EP2188525A1 - Pump, particularly high-pressure fuel pump - Google Patents

Pump, particularly high-pressure fuel pump

Info

Publication number
EP2188525A1
EP2188525A1 EP08802955A EP08802955A EP2188525A1 EP 2188525 A1 EP2188525 A1 EP 2188525A1 EP 08802955 A EP08802955 A EP 08802955A EP 08802955 A EP08802955 A EP 08802955A EP 2188525 A1 EP2188525 A1 EP 2188525A1
Authority
EP
European Patent Office
Prior art keywords
pump
drive shaft
pump piston
coupling device
indirectly
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
EP08802955A
Other languages
German (de)
French (fr)
Other versions
EP2188525B1 (en
Inventor
Friedrich Boecking
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 EP2188525A1 publication Critical patent/EP2188525A1/en
Application granted granted Critical
Publication of EP2188525B1 publication Critical patent/EP2188525B1/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
    • F04B1/0426—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 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
  • This pump has at least one pump piston, which is tightly guided in a cylinder bore of a housing part of the pump.
  • the pump also has a drive shaft, which with a
  • Drive section is provided in the form of a cam or eccentric, by which the at least one pump piston is driven at least indirectly in a stroke movement.
  • the at least one pump piston is acted upon by a spring element at least indirectly to the drive portion of the drive shaft. During the delivery stroke of the pump piston this is against the force of
  • the spring element is moved into the cylinder bore through the drive section and during the suction stroke of the pump piston this is moved out of the cylinder bore by the force of the spring element.
  • the spring element is designed as a cylindrical helical compression spring, which surrounds the housing part, in which the cylinder bore is formed and the pump piston is arranged. This arrangement of the spring element causes the wall thickness of the housing part in the cylinder bore surrounding area must be kept relatively low to allow the arrangement of the spring element. As a result of the high pressure generated during the delivery stroke of the pump piston, there may be a widening of the cylinder bore due to the relatively small wall thickness of the housing part, so that leakage losses occur. Disclosure of the invention
  • the pump according to the invention with the features of claim 1 has the advantage that by the arrangement of the spring element on the pump piston opposite side of the drive shaft, the housing part in the cylinder bore surrounding area can be formed with a large wall thickness, so that no or only small leakage losses caused by a widening of the cylinder bore.
  • FIG. 1 shows a detail of a pump in a longitudinal section
  • FIG. 2 shows the pump in a cross section along line N-II in FIG. 1
  • FIG. 3 shows a modified embodiment of the pump in cross section N-II.
  • 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 10, which may be designed in several parts and in which in a housing part 12, a rotationally driven drive shaft 14 is rotatably disposed about an axis of rotation 15.
  • the drive shaft 14 is mounted in the housing part 12 via two spaced apart in the direction of the axis of rotation 15 of the drive shaft 14 bearing points.
  • the drive shaft 14 has at least one drive section 16, which is a cam or an eccentric can be.
  • the pump has at least one or more pump elements, each with a pump piston 20 which is driven by the drive portion 16 of the drive shaft 14 at least indirectly in a lifting movement in at least approximately radial direction to the axis of rotation 15 of the drive shaft 14.
  • the pump piston 20 is in a cylinder bore 22 of a housing part
  • the pump piston 20 in the cylinder bore 22 defines a pump working chamber 26.
  • the pump working chamber 26 has an inlet check valve 30 opening into this connection with a feed 34 coming from a feed pump 32, via which the pump working space
  • the pump working chamber 26 is directed at the radially inwardly to the rotational axis 15 of the drive shaft 14 directed suction stroke of the pump piston 20 with fuel.
  • the pump working chamber 26 also has an outlet check valve 36 which opens out of this connection with a drain 38 which leads, for example, to a high-pressure fuel accumulator 40 and fuel via the delivery stroke of the pump piston 20 directed radially outward from the rotational axis 15 of the drive shaft 14 the pump working space 26 is displaced.
  • the housing part 24 has a flange-like portion 42 which on
  • Housing 12 rests, and projecting from the area 42 cylindrical projection 44, which projects into an at least approximately radially to the axis of rotation 15 of the drive shaft 14 extending opening 46, which is formed for example as a bore in the housing part 12.
  • the cylinder bore 22 extends from the end face of the projection 44 through the projection 44 into the
  • the drive portion 16 of the drive shaft 14 is formed as shown in FIG 2 as a double cam and the pump piston 20 is supported via a roller tappet 48 on the double cam. - A -
  • the roller tappet 48 comprises a sleeve-shaped tappet body 50 guided in the bore 46 of the housing part 24, a roller shoe 52 inserted in the tappet body 50 and a roller 54 rotatably mounted in a housing 53 in the roller shoe 52.
  • the roller 54 rolls on the double cam 16 and is slid in the receptacle 53.
  • the plunger body 50 may also be guided over its inner jacket on the projection 44 of the housing part 24.
  • the pump piston 20 has an enlarged diameter in relation to the area guided in the cylinder bore 22 in the area of the piston foot, via which the pump piston 20 is coupled to the roller tappet 48 in the direction of its longitudinal axis.
  • the drive portion 16 of the drive shaft 14 is formed as an eccentric, wherein the pump piston 20 directly or via a plunger, such as a cup tappet 148, on the eccentric or on one on the Eccentric rotatably mounted ring 150 is applied.
  • the ring 150 may have an at least approximately flat flattening 152 in the region of the abutment of the pump piston 20 or of the plunger 148.
  • the spring element 56 is arranged on the pump piston 20 opposite side of the drive shaft 14 in the housing 10 of the pump.
  • the spring element 56 engages via a coupling device 58 at least indirectly on the pump piston 20.
  • the coupling device 58 is connected to the plunger body 50 of the roller tappet 48 and the plunger 148 and thus indirectly via this with the pump piston 20.
  • the coupling device 58 has for example two carrier-shaped parts 60, wherein in each case a carrier 60 laterally adjacent to the drive section 16 of the drive shaft 14 is arranged.
  • Carrier 60 are formed so that they have a small thickness as shown in Figure 1 in the direction of the axis of rotation 15 of the drive shaft 14. Viewed in the direction of the axis of rotation 15 of the drive shaft 15, the carriers 60, as shown in FIGS. 2 and 3, have a central hub-like region 62 with a large width in the area of the drive shaft 14 and adjoining it the drive shaft 14 radially extending arms 64 with a smaller width. The arms 64 are arranged at least approximately diametrically opposite each other. In the hub region 62 of the carrier 60, a slot 66 is respectively introduced, through which the drive shaft 14 passes.
  • the two carriers 60 of the coupling device 58 are preferably formed identically to the
  • the arms 64 of the carriers 60 of the coupling device 58 which extend to the tappet body 50 are connected at their end regions to the tappet body 50 or the tappet 148, for example by means of screws, rivets, by a welded connection or in some other way.
  • the arms 64 of the carrier 60 of the coupling device 58 extend approximately to the level of the foot of the pump piston 20 and terminate at a distance in front of the end face of the projection 44 of the housing part 24.
  • the spring element 56 is designed, for example, as a cylindrical helical compression spring and clamped between the component 68 and a housing 10 of the pump, the drive portion 16 of the drive shaft 14 arranged adjacent stationary support 70.
  • Support 70 is arranged at a sufficient distance from the drive section 16 in order to avoid contact with the drive section 16 during the rotation of the drive shaft 14.
  • Roller tappet 48 a lifting movement.
  • This lifting movement also carries out the coupling device 58, wherein the spring element 56 is alternately compressed and relaxed.
  • the coupling device 58 Through the elongated holes 66 in the carriers 60 of the coupling device 58, the lifting movement of the coupling device 58 with respect to the drive shaft 14 is made possible. Due to the arrangement of the
  • Spring element 56 on the pump piston 20 opposite side of the drive shaft 14 is between the portion 44 of the housing part 24 and the bore 46 in the housing part 12, only an annular gap with a small width for receiving the plunger body 50 is required.
  • the plunger body 50 can be designed with a small wall thickness, so that the annular gap is correspondingly narrow can be held. This allows an embodiment of the projection 44 of the housing part 24 up to the front side with a large wall thickness, whereby the cylinder bore 22 under the action of the high pressure in the pump working chamber 26 during delivery of the pump piston 20 only slightly expands and correspondingly low leakage losses from the
  • the pump may also have a plurality of, for example, two pump pistons 20.
  • the two pump piston 20 can thereby at an angle of about
  • the coupling devices 58 of the two pump pistons 20 preferably extend in the direction of the axis of rotation 15 of the drive shaft 14 to each other, so that they do not interfere with each other.

Landscapes

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

Abstract

The invention relates to a pump, particularly a high-pressure fuel pump, having a housing, a drive shaft that is rotationally driven and has at least one drive section, and at least one pump piston, which is guided in a cylinder bore of a housing part of the pump in a sealed manner and which is driven by the drive section of the drive shaft at least indirectly in a lifting motion. The at least one pump piston is acted on by a spring element at least indirectly toward the drive section of the drive shaft. The spring element is disposed on the side of the drive shaft opposite the pump piston, and via a coupling device extending past the drive shaft it engages at least indirectly on the pump piston.

Description

Titel title
Pumpe, insbesondere KraftstoffhochdruckpumpePump, in particular high-pressure fuel pump
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 dieSuch a pump in the form of a high-pressure fuel pump is through
DE 198 48 040 Al bekannt. Diese Pumpe weist wenigstens einen Pumpenkolben auf, der in einer Zylinderbohrung eines Gehäuseteils der Pumpe dicht geführt ist. Die Pumpe weist außerdem eine Antriebswelle auf, die mit einemDE 198 48 040 Al known. This pump has at least one pump piston, which is tightly guided in a cylinder bore of a housing part of the pump. The pump also has a drive shaft, which with a
Antriebsabschnitt in Form eines Nockens oder Exzenters versehen ist, durch den der wenigstens eine Pumpenkolben zumindest mittelbar in einer Hubbewegung angetrieben wird. Der wenigstens eine Pumpenkolben ist durch ein Federelement zumindest mittelbar zum Antriebsabschnitt der Antriebswelle hin beaufschlagt. Beim Förderhub des Pumpenkolbens wird dieser gegen die Kraft desDrive section is provided in the form of a cam or eccentric, by which the at least one pump piston is driven at least indirectly in a stroke movement. The at least one pump piston is acted upon by a spring element at least indirectly to the drive portion of the drive shaft. During the delivery stroke of the pump piston this is against the force of
Federelements durch den Antriebsabschnitt in die Zylinderbohrung hineinbewegt und beim Saughub des Pumpenkolbens wird dieser durch die Kraft des Federelements aus der Zylinderbohrung herausbewegt. Das Federelement ist als eine zylindrische Schraubendruckfeder ausgebildet, die das Gehäuseteil, in dem die Zylinderbohrung ausgebildet ist und der Pumpenkolben angeordnet ist, umgibt. Diese Anordnung des Federelements führt dazu, dass die Wandstärke des Gehäuseteils in dessen die Zylinderbohrung umgebendem Bereich relativ gering gehalten werden muss, um die Anordnung des Federelements zu ermöglichen. Infolge des beim Förderhub des Pumpenkolbens erzeugten Hochdrucks kann es wegen der relativ geringen Wandstärke des Gehäuseteils zu einer Aufweitung der Zylinderbohrung kommen, so dass Leckageverluste auftreten. Offenbarung der ErfindungSpring element is moved into the cylinder bore through the drive section and during the suction stroke of the pump piston this is moved out of the cylinder bore by the force of the spring element. The spring element is designed as a cylindrical helical compression spring, which surrounds the housing part, in which the cylinder bore is formed and the pump piston is arranged. This arrangement of the spring element causes the wall thickness of the housing part in the cylinder bore surrounding area must be kept relatively low to allow the arrangement of the spring element. As a result of the high pressure generated during the delivery stroke of the pump piston, there may be a widening of the cylinder bore due to the relatively small wall thickness of the housing part, so that leakage losses occur. Disclosure of the invention
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Pumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass durch die Anordnung des Federelements auf der dem Pumpenkolben gegenüberliegenden Seite der Antriebswelle das Gehäuseteil in dessen die Zylinderbohrung umgebendem Bereich mit großer Wandstärke ausgebildet werden kann, so dass keine oder nur geringe Leckageverluste durch eine Aufweitung der Zylinderbohrung entstehen.The pump according to the invention with the features of claim 1 has the advantage that by the arrangement of the spring element on the pump piston opposite side of the drive shaft, the housing part in the cylinder bore surrounding area can be formed with a large wall thickness, so that no or only small leakage losses caused by a widening of the cylinder bore.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Pumpe angegeben. Durch die Ausbildung gemäß Anspruch 2 ist eine einfache Ausführung und platzsparende Anordnung der Kopplungsvorrichtung ermöglicht.In the dependent claims advantageous refinements and developments of the pump according to the invention are given. The embodiment according to claim 2, a simple design and space-saving arrangement of the coupling device allows.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ausschnittsweise eine Pumpe in einem Längsschnitt, Figur 2 die Pumpe in einem Querschnitt entlang Linie N-Il in Figur 1 und Figur 3 eine modifizierte Ausführung der Pumpe im Querschnitt N-Il.An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description. FIG. 1 shows a detail of a pump in a longitudinal section, FIG. 2 shows the pump in a cross section along line N-II in FIG. 1 and FIG. 3 shows a modified embodiment of the pump in cross section N-II.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In den Figuren 1 bis 3 ist eine Pumpe dargestellt, die insbesondere eine Kraftstoffhochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine ist. Die Pumpe weist ein Gehäuse 10 auf, das mehrteilig ausgebildet sein kann und in dem in einem Gehäuseteil 12 eine rotierend angetriebene Antriebswelle 14 um eine Drehachse 15 drehbar angeordnet ist. Die Antriebswelle 14 ist im Gehäuseteil 12 über zwei in Richtung der Drehachse 15 der Antriebswelle 14 voneinander beabstandete Lagerstellen gelagert. In einem zwischen den beiden Lagerstellen liegenden Bereich weist die Antriebswelle 14 wenigstens einen Antriebsabschnitt 16 auf, der ein Nocken oder ein Exzenter sein kann. Die Pumpe weist wenigstens ein oder mehrere Pumpenelemente mit jeweils einem Pumpenkolben 20 auf, der durch den Antriebsabschnitt 16 der Antriebswelle 14 zumindest mittelbar in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 15 der Antriebswelle 14 angetrieben wird. Der Pumpenkolben 20 ist in einer Zylinderbohrung 22 eines GehäuseteilsIn Figures 1 to 3, 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 10, which may be designed in several parts and in which in a housing part 12, a rotationally driven drive shaft 14 is rotatably disposed about an axis of rotation 15. The drive shaft 14 is mounted in the housing part 12 via two spaced apart in the direction of the axis of rotation 15 of the drive shaft 14 bearing points. In a region lying between the two bearing points, the drive shaft 14 has at least one drive section 16, which is a cam or an eccentric can be. The pump has at least one or more pump elements, each with a pump piston 20 which is driven by the drive portion 16 of the drive shaft 14 at least indirectly in a lifting movement in at least approximately radial direction to the axis of rotation 15 of the drive shaft 14. The pump piston 20 is in a cylinder bore 22 of a housing part
24 der Pumpe dicht geführt. Mit seinem der Antriebswelle 14 abgewandten Ende begrenzt der Pumpenkolben 20 in der Zylinderbohrung 22 einen Pumpenarbeitsraum 26. Der Pumpenarbeitsraum 26 weist über ein in diesen hinein öffnendes Einlassrückschlagventil 30 eine Verbindung mit einem von einer Förderpumpe 32 herführenden Zulauf 34 auf, über den der Pumpenarbeitsraum24 of the pump tightly guided. With its end facing away from the drive shaft 14, the pump piston 20 in the cylinder bore 22 defines a pump working chamber 26. The pump working chamber 26 has an inlet check valve 30 opening into this connection with a feed 34 coming from a feed pump 32, via which the pump working space
26 beim radial nach innen zur Drehachse 15 der Antriebswelle 14 gerichteten Saughub des Pumpenkolbens 20 mit Kraftstoff befüllt wird. Der Pumpenarbeitsraum 26 weist außerdem über ein aus diesem heraus öffnendes Auslassrückschlagventil 36 eine Verbindung mit einem Ablauf 38 auf, der beispielsweise zu einem Kraftstoffhochdruckspeicher 40 führt und über den beim radial nach außen von der Drehachse 15 der Antriebswelle 14 weg gerichteten Förderhub des Pumpenkolbens 20 Kraftstoff aus dem Pumpenarbeitsraum 26 verdrängt wird.26 is directed at the radially inwardly to the rotational axis 15 of the drive shaft 14 directed suction stroke of the pump piston 20 with fuel. The pump working chamber 26 also has an outlet check valve 36 which opens out of this connection with a drain 38 which leads, for example, to a high-pressure fuel accumulator 40 and fuel via the delivery stroke of the pump piston 20 directed radially outward from the rotational axis 15 of the drive shaft 14 the pump working space 26 is displaced.
Das Gehäuseteil 24 weist einen flanschartigen Bereich 42 auf, der amThe housing part 24 has a flange-like portion 42 which on
Gehäuseteil 12 aufliegt, und einen vom Bereich 42 abstehenden zylindrischen Ansatz 44 auf, der in eine zumindest annähernd radial zur Drehachse 15 der Antriebswelle 14 verlaufende Öffnung 46, die beispielsweise als Bohrung ausgebildet ist, im Gehäuseteil 12 hineinragt. Die Zylinderbohrung 22 verläuft ausgehend von der Stirnseite des Ansatzes 44 durch den Ansatz 44 bis in denHousing 12 rests, and projecting from the area 42 cylindrical projection 44, which projects into an at least approximately radially to the axis of rotation 15 of the drive shaft 14 extending opening 46, which is formed for example as a bore in the housing part 12. The cylinder bore 22 extends from the end face of the projection 44 through the projection 44 into the
Bereich 42, wo der Pumpenarbeitsraum 26 angeordnet ist. Im Bereich 42 sind auch das Einlassventil 30 und das Auslassventil 36 angeordnet. Am Übergang vom Bereich 42 zum Ansatz 44 ist ein im Durchmesser gegenüber dem Ansatz 44 größerer Zentrierbund 43 vorgesehen, der mit geringem Spiel in die Bohrung 46 eintritt und eine Zentrierung des Gehäuseteils 24 bezüglich des GehäuseteilsArea 42, where the pump chamber 26 is arranged. In the area 42, the inlet valve 30 and the outlet valve 36 are arranged. At the transition from the region 42 to the projection 44 a larger diameter centering collar 43 is provided in relation to the projection 44, which enters the bore 46 with little play and a centering of the housing part 24 with respect to the housing part
12 sicherstellt.12 ensures.
Beim dargestellten Ausführungsbeispiel ist der Antriebsabschnitt 16 der Antriebswelle 14 gemäß Figur 2 als Doppelnocken ausgebildet und der Pumpenkolben 20 stützt sich über einen Rollenstößel 48 am Doppelnocken ab. - A -In the illustrated embodiment, the drive portion 16 of the drive shaft 14 is formed as shown in FIG 2 as a double cam and the pump piston 20 is supported via a roller tappet 48 on the double cam. - A -
Der Rollenstößel 48 umfasst einen in der Bohrung 46 des Gehäuseteils 24 über seinen Außenmantel geführten hülsenförmigen Stößelkörper 50, einen im Stößelkörper 50 eingesetzten Rollenschuh 52 und eine in einer Aufnahme 53 im Rollenschuh 52 drehbar gelagerte Rolle 54. Die Rolle 54 rollt auf dem Doppelnocken 16 ab und ist in der Aufnahme 53 gleitend geführt. Alternativ kann der Stößelkörper 50 auch über seinen Innenmantel auf dem Ansatz 44 des Gehäuseteils 24 geführt sein. Der Pumpenkolben 20 weist einen im Durchmesser gegenüber dem in der Zylinderbohrung 22 geführten Bereich vergrößerten Kolbenfuß auf, über den der Pumpenkolben 20 mit dem Rollenstößel 48 in Richtung seiner Längsachse gekoppelt ist.The roller tappet 48 comprises a sleeve-shaped tappet body 50 guided in the bore 46 of the housing part 24, a roller shoe 52 inserted in the tappet body 50 and a roller 54 rotatably mounted in a housing 53 in the roller shoe 52. The roller 54 rolls on the double cam 16 and is slid in the receptacle 53. Alternatively, the plunger body 50 may also be guided over its inner jacket on the projection 44 of the housing part 24. The pump piston 20 has an enlarged diameter in relation to the area guided in the cylinder bore 22 in the area of the piston foot, via which the pump piston 20 is coupled to the roller tappet 48 in the direction of its longitudinal axis.
Alternativ kann auch gemäß einer in Figur 3 dargestellten modifizierten Ausführung der Pumpe vorgesehen sein, dass der Antriebsabschnitt 16 der Antriebswelle 14 als Exzenter ausgebildet ist, wobei der Pumpenkolben 20 direkt oder über einen Stößel, beispielsweise einen Tassenstößel 148, am Exzenter oder an einem auf dem Exzenter drehbar gelagerten Ring 150 anliegt. Der Ring 150 kann im Bereich der Anlage des Pumpenkolbens 20 bzw. des Stößels 148 eine zumindest annähernd ebene Abflachung 152 aufweisen.Alternatively, according to a modified embodiment of the pump shown in Figure 3 may be provided that the drive portion 16 of the drive shaft 14 is formed as an eccentric, wherein the pump piston 20 directly or via a plunger, such as a cup tappet 148, on the eccentric or on one on the Eccentric rotatably mounted ring 150 is applied. The ring 150 may have an at least approximately flat flattening 152 in the region of the abutment of the pump piston 20 or of the plunger 148.
Die Anlage des Pumpenkolbens 20 über den Rollenstößel 48 amThe system of the pump piston 20 via the roller tappet 48 on
Antriebsabschnitt 16 der Antriebswelle 14 beim Saughub des Pumpenkolbens 20 wird durch ein Federelement 56 sichergestellt. Das Federelement 56 ist auf der dem Pumpenkolben 20 gegenüberliegenden Seite der Antriebswelle 14 im Gehäuse 10 der Pumpe angeordnet. Das Federelement 56 greift über eine Kopplungsvorrichtung 58 zumindest mittelbar am Pumpenkolben 20 an. Beim dargestellten Ausführungsbeispiel ist die Kopplungsvorrichtung 58 mit dem Stößelkörper 50 des Rollenstößels 48 bzw. dem Stößel 148 verbunden und über diesen somit mittelbar mit dem Pumpenkolben 20. Die Kopplungsvorrichtung 58 weist beispielsweise zwei trägerförmige Teile 60 auf, wobei jeweils ein Träger 60 seitlich neben dem Antriebsabschnitt 16 der Antriebswelle 14 angeordnet ist. DieDrive section 16 of the drive shaft 14 during the suction stroke of the pump piston 20 is ensured by a spring element 56. The spring element 56 is arranged on the pump piston 20 opposite side of the drive shaft 14 in the housing 10 of the pump. The spring element 56 engages via a coupling device 58 at least indirectly on the pump piston 20. In the illustrated embodiment, the coupling device 58 is connected to the plunger body 50 of the roller tappet 48 and the plunger 148 and thus indirectly via this with the pump piston 20. The coupling device 58 has for example two carrier-shaped parts 60, wherein in each case a carrier 60 laterally adjacent to the drive section 16 of the drive shaft 14 is arranged. The
Träger 60 sind so ausgebildet, dass diese wie in Figur 1 dargestellt in Richtung der Drehachse 15 der Antriebswelle 14 eine geringe Dicke aufweisen. In Richtung der Drehachse 15 der Antriebswelle 15 betrachtet weisen die Träger 60 wie in den Figuren 2 und 3 dargestellt einen mittleren nabenartigen Bereich 62 mit großer Breite im Bereich der Antriebswelle 14 und an diesen anschließende, von der Antriebswelle 14 radial wegverlaufende Arme 64 mit geringerer Breite auf. Die Arme 64 sind einander zumindest annähernd diametral gegenüberliegende angeordnet. Im Nabenbereich 62 der Träger 60 ist jeweils ein Langloch 66 eingebracht, durch das die Antriebswelle 14 hindurchtritt. Die beiden Träger 60 der Kopplungsvorrichtung 58 sind vorzugsweise identisch ausgebildet, um denCarrier 60 are formed so that they have a small thickness as shown in Figure 1 in the direction of the axis of rotation 15 of the drive shaft 14. Viewed in the direction of the axis of rotation 15 of the drive shaft 15, the carriers 60, as shown in FIGS. 2 and 3, have a central hub-like region 62 with a large width in the area of the drive shaft 14 and adjoining it the drive shaft 14 radially extending arms 64 with a smaller width. The arms 64 are arranged at least approximately diametrically opposite each other. In the hub region 62 of the carrier 60, a slot 66 is respectively introduced, through which the drive shaft 14 passes. The two carriers 60 of the coupling device 58 are preferably formed identically to the
Fertigungsaufwand gering zu halten.To keep production costs low.
Die zum Stößelkörper 50 verlaufenden Arme 64 der Träger 60 der Kopplungsvorrichtung 58 sind an ihren Endbereichen mit dem Stößelkörper 50 bzw. dem Stößel 148 verbunden, beispielsweise mittels Schrauben, Nieten, durch eine Schweißverbindung oder auf andere Weise. Die Arme 64 der Träger 60 der Kopplungsvorrichtung 58 erstrecken sich etwa bis auf Höhe des Fußes des Pumpenkolbens 20 und enden mit Abstand vor der Stirnseite des Ansatzes 44 des Gehäuseteils 24. Die auf der dem Pumpenkolben 20 abgewandten Seite der Antriebswelle 14 angeordneten Arme 64 der Träger 60 der KopplungsvorrichtungThe arms 64 of the carriers 60 of the coupling device 58 which extend to the tappet body 50 are connected at their end regions to the tappet body 50 or the tappet 148, for example by means of screws, rivets, by a welded connection or in some other way. The arms 64 of the carrier 60 of the coupling device 58 extend approximately to the level of the foot of the pump piston 20 and terminate at a distance in front of the end face of the projection 44 of the housing part 24. The arranged on the pump piston 20 side facing away from the drive shaft 14 arms 64 of the carrier 60 of the coupling device
58 sind mittels eines tellerförmigen Bauteils 68 an ihren Enden miteinander verbunden. Das Federelement 56 ist beispielsweise als zylindrische Schraubendruckfeder ausgebildet und zwischen dem Bauteil 68 und einer im Gehäuse 10 der Pumpe dem Antriebsabschnitt 16 der Antriebswelle 14 benachbart angeordneten ortsfesten Abstützung 70 eingespannt. Die ortsfeste58 are connected together by means of a plate-shaped member 68 at their ends. The spring element 56 is designed, for example, as a cylindrical helical compression spring and clamped between the component 68 and a housing 10 of the pump, the drive portion 16 of the drive shaft 14 arranged adjacent stationary support 70. The stationary
Abstützung 70 ist dabei mit ausreichend Abstand vom Antriebsabschnitt 16 angeordnet, um bei der Drehung der Antriebswelle 14 eine Berührung mit dem Antriebsabschnitt 16 zu vermeiden.Support 70 is arranged at a sufficient distance from the drive section 16 in order to avoid contact with the drive section 16 during the rotation of the drive shaft 14.
Beim Betrieb der Pumpe führt der Pumpenkolben 20 zusammen mit demDuring operation of the pump, the pump piston 20 leads together with the
Rollenstößel 48 eine Hubbewegung aus. Diese Hubbewegung führt auch die Kopplungsvorrichtung 58 aus, wobei das Federelement 56 abwechselnd komprimiert und entspannt wird. Durch die Langlöcher 66 in den Trägern 60 der Kopplungsvorrichtung 58 ist die Hubbewegung der Kopplungsvorrichtung 58 bezüglich der Antriebswelle 14 ermöglicht. Durch die Anordnung desRoller tappet 48 a lifting movement. This lifting movement also carries out the coupling device 58, wherein the spring element 56 is alternately compressed and relaxed. Through the elongated holes 66 in the carriers 60 of the coupling device 58, the lifting movement of the coupling device 58 with respect to the drive shaft 14 is made possible. Due to the arrangement of the
Federelements 56 auf der dem Pumpenkolben 20 gegenüberliegenden Seite der Antriebswelle 14 ist zwischen dem Abschnitt 44 des Gehäuseteils 24 und der Bohrung 46 im Gehäuseteil 12 nur ein Ringspalt mit geringer Breite zur Aufnahme des Stößelkörpers 50 erforderlich. Der Stößelkörper 50 kann dabei mit geringer Wandstärke ausgeführt werden, so dass der Ringspalt entsprechend schmal gehalten werden kann. Dies ermöglicht eine Ausführung des Ansatzes 44 des Gehäuseteils 24 bis zu dessen Stirnseite mit großer Wandstärke, wodurch sich die Zylinderbohrung 22 unter der Wirkung des Hochdrucks im Pumpenarbeitsraum 26 beim Förderhub des Pumpenkolbens 20 nur wenig aufweitet und entsprechend geringe Leckageverluste aus demSpring element 56 on the pump piston 20 opposite side of the drive shaft 14 is between the portion 44 of the housing part 24 and the bore 46 in the housing part 12, only an annular gap with a small width for receiving the plunger body 50 is required. The plunger body 50 can be designed with a small wall thickness, so that the annular gap is correspondingly narrow can be held. This allows an embodiment of the projection 44 of the housing part 24 up to the front side with a large wall thickness, whereby the cylinder bore 22 under the action of the high pressure in the pump working chamber 26 during delivery of the pump piston 20 only slightly expands and correspondingly low leakage losses from the
Pumpenarbeitsraum 26 auftreten.Pump workspace 26 occur.
Bei der vorstehenden Beschreibung ist nur ein Pumpenkolben 20 erläutert, wobei die Pumpe auch mehrere, beispielsweise zwei Pumpenkolben 20 aufweisen kann. Die beiden Pumpenkolben 20 können dabei unter einem Winkel von etwaIn the above description, only one pump piston 20 is explained, wherein the pump may also have a plurality of, for example, two pump pistons 20. The two pump piston 20 can thereby at an angle of about
90° um die Drehachse 15 der Antriebswelle 14 zueinander verdreht angeordnet sein, wobei dann an jedem Pumpenkolben 20 über eine Kopplungsvorrichtung 58 das zugeordnete Federelement 56 angreift, das auf der dem Pumpenkolben 20 gegenüberliegenden Seite der Antriebswelle 14 angeordnet ist. Die Kopplungsvorrichtungen 58 der beiden Pumpenkolben 20 verlaufen dabei vorzugsweise in Richtung der Drehachse 15 der Antriebswelle 14 zu einander versetzt, so dass diese sich gegenseitig nicht behindern. 90 ° about the rotational axis 15 of the drive shaft 14 to be arranged rotated to each other, in which case the associated spring element 56 engages on each pump piston 20 via a coupling device 58, which is arranged on the pump piston 20 opposite side of the drive shaft 14. The coupling devices 58 of the two pump pistons 20 preferably extend in the direction of the axis of rotation 15 of the drive shaft 14 to each other, so that they do not interfere with each other.

Claims

Ansprüche claims
1. Pumpe, insbesondere Kraftstoffhochdruckpumpe, mit einem Gehäuse (10,12,24), mit einer Antriebswelle (14), die rotierend angetrieben wird und wenigstens einen Antriebsabschnitt (16) aufweist, mit wenigstens einem Pumpenkolben (20), der in einer Zylinderbohrung (22) eines Gehäuseteils (24) der Pumpe dicht geführt ist und der durch den Antriebsabschnitt (16) der1. Pump, in particular high-pressure fuel pump, with a housing (10,12,24), with a drive shaft (14) which is driven in rotation and at least one drive portion (16), with at least one pump piston (20) in a cylinder bore (22) of a housing part (24) of the pump is tightly guided and by the drive section (16) of the
Antriebswelle (14) zumindest mittelbar in einer Hubbewegung angetrieben wird, wobei der wenigstens eine Pumpenkolben (20) durch ein Federelement (56) zumindest mittelbar zum Antriebsabschnitt (16) der Antriebswelle (14) hin beaufschlagt ist, dadurch gekennzeichnet, dass das Federelement (56) auf der dem Pumpenkolben (20) gegenüberliegenden Seite der Antriebswelle (14) angeordnet ist und über eine an der Antriebswelle (14) vorbei verlaufende Kopplungsvorrichtung (58) zumindest mittelbar am Pumpenkolben (20) angreift.Drive shaft (14) is driven at least indirectly in a lifting movement, wherein the at least one pump piston (20) by a spring element (56) at least indirectly to the drive portion (16) of the drive shaft (14) is acted upon, characterized in that the spring element (56 ) is arranged on the pump piston (20) opposite side of the drive shaft (14) and at least indirectly on the drive shaft (14) extending coupling device (58) on the pump piston (20) engages.
2. Pumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Kopplungsvorrichtung (58) zwei Teile (60) aufweist, wobei jeweils ein Teil (60) seitlich neben dem Antriebsabschnitt (16) der Antriebswelle (14) angeordnet ist und zumindest mittelbar mit dem Pumpenkolben (20) verbunden ist.2. Pump according to claim 1, characterized in that the coupling device (58) has two parts (60), wherein in each case a part (60) laterally adjacent to the drive portion (16) of the drive shaft (14) is arranged and at least indirectly with the pump piston (20) is connected.
3. Pumpe nach Anspruch 2, dadurch gekennzeichnet, dass die beiden Teile (60) der Kopplungsvorrichtung (58) jeweils ein Langloch (66) aufweisen, durch das die3. Pump according to claim 2, characterized in that the two parts (60) of the coupling device (58) each have a slot (66) through which the
Antriebswelle (14) hindurchtritt.Drive shaft (14) passes.
4. Pumpe nach einem der Anspruch 3, dadurch gekennzeichnet, dass die Teile (60) der Kopplungsvorrichtung (58) in Richtung der Drehachse (15) der Antriebswelle (14) betrachtet jeweils einen mittleren Bereich (62) mit großer4. Pump according to one of claim 3, characterized in that the parts (60) of the coupling device (58) in the direction of the axis of rotation (15) of the drive shaft (14) viewed in each case a central region (62) with large
Breite aufweisen, in dem das Langloch (66) angeordnet ist, und jeweils zwei vom mittleren Bereich (62) ausgehende, einander gegenüberliegende Arme (64) mit geringerer Breite aufweisen. Have width, in which the slot (66) is arranged, and each have two from the central region (62) extending, opposing arms (64) having a smaller width.
5. Pumpe nach Anspruch 4, dadurch gekennzeichnet, dass die dem Pumpenkolben (20) zugewandten Arme (64) der Teile (60) der Kopplungsvorrichtung (58) an ihren Endbereichen zumindest mittelbar mit dem Pumpenkolben (20) verbunden sind.5. Pump according to claim 4, characterized in that the pump piston (20) facing arms (64) of the parts (60) of the coupling device (58) are connected at their end portions at least indirectly with the pump piston (20).
6. Pumpe nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass das Federelement (56) zwischen den Endbereichen der dem Pumpenkolben (20) abgewandten Arme (64) der Kopplungsvorrichtung (58) und einer nahe der Antriebswelle (14) angeordneten ortsfesten Abstützung (70) eingespannt ist.6. Pump according to claim 4 or 5, characterized in that the spring element (56) between the end regions of the pump piston (20) facing away from arms (64) of the coupling device (58) and a near the drive shaft (14) arranged stationary support (70 ) is clamped.
7. Pumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Pumpenkolben (20) über ein Stützelement (48) am Antriebsabschnitt (16) der Antriebswelle (14) anliegt und dass die Kopplungsvorrichtung (58) mit dem Stützelement (48) verbunden ist. 7. Pump according to one of the preceding claims, characterized in that the pump piston (20) via a support element (48) on the drive portion (16) of the drive shaft (14) and that the coupling device (58) with the support member (48) is connected ,
EP08802955A 2007-08-16 2008-08-01 Pump, particularly high-pressure fuel pump Not-in-force EP2188525B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007038525A DE102007038525A1 (en) 2007-08-16 2007-08-16 Pump, in particular high-pressure fuel pump
PCT/EP2008/060172 WO2009021865A1 (en) 2007-08-16 2008-08-01 Pump, particularly high-pressure fuel pump

Publications (2)

Publication Number Publication Date
EP2188525A1 true EP2188525A1 (en) 2010-05-26
EP2188525B1 EP2188525B1 (en) 2011-07-20

Family

ID=40010491

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08802955A Not-in-force EP2188525B1 (en) 2007-08-16 2008-08-01 Pump, particularly high-pressure fuel pump

Country Status (8)

Country Link
US (1) US8337178B2 (en)
EP (1) EP2188525B1 (en)
JP (1) JP5119332B2 (en)
KR (1) KR20100042646A (en)
CN (1) CN101779038B (en)
AT (1) ATE517257T1 (en)
DE (1) DE102007038525A1 (en)
WO (1) WO2009021865A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008000824A1 (en) * 2008-03-26 2009-10-01 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump
DE102010041340A1 (en) * 2010-09-24 2012-03-29 Robert Bosch Gmbh dowel pin
CN101985920B (en) * 2010-10-27 2012-07-04 牛彦波 Annular super-high pressure booster for water cutting machine or water cleaning machine
JP2013130114A (en) * 2011-12-21 2013-07-04 Bosch Corp Fuel supply pump
JP5677329B2 (en) * 2012-01-20 2015-02-25 日立オートモティブシステムズ株式会社 High pressure fuel supply pump with electromagnetically driven suction valve
DE102014220878A1 (en) * 2014-10-15 2016-04-21 Continental Automotive Gmbh High-pressure fuel pump

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1893216A (en) * 1928-03-15 1933-01-03 Abraham M Babitch Linkage for fuel pumps
US1893217A (en) * 1928-09-10 1933-01-03 Abraham M Babitch Fuel pump with lost motion lever
US2036452A (en) * 1934-12-06 1936-04-07 Gen Motors Corp Fuel pump
US2139347A (en) * 1936-04-08 1938-12-06 Gen Motors Corp Fuel pump
US2359960A (en) * 1943-08-12 1944-10-10 Chicago & Southern Air Lines I Pumping mechanism
US3314365A (en) * 1964-08-24 1967-04-18 Douglas E Ritchie Direct acting variable pump
DE7305570U (en) 1973-02-14 1973-08-16 Zahnradfabrik Friedrichshafen Ag Resilient mounting of the piston in a radial piston machine
US3924970A (en) * 1973-11-28 1975-12-09 Gen Motors Corp Electrically controlled fuel pump
DE4027794C2 (en) * 1990-09-01 2002-06-20 Continental Teves Ag & Co Ohg Hydraulic radial piston pump
DE19503621A1 (en) * 1995-02-03 1996-08-08 Bosch Gmbh Robert Reciprocating pump
DE19848040A1 (en) 1998-10-17 2000-04-20 Bosch Gmbh Robert Radial piston pump for high fuel pressure in IC engines with common-rail injection systems has two plates engaging fully on each other, and second back pressure valve between first plate and pump housing
US6506033B2 (en) * 2000-10-26 2003-01-14 Okenseiko Co., Ltd. Miniature pump with ball-plate drive
JP4439723B2 (en) * 2000-12-28 2010-03-24 株式会社ミクニ Fuel pump
DE102008000824A1 (en) * 2008-03-26 2009-10-01 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009021865A1 *

Also Published As

Publication number Publication date
KR20100042646A (en) 2010-04-26
CN101779038A (en) 2010-07-14
US20110200463A1 (en) 2011-08-18
JP5119332B2 (en) 2013-01-16
US8337178B2 (en) 2012-12-25
ATE517257T1 (en) 2011-08-15
CN101779038B (en) 2012-11-14
JP2010537096A (en) 2010-12-02
EP2188525B1 (en) 2011-07-20
WO2009021865A1 (en) 2009-02-19
DE102007038525A1 (en) 2009-02-19

Similar Documents

Publication Publication Date Title
EP2076669B1 (en) Tappet assembly for a high-pressure pump and high-pressure pump comprising at least one tappet assembly
EP2585707B1 (en) Pump, in particular a high-pressure fuel pump
EP1931875B1 (en) High pressure pump, in particular for a fuel injection device of an internal combustion engine
EP2235368B1 (en) Pump, particularly high-pressure fuel pump
EP1714030B1 (en) High-pressure pump, particularly for a fuel injection device of a combustion engine
WO2005111405A1 (en) High-pressure pump for a fuel injection device pertaining to an internal combustion engine
EP2464866B1 (en) High pressure pump
EP2188525B1 (en) Pump, particularly high-pressure fuel pump
EP2271838B1 (en) Pump, particularly a high-pressure fuel pump
WO2013092968A2 (en) Pump, in particular a high pressure fuel pump for a fuel injection device
WO2005031151A1 (en) Tappet for a high-pressure pump and high-pressure pump comprising at least one tappet
EP3014107B1 (en) Pumping device, in particular high pressure fuel pumping device for a fuel injection device
DE10345061A1 (en) Plunger assembly for a high pressure pump and high pressure pump with at least one plunger assembly
DE10337847A1 (en) Pump arrangement with a high-pressure pump and a low-pressure pump upstream of this for a fuel injection device of an internal combustion engine
EP2134966B1 (en) Pump, in particular high-pressure fuel pump
WO2012045541A1 (en) Bearing element having a roller rotatably mounted therein, in particular in the drive of a pump piston of a high-pressure fuel pump
DE10313745A1 (en) High pressure pump for IC engine fuel injection device e.g. for automobile, with hydrodynamic lubrication of bearings for ring segments operating pistons of pump elements
DE10355028A1 (en) High pressure pump especially for vehicle has the piston rod and cam follower made in one piece and spring loaded to press onto the drive cam
EP2635797B1 (en) Pump, in particular high-pressure fuel pump
WO2016142072A1 (en) High-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine
WO2013037543A1 (en) Pump, in particular a high-pressure fuel pump
WO2012059319A1 (en) Pump, in particular a high-pressure fuel pump
DE102004053270A1 (en) High-pressure pump, in particular for a fuel injection device of an internal combustion engine

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: 20100316

AK Designated contracting states

Kind code of ref document: A1

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

AX Request for extension of the european patent

Extension state: AL BA MK RS

17Q First examination report despatched

Effective date: 20100706

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

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

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502008004270

Country of ref document: DE

Effective date: 20110922

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20110720

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: 20110720

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: 20111121

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: 20111120

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: 20110720

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: 20110720

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: 20110720

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: 20110720

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: 20111020

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: 20110720

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

BERE Be: lapsed

Owner name: ROBERT BOSCH G.M.B.H.

Effective date: 20110831

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

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: 20111021

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: 20110720

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: 20110720

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: 20110720

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: 20110720

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 NON-PAYMENT OF DUE FEES

Effective date: 20110831

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

Ref country code: SK

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

Effective date: 20110720

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: 20110720

Ref country code: IE

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: 20110720

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: 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: 20110720

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: 20110720

Ref country code: BE

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

Effective date: 20110831

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: 20110720

26N No opposition filed

Effective date: 20120423

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

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: 20110720

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20120525

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502008004270

Country of ref document: DE

Effective date: 20120423

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: 20110920

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: 20120801

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: 20120831

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: 20111031

Ref country code: CH

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

Effective date: 20120831

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

Ref country code: LU

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

Effective date: 20110801

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

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: 20111020

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: 20120801

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: 20110720

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

Effective date: 20110720

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 517257

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130801

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: 20130801

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

Ref country code: DE

Payment date: 20171026

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502008004270

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: 20190301