EP2627903A1 - High-pressure pump for a fuel injection device - Google Patents

High-pressure pump for a fuel injection device

Info

Publication number
EP2627903A1
EP2627903A1 EP11754404.9A EP11754404A EP2627903A1 EP 2627903 A1 EP2627903 A1 EP 2627903A1 EP 11754404 A EP11754404 A EP 11754404A EP 2627903 A1 EP2627903 A1 EP 2627903A1
Authority
EP
European Patent Office
Prior art keywords
tappet
pressure pump
eccentric
pump
pump according
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.)
Granted
Application number
EP11754404.9A
Other languages
German (de)
French (fr)
Other versions
EP2627903B1 (en
Inventor
Alfons Schoetz
Markus Schetter
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 EP2627903A1 publication Critical patent/EP2627903A1/en
Application granted granted Critical
Publication of EP2627903B1 publication Critical patent/EP2627903B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the present invention relates to a high pressure pump of a fuel injection device, which can be used in particular for a common rail injection device of an internal combustion engine.
  • the high-pressure pump comprises a pump or drive shaft, which is rotationally rigidly connected to an eccentric and is in operative connection with a pump element.
  • the one bucket tappet, an element piston and a plunger spring enclosing pump element is associated with a housing bore of an engine block.
  • the element piston which is drive-connected to the eccentric via the cup tappet and can be moved in a cylinder bore, delimits a pump working chamber connected to a suction valve and a high-pressure valve.
  • Such high-pressure pumps are used in motor vehicle construction in order to achieve a necessary volume flow and required fluid pressure for a common-rail system.
  • the high-pressure pump is subject to heavy loads, in particular mechanical stresses, so that high demands are placed on the material and on the construction.
  • the bucket tappet operatively connected to an eccentric or a cam track effects a conversion from the rotational movement of the drive shaft into an oscillating stroke movement of an element or pump piston.
  • the lifting movement of the element piston can be divided into a suction and compression stroke.
  • fuel is sucked into a pump working space via a suction valve.
  • the fuel is compressed and conveyed via an open high-pressure valve in a memory (rail).
  • DE 101 57 076 A1 discloses a plunger piston for a high-pressure pump with a plunger, which includes an axially and radially guided roller and a piston fixedly connected to the plunger. To guide the roller on the plunger it is provided with a roller shoe in which the roller is rotatable and inserted with an axial play.
  • a high-pressure pump which has a drive shaft with eccentric, which cooperates with a pump element. Between the element piston and the eccentric, a support element or a roller shoe is arranged, in which a rotatably mounted, rolling on the eccentric roller is inserted.
  • a relatively large amount of wear due to increased friction between the directly operatively connected components arises.
  • the increased friction affects the rotational movement of the roller, whereby slippage between the roller and the eccentric can occur and the wear increases.
  • the object of the invention is to provide a high-pressure pump with a simplified, robust and friction-optimized drive connection between the eccentric and the bucket tappet, which withstands high mechanical loads and is easy to produce.
  • a drive connection between the bucket tappet and the eccentric comprises a rotatably mounted on the eccentric race on which the bucket tappet is non-positively supported.
  • the tappet is thus drivingly connected via the rotatably mounted race indirectly to the eccentric.
  • the eccentric enclosing and a relative movement to the eccentric exercising race advantageously causes a decoupled drive connection or power transmission between the tappet and the eccentric.
  • This arrangement reduces the transverse force absorption of the bucket tappet and consequently advantageously reduced lateral or transverse forces can be realized by the bucket tappet in its guide on the housing bore.
  • the inventive concept provides a simplified and robust drive connection between the eccentric and bucket tappets, the advantageous heavy loads, in particular mechanical stresses withstand, which has a positive effect on the life.
  • the friction-optimized drive connection is also independent of friction conditions, which were to be considered in previous solutions between a bucket tappet and eccentric, for example between a roller and an eccentric.
  • the inventive robust drive connection is insensitive to different
  • a further advantage of the invention is that the drive connection according to the invention can be transferred both to high-pressure pumps with a 1-fold cam system or eccentric system and to high-pressure pumps with a 2-fold cam system.
  • the friction connection according to the invention advantageously results in reduced friction.
  • the invention can advantageously be realized a permanent drive connection between the eccentric and the bucket tappet, which can also be used for highly dynamic systems with correspondingly high pump pressures and pump speeds.
  • the concept according to the invention which can be implemented easily, ensures reliable, precise operation, combined with low wear, which results in an overall increase in efficiency.
  • a preferred embodiment of the invention provides that the bucket tappet on the drive side is associated with a designated also as a force receiving device sliding plate.
  • the preferably pressed into the cup tappet and fixed in position sliding plate is supported with a contact surface on the associated contact surface of the eccentric enclosing race, wherein the contact surfaces together form a contact zone.
  • the sliding plate is made of a material adapted to the given loads and lubricant conditions. To achieve a high wear resistance, it makes sense, for example, to produce the sliding plate made of hard metal or a ceramic material.
  • the tappet with integrated sliding plate is further characterized by a simplified and component-optimized
  • the tappet advantageously requires neither a position-oriented mounting position nor an anti-twist device, which simplifies assembly.
  • the inventive simplified and cost-optimized bucket tappet concept also offers a cost advantage over known solutions of tappets with roller shoe and integrated role.
  • the race is rotatably mounted on the eccentric shaft via a rolling bearing or sliding bearing.
  • a rolling bearing or sliding bearing By the use of commercial Wälz- or Plain bearings can be a robust, proven and inexpensive storage of the race on the eccentric shaft can be realized.
  • roller bearings are preferably cylindrical roller bearings, since the storage has to absorb any axial forces. Due to the small radial space required, it is preferable to use needle bearings for the bearing of the race.
  • Another particular embodiment of the invention is characterized in that at least one of the mutually facing contact surfaces of the sliding plate and the race is slightly convex or convex. This measure advantageously compensates for slight angular errors that can occur during production due to permissible position and / or shape tolerances.
  • the convexity also serves to reduce the contact area between the slide plate and the raceway to line contact, thereby advantageously reducing friction.
  • the invention further includes a coating of at least one contact surface with a friction-reducing material.
  • the high pressure pump designed as a plug-in pump is used as a structural unit with a plug-in pump body in a housing bore of the engine block.
  • a cylinder bore is introduced, which is intended to guide the element piston and at the same time forms the pump working space.
  • the structural design of the invention further includes different solutions for guiding the bucket tappet.
  • An outer guide of the tappet is preferred, in which a tappet body of the tappet is guided over a lateral surface in the housing bore of the engine block. This outer guide of the tappet prevents deformation of the guide of the element piston in the shaft portion.
  • a space-optimized arrangement of the plunger spring is also provided for the designed as a plug-pump high-pressure pump.
  • the plunger spring is supported on an integrated inside the cup tappet spring plate, wherein the plunger spring is guided over a greater length within the plunger body. The mutual spring end of the plunger spring is enclosed for guiding by a board of the plug-in pump body.
  • At least one preferably circumferential lubrication groove is introduced in a lateral surface of the tappet body, which are connected via associated passage bores with a plunger interior.
  • This measure has the effect that a lubricant, in particular the fuel delivered by the high-pressure pump, enters the annular gap which is established between the housing bore of the engine block and the lateral surface of the cup tappet.
  • the lubricant passes for cooling and lubrication in the defined by the race and the sliding plate contact zone of the drive connection between the eccentric and the bucket tappet.
  • the sliding plate of the tappet includes at least one flood hole.
  • Figure 1 is a sectional view of a high-pressure pump with a drive connection according to the invention between eccentric and bucket tappets.
  • a high-pressure pump 1 for a fuel injection device is one
  • Internal combustion engine is shown, which is preferably intended for a common rail injection system of a diesel internal combustion engine.
  • fuel under high pressure in a not shown in Fig. 1 memory (rail) is promoted. dert, from which the fuel is injected via fuel injectors targeted in associated combustion chambers of an internal combustion engine.
  • the high-pressure pump 1 forms a radial piston pump, which is used as a plug-in pump with a plug-in pump body 2 in an engine block 3 or housing.
  • the plug-in pump body 2 is adjoined by a low-pressure unit 4, which may also be referred to as a cylinder head.
  • a low-pressure unit 4 which may also be referred to as a cylinder head.
  • the drive shaft may be a shaft of the internal combustion engine, for example, the camshaft or a balancer shaft.
  • the eccentric 6 is surrounded by a race 9, which is rotatably mounted on the eccentric 6 via a roller bearing 10, in particular a needle bearing with cylindrical rolling elements 1 1 and which is drivingly connected to a tappet 13 of a pump element 8.
  • the pump element 8 comprises the bucket tappet 13, in which an element piston 12 or pump piston is held, as well as a tappet spring 14.
  • the cup tappet 13 is guided without rotation in a radially extending to the axis 5 of the drive shaft housing bore 16 of the engine block 3.
  • the cup tappet 13 is supported on the raceway 9 of the eccentric member 6 via a sliding plate 18 inserted in a form-fitting manner in a receptacle 17 of the cup tappet 5 and fixed in position.
  • In the operating state causes the rotating eccentric 6 in conjunction with the race 9, an oscillating movement of the tappet 13 and the associated element piston 12 which is guided in a cylinder bore 19 of a shaft portion 20 of the plug-in pump body 2.
  • the element piston 8 defines a pump working space 21 to which a suction valve 22 and a high-pressure valve 23 are assigned.
  • the suction valve 22 opens, whereby the pump working chamber 21 fuel from the low pressure unit 4 can be supplied.
  • a delivery stroke (upward movement) of the element piston 8 leads to the closure of the suction valve 22 and a fuel compression, before the fuel on the the function of a
  • Non-return valve exerting high-pressure valve 23 is conveyed in a further fuel line to a high-pressure accumulator (Rail).
  • the one restoring force on the tappet 13 triggering plunger spring 14 is supported between the plug-in pump body 2 and a spring plate 24 of the tappet 13 and causes a frictional support of the tappet 13 on the Running ring 9.
  • the plunger spring 14 surrounds the shaft portion 20 of the plug-in pump body 2, wherein a first spring end of the plunger spring 14 is enclosed by a board 25 of the plug-in pump body 2 and the further entering the tappet 13, supported on the spring plate 24 spring end on the outside of the plunger body 15 is enclosed.
  • the eccentric 6 enclosing raceway 9 is supported via a convex, convex contact surface 27 on a correspondingly shaped counter surface, the contact surface 28 of the sliding plate 18 of the tappet 13.
  • a friction-reducing coating at least one contact surface 27, 28 is additionally suitable.
  • the tappet 13 shows the tappet 13 as a single part in an enlarged view and illustrates further details.
  • the used in the tappet 13, for supporting the plunger spring 14 certain spring plate 24 simultaneously causes a support of the element piston 12 on the tappet 13.
  • the element piston 12 is inserted in a central opening 26 of the spring plate 24 and through an opening 26 cross-end board 35 secured. Since the plunger body 15 are guided in the engine block 3 and the element piston 12 in the shaft portion 20 and thus in separate components, the element piston 12 is preferably performed with a small angular error compensating clearance in the opening 26 of the spring plate 24.
  • Lubricant also in the direction of the eccentric 6 and applied for lubrication and cooling a contact zone 33 (Fig. 1) between the raceway 9 and the slide plate 18.
  • a plurality of flood bores 34 are introduced in the slide plate 18, which allow a flow of lubricant to targeted to lubricate and cool the components of the contact zone 33.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)

Abstract

The invention relates to a high-pressure pump (1) of a fuel injection device, which can be used in particular for a common rail injection device of an internal combustion engine. The high-pressure pump (1) comprises a pump shaft or drive shaft, which is connected to an eccentric (6) in a rotationally rigid manner, and at least one pump element (8). The pump element (8), including a bucket tappet (13), a piston element (12) and a tappet spring (14), is inserted into a housing bore (16) of an engine block (3). The bucket tappet (13), on which the tappet spring (14) acts, is connected to the piston element (12), which is guided such that it can be moved in a reciprocating manner in a cylinder bore (19) of a shaft section (20) and which delimits a pump working chamber (21) connected to a suction valve (22) and a high-pressure valve (23). A drive connection between the bucket tappet (13) and the eccentric (6) comprises a running ring (9) rotatably mounted on the eccentric (6), on which the sliding plate (18) of the bucket tappet (13) is supported in a force-closed manner.

Description

Beschreibung  description
Titel title
Hochdruckpumpe für eine Kraftstoffeinspritzvorrichtunq  High pressure pump for a Kraftstoffeinspritzvorununq
Die vorliegende Erfindung betrifft eine Hochdruckpumpe einer Kraftstoffeinspritzeinrichtung, die insbesondere für eine Common-Rail-Einspritzeinrichtung einer Brennkraftmaschine eingesetzt werden kann. Die Hochdruckpumpe umfasst eine Pumpen- oder Antriebswelle, die mit einem Exzenter drehstarr verbunden ist sowie mit einem Pumpen- element in einer Wirkverbindung steht. Das einen Tassenstößel, einen Elementkolben sowie eine Stößelfeder einschließende Pumpenelement ist einer Gehäusebohrung eines Motorblocks zugeordnet. Der mit dem Exzenter über den Tassenstößel antriebsverbundene und hubbeweglich in einer Zylinderbohrung geführte Elementkolben begrenzt einen mit einem Saugventil und einem Hochdruckventil verbundenen Pumpen- arbeitsraum. The present invention relates to a high pressure pump of a fuel injection device, which can be used in particular for a common rail injection device of an internal combustion engine. The high-pressure pump comprises a pump or drive shaft, which is rotationally rigidly connected to an eccentric and is in operative connection with a pump element. The one bucket tappet, an element piston and a plunger spring enclosing pump element is associated with a housing bore of an engine block. The element piston, which is drive-connected to the eccentric via the cup tappet and can be moved in a cylinder bore, delimits a pump working chamber connected to a suction valve and a high-pressure valve.
Stand der Technik State of the art
Derartige Hochdruckpumpen werden im Kraftfahrzeugbau eingesetzt, um einen not- wendigen Volumenstrom und erforderlichen Fluiddruck für eine Common-Rail-Such high-pressure pumps are used in motor vehicle construction in order to achieve a necessary volume flow and required fluid pressure for a common-rail system.
Kraftstoffeinrichtung bereit zu stellen. Die Hochdruckpumpe unterliegt starken Belastungen, insbesondere mechanischen Beanspruchungen, so dass an das Material und an die Konstruktion hohe Anforderungen gestellt werden. Der mit einem Exzenter oder einer Nockenbahn in Wirkverbindung stehende Tassenstößel bewirkt eine Umwand- lung von der Drehbewegung der Antriebswelle in eine oszillierende Hubbewegung eines Element- oder Pumpenkolbens. Die Hubbewegung des Elementkolbens kann in einen Saug- und Verdichtungshub unterteilt werden. Beim Saughub wird Kraftstoff über ein Saugventil in einen Pumpenarbeitsraum angesaugt. Bei dem sich anschließenden Verdichtungshub wird der Kraftstoff verdichtet und über ein geöffnetes Hochdruckventil in einen Speicher (Rail) gefördert. Aufgrund der sich einstellenden Reibung zwischen dem Elementkolben und einer Zylinderbohrung sowie einer Tassenstößelführung ist eine die Rückstellkraft ausübende Stößelfeder eingesetzt, die einen kraftschlüssigen Kontakt zwischen dem Tassenstößel und dem Exzenter herstellt. Die DE 101 57 076 A1 offenbart einen Stößelkolben für eine Hochdruckpumpe mit einem Stößel, der eine axial und radial geführte Rolle einschließt sowie einen mit dem Stößel fest verbundenen Kolben. Zur Führung der Rolle an dem Stößel ist dieser mit einem Rollenschuh versehen, in dem die Rolle mit einem axialen Spiel drehbar und eingesetzt ist. Fuel system to provide. The high-pressure pump is subject to heavy loads, in particular mechanical stresses, so that high demands are placed on the material and on the construction. The bucket tappet operatively connected to an eccentric or a cam track effects a conversion from the rotational movement of the drive shaft into an oscillating stroke movement of an element or pump piston. The lifting movement of the element piston can be divided into a suction and compression stroke. During the suction stroke, fuel is sucked into a pump working space via a suction valve. In the subsequent compression stroke, the fuel is compressed and conveyed via an open high-pressure valve in a memory (rail). Due to the self-adjusting friction between the element piston and a cylinder bore and a tappet guide a restoring force performing pestle spring is used, which establishes a non-positive contact between the tappet and the eccentric. DE 101 57 076 A1 discloses a plunger piston for a high-pressure pump with a plunger, which includes an axially and radially guided roller and a piston fixedly connected to the plunger. To guide the roller on the plunger it is provided with a roller shoe in which the roller is rotatable and inserted with an axial play.
Aus der DE 199 07 31 1 A1 ist eine Hochdruckpumpe bekannt, die eine Antriebswelle mit Exzenter aufweist, der mit einem Pumpenelement zusammenwirkt. Zwischen dem Elementkolben und dem Exzenter ist ein Stützelement oder ein Rollenschuh angeordnet, in dem eine drehbar gelagerte, auf dem Exzenter abrollende Rolle eingesetzt ist. Bei diesem Aufbau besteht die Gefahr, dass ein relativ großer Verschleiß aufgrund erhöhter Reibung zwischen den in einer unmittelbaren Wirkverbindung stehenden Bauteilen entsteht. Die erhöhte Reibung beeinflusst die Drehbewegung der Rolle, wodurch Schlupf zwischen der Rolle und dem Exzenter auftreten kann und der Verschleiß zunimmt. From DE 199 07 31 1 A1 discloses a high-pressure pump is known, which has a drive shaft with eccentric, which cooperates with a pump element. Between the element piston and the eccentric, a support element or a roller shoe is arranged, in which a rotatably mounted, rolling on the eccentric roller is inserted. In this structure, there is a risk that a relatively large amount of wear due to increased friction between the directly operatively connected components arises. The increased friction affects the rotational movement of the roller, whereby slippage between the roller and the eccentric can occur and the wear increases.
Die Aufgabe der Erfindung besteht darin, eine Hochdruckpumpe mit einer vereinfachten, robusten und reibungsoptimierten Antriebsverbindung zwischen dem Exzenter und dem Tassenstößel zu schaffen, die hohen mechanischen Belastungen standhält und einfach herstellbar ist. The object of the invention is to provide a high-pressure pump with a simplified, robust and friction-optimized drive connection between the eccentric and the bucket tappet, which withstands high mechanical loads and is easy to produce.
Offenbarung der Erfindung Diese Aufgabe wird dadurch gelöst, dass eine Antriebsverbindung zwischen dem Tassenstößel und dem Exzenter einen drehbar auf dem Exzenter gelagerten Laufring um- fasst, an dem der Tassenstößel kraftschlüssig abgestützt ist. Der Tassenstößel ist somit über den drehbar gelagerten Laufring mittelbar mit dem Exzenter antriebsverbunden. DISCLOSURE OF THE INVENTION This object is achieved in that a drive connection between the bucket tappet and the eccentric comprises a rotatably mounted on the eccentric race on which the bucket tappet is non-positively supported. The tappet is thus drivingly connected via the rotatably mounted race indirectly to the eccentric.
Der erfindungsgemäße, den Exzenter umschließende sowie eine Relativbewegung zu dem Exzenter ausübende Laufring bewirkt vorteilhaft eine entkoppelte Antriebsverbindung oder Kraftübertragung zwischen dem Tassenstößel und dem Exzenter. Diese Anordnung reduziert die Querkraftaufnahme des Tassenstößels und folglich lassen sich vorteilhaft reduzierte Seiten- oder Querkräfte vom Tassenstößel in dessen Führung an der Gehäusebohrung realisieren. Das erfindungsgemäße Konzept schafft eine vereinfachte und robuste Antriebsverbindung zwischen Exzenter und Tassenstößel, die vorteilhaft starken Belastungen, insbesondere mechanischen Beanspruchungen standhält, was sich positiv auf die Lebensdauer auswirkt. Die reibungsoptimierte Antriebsverbindung ist weiterhin unabhängig gegenüber Reibverhältnissen, die bei bisherigen Lösungen zwischen einem Tassenstößel und Exzenter zu berücksichtigen waren, beispielsweise zwischen einer Rolle und einem Exzenter. Außerdem ist die erfin- dungsgemäße robuste Antriebsverbindung unempfindlich gegenüber unterschiedlichenThe inventive, the eccentric enclosing and a relative movement to the eccentric exercising race advantageously causes a decoupled drive connection or power transmission between the tappet and the eccentric. This arrangement reduces the transverse force absorption of the bucket tappet and consequently advantageously reduced lateral or transverse forces can be realized by the bucket tappet in its guide on the housing bore. The inventive concept provides a simplified and robust drive connection between the eccentric and bucket tappets, the advantageous heavy loads, in particular mechanical stresses withstand, which has a positive effect on the life. The friction-optimized drive connection is also independent of friction conditions, which were to be considered in previous solutions between a bucket tappet and eccentric, for example between a roller and an eccentric. In addition, the inventive robust drive connection is insensitive to different
Kraftstoffviskositäten . Fuel viscosities.
Ein weiterer Vorteil der Erfindung besteht darin, dass die Antriebsverbindung gemäß der Erfindung sowohl auf Hochdruckpumpen mit einem 1 -fach Nockensystem oder Ex- zentersystem als auch auf Hochdruckpumpen mit einem 2-fach Nockensystem übertragbar ist. Im Vergleich zu bekannten Lösungen, bei denen der Tassenstößel über eine im Rollenschuh integrierte Rolle an dem Exzenter abgestützt ist, stellt sich durch die erfindungsgemäße Antriebsverbindung vorteilhaft eine reduzierte Reibung ein. Durch die Erfindung kann vorteilhaft eine dauerfeste Antriebsverbindung zwischen dem Ex- zenter und dem Tassenstößel realisiert werden, die auch für hochdynamische Systeme mit entsprechend hohen Pumpendrücken und Pumpendrehzahlen einsetzbar ist. A further advantage of the invention is that the drive connection according to the invention can be transferred both to high-pressure pumps with a 1-fold cam system or eccentric system and to high-pressure pumps with a 2-fold cam system. In comparison to known solutions, in which the tappet is supported on the eccentric via a roll integrated in the roller shoe, the friction connection according to the invention advantageously results in reduced friction. By the invention can advantageously be realized a permanent drive connection between the eccentric and the bucket tappet, which can also be used for highly dynamic systems with correspondingly high pump pressures and pump speeds.
Gleichzeitig gewährt das erfindungsgemäße, einfach umsetzbare Konzept einen zuverlässigen, präzisen Betrieb, verbunden mit einem geringen Verschleiß, wodurch sich insgesamt eine Effizienzsteigerung einstellt. At the same time, the concept according to the invention, which can be implemented easily, ensures reliable, precise operation, combined with low wear, which results in an overall increase in efficiency.
Eine bevorzugte Weiterbildung der Erfindung sieht vor, dass dem Tassenstößel an- triebsseitig eine auch als Kraftaufnahmeeinrichtung zu bezeichnende Gleitplatte zugeordnet ist. Die vorzugsweise in den Tassenstößel eingepresste und lagefixierte Gleitplatte ist mit einer Kontaktfläche an der zugehörigen Kontaktfläche des den Exzenter umschließenden Laufrings abgestützt, wobei die Kontaktflächen gemeinsam eine Kontaktzone bilden. Vorteilhaft ist die Gleitplatte aus einem an die gegebenen Belastungen und Schmierstoffverhältnisse angepassten Werkstoff hergestellt. Zur Erzielung einer hohen Verschleißfestigkeit bietet es sich beispielsweise an, die Gleitplatte aus Hartmetall oder einem keramischen Werkstoff herzustellen. Der Tassenstößel mit integrierter Gleitplatte zeichnet sich weiterhin aus durch einen vereinfachten und bauteiloptimiertenA preferred embodiment of the invention provides that the bucket tappet on the drive side is associated with a designated also as a force receiving device sliding plate. The preferably pressed into the cup tappet and fixed in position sliding plate is supported with a contact surface on the associated contact surface of the eccentric enclosing race, wherein the contact surfaces together form a contact zone. Advantageously, the sliding plate is made of a material adapted to the given loads and lubricant conditions. To achieve a high wear resistance, it makes sense, for example, to produce the sliding plate made of hard metal or a ceramic material. The tappet with integrated sliding plate is further characterized by a simplified and component-optimized
Aufbau. Bedingt durch die Gleitplatte benötigt der Tassenstößel vorteilhaft weder eine lageorientierte Einbaulage noch eine Verdrehsicherung, wodurch sich die Montage vereinfacht. Das erfindungsgemäße vereinfachte und kostenoptimierte Tassenstößel- konzept bietet außerdem gegenüber bekannten Lösungen von Tassenstößeln mit Rol- lenschuh und integrierter Rolle einen Kostenvorteil. Construction. Due to the sliding plate, the tappet advantageously requires neither a position-oriented mounting position nor an anti-twist device, which simplifies assembly. The inventive simplified and cost-optimized bucket tappet concept also offers a cost advantage over known solutions of tappets with roller shoe and integrated role.
Zur Reibungsminimierung ist der Laufring über ein Wälzlager oder Gleitlager auf der Exzenterwelle drehbar gelagert. Durch die Verwendung handelsüblicher Wälz- oder Gleitlager kann eine robuste, bewährte und kostengünstige Lagerung des Laufrings auf der Exzenterwelle realisiert werden. Als Wälzlager eignen sich bevorzugt Zylinderrollenlager, da die Lagerung keine axialen Kräfte aufzunehmen hat. Aufgrund des geringen erforderlichen radialen Bauraums können für die Lagerung des Laufrings bevor- zugt Nadellager eingesetzt werden. To minimize friction, the race is rotatably mounted on the eccentric shaft via a rolling bearing or sliding bearing. By the use of commercial Wälz- or Plain bearings can be a robust, proven and inexpensive storage of the race on the eccentric shaft can be realized. As roller bearings are preferably cylindrical roller bearings, since the storage has to absorb any axial forces. Due to the small radial space required, it is preferable to use needle bearings for the bearing of the race.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass zumindest eine der zueinander gerichteten Kontaktflächen der Gleitplatte sowie des Laufrings leicht ballig oder konvex ausgebildet ist. Diese Maßnahme gleicht vor- teilhaft leichte Winkelfehler aus, die bei der Fertigung aufgrund zulässiger Lage- und / oder Formtoleranzen auftreten können. Die konvexe Ausbildung dient außerdem dazu, die Kontaktzone zwischen der Gleitplatte und dem Laufring bis auf einen Linienkontakt zu verkleinern, wodurch sich die Reibung vorteilhaft reduziert. Zur Erzielung einer erhöhten Lebensdauer der Antriebsverbindung ist erfindungsgemäß vorgesehen, zumindest eine Kontaktfläche des Laufrings oder der Gleitplatte mit einem Werkstoff hoher Verschleißfestigkeit zu beschichten. Alternativ oder ergänzend dazu schließt die Erfindung weiterhin eine Beschichtung zumindest einer Kontaktfläche mit einem reibungsmindernden Werkstoff ein. Another particular embodiment of the invention is characterized in that at least one of the mutually facing contact surfaces of the sliding plate and the race is slightly convex or convex. This measure advantageously compensates for slight angular errors that can occur during production due to permissible position and / or shape tolerances. The convexity also serves to reduce the contact area between the slide plate and the raceway to line contact, thereby advantageously reducing friction. To achieve an increased service life of the drive connection, it is provided according to the invention to coat at least one contact surface of the race or the sliding plate with a material of high wear resistance. Alternatively or additionally, the invention further includes a coating of at least one contact surface with a friction-reducing material.
Gemäß einer weiteren vorteilhaften Ausführungsform ist die als Steckpumpe ausgebildete Hochdruckpumpe als eine Baueinheit mit einem Steckpumpenkörper in einer Gehäusebohrung des Motorblocks eingesetzt. In einem Schaftabschnitt des Steckpumpenkörpers ist eine Zylinderbohrung eingebracht, die zur Führung des Elementkolbens bestimmt ist und die gleichzeitig den Pumpenarbeitsraum bildet. Vorteilhaft bietet dieAccording to a further advantageous embodiment, the high pressure pump designed as a plug-in pump is used as a structural unit with a plug-in pump body in a housing bore of the engine block. In a shaft portion of the plug-in pump body, a cylinder bore is introduced, which is intended to guide the element piston and at the same time forms the pump working space. Advantageously, the offers
Erfindung die Möglichkeit eine Hochdruckpumpe zu schaffen, bei der das Prinzip einer Steckpumpe mit einer Antriebsverbindung kombiniert ist, die einen auf der Exzenterwelle gelagerten Laufring sowie einen Tassenstößel mit integrierter Gleitplatte aufweist. Invention, the possibility of creating a high-pressure pump in which the principle of a plug-in pump is combined with a drive connection having a mounted on the eccentric shaft raceway and a bucket tappets with integrated sliding plate.
Der konstruktive Aufbau der Erfindung schließt weiterhin unterschiedliche Lösungen zur Führung des Tassenstößels ein. Bevorzugt ist eine äußere Führung des Tassenstößels, bei der ein Stößelkörper des Tassenstößels über eine Mantelfläche in der Gehäusebohrung des Motorblocks geführt ist. Diese Außenführung des Tassenstößels unterbindet eine Deformation der Führung des Elementkolbens in dem Schaftabschnitt.The structural design of the invention further includes different solutions for guiding the bucket tappet. An outer guide of the tappet is preferred, in which a tappet body of the tappet is guided over a lateral surface in the housing bore of the engine block. This outer guide of the tappet prevents deformation of the guide of the element piston in the shaft portion.
Alternativ dazu bietet sich an, den Tassenstößel innenseitig an dem Schaftabschnitt des Steckpumpenkörpers zu führen. In weiterer Ausgestaltung der Erfindung ist für die als Steckpumpe ausgeführte Hochdruckpumpe außerdem eine bauraumoptimierte Anordnung der Stößelfeder vorgesehen. Dazu ist die Stößelfeder an einem innerhalb des Tassenstößels integrierten Federteller abgestützt, wobei die Stößelfeder über eine größere Länge innerhalb des Stößelkörpers geführt ist. Das gegenseitige Federende der Stößelfeder ist zur Führung von einem Bord des Steckpumpenkörpers umschlossen. Alternatively, it is advisable to guide the tappet inside the shaft portion of the plug-in pump body. In a further embodiment of the invention, a space-optimized arrangement of the plunger spring is also provided for the designed as a plug-pump high-pressure pump. For this purpose, the plunger spring is supported on an integrated inside the cup tappet spring plate, wherein the plunger spring is guided over a greater length within the plunger body. The mutual spring end of the plunger spring is enclosed for guiding by a board of the plug-in pump body.
Zur gezielten und effektiven Schmierung der Führung des Tassenstößels in der Gehäusebohrung ist in einer Mantelfläche des Stößelkörpers zumindest eine bevorzugt umlaufende Schmiernut eingebracht, die über zugehörige Durchtrittsbohrungen mit einem Stößelinnenraum verbunden sind. Diese Maßnahme bewirkt, dass ein Schmierstoff, insbesondere der durch die Hochdruckpumpe geförderte Kraftstoff in den sich zwischen der Gehäusebohrung des Motorblocks und der Mantelfläche des Tassenstößels einstellenden Ringspalt eintritt. Dadurch kann eine optimale, reibungsmindernde Schmierung des Tassenstößels realisiert werden. Weiterhin gelangt der Schmierstoff zur Kühlung und Schmierung in die von dem Laufring und der Gleitplatte definierte Kontaktzone der Antriebsverbindung zwischen dem Exzenter und dem Tassenstößel. Als eine ergänzende Maßnahme zur Schmierstoffversorgung der Kontaktzone schließt die Gleitplatte des Tassenstößels zumindest eine Flutbohrung ein. For targeted and effective lubrication of the leadership of the tappet in the housing bore at least one preferably circumferential lubrication groove is introduced in a lateral surface of the tappet body, which are connected via associated passage bores with a plunger interior. This measure has the effect that a lubricant, in particular the fuel delivered by the high-pressure pump, enters the annular gap which is established between the housing bore of the engine block and the lateral surface of the cup tappet. As a result, an optimal, friction-reducing lubrication of the bucket tappet can be realized. Furthermore, the lubricant passes for cooling and lubrication in the defined by the race and the sliding plate contact zone of the drive connection between the eccentric and the bucket tappet. As a supplementary measure for the supply of lubricant to the contact zone, the sliding plate of the tappet includes at least one flood hole.
Weitere vorteilhafte Ausgestaltungen der Erfindung sind der Zeichnungsbeschreibung zu entnehmen, in der in den Figuren dargestellte Ausführungsbeispiele der Erfindung näher beschrieben sind. Kurze Beschreibung der Zeichnungen Further advantageous embodiments of the invention are described in the drawings, are described in more detail in the embodiments illustrated in the figures of the invention. Brief description of the drawings
Es zeigen: Show it:
Fig. 1 eine Schnittdarstellung einer Hochdruckpumpe mit einer erfindungsgemäßen Antriebsverbindung zwischen Exzenter und Tassenstößel; Figure 1 is a sectional view of a high-pressure pump with a drive connection according to the invention between eccentric and bucket tappets.
Fig. 2 als Einzelteilzeichnung den Tassenstößel gemäß Fig. 1. 2 as a single part drawing of the bucket tappet according to FIG. 1.
In Figur 1 ist eine Hochdruckpumpe 1 für eine Kraftstoffeinspritzeinrichtung einerIn FIG. 1, a high-pressure pump 1 for a fuel injection device is one
Brennkraftmaschine dargestellt, die bevorzugt für ein Common-Rail-Einspritzsystem einer Diesel-Brennkraftmaschine bestimmt ist. Durch die Hochdruckpumpe 1 wird Kraftstoff unter Hochdruck in einen in Fig. 1 nicht abgebildeten Speicher (Rail) geför- dert, aus dem der Kraftstoff über Kraftstoffinjektoren gezielt in zugeordnete Brennräume einer Brennkraftmaschine eingespritzt wird. Die Hochdruckpumpe 1 bildet eine Radialkolbenpumpe, die als Steckpumpe mit einem Steckpumpenkörper 2 in einem Motorblock 3 oder Gehäuse eingesetzt ist. An den Steckpumpenkörper 2 schließt sich ei- ne auch als Zylinderkopf zu bezeichnende Niederdruckeinheit 4 an. Eine im MotorblockInternal combustion engine is shown, which is preferably intended for a common rail injection system of a diesel internal combustion engine. By the high-pressure pump 1 fuel under high pressure in a not shown in Fig. 1 memory (rail) is promoted. dert, from which the fuel is injected via fuel injectors targeted in associated combustion chambers of an internal combustion engine. The high-pressure pump 1 forms a radial piston pump, which is used as a plug-in pump with a plug-in pump body 2 in an engine block 3 or housing. The plug-in pump body 2 is adjoined by a low-pressure unit 4, which may also be referred to as a cylinder head. One in the engine block
3 drehbare Antriebswelle mit einer Achse 5 ist mit einem Exzenter 6 verbunden, dessen Mittelachse 7 eine Exzentrizität S gegenüber der Achse 5 aufweist. Die Antriebswelle kann eine Welle der Brennkraftmaschine sein, beispielsweise deren Nockenwelle oder eine Ausgleichswelle. 3 rotatable drive shaft with an axis 5 is connected to an eccentric 6, whose central axis 7 has an eccentricity S with respect to the axis 5. The drive shaft may be a shaft of the internal combustion engine, for example, the camshaft or a balancer shaft.
Der Exzenter 6 ist von einem Laufring 9 umschlossen, der über ein Wälzlager 10, insbesondere ein Nadellager, mit zylindrischen Wälzkörpern 1 1 drehbar auf dem Exzenter 6 gelagert ist und der mit einem Tassenstößel 13 eines Pumpenelements 8 antriebsverbunden ist. Das Pumpenelement 8 umfasst den Tassenstößel 13, in dem ein Ele- mentkolben 12 oder Pumpenkolben gehalten ist sowie eine Stößelfeder 14. Über einenThe eccentric 6 is surrounded by a race 9, which is rotatably mounted on the eccentric 6 via a roller bearing 10, in particular a needle bearing with cylindrical rolling elements 1 1 and which is drivingly connected to a tappet 13 of a pump element 8. The pump element 8 comprises the bucket tappet 13, in which an element piston 12 or pump piston is held, as well as a tappet spring 14. About a
Stößelkörper 15 ist der Tassenstößel 13 ohne eine Verdrehsicherung in einer radial zur Achse 5 der Antriebswelle verlaufenden Gehäusebohrung 16 des Motorblocks 3 geführt. Über eine formschlüssig in einer Aufnahme 17 des Tassenstößels 5 eingesetzten und lagefixierten Gleitplatte 18 ist der Tassenstößel 13 an dem Laufring 9 des Exzen- ters 6 abgestützt. Im Betriebszustand bewirkt der rotierende Exzenter 6 in Verbindung mit dem Laufring 9 eine oszillierende Bewegung des Tassenstößels 13 und des damit verbundenen Elementkolbens 12, der in einer Zylinderbohrung 19 eines Schaftabschnitts 20 des Steckpumpenkörpers 2 geführt ist. Der Elementkolben 8 begrenzt einen Pumpenarbeitsraum 21 , dem ein Saugventil 22 sowie ein Hochdruckventil 23 zugeordnet ist. Bei einem Saughub (Abwärtsbewegung) des Elementkolbens 8 öffnet sich das Saugventil 22, wodurch dem Pumpenarbeitsraum 21 Kraftstoff aus der Niederdruckeinheit 4 zugeführt werden kann. Ein Förderhub (Aufwärtsbewegung) des Elementkolbens 8 führt zur Schließung des Saugventils 22 und einer Kraftstoffkomprimierung, bevor der Kraftstoff über ein die Funktion einesPlunger body 15, the cup tappet 13 is guided without rotation in a radially extending to the axis 5 of the drive shaft housing bore 16 of the engine block 3. The cup tappet 13 is supported on the raceway 9 of the eccentric member 6 via a sliding plate 18 inserted in a form-fitting manner in a receptacle 17 of the cup tappet 5 and fixed in position. In the operating state causes the rotating eccentric 6 in conjunction with the race 9, an oscillating movement of the tappet 13 and the associated element piston 12 which is guided in a cylinder bore 19 of a shaft portion 20 of the plug-in pump body 2. The element piston 8 defines a pump working space 21 to which a suction valve 22 and a high-pressure valve 23 are assigned. During a suction stroke (downward movement) of the element piston 8, the suction valve 22 opens, whereby the pump working chamber 21 fuel from the low pressure unit 4 can be supplied. A delivery stroke (upward movement) of the element piston 8 leads to the closure of the suction valve 22 and a fuel compression, before the fuel on the the function of a
Rückschlagventils ausübendes Hochdruckventil 23 in eine weiterführende Kraftstoffleitung zu einem Hochdruckspeicher (Rail) gefördert wird. Eine Exzentrizität S zwischen der Achse 5 der Antriebs- oder Pumpenwelle zu der Mittelachse 7 des Exzenters 6 bestimmt gleichzeitig einen maximalen Hub des Elementkolbens 12. Non-return valve exerting high-pressure valve 23 is conveyed in a further fuel line to a high-pressure accumulator (Rail). An eccentricity S between the axis 5 of the drive or pump shaft to the central axis 7 of the eccentric 6 simultaneously determines a maximum stroke of the element piston 12th
Die eine Rückstellkraft auf den Tassenstößel 13 auslösende Stößelfeder 14 ist zwischen dem Steckpumpenkörper 2 und einem Federteller 24 des Tassenstößels 13 abgestützt und bewirkt eine kraftschlüssige Abstützung des Tassenstößels 13 an dem Laufring 9. Dabei umschließt die Stößelfeder 14 den Schaftabschnitt 20 des Steckpumpenkörpers 2, wobei ein erstes Federende der Stößelfeder 14 von einem Bord 25 des Steckpumpenkörpers 2 umschlossen ist und das weitere in den Tassenstößel 13 eintretende, an dem Federteller 24 abgestützte Federende außenseitig von dem Stößelkörper 15 umschlossen wird. The one restoring force on the tappet 13 triggering plunger spring 14 is supported between the plug-in pump body 2 and a spring plate 24 of the tappet 13 and causes a frictional support of the tappet 13 on the Running ring 9. In this case, the plunger spring 14 surrounds the shaft portion 20 of the plug-in pump body 2, wherein a first spring end of the plunger spring 14 is enclosed by a board 25 of the plug-in pump body 2 and the further entering the tappet 13, supported on the spring plate 24 spring end on the outside of the plunger body 15 is enclosed.
Zum Ausgleich von kleinen Winkelfehlern, beispielsweise bedingt durch Fertigungstoleranzen einzelner Bauteile, ist der den Exzenter 6 umschließende Laufring 9 über eine ballige, konvexe Kontaktfläche 27 an einer entsprechend gestalteten Gegenfläche, der Kontaktfläche 28 der Gleitplatte 18 des Tassenstößels 13 abgestützt. Zur Erzielung optimaler Reibungsverhältnisse bietet sich ergänzend dazu eine reibungsmindernde Be- schichtung zumindest einer Kontaktfläche 27, 28 an. To compensate for small angular errors, for example due to manufacturing tolerances of individual components, the eccentric 6 enclosing raceway 9 is supported via a convex, convex contact surface 27 on a correspondingly shaped counter surface, the contact surface 28 of the sliding plate 18 of the tappet 13. To achieve optimum friction conditions, a friction-reducing coating at least one contact surface 27, 28 is additionally suitable.
Die Figur 2 zeigt den Tassenstößel 13 als Einzelteil in einer vergrößerten Darstellung und verdeutlicht weitere Details. Der in dem Tassenstößel 13 eingesetzte, zur AbStützung der Stößelfeder 14 bestimmte Federteller 24 bewirkt gleichzeitig eine Halterung des Elementkolbens 12 an dem Tassenstößel 13. Dazu ist der Elementkolben 12 in einer zentralen Öffnung 26 des Federtellers 24 eingesetzt und durch einen die Öffnung 26 übergreifenden endseitigen Bord 35 gesichert. Da der Stößelkörper 15 im Motorblock 3 und der Elementkolben 12 im Schaftabschnitt 20 und damit in getrennten Bauteilen geführt sind, ist der Elementkolben 12 bevorzugt mit einer kleine Winkelfehler ausgleichenden Spielpassung in der Öffnung 26 des Federtellers 24 geführt. Als Maßnahme um die Reibung des Stößelkörpers 15 in der Gehäusebohrung 16 des Motorblocks 3 zu verbessern ist in einer Mantelfläche 29 des Stößelkörpers 15 eine bevorzugt umlaufende Schmiernut 30 eingebracht mit umfangsverteilt angeordneten Durchtrittsbohrungen 31 . Damit kann gezielt ein Schmierstoff oder der von der Hochdruckpumpe 1 geförderte Kraftstoff in einen von dem Stößelkörper 15 und der Gehäusebohrung 16 radial begrenzten Ringspalt 32 (Fig. 1 ) eintreten. Von dort gelangt der 2 shows the tappet 13 as a single part in an enlarged view and illustrates further details. The used in the tappet 13, for supporting the plunger spring 14 certain spring plate 24 simultaneously causes a support of the element piston 12 on the tappet 13. For this, the element piston 12 is inserted in a central opening 26 of the spring plate 24 and through an opening 26 cross-end board 35 secured. Since the plunger body 15 are guided in the engine block 3 and the element piston 12 in the shaft portion 20 and thus in separate components, the element piston 12 is preferably performed with a small angular error compensating clearance in the opening 26 of the spring plate 24. As a measure to improve the friction of the plunger body 15 in the housing bore 16 of the engine block 3 is in a lateral surface 29 of the plunger body 15, a preferably circumferential lubrication 30 introduced circumferentially arranged through holes 31st In this way, a lubricant or the fuel delivered by the high-pressure pump 1 can selectively enter an annular gap 32 (FIG. 1) which is radially delimited by the plunger body 15 and the housing bore 16. From there comes the
Schmierstoff auch in Richtung des Exzenters 6 und beaufschlagt zur Schmierung und Kühlung eine Kontaktzone 33 (Fig. 1 ) zwischen dem Laufring 9 und der Gleitplatte 18. Zusätzlich sind in der Gleitplatte 18 mehrere Flutbohrungen 34 eingebracht, die ein Durchströmen von Schmierstoff ermöglichen, um gezielt die Bauteile der Kontaktzone 33 zu schmieren und zu kühlen. Lubricant also in the direction of the eccentric 6 and applied for lubrication and cooling a contact zone 33 (Fig. 1) between the raceway 9 and the slide plate 18. In addition, a plurality of flood bores 34 are introduced in the slide plate 18, which allow a flow of lubricant to targeted to lubricate and cool the components of the contact zone 33.

Claims

Patentansprüche claims
1 . Hochdruckpumpe (1 ) einer Kraftstoffeinspritzeinrichtung, insbesondere für eine Common-Rail-Einspritzeinrichtung einer Brennkraftmaschine, mit einer Pumpenwel- le, die mit einem Exzenter (6) drehstarr verbunden ist sowie mit zumindest einem in einer Gehäusebohrung (16) eines Motorblocks (3) eingesetzten Pumpenelement (8), das einen mit dem Exzenter (6) über einen Tassenstößel (13) antriebsverbundenen, hubbeweglich in einer Zylinderbohrung (19) eines Schaftabschnitts (20) geführten Elementkolben (12) einschließt sowie eine den Tassenstößel (13) beaufschlagende Stö- ßelfeder (14), wobei der Elementkolben (12) einen mit einem Saugventil (22) und einem Hochdruckventil (23) verbundenen Pumpenarbeitsraum (21 ) begrenzt, dadurch gekennzeichnet, dass eine Antriebsverbindung zwischen dem Tassenstößel (13) und dem Exzenter (6) einen drehbar auf dem Exzenter (6) gelagerten Laufring (9) umfasst, an dem der Tassenstößel (13) kraftschlüssig abgestützt ist. 1 . High-pressure pump (1) of a fuel injection device, in particular for a common-rail injection device of an internal combustion engine, with a Pumpenwel- le with an eccentric (6) is rotationally rigidly connected and at least one in a housing bore (16) of an engine block (3) used Pump element (8) which includes a with the eccentric (6) via a bucket tappet (13) connected, hubbeweglich in a cylinder bore (19) of a shaft portion (20) guided element piston (12) and a tappet (13) acting on bump spring (14), wherein the element piston (12) bounded with a suction valve (22) and a high pressure valve (23) pump working space (21), characterized in that a drive connection between the tappet (13) and the eccentric (6) rotatable one on the eccentric (6) mounted raceway (9) on which the tappet (13) is non-positively supported.
2. Hochdruckpumpe nach Anspruch 1 , dadurch gekennzeichnet, dass der Tassenstößel (13) antriebsseitig eine Gleitplatte (18) einschließt, die als Kontaktfläche (28) gemeinsam mit einer Kontaktfläche (27) des den Exzenter (6) umschließenden Laufrings (9) eine Kontaktzone (33) bildet. 2. High-pressure pump according to claim 1, characterized in that the tappet (13) on the drive side includes a sliding plate (18) as a contact surface (28) together with a contact surface (27) of the eccentric (6) enclosing race (9) has a contact zone (33) forms.
3. Hochdruckpumpe nach Anspruch 1 , dadurch gekennzeichnet, dass der Laufring (9) über ein Wälzlager (10) oder Gleitlager auf dem Exzenter (6) drehbar gelagert ist. 3. High-pressure pump according to claim 1, characterized in that the raceway (9) via a rolling bearing (10) or plain bearing on the eccentric (6) is rotatably mounted.
4. Hochdruckpumpe nach Anspruch 3, dadurch gekennzeichnet, dass als Wälzlager (10) ein Zylinderrollenlager oder Nadellager zur Lagerung des Laufrings (9) vorgesehen ist. 4. High-pressure pump according to claim 3, characterized in that as a rolling bearing (10) is provided a cylindrical roller bearing or needle bearing for supporting the race (9).
5. Hochdruckpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Laufring (9) und / oder die Gleitplatte (18) eine ballig oder konvex ausgebildete Kontaktfläche (27,28) aufweisen. 5. High-pressure pump according to claim 1 or 2, characterized in that the race (9) and / or the sliding plate (18) has a convex or convex contact surface (27,28).
6. Hochdruckpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Kontaktfläche (27) des Laufrings (9) und / oder die Kontaktfläche (28) der Gleitplatte (18) reibungsmindernd beschichtet ist. 6. High-pressure pump according to claim 1 or 2, characterized in that the contact surface (27) of the race (9) and / or the contact surface (28) of the sliding plate (18) is coated friction-reducing.
7. Hochdruckpumpe nach Anspruch 1 , dadurch gekennzeichnet, dass die als Steckpumpe ausgebildete Hochdruckpumpe (1 ) mit einem Steckpumpenkörper (2) in der Gehäusebohrung (16) des Motorblocks (3) eingesetzt ist und die zur Führung des Elementkolbens (12) und Bildung eines Pumpenarbeitsraums (8) bestimmte Zylinderbohrung (19) in einem Schaftabschnitt (20) des Steckpumpenkörpers (2) eingebracht ist. 7. High-pressure pump according to claim 1, characterized in that the plug pump designed as a high pressure pump (1) with a plug pump body (2) in the housing bore (16) of the engine block (3) is used and for guiding the element piston (12) and forming a Pump working space (8) certain cylinder bore (19) in a shaft portion (20) of the plug-in pump body (2) is introduced.
8. Hochdruckpumpe nach Anspruch 1 , dadurch gekennzeichnet, dass der Tassenstößel (13) außenseitig über einen Stößelkörper (15) in der Gehäusebohrung (16) des Motorblocks (3) oder innenseitig an dem Steckpumpenschaft (20) des Steckpumpenkörpers (2) geführt ist. 8. High-pressure pump according to claim 1, characterized in that the tappet (13) on the outside via a plunger body (15) in the housing bore (16) of the engine block (3) or on the inside of the plug-in pump shaft (20) of the plug-in pump body (2) is guided.
9. Hochdruckpumpe nach Anspruch 1 , dadurch gekennzeichnet, dass die Stößelfeder (14) mit einem Federende an einem Federteller (24) abgestützt ist, der in dem Tassenstößel (13) integriert ist. 9. High-pressure pump according to claim 1, characterized in that the plunger spring (14) is supported by a spring end on a spring plate (24) which is integrated in the cup tappet (13).
10. Hochdruckpumpe nach Anspruch 1 , dadurch gekennzeichnet, dass zur Schmierstoffversorgung einer Führung des Tassenstößels (13) in dem Stößelkörper (15) zumindest eine Schmiernut (30) eingebracht ist, die über zugehörige Durchtrittsbohrungen (31 ) mit einem Innenraum des Tassenstößels (13) verbunden ist. 10. High-pressure pump according to claim 1, characterized in that for lubricant supply of a guide of the tappet (13) in the plunger body (15) at least one lubrication groove (30) is introduced, which via associated through-holes (31) having an interior of the tappet (13). connected is.
1 1 . Hochdruckpumpe nach Anspruchl oder 2, dadurch gekennzeichnet, dass zur Schmierstoffversorgung der Kontaktzone (33) zwischen der Gleitplatte (18) und dem Laufring (9) zumindest eine Flutbohrung (34) in der Gleitplatte (18) eingebracht ist. 1 1. High-pressure pump according to claim 1 or 2, characterized in that for the lubricant supply to the contact zone (33) between the sliding plate (18) and the raceway (9) at least one flood bore (34) in the sliding plate (18) is introduced.
EP11754404.9A 2010-10-15 2011-09-07 High-pressure pump for a fuel injection device Not-in-force EP2627903B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010042484 DE102010042484A1 (en) 2010-10-15 2010-10-15 High pressure pump for a fuel injection device
PCT/EP2011/065472 WO2012048961A1 (en) 2010-10-15 2011-09-07 High-pressure pump for a fuel injection device

Publications (2)

Publication Number Publication Date
EP2627903A1 true EP2627903A1 (en) 2013-08-21
EP2627903B1 EP2627903B1 (en) 2016-07-13

Family

ID=44583058

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11754404.9A Not-in-force EP2627903B1 (en) 2010-10-15 2011-09-07 High-pressure pump for a fuel injection device

Country Status (4)

Country Link
EP (1) EP2627903B1 (en)
CN (1) CN103154512B (en)
DE (1) DE102010042484A1 (en)
WO (1) WO2012048961A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016102138A1 (en) * 2014-12-24 2016-06-30 Robert Bosch Gmbh Pump unit for feeding fuel, preferably diesel fuel, to an internal combustion engine
DE102015111025A1 (en) 2015-07-08 2017-01-12 Volkswagen Ag Self lubricated high pressure pump
DE102016203768B4 (en) * 2015-11-12 2017-10-26 Robert Bosch Gmbh Pump, in particular high-pressure pump of a fuel injection system, with a mounting assembly of plunger assembly and pump cylinder head, in particular by a latching connection between spring plate and plunger body
CN107939628B (en) * 2017-12-26 2023-07-18 浙江三浪润滑科技有限公司 Multi-head radial plunger pump and application method thereof
DE102018120777A1 (en) * 2018-08-24 2020-02-27 Volkswagen Aktiengesellschaft High-pressure pump comprising pressure lubrication
CN116324156A (en) 2020-09-24 2023-06-23 康明斯有限公司 Pump housing with relief cut for lobe clearance

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4315826C5 (en) * 1993-05-12 2012-04-05 Continental Teves Ag & Co. Ohg Motor-pump assembly
JPH09303252A (en) * 1996-05-13 1997-11-25 Nissan Motor Co Ltd Hydraulic pump device
IT1289796B1 (en) * 1996-12-23 1998-10-16 Elasis Sistema Ricerca Fiat IMPROVEMENTS TO A PUMP DEVICE FOR SUPPLYING FUEL FROM A TANK TO AN INTERNAL COMBUSTION ENGINE.
DE19907311A1 (en) 1999-02-22 2000-08-31 Bosch Gmbh Robert Hydraulic pump unit
JP2004537005A (en) * 2001-08-08 2004-12-09 シーアールティー コモンレールテクノロジーズ エージー High pressure supply pump
DE10157076A1 (en) 2001-11-21 2003-05-28 Bosch Gmbh Robert Tappet with piston has axial and/or radial roller guide adjustable on tappet by means of roller shoe fixed to tappet
DE10158768B4 (en) * 2001-11-29 2012-10-25 Schaeffler Technologies AG & Co. KG Radial piston pump
WO2006037676A1 (en) * 2004-10-06 2006-04-13 Siemens Aktiengesellschaft Radial piston pump comprising a roller tappet
DE102006041673A1 (en) * 2006-02-20 2007-08-23 Robert Bosch Gmbh High pressure pump especially for fuel injection in IC engine has the cam follower supported axially by hardened low wear surfaces
DE102006043187B3 (en) * 2006-09-14 2008-04-03 Siemens Ag Fluid pump, in particular high-pressure fuel pump for injection systems of internal combustion engines
DE102006060680A1 (en) * 2006-12-21 2008-06-26 Schaeffler Kg Rolling bearings for a radial piston pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012048961A1 *

Also Published As

Publication number Publication date
DE102010042484A1 (en) 2012-04-19
EP2627903B1 (en) 2016-07-13
CN103154512A (en) 2013-06-12
CN103154512B (en) 2017-03-01
WO2012048961A1 (en) 2012-04-19

Similar Documents

Publication Publication Date Title
WO2007096224A1 (en) High pressure pump in particular for a fuel injection device on an internal combustion engine
WO2013124103A1 (en) High-pressure pump
EP3519695B1 (en) Roller tappet for a piston pump, piston pump
WO2012048961A1 (en) High-pressure pump for a fuel injection device
EP2652309B1 (en) High pressure pump
WO2005111405A1 (en) High-pressure pump for a fuel injection device pertaining to an internal combustion engine
EP2828516A1 (en) High-pressure pump
WO1998058172A1 (en) Radial piston pump
WO2009013068A1 (en) High-pressure fuel pump with roller tappet
DE102009029297A1 (en) Piston pump, particularly high-pressure pump for fuel injection device of internal combustion engine, comprises pump piston, which is adjustably guided to shaft in radial manner
DE102018204505A1 (en) Roller tappets, in particular for a pump and pump with roller tappet
EP2809943B1 (en) High-pressure pump
EP3014107B1 (en) Pumping device, in particular high pressure fuel pumping device for a fuel injection device
DE102012212154A1 (en) High pressure pump for conveying fluid e.g. diesel, in common-rail-injection system of diesel engine of motor vehicle, has shaft comprising recess such that channel discharging fluid from lubricating area is formed between shaft and bearing
EP2872771B1 (en) High-pressure pump
WO2012080340A1 (en) High-pressure pump
DE102009028392A1 (en) High-pressure pump, particularly radial or reciprocating-piston-pump for fuel injection plant of air-compressing, self-igniting internal combustion engines, has pump assembly and drive shaft
EP2850318B1 (en) High pressure pump
DE102009003097B4 (en) High-pressure pump, in particular radial piston pump, with at least one plunger body, a rotatable roller shoe, a roller and an axial contact point for the roller, which is arranged at a distance from the axis of rotation of the roller
DE102012211976B3 (en) high pressure pump
WO2011003821A1 (en) Bearing for a radial piston pump
DE102012202717A1 (en) High pressure pump for use in common-rail injection system to convey e.g. diesel to diesel engine of motor car, has working chamber comprising dead volume that is narrowed by additional insert in addition to housing
DE102011076016A1 (en) High pressure pump for promotion of fluid, has one-piece formed housing portion with housing recess, and drive shaft with longitudinal axis
DE102007053803A1 (en) High-pressure pump for fuel injection device of internal-combustion engine i.e. diesel engine, has upper concave recess cooperating with corresponding shaping at cylinder head in form-fit manner such that component is pivoted movably
DE102009000949A1 (en) Radial piston pump for fuel high pressure production with common rail injection system of internal-combustion engine, has tappet guided into housing, and another tappet arranged in direction, where tappets are coupled in desmodromic manner

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: 20130515

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: 20160413

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: 812566

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160715

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: 502011010165

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20160713

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: 20160713

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: 20161113

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: 20161013

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: 20160713

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: 20160713

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: 20160713

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: 20160713

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

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: 20161114

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: 20160713

Ref country code: BE

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

Effective date: 20160930

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: 20161014

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: 20160713

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: 20160713

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: 20160713

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011010165

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: 20160713

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: 20160713

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: 20160713

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: 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: 20160713

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: 20160713

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: 20160713

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: 20160713

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: 20161013

26N No opposition filed

Effective date: 20170418

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

Effective date: 20161013

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: CH

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

Effective date: 20160930

Ref country code: GB

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

Effective date: 20161013

Ref country code: LI

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

Effective date: 20160930

Ref country code: IE

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

Effective date: 20160907

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: 20160713

Ref country code: LU

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

Effective date: 20160907

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: 812566

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160907

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20160930

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: 20160907

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: 20110907

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: 20160713

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: 20160713

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: 20160713

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: 20160713

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

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

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: 20160713

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

Ref country code: FR

Payment date: 20180921

Year of fee payment: 8

Ref country code: IT

Payment date: 20180921

Year of fee payment: 8

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

Ref country code: DE

Payment date: 20181121

Year of fee payment: 8

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502011010165

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: 20200401

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: 20190907

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: 20190930