckmodul führen kann. Der Zulauf verläuft von der Zumesseinrichtung im Niederdruckmodul durch das Gehäuseteil der Pumpe zu dem im Gehäuseteil angeordneten Einlassventil. Das Gehäuseteil der Pumpe weist einen an die Zylinderbohrung anschließenden hohlzylinderförmigen Ansatz auf, in dem das Einlassventil mit dessen Ventilgehäuse angeordnet ist. Das Niederdruckmodul weist eine Ausnehmung auf, in die der Ansatz des Gehäuseteils hineinragt, wobei der Zulauf von der Zumesseinrichtung zum Einlassventil im hohlzylinderförmigen Ansatz verläuft. Das Ventilgehäuse des Einlassventils wird durch einen mit einer zentralen Öffnung versehenen Schraubring in den hohlzylinderförmigen Ansatz des Gehäuseteils gepresst, so dass der Pumpenarbeitsraum zum Ansatz hin abgedichtet wird. Durch den Ansatz und den Schraubring wird in der Ausnehmung des Niederdruckmoduls ein an den Ansatz anschließender Raum begrenzt, aus dem durch im Schraubring von dessen zentraler Öffnung ausgehend verlaufende Bohrungen Kraftstoff aus dem Raum zum Einlassventil gelangen kann. Diese Ausbildung ist nur verwendbar wenn der Raum, aus dem der Zulauf zum Einlassventil erfolgt, an den hohlzylinderförmigen Ansatz des Gehäuseteils anschließend angeordnet ist und dieser Raum durch die Ausnehmung des Niederdruckmoduls geschlossen ist, da dieser Raum und der hohlzylinderförmige Ansatz des Gehäuseteils durch den offenen Schraubring nicht verschlossen wird. Hierdurch benötigt die Pumpe einen großen Bauraum und ist aufwendig in der Herstellung.Such a pump in the form of a high-pressure fuel pump is through DE 10 2009 000 835 A1 known. This pump has a housing part in which a pump piston is movably arranged in a cylinder bore, which delimits a pump working chamber in the cylinder bore. The pump has an inlet valve which is arranged in the housing part and through which the pump working space can be connected to an inlet for conveying medium. In the inlet a metering device is provided, through which the pump working space supplied amount of conveying medium is variably adjustable. The inlet partially runs through a low-pressure module, in which the metering device is arranged and which is connected to the housing part of the pump. At the low pressure module, a connection for the inlet is arranged, which can lead, for example, from a feed pump to the low pressure module. The inlet runs from the metering device in the low-pressure module through the housing part of the pump to the inlet valve arranged in the housing part. The housing part of the pump has a subsequent to the cylinder bore hollow cylindrical projection, in which the inlet valve is arranged with the valve housing. The low-pressure module has a recess into which protrudes the projection of the housing part, wherein the inlet from the metering device to the inlet valve in the hollow-cylindrical projection extends. The valve housing of the inlet valve is pressed by a provided with a central opening screw ring into the hollow cylindrical projection of the housing part, so that the pump working space is sealed to the approach. Through the neck and the threaded ring In the recess of the low-pressure module, a space adjoining the projection is delimited, from which fuel can pass from the space to the inlet valve through bores extending from the central opening in the screw ring. This training is only usable if the space from which the inlet to the inlet valve takes place, is then arranged on the hollow cylindrical projection of the housing part and this space is closed by the recess of the low pressure module, since this space and the hollow cylindrical projection of the housing part through the open screw ring not closed. As a result, the pump requires a large space and is expensive to manufacture.

Offenbarung der ErfindungDisclosure of the invention Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Pumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass diese einfach, kostengünstig und mit kompakter Baugröße herstellbar ist, da der Zulauf zum Einlassventil aus dem den Außenmantel des hohlzylinderförmigen Ansatzes des Gehäuseteils angeordneten Ringraum erfolgt und der hohlzylinderförmige Ansatz nach außen durch die Verschlussschraube verschlossen ist.The pump according to the invention with the features of claim 1 has the advantage that it is simple, inexpensive and compact in size to produce, since the inlet to the inlet valve from the outer shell of the hollow cylindrical projection of the housing part arranged annulus takes place and the hollow cylindrical approach to the outside the screw plug is closed.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Pumpe angegeben. Durch die Ausbildung gemäß Anspruch 2 ist eine flexible Ausrichtung des Anschlusses für den Zulauf an der Pumpe ermöglicht. Die Ausbildung gemäß Anspruch 3 und insbesondere Anspruch 4 ermöglicht eine günstige Strömungsführung von der Zumesseinrichtung zum Einlassventil. Durch die Ausbildung gemäß Anspruch 5 ist ein geringes Gewicht und eine einfache Herstellung des Niederdruckmoduls und damit der Pumpe ermöglicht. Die Ausbildung gemäß Anspruch 7 ermöglicht eine günstige Strömungsführung im Niederdruckmodul vom Zulaufanschluss zur Zumesseinrichtung.In the dependent claims advantageous refinements and developments of the pump according to the invention are given. Due to the design according to claim 2, a flexible alignment of the connection for the inlet to the pump is made possible. The embodiment according to claim 3 and in particular claim 4 enables a favorable flow guidance from the metering device to the inlet valve. Due to the design according to claim 5, a low weight and a simple production of the low-pressure module and thus the pump is possible. The embodiment according to claim 7 enables a favorable flow guidance in the low-pressure module from the inlet connection to the metering device.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Pumpe in vereinfachter Darstellung in einem Längsschnitt mit einem dieser zugeordneten Niederdruckmodul gemäß einem ersten Ausführungsbeispiel, Figur 2 die Pumpe in einer Ansicht in Pfeilrichtung II in Figur 1 und Figur 3 die Pumpe mit dem Niederdruckmodul gemäß einem zweiten Ausführungsbeispiel.Two embodiments of the invention are illustrated in the drawing and explained in more detail in the following description. Show it FIG. 1 a simplified representation of a pump in a longitudinal section with one of these associated low-pressure module according to a first embodiment, FIG. 2 the pump in a view in the direction of arrow II in FIG. 1 and FIG. 3 the pump with the low pressure module according to a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist eine Pumpe dargestellt, die insbesondere eine Kraftstoffhochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine ist. Die Pumpe weist ein Gehäuseteil 10 auf, das nachfolgend als Zylinderkopf bezeichnet wird. Der Zylinderkopf 10 weist eine Zylinderbohrung 12 auf, in der ein Pumpenkolben 14 verschiebbar dicht geführt ist. Der Pumpenkolben 14 begrenzt mit seinem in die Zylinderbohrung 12 ragenden Ende einen Pumpenarbeitsraum 16. Das aus der Zylinderbohrung 12 ragende Ende des Pumpenkolbens 14 ist mit einer Übertragungseinrichtung beispielsweise in Form eines Rollenstößels 20 verbunden. Der Rollenstößel 20 stützt sich an einem Nocken 22 einer Antriebswelle 24 ab, durch den bei der Drehbewegung der Antriebswelle 24 eine Hubbewegung des Pumpenkolbens 14 in der Zylinderbohrung 12 bewirkt wird. Die Antriebswelle 24 kann Teil der Pumpe sein oder Teil der Brennkraftmaschine, beispielsweise deren Nockenwelle oder eine andere Welle.In FIG. 1 a pump is shown, which is in particular a high-pressure fuel pump for a fuel injection device of an internal combustion engine. The pump has a housing part 10, which is referred to below as the cylinder head. The cylinder head 10 has a cylinder bore 12 in which a pump piston 14 is displaceably guided. The pump piston 14 defines with its protruding into the cylinder bore 12 end of a pump working chamber 16. The protruding from the cylinder bore 12 end of the pump piston 14 is connected to a transmission device, for example in the form of a roller tappet 20. The roller tappet 20 is supported on a cam 22 of a drive shaft 24, through which a rotational movement of the pump piston 14 in the cylinder bore 12 is effected during the rotational movement of the drive shaft 24. The drive shaft 24 may be part of the pump or part of the internal combustion engine, such as the camshaft or another shaft.

Der Pumpenarbeitsraum 16 ist über ein Einlassventil 26 mit einem Niederdruckzulauf 27 zur Pumpe und über ein Auslassventil 28 mit einem Hochdruckablauf verbindbar, der beispielsweise zu einem Hochdruckspeicher 30 führt. Der Niederdruckzulauf 27 kann beispielsweise von einer Förderpumpe, die Kraftstoff aus einem Vorratsbehälter ansaugt, gespeist werden. Das Einlassventil 26 weist ein Ventilgehäuse 32 auf und ist als Rückschlagventil ausgebildet. Das Einlassventil 26 weist ein kolbenförmiges Ventilglied 34 auf, das über seinen Schaft 36 im Ventilgehäuse 32 geführt ist und das mit einer an seinem im Durchmesser gegenüber dem Schaft 36 vergrößerten Kopf 38 ausgebildeten Dichtfläche mit einem am Ventilgehäuse 32 ausgebildeten Ventilsitz zusammenwirkt. Das Ventilglied 34 ist durch eine Schließfeder 40 in Schließrichtung beaufschlagt.The pump working chamber 16 can be connected via an inlet valve 26 to a low-pressure inlet 27 to the pump and via an outlet valve 28 to a high-pressure outlet which leads, for example, to a high-pressure accumulator 30. The low-pressure inlet 27 can be fed, for example, from a feed pump, which sucks fuel from a reservoir. The inlet valve 26 has a valve housing 32 and is designed as a check valve. The inlet valve 26 has a piston-shaped valve member 34, which is guided via its shaft 36 in the valve housing 32 and which cooperates with a formed at its diameter in relation to the shaft 36 enlarged head 38 sealing surface with a valve housing 32 formed on the valve seat. The valve member 34 is acted upon by a closing spring 40 in the closing direction.

Der Zylinderkopf 10 ist in einer Aufnahme 44 eines Grundgehäuses der Pumpe oder eines Gehäuses der Brennkraftmaschine, beispielsweise deren Zylinderkopf oder Motorblock, eingesetzt, wobei die Aufnahme 44 beispielsweise als Bohrung ausgebildet ist. Der Zylinderkopf 10 weist dabei einen flanschartigen Bereich 46 auf, der einen größeren Querschnitt aufweist als die Aufnahme 44 und der auf der die Aufnahme 44 umgebenden Außenseite anliegt. An den flanschartigen Bereich 46 des Zylinderkopfs 10 schließt sich ein durch die Aufnahme 44 ragender Fortsatz 48 an, in dem die Zylinderbohrung 12 verläuft und aus dem das mit dem Rollenstößel 20 verbundene Ende des Pumpenkolbens 14 herausragt. Auf der dem Fortsatz 48 gegenüberliegenden Seite des flanschartigen Bereichs 48 schließt sich ein hohlzylinderförmiger Ansatz 50 am Zylinderkopf 10 an, der zumindest annähernd koaxial zur Zylinderbohrung 12 verläuft.The cylinder head 10 is inserted in a receptacle 44 of a basic housing of the pump or a housing of the internal combustion engine, for example, the cylinder head or engine block, wherein the receptacle 44 is formed for example as a bore. The cylinder head 10 in this case has a flange-like region 46, which has a larger cross section than the receptacle 44 and on which the receptacle 44 surrounding outside rests. To the flange-like portion 46 of the cylinder head 10, a projecting through the receptacle 44 extension 48 connects, in which the cylinder bore 12 extends and from which the connected to the roller tappet 20 end of the pump piston 14 protrudes. On the opposite side of the extension 48 of the flange-like portion 48, a hollow cylindrical projection 50 connects to the cylinder head 10, which extends at least approximately coaxial with the cylinder bore 12.

Das Ventilgehäuse 32 des Einlassventils 26 ist von der der Zylinderbohrung 12 abgewandten Außenseite her in den hohlzylinderförmigen Ansatz 50 eingesetzt, wobei das Ventilgehäuse 32 an einer am Übergang von der Zylinderbohrung 12 zum Ansatz 50 gebildeten Ringschulter 52 des Zylinderkopfs 10 anliegt. Von der Außenseite her ist in den Ansatz 50 eine Verschlussschraube 56 eingefügt, die ein Außengewinde aufweist, welches mit einem Innengewinde des Ansatzes 50 zusammenwirkt. Durch die Verschlussschraube 56 wird das Ventilgehäuse 32 gegen die Ringschulter 52 gepresst, um den Pumpenarbeitsraum 16 zum Ansatz 50 hin abzudichten. Gegebenenfalls kann zwischen dem Ventilgehäuse 32 und der Ringschulter 52 ein Dichtring angeordnet sein. Die Verschlussschraube 56 weist auf ihrer dem Ventilgehäuse 32 zugewandten Innenseite eine zentrale Ausnehmung 58 auf, in der das aus dem Ventilgehäuse 32 ragende Ende des Schafts 36 des Ventilglieds 34 und die Schließfeder 40 angeordnet sind.The valve housing 32 of the inlet valve 26 is inserted from the cylinder bore 12 facing away from the outside in the hollow cylindrical projection 50, wherein the valve housing 32 rests against an annular shoulder 52 of the cylinder head 10 formed at the transition from the cylinder bore 12 to the projection 50. From the outside, a closure screw 56 is inserted into the projection 50, which has an external thread which cooperates with an internal thread of the projection 50. By the screw plug 56, the valve housing 32 is pressed against the annular shoulder 52 to seal the pump working chamber 16 to the approach 50 out. Optionally, 52 may be disposed between the valve housing 32 and the annular shoulder a sealing ring. The closure screw 56 has, on its inner side facing the valve housing 32, a central recess 58 in which the end of the shaft 36 of the valve member 34 projecting from the valve housing 32 and the closing spring 40 are arranged.

Im Umfang des Ventilgehäuses 32 sind wenigstens eine oder vorzugsweise mehrere über den Umfang verteilt angeordnete Zulaufbohrungen 60 vorgesehen, durch die Kraftstoff in das Einlassventil 26 eintritt. Das Ventilgehäuse 32 ist im Ansatz 50 von einer Ringnut 62 umgeben, in die die Zulaufbohrungen 60 münden. Die Ringnut 62 ist mit dem Außenumfang des Ansatzes 50 über wenigstens eine durch den Ansatz 50 verlaufende Bohrung 64 verbunden.Provided in the circumference of the valve housing 32 are at least one or preferably a plurality of inlet bores 60 distributed over the circumference, through which fuel enters the inlet valve 26. The valve housing 32 is surrounded in the projection 50 by an annular groove 62, into which the inlet bores 60 open. The annular groove 62 is connected to the outer periphery of the lug 50 via at least one bore 64 extending through the lug 50.

Am Zylinderkopf 10 ist seitlich, zumindest annähernd senkrecht zur Längsachse 13 der Zylinderbohrung 12, ein Stutzen 66 ausgebildet, in dem das Auslassventil 28 angeordnet ist. Am Stutzen 66 ist eine zum Speicher 30 führende hydraulische Leitung anschließbar.On the cylinder head 10 is laterally, at least approximately perpendicular to the longitudinal axis 13 of the cylinder bore 12, a nozzle 66 is formed, in which the outlet valve 28 is arranged. At the nozzle 66 to the memory 30 leading hydraulic line can be connected.

In den Figuren 1 und 2 ist die Pumpe gemäß einem ersten Ausführungsbeispiel dargestellt. Für den Zylinderkopf 10 ist ein Niederdruckmodul 70 vorgesehen, durch das der Zulauf 27 zum Einlassventil 26 verläuft. Das Niederdruckmodul 70 weist ein Modulgehäuse 72 auf, das mit dem Zylinderkopf 10 verbunden ist und das auf den hohlzylinderförmigen Ansatz 50 des Zylinderkopfs 10 aufgesetzt ist. Das Modulgehäuse 72 ist aus einem Werkstoff mit geringem Gewicht, beispielsweise Leichtmetall wie Aluminium oder einer Aluminiumlegierung oder aus Kunststoff hergestellt. Das Modulgehäuse 72 weist eine näherungsweise zylindrische Form auf, wobei dieses auf den Ansatz 50 des Zylinderkopfs 10 aufgesetzt ist und eine den Ansatz 50 aufnehmende Ausnehmung 74 aufweist. Das Modulgehäuse 72 liegt am flanschartigen Bereich 46 des Zylinderkopfs 10 an und zwischen dem Modulgehäuse 72 und dem Bereich 46 ist ein Dichtelement 76, beispielsweise in Form eines Dichtrings, eingespannt. Das Modulgehäuse 72 kann beispielsweise auf den Zylinderkopf 10 aufgepresst oder mittels einer Rastverbindung oder über wenigstens eine oder mehrere Schrauben am Zylinderkopf 10 befestigt sein.In the FIGS. 1 and 2 the pump is shown according to a first embodiment. For the cylinder head 10, a low pressure module 70 is provided, through which the inlet 27 extends to the inlet valve 26. The low-pressure module 70 has a module housing 72, which is connected to the cylinder head 10 and which is placed on the hollow cylindrical projection 50 of the cylinder head 10. The module housing 72 is made of a lightweight material such as light metal such as aluminum or an aluminum alloy or plastic. The module housing 72 has an approximately cylindrical shape, which is placed on the projection 50 of the cylinder head 10 and has a projection 50 receiving recess 74. The module housing 72 bears against the flange-like region 46 of the cylinder head 10 and between the module housing 72 and the region 46 a sealing element 76, for example in the form of a sealing ring, is clamped. The module housing 72 may, for example, be pressed onto the cylinder head 10 or fastened to the cylinder head 10 by means of a latching connection or via at least one or more screws.

An die Ausnehmung 74 schließt sich im Modulgehäuse 72 eine Öffnung 78 an, in die eine Zumesseinrichtung 80 eingesetzt ist, die dazu dient die dem Einlassventil 26 zugeführte Kraftstoffmenge variabel einstellen zu können. Die Zumesseinrichtung 80 ist beispielsweise als Proportionalventil ausgebildet, durch das unterschiedlich große Durchflussquerschnitte eingestellt werden können. Die Zumesseinrichtung 80 weist ein Gehäuse auf, in dem ein Kolben 82 angeordnet ist, durch den der Durchflussquerschnitt zwischen einem in die Zumesseinrichtung 80 mündenden Zulauf und einem von dieser abführenden Ablauf eingestellt wird. Der Kolben 82 ist mittels eines elektrischen Aktors 84, beispielsweise eines Elektromagneten, gegen eine Feder 85 verschiebbar. Abhängig von der Stellung des Kolbens 82 werden durch diesen unterschiedlich große Durchflussquerschnitte eingestellt. Der Zulauf in die Zumesseinrichtung 80 erfolgt zumindest annähernd radial zur Längsachse 83 des Kolbens 82 und der Ablauf führt zumindest annähernd koaxial zur Längsachse 83 des Kolbens 82 von der Zumesseinrichtung 80 ab und mündet in der Ausnehmung 74 des Modulgehäuses 72. Zwischen dem Außenumfang des Ansatzes 50 des Zylinderkopfs 10 und der Ausnehmung 74 ist ein Ringraum gebildet, so dass Kraftstoff von der Ausnehmung 74 über die Bohrung 64 im Ansatz 50 zum Einlassventil 26 gelangen kann. An der Zumesseinrichtung 80 ist ein elektrischer Anschluss 81 zur Verbindung mit einer elektronischen Steuereinrichtung angeordnet, durch die der Aktor 84 angesteuert wird. Bei mit dem Zylinderkopf 10 verbundenem Niederdruckmodul 70 ist die Zumesseinrichtung 80 so angeordnet, dass die Längsachse 83 von deren Kolben 82 zumindest annähernd koaxial zur Zylinderbohrung 12 verläuft.Adjoining the recess 74 in the module housing 72 is an opening 78 into which a metering device 80 is inserted which serves to be able to variably set the amount of fuel supplied to the inlet valve 26. The metering device 80 is designed, for example, as a proportional valve, by means of which flow cross sections of different sizes can be set. The metering device 80 has a housing in which a piston 82 is arranged, through which the flow cross-section is set between an inlet opening into the metering device 80 and a drain discharging therefrom. The piston 82 is displaceable against a spring 85 by means of an electrical actuator 84, for example an electromagnet. Depending on the position of the piston 82 are set by this differently sized flow cross sections. The feed into the metering device 80 takes place at least approximately radially to the longitudinal axis 83 of the piston 82 and the drain at least approximately coaxial with the longitudinal axis 83 of the piston 82 of the metering device 80 and opens into the recess 74 of the module housing 72. Between the outer periphery of the neck 50 of the cylinder head 10 and the recess 74 an annular space is formed so that fuel from the recess 74 on the Bore 64 in approach 50 can reach the inlet valve 26. At the metering device 80, an electrical terminal 81 is arranged for connection to an electronic control device, by which the actuator 84 is driven. When connected to the cylinder head 10 low-pressure module 70, the metering device 80 is arranged so that the longitudinal axis 83 of the piston 82 at least approximately coaxial with the cylinder bore 12 extends.

Das Modulgehäuse 72 weist einen zumindest annähernd radial zur Ausnehmung 74 nach außen ragenden Vorsprung 86 mit einer Bohrung 87 auf. In die Bohrung 87 ist ein Anschlussstutzen 88 eingefügt, beispielsweise eingepresst. Am Anschlussstutzen 88 ist eine hydraulische Leitung anschließbar, die beispielsweise von einer Förderpumpe zum Niederdruckmodul 70 führt. Die Bohrung 87 im Modulgehäuse 72 ist über eine weitere Bohrung 89 mit der Zumesseinrichtung 80 verbunden, wobei die weitere Bohrung 89 in einem den Kolben 82 der Zumesseinrichtung 80 umgebenden Ringraum 90 im Modulgehäuse 72 mündet. Der Ringraum 90 und die Bohrung 87 können dabei in Richtung der Längsachse 83 des Kolbens 82 zueinander versetzt angeordnet sein, so dass die weitere Bohrung 89 entsprechend schräg im Modulgehäuse 72 verläuft.The module housing 72 has an at least approximately radially to the recess 74 outwardly projecting projection 86 with a bore 87. In the bore 87, a connecting piece 88 is inserted, for example, pressed. At the connecting piece 88, a hydraulic line can be connected, which leads, for example, from a feed pump to the low-pressure module 70. The bore 87 in the module housing 72 is connected via a further bore 89 with the metering device 80, wherein the further bore 89 opens in a surrounding the piston 82 of the metering device 80 annular space 90 in the module housing 72. The annular space 90 and the bore 87 can be arranged offset to one another in the direction of the longitudinal axis 83 of the piston 82, so that the further bore 89 extends correspondingly obliquely in the module housing 72.

Im Betrieb der Pumpe gelangt Kraftstoff beispielsweise von einer Förderpumpe gefördert aus einem Vorratsbehälter über den Anschlussstutzen 88 in die Bohrung 87 im Modulgehäuse 72 und von dort über die weitere Bohrung 89 in den Ringraum 90. Vom Ringraum 90 gelangt der Kraftstoff über den vom Kolben 82 der Zumesseinrichtung 80 eingestellten Durchflussquerschnitt und durch den Kolben 82 in die Ausnehmung 74 und von dieser über die Bohrung 64 und die Zulaufbohrungen 60 im Ventilgehäuse 32 zum Einlassventil 26. Durch die koaxiale Anordnung des Kolbens 82 der Zumesseinrichtung 80 zum Einlassventil 26, das wiederum koaxial zur Zylinderbohrung 12 angeordnet ist, wird eine günstige Einströmung des Kraftstoffs erreicht. Beim Saughub des Pumpenkolbens 14 öffnet das Einlassventil 26, so dass Kraftstoff in den Pumpenarbeitsraum 16 einströmt. Die beim Saughub des Pumpenkolbens 14 über das Einlassventil 26 in den Pumpenarbeitsraum 16 einströmende Kraftstoffmenge ist abhängig von dem durch den Kolben 82 der Zumesseinrichtung 80 eingestellten Durchflussquerschnitt. Wenn durch die Pumpe kein Kraftstoff gefördert werden soll, so wird die Zumesseinrichtung 80 geschlossen, so dass diese den Durchflussquerschnitt sperrt. Sollte infolge einer Leckage der Zumesseinrichtung dennoch Kraftstoff zur Pumpe gelangen und durch diese gefördert werden, so kann durch geeignete Maßnahmen in der Kraftstoffeinspritzeinrichtung der zu viel geförderte Kraftstoff abgeleitet werden. Gegebenenfalls kann zwischen der Förderpumpe, durch die Kraftstoff aus dem Vorratsbehälter zum Niederdruckmodul 70 gefördert wird, und dem Niederdruckmodul 70 ein Überströmventil angeordnet sein, durch das von der Förderpumpe zu viel geförderter Kraftstoff, der nicht durch die Zumesseinrichtung 80 der Pumpe zugeführt wird, abgeleitet werden kann. Das Überströmventil ist dabei nicht am Niederdruckmodul 70 angeordnet, sondern beispielsweise an der Förderpumpe.During operation of the pump fuel passes, for example, from a supply pump from a reservoir via the connecting piece 88 into the bore 87 in the module housing 72 and from there via the further bore 89 in the annular space 90. From the annular space 90 of the fuel passes through the piston 82 of the The coaxial arrangement of the piston 82 of the metering device 80 to the inlet valve 26, which in turn is coaxial with the cylinder bore 12 is arranged, a favorable inflow of the fuel is achieved. During the suction stroke of the pump piston 14, the inlet valve 26 opens, so that fuel flows into the pump working chamber 16. During the suction stroke of the pump piston 14 via the inlet valve 26 in The amount of fuel flowing into the pump working chamber 16 depends on the flow cross section set by the piston 82 of the metering device 80. If no fuel is to be delivered by the pump, the metering device 80 is closed so that it blocks the flow cross-section. If, due to leakage of the metering device, fuel still reaches the pump and is pumped through it, the excess fuel delivered can be discharged by suitable measures in the fuel injector. Optionally, between the feed pump, is conveyed by the fuel from the reservoir to the low-pressure module 70, and the low-pressure module 70, an overflow valve, are discharged by the pump from the pump too much subsidized fuel that is not supplied by the metering device 80 of the pump can. The overflow valve is not arranged on the low pressure module 70, but for example on the feed pump.

Am Niederdruckmodul 70 ist als einziger hydraulischer Anschluss der Anschlussstutzen 88 angeordnet sowie der elektrische Anschluss 81 für die Zumesseinrichtung 80 vorgesehen. Weitere hydraulische Anschlüsse, beispielsweise für einen Rücklauf, sind nicht vorgesehen. Das Niederdruckmodul 70 kann infolge der kreiszylinderförmigen Ausbildung des Ansatzes 50 des Zylinderkopfs 10 in beliebigen Drehstellungen auf den Zylinderkopf 10 aufgesetzt werden, wobei über die Ausnehmung 74 und den zwischen dieser und dem Ansatz 50 des Zylinderkopfs 10 vorhandenen Ringraum stets eine Verbindung zwischen dem Ablauf der Zumesseinrichtung 80 und dem Einlassventil 26 vorhanden ist.At the low-pressure module 70, the connecting piece 88 is arranged as the only hydraulic connection and the electrical connection 81 for the metering device 80 is provided. Other hydraulic connections, such as a return, are not provided. The low-pressure module 70 can be placed in any rotational positions on the cylinder head 10 due to the circular cylindrical design of the projection 50 of the cylinder head 10, via the recess 74 and existing between this and the neck 50 of the cylinder head 10 annulus always a connection between the flow of the metering device 80 and the inlet valve 26 is present.

In Figur 3 ist die Pumpe mit dem Niederdruckmodul 170 gemäß einem zweiten Ausführungsbeispiel dargestellt. Der Zylinderkopf 10 der Pumpe ist gleich ausgebildet wie beim ersten Ausführungsbeispiel, jedoch ist das Niederdruckmodul 170 anders ausgebildet und die Zumesseinrichtung 180 ist anders angeordnet. Das Modulgehäuse 172 gemäß dem zweiten Ausführungsbeispiel ist flacher ausgebildet als beim ersten Ausführungsbeispiel und weist einen Flansch 173 mit einer Öffnung 174 auf, wobei das Modulgehäuse 172 so auf den Zylinderkopf 10 aufgesetzt ist, dass dessen Öffnung 174 den Ansatz 50 des Zylinderkopfs 10 umgibt. Seitlich an den Flansch 173 anschließend weist das Modulgehäuse 172 einen Vorsprung 186 auf, an dessen Ende in eine Bohrung 187 der Anschlussstutzen 88 eingesetzt ist. Zwischen dem Anschlussstutzen 88 und dem Flansch 173 ist im Modulgehäuse 172 eine weitere Öffnung 178 vorgesehen, in die die Zumesseinrichtung 80 eingesetzt ist. Die Öffnung 178 ist mit ihrer Längsachse zumindest annähernd parallel zur Längsachse der Öffnung 174 ausgerichtet. An die Bohrung 187 schließt sich im Modulgehäuse 172 eine weitere Bohrung 189 an, die in einen den Kolben 82 der Zumesseinrichtung 80 radial umgebenden Ringraum 190 mündet. Zwischen der Zumesseinrichtung 80 und dem Modulgehäuse 172 ist ein Raum 191 gebildet, in den der Ablauf der Zumesseinrichtung 80 mündet und der mit einer in die Öffnung 174 mündenden Bohrung 192 verbunden ist. Zwischen dem Ansatz 50 und der Öffnung 174 im Flansch 173 des Modulgehäuses 172 ist ein Ringraum gebildet.In FIG. 3 the pump is shown with the low pressure module 170 according to a second embodiment. The cylinder head 10 of the pump is the same as in the first embodiment, but the low-pressure module 170 is formed differently and the metering device 180 is arranged differently. The module housing 172 according to the second embodiment is flatter than in the first embodiment and has a flange 173 with an opening 174, wherein the module housing 172 is placed on the cylinder head 10 so that its opening 174 surrounds the projection 50 of the cylinder head 10. Laterally to the flange 173 then the module housing 172 has a projection 186, at the end in a bore 187 of the connecting piece 88 is used. Between the connecting piece 88 and the flange 173, a further opening 178 is provided in the module housing 172, into which the metering device 80 is inserted. The opening 178 is aligned with its longitudinal axis at least approximately parallel to the longitudinal axis of the opening 174. The bore 187 is followed in the module housing 172 by a further bore 189, which opens into a piston 82 of the metering device 80 radially surrounding annular space 190. Between the metering device 80 and the module housing 172, a space 191 is formed, into which the outlet of the metering device 80 opens and which is connected to a bore 192 opening into the opening 174. Between the projection 50 and the opening 174 in the flange 173 of the module housing 172, an annular space is formed.

Zwischen dem Flansch 173 des Modulgehäuses 172 und dem flanschartigen Bereich 46 des Zylinderkopfs 10 ist ein Dichtelement 76 angeordnet. Außerdem ist oberhalb der Bohrung 64 im Ansatz 50 des Zylinderkopfs 10 zwischen dem Ansatz 50 und der Öffnung 174 des Flanschs 173 ein Dichtelement 193, beispielsweise in Form eines Dichtrings, angeordnet. Weiterhin ist zwischen der Verschlussschraube 56 und dem Innenmantel des Ansatzes 50 ein Dichtelement 194, beispielsweise in Form eines Dichtrings, angeordnet. Somit ist der Übergang zwischen dem Zylinderkopf 10 und dem Niederdruckmodul sowie das Einlassventil 26 nach außen abgedichtet.Between the flange 173 of the module housing 172 and the flange-like region 46 of the cylinder head 10, a sealing element 76 is arranged. In addition, above the bore 64 in the projection 50 of the cylinder head 10 between the projection 50 and the opening 174 of the flange 173, a sealing element 193, for example in the form of a sealing ring arranged. Furthermore, a sealing element 194, for example in the form of a sealing ring, is arranged between the closure screw 56 and the inner jacket of the extension 50. Thus, the transition between the cylinder head 10 and the low pressure module and the inlet valve 26 is sealed to the outside.

Das Niederdruckmodul 170 kann infolge der kreiszylinderförmigen Ausbildung des Ansatzes 50 des Zylinderkopfs 10 in beliebigen Drehstellungen mit dem Zylinderkopf 10 verbunden werden. Über den zwischen dem Ansatz 50 und der Öffnung 174 des Flanschs 173 vorhandenen Ringraum ist unabhängig von der Drehstellung des Niederdruckmoduls 70 stets eine Verbindung zwischen der Bohrung 192 des Modulgehäuses 172 mit der Bohrung 64 des Ansatzes 50 und somit dem Einlassventil 26 vorhanden.The low-pressure module 170 can be connected as a result of the circular cylindrical design of the projection 50 of the cylinder head 10 in any rotational positions with the cylinder head 10. Irrespective of the rotational position of the low-pressure module 70, a connection between the bore 192 of the module housing 172 with the bore 64 of the projection 50 and thus with the inlet valve 26 is always present via the annular space present between the projection 50 and the opening 174 of the flange 173.

Claims (8)

  1. Pump, in particular high-pressure fuel pump, having a housing part (10) in which a pump piston (14) is arranged in movable fashion in a cylinder bore (12), which pump piston delimits a pump working chamber (16) in the cylinder bore (12), having an inlet valve (26) which is arranged in the housing part (10) and by means of which the pump working chamber (16) is connectable to a feed line (27), wherein, in the feed line (27), there is arranged a metering device (80) by means of which the quantity of medium for conveying which is fed to the pump working chamber (16) can be variably adjusted, wherein the feed line (27) runs at least partially in a low-pressure module (70; 170) connected to the pump, and the metering device (80) is arranged on the low-pressure module (70), wherein the housing part (10) has a hollow cylindrical projection (50) which adjoins the cylinder bore (12) and in which the inlet valve (26) is arranged, wherein the low-pressure module (70; 170) is mounted onto the hollow cylindrical projection (50) of the housing part (10), wherein the feed line runs from the metering device (80) to the inlet valve (26) through the hollow cylindrical projection (50), wherein the inlet valve (26) has a valve housing (32) which is inserted into the hollow cylindrical projection (50) and which is pressed by means of a screw (56) into the hollow cylindrical projection (50) such that the pump working chamber (16) is sealed off in the direction of the hollow cylindrical projection (50), and wherein the low-pressure module (70; 170) has a recess (74; 174) into which the hollow cylindrical projection (50) of the housing part (10) projects, characterized in that the screw (56) is a closure screw (56) and in that a ring-shaped chamber is formed between the outer circumference of the hollow cylindrical projection (50) and the recess (74; 174) of the low-pressure module (70; 170), such that fuel can pass from the recess (74; 174) to the inlet valve (26) via the at least one bore (64) which runs through the hollow cylindrical projection (50).
  2. Pump according to Claim 1, characterized in that the low-pressure module (70) can be mounted in any desired rotational positions on the hollow cylindrical rejection (50) of the housing part (10).
  3. Pump according to Claim 1 or 2, characterized in that the metering device (80) has a displaceably guided piston (82) by means of which the throughflow cross section in the feed line (27) can be variably adjusted, and in that the metering device (80) is arranged such that, when the low-pressure module (70) has been mounted onto the projection (50), the longitudinal axis (83) of the piston (82) of said low-pressure module runs at least approximately parallel to the longitudinal axis (13) of the cylinder bore (12) of the housing part (10).
  4. Pump according to Claim 3, characterized in that the metering device (80) is arranged such that, when the low-pressure module (70) has been mounted onto the projection (50), the longitudinal axis (83) of the piston (82) of said low-pressure module runs at least approximately coaxially with respect to the longitudinal axis (13) of the cylinder bore (12) of the housing part (10).
  5. Pump according to any of the preceding claims, characterized in that the low-pressure module (70) has a module housing (72) which is produced from light metal or plastic.
  6. Pump according to any of the preceding claims, characterized in that, on the low-pressure module (70), there is provided a single external hydraulic port (88) by means of which the feed line (27) is connected to the low-pressure module (70).
  7. Pump according to Claim 6, characterized in that the external hydraulic port (88) is arranged such that its longitudinal axis runs at least approximately perpendicular to the longitudinal axis (83) of the piston (82) of the metering device (80).
  8. Pump according to Claim 7, characterized in that the feed line, from the piston (82) of the metering device (80) to the inlet valve (26), runs at least approximately in the direction of the longitudinal axis (83) of the piston (82).
EP14742485.7A 2013-08-30 2014-07-17 Pump, in particular a high-pressure fuel pump Not-in-force EP3039282B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310217357 DE102013217357A1 (en) 2013-08-30 2013-08-30 Pump, in particular a high-pressure fuel pump
PCT/EP2014/065390 WO2015028196A1 (en) 2013-08-30 2014-07-17 Pump, in particular a high-pressure fuel pump

Publications (2)

Publication Number Publication Date
EP3039282A1 EP3039282A1 (en) 2016-07-06
EP3039282B1 true EP3039282B1 (en) 2019-02-27

Family

ID=51224919

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14742485.7A Not-in-force EP3039282B1 (en) 2013-08-30 2014-07-17 Pump, in particular a high-pressure fuel pump

Country Status (5)

Country Link
EP (1) EP3039282B1 (en)
JP (1) JP6175567B2 (en)
CN (1) CN105492756B (en)
DE (1) DE102013217357A1 (en)
WO (1) WO2015028196A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11713755B2 (en) 2016-07-08 2023-08-01 Delphi Technologies Ip Limited High-pressure fuel pump

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009000835A1 (en) * 2009-02-13 2010-08-19 Robert Bosch Gmbh Modular low pressure unit and modular pump arrangement

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0816672B1 (en) * 1996-07-05 2003-04-09 Nippon Soken, Inc. High-pressure pump
JP2003120468A (en) * 2001-10-15 2003-04-23 Bosch Automotive Systems Corp Liquid fuel flow rate regulating valve, and fuel injection system of internal combustion engine having the liquid fuel flow rate regulating valve
JP4221760B2 (en) * 2005-01-17 2009-02-12 株式会社デンソー High pressure fuel pump
DE102006061558A1 (en) * 2006-12-27 2008-07-03 Robert Bosch Gmbh Fuel delivery device for internal combustion engine of motor vehicle, has adjustable throttle device arranged upstream to suction valve, where outlet of throttle device is arranged directly proximate to suction valve
DE102007038984A1 (en) * 2007-08-17 2009-02-19 Robert Bosch Gmbh Fuel pump for a fuel system of an internal combustion engine
US7677872B2 (en) * 2007-09-07 2010-03-16 Gm Global Technology Operations, Inc. Low back-flow pulsation fuel injection pump
JP4985476B2 (en) * 2008-03-04 2012-07-25 株式会社デンソー Check valve for fuel supply pump
GB0812888D0 (en) * 2008-07-15 2008-08-20 Delphi Tech Inc Improvements relating to fuel pumps
JP2010112304A (en) * 2008-11-07 2010-05-20 Bosch Corp Fuel supply pump
DE102009000857A1 (en) * 2009-02-13 2010-08-19 Robert Bosch Gmbh Pump arrangement for use in fuel injection system of air-compressed, self-igniting internal combustion engine, has suction valve for filling pump operating chamber of pump component with diesel fuel from recess of housing
JP5187255B2 (en) * 2009-03-27 2013-04-24 株式会社デンソー High pressure pump
DE102011087701A1 (en) 2011-12-05 2013-06-06 Robert Bosch Gmbh Low pressure unit for a pump, in particular a high-pressure fuel pump of a fuel injection device

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009000835A1 (en) * 2009-02-13 2010-08-19 Robert Bosch Gmbh Modular low pressure unit and modular pump arrangement

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11713755B2 (en) 2016-07-08 2023-08-01 Delphi Technologies Ip Limited High-pressure fuel pump

Also Published As

Publication number Publication date
CN105492756B (en) 2019-03-08
EP3039282A1 (en) 2016-07-06
CN105492756A (en) 2016-04-13
JP2016532815A (en) 2016-10-20
WO2015028196A1 (en) 2015-03-05
DE102013217357A1 (en) 2015-03-05
JP6175567B2 (en) 2017-08-02

Similar Documents

Publication Publication Date Title
EP1931875B1 (en) High pressure pump, in particular for a fuel injection device of an internal combustion engine
EP2798191B1 (en) Fuel overflow valve for a fuel injection device, and fuel injection device comprising fuel overflow valve
EP1636488B1 (en) Check valve, especially for a high pressure pump of a fuel injection device for an internal combustion engine
WO2013083517A1 (en) Low-pressure unit for a pump, in particular a fuel high-pressure pump of a fuel injection device
EP1784571B1 (en) High-pressure pump for a fuel injection device of an internal combustion engine
EP2561213B1 (en) High pressure pump
DE102011089857A1 (en) Pump, in particular high-pressure fuel pump for a fuel injection device
EP3189227B1 (en) High-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine
EP1736662B1 (en) Check valve, especially for a high pressure pump of a fuel injection device for an internal combustion engine
DE102008041594A1 (en) Fuel high pressure pump i.e. plug-in pump, for internal combustion engine, has cylindrical pump housing, piston, conveyor chamber, inlet valve and outlet valve, where outlet valve and piston longitudinal axis are parallel to each other
EP3039282B1 (en) Pump, in particular a high-pressure fuel pump
EP2795094B1 (en) Pump, in particular high-pressure fuel pump for a fuel injection device
EP3061967B1 (en) Pump, in particular high-pressure fuel pump
DE102013210957A1 (en) Controllable suction valve for a high-pressure pump
DE102010063398A1 (en) Fuel conveying device for fuel injector of internal combustion engine, has pressure reduction device provided in form of venturi tube in by-pass pipe, where venturi tube is formed in hollow screw screwed into housing portion
DE102012215068A1 (en) Cylinder head for one pump, in particular high-pressure fuel pump, and pump with cylinder head
EP3054144A1 (en) Relief valve for a high-pressure pump, in particular plug-in pump, and high pressure pump with such a relief valve
DE102013212479A1 (en) Inlet valve for one pump and pump with inlet valve
EP3034858B1 (en) Relief valve for a fuel pump
DE102008001824A1 (en) Pump, particularly high pressure fuel pump for fuel injection device of internal-combustion engine, has non-return valve that has cup-shaped valve housing
DE102012221611A1 (en) Pump e.g. high-pressure fuel pump for fuel injector of internal combustion engine, has housing portion that is fastened at support element by attachment element such that other housing portion is held on support element
DE102013204897A1 (en) Pump, in particular high-pressure fuel pump for a fuel injection device
WO2013037543A1 (en) Pump, in particular a high-pressure fuel pump
DE102013210041A1 (en) High pressure pump for a fuel injection system
WO2019015878A1 (en) Check valve, in particular for a high-pressure fuel pump, and pump comprising a check 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: 20160330

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: 20170616

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: 20181012

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: AT

Ref legal event code: REF

Ref document number: 1101709

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190315

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: 502014010956

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190227

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: 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: 20190227

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: 20190227

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: 20190227

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: 20190527

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: 20190627

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: 20190227

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: 20190627

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: 20190227

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: 20190227

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: 20190527

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: 20190528

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: 20190227

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: 20190227

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: 20190227

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: 20190227

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: 20190227

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: 20190227

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: 20190227

Ref country code: IT

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: 20190227

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: 20190227

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502014010956

Country of ref document: DE

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

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: 20190227

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: 20190227

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

26N No opposition filed

Effective date: 20191128

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: 20190227

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: 20190227

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Effective date: 20190717

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: 20190227

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190731

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: 20190717

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: 20190731

Ref country code: CH

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

Effective date: 20190731

Ref country code: LU

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

Effective date: 20190717

Ref country code: BE

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

Effective date: 20190731

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: 20190731

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: 20190717

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1101709

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190717

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: 20190717

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: 20190227

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: 20190227

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: 20140717

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

Ref country code: DE

Payment date: 20210924

Year of fee payment: 8

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: 20190227

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502014010956

Country of ref document: DE

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: 20230201