EP1576288A1 - Pompe a piston radial pourvue d'une garniture d'etancheite plane entre le flasque et le carter - Google Patents

Pompe a piston radial pourvue d'une garniture d'etancheite plane entre le flasque et le carter

Info

Publication number
EP1576288A1
EP1576288A1 EP03799410A EP03799410A EP1576288A1 EP 1576288 A1 EP1576288 A1 EP 1576288A1 EP 03799410 A EP03799410 A EP 03799410A EP 03799410 A EP03799410 A EP 03799410A EP 1576288 A1 EP1576288 A1 EP 1576288A1
Authority
EP
European Patent Office
Prior art keywords
piston pump
radial piston
pump
radial
fuel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP03799410A
Other languages
German (de)
English (en)
Inventor
Burkhard Boos
Alfons Schoetz
Matthias Distel
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 EP1576288A1 publication Critical patent/EP1576288A1/fr
Withdrawn legal-status Critical Current

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
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • 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
    • F04B1/0421—Cylinders

Definitions

  • the invention relates to a radial piston pump, with
  • a flange part a housing part, an interior space and a suction space
  • An eccentric drive shaft which extends in the axial direction through the interior and actuates the piston in the radial direction, so that the piston delivers fuel from the suction chamber into the pump volume, pressurizes the fuel in the pump volume and delivers it out of the pump volume under high pressure , and
  • Radial piston pumps of this type are used in injection systems for combustion processes, in particular for generating injection pressures of more than 1000 bar in Co mon rail direct injection systems for combustion processes.
  • the suction chamber is supplied with fuel from a low-pressure pump via bores and channels that run inside the flange and the housing and via a controllable metering unit.
  • a radial piston pump generally has a plurality of pump elements which are arranged radially to a central drive shaft. The fueling of the pumping volumes of the pumping elements takes place in each case on the side facing away from the drive and thus, viewed in the radial direction, away from the center of the pump in outer areas of the radial piston pump.
  • the individual pump elements are often supplied with fuel through radially constructed channels which run parallel to the separating surface through the flange and open into a central supply line common to all pump elements.
  • the central supply line is supplied with fuel through a supply channel that runs axially through the radial piston pump and pierces the separating surface between the flange and the housing.
  • the pump volumes of the pump elements lying radially far outward are each connected with axially arranged channels with their associated radially outward-running supply bores. These channels also pierce the separating surface between the flange and the housing in the known radial piston pump. Furthermore Depending on the design of the radial piston pump, the separating surface is pierced by further channels, for example by a channel which serves to vent the interior, an inlet line for a low-pressure fuel delivery pump flanged to the radial piston pump.
  • Another opening in the flange and in the housing results from the guidance of the axially and centrally arranged drive shaft.
  • the openings mentioned are rotationally symmetrical in the known radial piston pump.
  • the interior of the radial piston pump, in which the drive shaft rotates, is usually filled with fuel. However, the fuel pressure in the interior does not correspond to the fuel pressure in the suction space.
  • This type of sealing is relatively complex in the manufacture of a radial piston pump. Every single one of the large number of O-rings must be inserted exactly into a recess provided in the surface of the flange and / or the housing. Such a puncture must be done for each O-ring Removal of material can be produced, for example by milling, drilling, countersinking or turning.
  • the radially extending connection channel must be routed between a supply line arranged centrally in the radial piston pump and the radially outer connection of a pump volume in the interior of the flange or the housing and connected through a hole in the separating surface.
  • the radial bore is usually made from the outside through a .radial inward bore.
  • the remaining, annoying boreholes in the outer wall of the radial piston pump are closed, for example, by press-fitted metal sealing balls. This closing of the bores represents an additional production step, which increases the cost of production.
  • the pressed-in balls represent a deviation from the ideal of a largely closed pump housing.
  • the O-rings used in the interface itself are in principle susceptible to aging and therefore represent a possible cause of leaks in the later operation of the radial piston pump.
  • the object of the invention is to provide a seal between a flange part and a housing part in a radial piston pump which does not have the disadvantages mentioned.
  • This task is the beginning of a radial piston pump mentioned type solved by a one-piece, flat seal arranged in the separating surface, which seals the suction chamber against the environment of the radial piston pump.
  • This solution has the advantage that a one-piece flat seal is particularly easy and reliable to install, since a correct position of two points of the flat seal already brings the correct position of all other points with it. In this way, especially when the flange and housing are being joined together, it can be avoided that sealing structures in central areas of the radial piston pump slip without being noticed during assembly.
  • the separating surface intersects the suction space and the interior and the one-piece flat seal seals the interior against the suction space and the suction space against the environment.
  • This configuration has the advantage that the suction chamber can be separated from the interior as well as from the environment by a single component, namely the flat seal. It is further preferred that the flat seal has a sheet metal layer.
  • Sheet metal seals are aging-resistant and fuel-resistant, dimensionally stable and inexpensive.
  • the sheet metal seal has a coating.
  • a coating can further improve the sealing effect of the sheet metal gasket, in particular if it contains flexible, elastic material.
  • the coating contains elastic plastic material.
  • the flat seal has a bead which, when installed, runs between the interior and the suction space.
  • the flat seal has a bead which, when installed, runs between the suction space and the surroundings.
  • This bead also improves the sealing effect of the flat seal, so that there is a particularly good seal between the suction chamber and the environment.
  • the sheet thickness is 0.1 to 0.3 mm.
  • bead height be 0.2 to 0.4 mm is.
  • suction space is at least partially supplied with fuel by grooves in the housing or flange that are open to the separating surface.
  • This configuration is related to the possibility mentioned above of also realizing sealing contours with the flat seal, the shape of which deviates from the circular shape of O-rings. It is therefore no longer necessary to let the above-mentioned radial fuel channel run inside the flange material or the housing material and then to connect the channel through bores that penetrate the separating surface.
  • Figure 1 schematically shows a sectional view of a
  • Figure 2 is a plan view of the flange of Figure 1 in a schematic representation
  • Figure 3 is a schematic sectional view of a
  • FIG. 4 shows a schematic top view of a flange of the radial piston pump from FIG. 3;
  • FIG. 5 shows a plan view of an embodiment of a flat seal for arrangement in the separating surface between a housing part and a flange part of a radial piston pump;
  • FIG. 6 shows a section through the flat seal according to FIG. 5.
  • the number 10 in FIG. 1 denotes a radial piston pump with a housing 12 and a flange 14. Housing 12 and flange 14 are connected to one another at a separating surface 16, the connecting elements, for example screws, not being shown for reasons of clarity.
  • a drive shaft 18 is guided in a central position by the radial piston pump 10 and mounted in bearings 20, 22.
  • the drive shaft 18 has one eccentric area 24, which actuates a piston 28 via a sliding element 26.
  • the piston is arranged radially in a bore in the housing 12 and movably seals a pump volume 30 in the housing 12.
  • the pump volume 30 is coupled via a valve 32 to a suction space 34, via which fuel is supplied to the pump volume 30.
  • the pump volume 30 is connected via a valve 36 to a high-pressure channel 38, via which fuel is pumped out of the pump volume 30 under high pressure.
  • the piston 28 is actuated periodically by the drive shaft 18 rotating in the bearings 20, 22, so that the pump volume 30 is periodically reduced and enlarged.
  • the valve 32 opens and fuel flows from the suction space 34 into the pump volume 30.
  • a reduction in the pump volume 30 causes the valve 32 to close and, provided the pressure is sufficiently high, the valve 36 to open via the fuel is expelled from the pump volume 30 under high pressure.
  • the radial piston pump 10 is integrated in a low-pressure circuit, not shown, in which a low-pressure delivery pump, also not shown, feeds fuel into a feed channel 40 in the housing 12. Fuel from the supply channel 40 is passed via the separating surface 16 into the first connection bore 42 in the flange 14. From there, the fuel flows through a first radial bore 44, which runs inside the flange 14, and through a second connection bore 48 into an annular channel or an annular groove 50.
  • the first radial bore 44 is drilled radially from the outside inwards during manufacture, and the disruptive opening in the housing 12 which remains after the bore has been produced is sealed with a first sealing ball 46.
  • the annular groove 50 leads around the central region of the radial piston pump 10, in which the drive shaft 18 is rotatably mounted. Fuel passes from the annular groove 50 into a second radial bore 54 via a third connection bore.
  • the second radial bore 54 has been produced analogously to the production of the first radial bore 44 by drilling from the outside inwards.
  • the remaining disruptive opening is closed to the outside by a closure ball, here by the second closure ball 56.
  • the fuel reaches the suction chamber 34 from the second radial bore 54 via a fourth connection bore 58, which intersects the separating surface 16.
  • the radial piston pump according to FIG. 1 therefore has several fuel paths which are cut by the separating surface 16 between the flange 14 and the housing 12.
  • the separating surface 16 between the housing 12 and the flange 14 also cuts the interior 60 inside the housing 12, in which the eccentric section 24 of the drive shaft 18 rotates and actuates the piston 28.
  • the fuel paths (40, 42, 50, 54, 58) cut by the separating surface 16 are under a pressure which prevails in the suction space 34.
  • the interior 60 is usually filled with fuel and / or fuel flows through it. However, there is usually a different pressure in the interior 60 than in the suction chamber 34 and the fuel paths (40, 42, 50, 54, 58) communicating with the suction chamber 34.
  • an O-ring 62 is provided which is concentric with the recess 14 in a recess of the flange 14 Drive shaft is arranged.
  • Another O-ring 64 seals the annular groove 50 in the separating surface 16 from the environment.
  • Another O-ring 66 seals the first connection bore 42 in the separating surface 16.
  • another O-ring 68 seals the fourth connection bore 58 in the separating surface 16.
  • FIG. 3 schematically shows a radial piston pump 10 within the scope of an embodiment of the invention.
  • the embodiment according to FIG. 3 has no O-rings 62, 64, 66 and 68 in the separating surface 16 between the housing 12 and flange 14 of the radial piston pump 10.
  • the same reference symbols in the various figures denote the same features.
  • FIGS. 3 and 4 The 0-rings provided in the subject of FIGS. 1 and 2 are replaced in the embodiment according to FIGS. 3 and 4 by a flat seal 70 which is arranged in the separating surface 16 between the housing 12 and the flange 14.
  • the structure of this flat seal 70 is explained in more detail below in connection with FIGS. 5 and 6.
  • a major advantage of using a flat seal 70 is that the flat seal 70 allows a changed fuel supply.
  • the feed channel 40 opens into a radial groove 72, which can be open towards the separating surface 16.
  • the radial groove 72 connects the feed channel 40 to the annular groove 50 and thus replaces the first connection bore 42, the first radial bore 44 with a locking ball 46 and the second connection bore 48 from FIG. 1.
  • the radial groove 74 in FIG. 3 replaces the third connection bore 52, the second radial bore 54 with locking ball 56 and the fourth Connection bore 58 from FIG. 1.
  • the radial groove 74 is also open with respect to the separating surface 16.
  • the top view of the flange 14 shown in FIG. 4 without a flat seal 70 illustrates the open course of the radial grooves 72 and 74, the lack of O-rings 62, 64, 66 and 68 and the lack of the corresponding recesses for receiving the aforementioned O- Rings in the flange 14.
  • FIG. 5 shows a top view of an embodiment of a flexible seal 70 for a radial piston pump.
  • This configuration corresponds to the radial piston pump is actually used rather than the schematic representations of Figures 1 - 4.
  • the in figure 5 'shown flat gasket 70 is also in a separation surface 16 between a housing 12 and a flange 14 to be arranged a radial piston pump 10th
  • the flat seal 70 has three regions 76, 78 and 80 arranged in a star shape, in each of which an opening 77, 19 and 81 is arranged.
  • Each of the three star-shaped, radially disposed portions 76, 78 and 80 cover in the installed state an open radial groove in the flange of a radial piston pump 's from.
  • the associated radial piston pump accordingly has three pump elements which are arranged radially and in a star shape.
  • the radial grooves are designed, for example, like the radial groove 74 in the embodiment according to FIGS. 3 and 4.
  • the openings 77, 79 and 81 each allow fuel to flow from the radial groove through the flat seal 70 to the associated pump volumes.
  • the opening in the seal 70 which allows a flow from the radial groove 74 in the suction space 34 corresponds to one of the openings 77, 79 and 81.
  • This suction chamber pressure is sealed against the interior of the radial piston pump by an internal bead 82.
  • This interior corresponds to the interior 60 in FIGS. 1 and 3.
  • the suction space is sealed off from the outside by a further bead 84, which runs around all three star-shaped regions 76, 78 and 80 in a closed line.
  • the flat seal 70 has further openings 86, 88, 90 and 92, each of which is surrounded by associated concentrically arranged beads 87, 89, 91 and 93. These openings result from the fact that the separating surface 16 cuts further channels and / or pressure spaces.
  • the opening 92 can be assigned to a metering unit, via which the inflow of fuel to the radial piston pump is controlled.
  • the openings 86, 88 and 90 can, for example, channel inlet and outlet channels for a low-pressure gear feed pump flanged to the radial piston pump, while the opening 90 can be assigned, for example, to a vent hole for the interior 60 of the radial piston pump. Openings 95 serve to carry out fastening elements such as screws.
  • FIG. 5 illustrates in a special way the possibility of using a flat seal to form sealing contours in the form of beads which deviate from the concentric shape of the O-rings usually used.
  • This results in the possibility of moving the fuel channels running radially outwards into the parting plane, as represented by a radial groove 74 in FIGS. 3 and 4.
  • a radial groove corresponding to the radial groove 74 in FIGS. 3 and 4 can be produced largely preformed in a cast flange 14, so that further processing steps are largely unnecessary.
  • Figure 6 shows the seal 70 of Figure 5 in a sectional view.
  • the seal 70 has a sheet metal layer 94 which gives the flat seal 70 structure and strength.
  • the sheet metal layer 94 is coated with a layer of resilient plastic 96 which improves the sealing effect.
  • the beads 84 and 82 are visible in the sectional view of Figure 6 as ridges.

Landscapes

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

Abstract

L'invention concerne une pompe à piston radial comprenant : une partie flasque et une partie carter ; un élément de pompage disposé dans la partie carter et un arbre d'entraînement excentrique actionnant un piston qui peut se déplacer radialement par rapport à l'arbre d'entraînement dans l'élément de pompage, obture un volume de pompage de manière mobile, assure le transport de carburant contenu dans une chambre d'aspiration vers le volume de pompage lorsque ce volume augmente et, lorsque ce volume diminue, met le carburant contenu dans le volume de pompage sous pression et assure sa sortie dudit volume à une pression élevée ; une chambre intérieure qui permet l'excentricité de l'arbre d'entraînement ; ainsi qu'un plan de séparation qui est situé entre la partie carter et la partie flasque et coupe la chambre intérieure ainsi que la chambre d'aspiration. La pompe à piston radial selon l'invention est caractérisée en ce qu'elle comporte une garniture d'étanchéité plane, monobloc, disposée dans le plan de séparation, assurant une étanchéification réciproque entre la chambre d'aspiration, l'environnement de ladite pompe à piston radial ainsi que la chambre intérieure.
EP03799410A 2002-11-15 2003-08-11 Pompe a piston radial pourvue d'une garniture d'etancheite plane entre le flasque et le carter Withdrawn EP1576288A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10253189A DE10253189A1 (de) 2002-11-15 2002-11-15 Radialkolbenpumpe mit flächiger Dichtung zwischen Flansch und Gehäuse
DE10253189 2002-11-15
PCT/DE2003/002705 WO2004046547A1 (fr) 2002-11-15 2003-08-11 Pompe a piston radial pourvue d'une garniture d'etancheite plane entre le flasque et le carter

Publications (1)

Publication Number Publication Date
EP1576288A1 true EP1576288A1 (fr) 2005-09-21

Family

ID=32185685

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03799410A Withdrawn EP1576288A1 (fr) 2002-11-15 2003-08-11 Pompe a piston radial pourvue d'une garniture d'etancheite plane entre le flasque et le carter

Country Status (6)

Country Link
US (1) US20050084389A1 (fr)
EP (1) EP1576288A1 (fr)
JP (1) JP2006506572A (fr)
CN (1) CN100429398C (fr)
DE (1) DE10253189A1 (fr)
WO (1) WO2004046547A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7377757B2 (en) * 2005-09-22 2008-05-27 Graves Spray Supply, Inc. Fluid pump with enhanced seal
DE102007047419A1 (de) * 2007-10-04 2009-04-09 Robert Bosch Gmbh Kolbenpumpe zur Förderung eines Fluids und zugehöriges Bremssystem
ITMI20072300A1 (it) * 2007-12-06 2009-06-07 Bosch Gmbh Robert Guarnizione per pompa di alta pressione e pompa di alta pressione comprendente tale guarnizione
EP2072818A1 (fr) * 2007-12-21 2009-06-24 Reinz-Dichtungs-GmbH & Co. KG Joint plat métallique et son utilisation
KR101163275B1 (ko) * 2008-03-17 2012-07-05 엘지전자 주식회사 Ｐｄｃｐ 상태 보고 전송 방법
DE102008041751A1 (de) * 2008-09-02 2010-03-04 Robert Bosch Gmbh Hochdruck-Radialkolbenpumpe
GB2551562B (en) * 2016-06-23 2020-03-18 Delphi Tech Ip Ltd Gasket of a front plate of a high pressure pump
IT201600081962A1 (it) * 2016-08-03 2018-02-03 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2543796A (en) * 1949-04-18 1951-03-06 Leland T Mcgee Hydraulic pump
DE2732247A1 (de) * 1977-07-16 1979-02-01 Bosch Gmbh Robert Druck- oder saugventil fuer eine pumpe
DE3513164A1 (de) * 1985-04-12 1986-10-23 Robert Bosch Gmbh, 7000 Stuttgart Radialkolbenpumpe
CN2213890Y (zh) * 1992-09-10 1995-11-29 孙宝伟 新型复合密封材料及密封垫片
US5354183A (en) * 1993-02-11 1994-10-11 Elasis Sistema Ricerca Fiat Nel Mezzogiorno Societa Consortile Per Azioni Pumping device with a main pumping stage and a supply pump
WO1998058172A1 (fr) * 1997-06-17 1998-12-23 Mannesmann Rexroth Ag Pompe a pistons radiaux
DE19848035A1 (de) * 1998-10-17 2000-04-20 Bosch Gmbh Robert Radialkolbenpumpe für Kraftstoffhochdruckerzeugung
JP4404393B2 (ja) * 1998-11-13 2010-01-27 日本ガスケット株式会社 ガスケット
DE10042305A1 (de) * 2000-08-29 2002-03-21 Siemens Ag Abdichtungsvorrichtung für einen Übergangsbereich an Hochdruckbauteilen
DE10060514B4 (de) * 2000-12-06 2006-11-30 Carl Freudenberg Kg Flachdichtung für eine Kolbenkraft- oder Arbeitsmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004046547A1 *

Also Published As

Publication number Publication date
US20050084389A1 (en) 2005-04-21
CN100429398C (zh) 2008-10-29
WO2004046547A1 (fr) 2004-06-03
CN1695008A (zh) 2005-11-09
JP2006506572A (ja) 2006-02-23
DE10253189A1 (de) 2004-05-27

Similar Documents

Publication Publication Date Title
EP0536159B1 (fr) Organe pour l'alimentation du moteur a combustion interne d'un vehicule a moteur avec du carburant provenant d'un reservoir
EP0699826B1 (fr) Circuit de liquide avec un filtre au courant principal
EP1671031B1 (fr) Pompe a fluide, en particulier pompe a carburant haute pression
DE102004035743B4 (de) Variable Verdrängungspumpe
EP1101931A2 (fr) Système d'injection à haute pression avec common rail
DE4213798C2 (de) Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren
DE3235427A1 (de) Fluegelpumpe
DE102004047601A1 (de) Fluidpumpe, insbesondere Kraftstoff-Hochdruckpumpe
DE2907058A1 (de) Verdraengungspumpe, insbesondere fuer servo-einrichtungen in kraftfahrzeugen
DE102004002489A1 (de) Fluidpumpe, insbesondere Kraftstoff-Hochdruckpumpe
DE10105119A1 (de) Kraftstoffzufuhrvorrichtung für eine Kraftstoffeinspritzdüse
EP1576288A1 (fr) Pompe a piston radial pourvue d'une garniture d'etancheite plane entre le flasque et le carter
DE102007057503A1 (de) Radialkolbenpumpe für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine
DE602004011682T2 (de) Verdichter und saugventilkonstruktion
DE102009001433A1 (de) Saugventil für eine Kraftstoffhochdruckpumpe
DE60029659T2 (de) Flügelzellenpumpe
DE102013207169A1 (de) Niederdruckkreislauf für ein Kraftstoffeinspritzsystem
DE3117743C2 (de) Ölpumpe
DE2243430A1 (de) Drehkolbenpumpe, insbesondere zur verwendung fuer ein mit einer hydraulischen lenkhilfe ausgeruestetes lenkgetriebe von kraftfahrzeugen
DE19920997B4 (de) Radialkolbenpumpe
DE10218551A1 (de) Rückschlagventil
EP1690000A1 (fr) Injecteur
DE102007038530A1 (de) Kraftstoffhochdruckpumpe
WO2020182921A9 (fr) Dispositifs de clapet destinés à une pompe à membrane
DE3015873A1 (de) Automatisches zeitsteuerventil zur wasserabgabesteuerung in bewaesserungsanlagen

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: 20050615

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 HU IE IT LI LU MC NL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR IT

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20110301