EP0524437A1 - Moteur hydraulique à piston - Google Patents

Moteur hydraulique à piston Download PDF

Info

Publication number
EP0524437A1
EP0524437A1 EP92110445A EP92110445A EP0524437A1 EP 0524437 A1 EP0524437 A1 EP 0524437A1 EP 92110445 A EP92110445 A EP 92110445A EP 92110445 A EP92110445 A EP 92110445A EP 0524437 A1 EP0524437 A1 EP 0524437A1
Authority
EP
European Patent Office
Prior art keywords
piston
roller cage
roller
hydraulic piston
motor 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
EP92110445A
Other languages
German (de)
English (en)
Other versions
EP0524437B1 (fr
Inventor
Sten-Gullik Jansson
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.)
Hagglunds Denison Drives AB
Original Assignee
Hagglunds Denison Drives AB
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 Hagglunds Denison Drives AB filed Critical Hagglunds Denison Drives AB
Publication of EP0524437A1 publication Critical patent/EP0524437A1/fr
Application granted granted Critical
Publication of EP0524437B1 publication Critical patent/EP0524437B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04B1/0408—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/047—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the outer ends of the cylinders

Definitions

  • the invention relates to a hydraulic piston motor according to the precharacterising part of claim 1.
  • Such hydraulic piston motors can be connected to a driven shaft, to a wheel or to a cable drum for a winch or the like
  • the invention may, for example, be arranged in a motor of the type described in SE-B-456 517 entitled "Hydraulic radial piston motor". It is a hydraulic piston motor with a cam disk with an internal cam curve and a cylinder block with a number of cylinders. In each cylinder runs a piston which presses a roller against the cam curve so that a torque arises on the cylinder block.
  • the rollers are formed with guide members which run in slits in guide units which take up tangential forces.
  • the rollers are journalled in roller cages which are formed with hydrostatic bearings with a bearing surface, which is adapted to the roller path of the rollers. Either the housing of the hydraulic piston motor may be stationary and the cylinder block rotatable, or the cylinder block may be stationary and the motor housing rotatable.
  • the pistons are formed at their outer end with a spherical annular bearing surface.
  • the roller cages are correspondingly-formed with a spherical bearing surface cooperating with the bearing surface of the pistons. This allows the roller cages to tilt in all directions around the centre of the spherical bearing.
  • the mechanical load is to be absorbed by as large a part of the mechanical bearing surface as possible so as to equalize the surface pressure.
  • bearing leakage arises when the roller cages are deformed upon loading.
  • the balancing of the compressive forces takes place with the aid of hydrostatic balancing between the rollers and the roller cages. This results in a reduction of the mechanical contact pressure.
  • the bearing surface of the roller cage has been provided with slots between which a sealing surface, cooperating with the roller, is formed.
  • the bearing surface has been provided with a recess to make possible a certain deformation without the roller and the sealing surface separating. Because of the slots and the recess, the bearing surface has been reduced.
  • the invention aims at developing a hydraulic piston motor of the above-mentioned kind which is largely freed from the problems of the conventional hydraulic piston motors described above.
  • the invention relates to a device, called roller cage piston, in a hydraulic piston motor, which device comprises a piston part and a roller cage part which together form an integral unit.
  • This roller cage piston may, for example, be arranged in a hydraulic piston motor of the type referred to above.
  • roller cage piston At its outer end the roller cage piston is formed as a roller cage, this part thus constituting the roller cage part.
  • the roller cage part is formed as a hydrostatic bearing with a bearing surface which is adapted to a roller running against a roller path arranged in the hydraulic piston motor.
  • the roller cage part may either be made rigid to provide negligible deformations in the roller cage part, or weak for absorption of any deformations.
  • the advantage of the weak roller cage part is that the maximum allowed power can be further increased while at the same time the bearing leakage can be reduced by forming the roller cage part according to the roller.
  • the maximum allowed power is increased by increasing the mechanical bearing surface and utilizing it more efficiently, which in turn entails a reduction and equalization of the mechanical surface pressure and an increase of the maximum allowed power of the roller cage part.
  • the bearing leakage is reduced by the roller and the roller cage making close contact with each other.
  • a suitable pattern of holes and/or slots for pressure medium is arranged.
  • the holes and/or the slots are connected to each other by means of one or more channels.
  • the roller cage piston is formed with a continuous bore. Via the bore, pressure medium in the cylinder has free passage through the roller cage piston to a channel in the roller cage part which supplies pressure medium to the holes and/or slots in the bearing surface of the roller cage part.
  • the inner end of the roller cage piston is formed with a double-curved surface, which makes contact with the cylinder bore, and is formed such that the roller cage piston can be guided by the cylinder bore.
  • the guiding part of the roller cage is short.
  • the double-curved surface may, for example, be formed with the aid of two flanges with an intermediate piston ring slot.
  • the contact surfaces of the two flanges with the cylinder bore together exhibit a convex surface of revolution.
  • an annular recess which constitutes the piston ring slot.
  • a piston ring is arranged to limit the leakage of pressure medium between the roller cage piston and the cylinder bore, the so-called piston leakage.
  • the two flanges have a larger diameter than that of the other piston part whereas the piston ring slot has a smaller diameter than that of the flanges.
  • the piston ring can, of course, be arranged also outside the double-curved surface and then suitably axially displaced towards the internal part of the piston part.
  • the double-curved surface can then consist of one single flange with a double-curved surface.
  • the advantage of the invention is thus that the maximum allowed power is increased by the relatively large contact surface between the roller and the roller cage part and that the surface is utilized more efficiently.
  • the roller cage and the piston together constitute one unit which can allow angular deviations of the piston part in relation to the cylinder bore since the piston part, with the aid of the double-curved surfaces of the piston part, is guided by the cylinder bore.
  • the leakage is reduced because of a smaller number of leakage points and by avoiding undesired deformations.
  • the fewer parts and the simpler embodiment of the roller cage piston make it both simple and inexpensive to manufacture.
  • the invention relates to a roller cage piston 1, according to Figures 3a or 3b, which is formed integral as a roller cage part 2 and a piston part 3.
  • roller cage piston 1 can be arranged, as shown, on reduced scale, in Figure 1, in a conventional hydraulic piston motor of the type referred to above.
  • the roller cage pistons 1 according to the invention run in cylinders 5 arranged in a cylinder block 6.
  • Each roller cage piston 1 presses a roller 7 against an internal cam curve 8 such that a torque on the cylinder block 6 and the cam curve 8 arises.
  • Inside the cylinder block 6 there is a rotatable slide 9 for distributing pressure medium 10 to the cylinders 5.
  • roller cage piston 1 At its outer end, that is the end protruding from the cylinder, the roller cage piston 1 is formed as a roller cage, this part thus being designated “roller cage part" 2.
  • roller cage part 2 is formed as a hydrostatic bearing with a bearing surface 11, which has the form of a cylindrical segment and is adapted to the rollers 7, according to Figure 1, running against the cam curve 8.
  • the roller cage part 2 can either be made rigid or weak (elastically deformable).
  • the piston part 3, according to Figures 3a and 4a, is substantially made solid.
  • the roller cage part 2 is thus dimensioned such that the rigidity allows only a negligible deformation of the roller cage part 2, which in turn means that the area of the bearing surface 11 can be increased and utilized efficiently due to the fact that a recess in the bearing surface 11 is not needed.
  • a recess is provided in the bearing surface such that deformations can be allowed without the roller separating from a sealing surface cooperating with the roller.
  • roller cage part 2 Another way is to make the roller cage part 2 weak so that it may adapt to the shape and diameter of the rollers 7.
  • the weakness is obtained by making the roller cage part 2 thin and forming the area between the roller cage part 2 and the inner end of the piston part 3 with at least tow legs 12, 13 according to Figure 4b.
  • a roller cage piston 1 with such legs 12, 13 is called a leg piston.
  • the legs 12, 13 transmit the load, in the form of compressive forces from the piston part 3 to the roller cage part 2.
  • the roller cage part 2 is subjected to tangential tensile forces in a section parallel to the axial direction of the roller 7 and is thus extended around the roller 7 such that it may adapt thereto. It is important that the attachment of the legs 12, 13 to the roller cage part 2 is made such that the roller cage part 2 is extended around the roller 7.
  • the surface pressure may otherwise become too low which leads to leakage of pressure medium 10 between the roller 7 and the roller cage 2.
  • a suitable pattern of pressure medium holes and/or pressure medium grooves is arranged.
  • An advantageous embodiment, according to Figure 2 is obtained if one or more, but preferably two, annular grooves 14, 15 are chosen, one of the grooves serving as a drainage groove 14 and the other as a pressure medium groove 15.
  • the roller cage piston 1 is formed with a continuous bore 16, through which the bearing surface 11 is supplied with pressure medium 10. The continuous bore 16 opens out into a hole 17 at the pressure medium groove 15.
  • annular sealing surface 18 is formed, which cooperates with the roller 7.
  • a pressurized area is created inside the sealing surface 18 and has a size approximately consisting of a mean value of the area inside the drainage groove 14 and the area inside the pressure medium groove 15.
  • the pressurized area is used as supporting hydraulic bearing surface, and its size is chosen such that the desired hydrostatic balancing of radial compressive forces from the roller cage piston 1 towards the roller 7 is obtained.
  • the radial compressive forces acting on the roller cage part 2 are hydrostatically balanced at a rate of more than 75 %, suitably at a rate of between 85 % and 95 %, that is, the mechanical surface pressure is replaced by a hydraulic surface pressure.
  • the large mechanical bearing surface, that is the bearing surface 11 reduced by the grooves 14, 15 and the hole 17, and the hydraulic balancing cause the mechanical pressure on the rollers 7 from the bearing surface 11 of the roller cage part 2 to become relatively low.
  • the continuous bore 16 may be arranged in one or more legs or, for example, via a tube between the piston part 3 and the roller cage part 2.
  • Pressure medium 10 for example in the form of oil or oil-water mixture, in the cylinder has free passage, via the bore 16, through the roller cage piston 1 to the annular pressure medium groove 15 in the bearing surface 11 of the roller cage part 2 and thereby conveys pressure medium 10 to the bearing surface 11.
  • the pressure medium 10 is drained via the drainage groove 14.
  • the roller cage piston 1 is formed with a double-curved surface which constitutes the guiding part of the roller cage piston 1.
  • the double-curved surface may, for example, be formed according to Figure 3 with the aid of two adjacent flanges 19, 20 separated from one another by an intermediate piston ring slot 21.
  • the two flanges 19, 20 have a larger diameter than the rest of the piston part 3.
  • the piston ring slot in its turn, has a smaller diameter than the flanges 19, 20.
  • the guiding part of the roller cage piston 1 is made short.
  • the guiding part means that the roller cage piston 1 can be allowed a certain angular deviation but that it is guided by the cylinder bore when a maximum allowed angle between the roller cage piston 1 and the cylinder bore is attained.
  • the maximum allowed angle may be different in different lateral directions.
  • Part of the double-curved surface constitutes a contact surface which is suitably formed as a convex surface of revolution.
  • the contact surface is limited, in case of maximum allowed angular deviation, by a first and a second contact point.
  • the diametrical distance between the first and second contact points on either side of the piston part 3 in the vertical Section is larger than the diameter of the cylinder bore. In normal operation, the contact surface only has one contact point towards the cylinder bore.
  • a piston ring in the form of a completely closed metallic seal 22 which may have a secondary seal 23 on the inside.
  • the secondary seal 23 may, for example, consist of an O-ring of rubber.
  • the piston ring may be designed completely closed since it has such a small cross section in relation to its outer envelope surface that no high, harmful surface pressures, for example caused by temperature differences, arise.
  • the advantage of this piston ring is that it is a wear-resistant metallic seal which is almost completely tight. Thus, the piston ring only lets through an amount of pressure medium 10 which is needed to lubricate the cylinder bore.
  • the piston ring can also be arranged outside the double-curved surface. It is then suitably arranged with an axial displacement towards the interior part of the piston part 3.
  • the double-curved surface suitably consists of one flange only.
  • roller cage part 2 In freewheeling operating mode, hydraulic motors with a freewheeling facility may be pressurized such that the pistons 1 are held down at the bottom of the cylinders 5, the motor thus being disengaged. There are also motors where the pistons are held down in the cylinders in some other way, for example by magnets or springs.
  • the roller cage part 2 must surround the rollers 7 by more than 180° so that the rollers 7 are radially fixed in the roller cage part 2. In case of such a winding angle the roller cage part 2 may be divisible, as shown for example in Figure 6.
  • the roller cage part 2 here comprises two parts 24, 25 which can be retained with the aid of bolts 26.
  • the winding angle may be less than 180°. The reason is that in this case the rollers 7 need not be fixed since, because of the feed pressure of the pressure medium 10, the rollers 7 are all the time pressed out against the cam curve 8 by the roller cage pistons 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
EP19920110445 1991-06-25 1992-06-20 Moteur hydraulique à piston Expired - Lifetime EP0524437B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9101950 1991-06-25
SE9101950A SE503563C2 (sv) 1991-06-25 1991-06-25 Anordning vid hydraulkolvmotor

Publications (2)

Publication Number Publication Date
EP0524437A1 true EP0524437A1 (fr) 1993-01-27
EP0524437B1 EP0524437B1 (fr) 1996-06-05

Family

ID=20383142

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19920110445 Expired - Lifetime EP0524437B1 (fr) 1991-06-25 1992-06-20 Moteur hydraulique à piston

Country Status (3)

Country Link
EP (1) EP0524437B1 (fr)
DE (1) DE69211238T2 (fr)
SE (1) SE503563C2 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5979295A (en) * 1997-04-10 1999-11-09 Hagglunds Drives AB Hydraulic motor piston
WO1999046504A3 (fr) * 1998-03-10 1999-12-09 Mannesmann Rexroth Ag Moteur a pistons radiaux avec guidage des galets
WO2003046379A1 (fr) * 2001-11-21 2003-06-05 Robert Bosch Gmbh Piston-poussoir
GB2417990A (en) * 2004-09-14 2006-03-15 Linde Ag Hydrostatic displacement unit
DE102011012306A1 (de) 2011-02-25 2012-09-27 Robert Bosch Gmbh Radialkolbenmaschine mit hydrostatisch entlasteten Rollen
WO2012159725A1 (fr) 2011-05-23 2012-11-29 Robert Bosch Gmbh Machine hydrostatique à pistons radiaux et piston pour une machine hydrostatique à pistons radiaux
WO2014002143A1 (fr) 2012-06-29 2014-01-03 Mitsubishi Heavy Industries, Ltd. Machine de travail à fluide et génératrice de turbine éolienne
WO2024121482A1 (fr) * 2022-12-09 2024-06-13 Poclain Hydraulics Industrie Machine hydraulique tournante équipée de pistons

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010032056B4 (de) * 2010-07-23 2019-11-28 Robert Bosch Gmbh Kolbeneinheit

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2215543A1 (fr) * 1973-01-26 1974-08-23 Hitachi Construction Machinery
US3978771A (en) * 1975-04-21 1976-09-07 Clark Equipment Company Mechanical piston retention for free wheeling
FR2358566A1 (fr) * 1976-07-15 1978-02-10 Cyphelly Ivan J Machine a refoulement a transmission de couple hydrostatique au moyen de pistons a rouleaux
EP0102915A2 (fr) * 1982-09-08 1984-03-14 AB Hägglund & Söner Moteur hydraulique à piston radial
WO1987001783A1 (fr) * 1985-09-16 1987-03-26 Flutron Ab Dispositif d'etancheite

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2215543A1 (fr) * 1973-01-26 1974-08-23 Hitachi Construction Machinery
US3978771A (en) * 1975-04-21 1976-09-07 Clark Equipment Company Mechanical piston retention for free wheeling
FR2358566A1 (fr) * 1976-07-15 1978-02-10 Cyphelly Ivan J Machine a refoulement a transmission de couple hydrostatique au moyen de pistons a rouleaux
EP0102915A2 (fr) * 1982-09-08 1984-03-14 AB Hägglund & Söner Moteur hydraulique à piston radial
WO1987001783A1 (fr) * 1985-09-16 1987-03-26 Flutron Ab Dispositif d'etancheite

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5979295A (en) * 1997-04-10 1999-11-09 Hagglunds Drives AB Hydraulic motor piston
WO1999046504A3 (fr) * 1998-03-10 1999-12-09 Mannesmann Rexroth Ag Moteur a pistons radiaux avec guidage des galets
US6494127B1 (en) 1998-03-10 2002-12-17 Mannesmann Rexroth Ag Radial piston engine with guide rollers
WO2003046379A1 (fr) * 2001-11-21 2003-06-05 Robert Bosch Gmbh Piston-poussoir
GB2417990A (en) * 2004-09-14 2006-03-15 Linde Ag Hydrostatic displacement unit
GB2417990B (en) * 2004-09-14 2009-08-12 Linde Ag Hydrostatic displacement unit
DE102011012306A1 (de) 2011-02-25 2012-09-27 Robert Bosch Gmbh Radialkolbenmaschine mit hydrostatisch entlasteten Rollen
WO2012159725A1 (fr) 2011-05-23 2012-11-29 Robert Bosch Gmbh Machine hydrostatique à pistons radiaux et piston pour une machine hydrostatique à pistons radiaux
DE102012009794A1 (de) 2011-05-23 2012-11-29 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine und Kolben für eine hydrostatische Radialkolbenmaschine
CN103562544A (zh) * 2011-05-23 2014-02-05 罗伯特·博世有限公司 液压静力的径向活塞机和用于液压静力的径向活塞机的活塞
CN103562544B (zh) * 2011-05-23 2016-04-13 罗伯特·博世有限公司 液压静力的径向活塞机和用于液压静力的径向活塞机的活塞
WO2014002143A1 (fr) 2012-06-29 2014-01-03 Mitsubishi Heavy Industries, Ltd. Machine de travail à fluide et génératrice de turbine éolienne
WO2024121482A1 (fr) * 2022-12-09 2024-06-13 Poclain Hydraulics Industrie Machine hydraulique tournante équipée de pistons
FR3143069A1 (fr) * 2022-12-09 2024-06-14 Poclain Hydraulics Industrie Machine hydraulique tournante équipée de pistons

Also Published As

Publication number Publication date
DE69211238D1 (de) 1996-07-11
SE9101950D0 (sv) 1991-06-25
EP0524437B1 (fr) 1996-06-05
SE503563C2 (sv) 1996-07-08
SE9101950L (sv) 1992-12-26
DE69211238T2 (de) 1997-01-23

Similar Documents

Publication Publication Date Title
US4522110A (en) Hydraulic radial piston motor
US4981415A (en) Support for oil film dampers
US4123666A (en) Rim-type hydroelectric machine
US3223046A (en) Rotary radial piston machines
US3124079A (en) Jxanjacquxs j joyer
EP0524437B1 (fr) Moteur hydraulique à piston
US4905577A (en) Line-contact-type spherical bearing for connecting piston to connecting rod
GB2250784A (en) Radial piston motor.
US3187681A (en) Hydraulic ball pumps and motors
US4752077A (en) Sliding ring seal
US5018258A (en) Support system for a variable-crown roll
US9488050B2 (en) Radial cylinder hydraulic machine with improved oscillating radial cylinder
US4241482A (en) Deflection compensating roll
JP2952311B2 (ja) 回転スリーブを備えるローラ
EP0733165B1 (fr) Portee de tourillon radiale a coulisse, et coulisse pour portee de tourillon radiale
CA1307967C (fr) Rouleur presseur
US3584648A (en) Hydrostatic machine
US6193639B1 (en) Deflection compensation roll
US4508010A (en) Hydraulic motor
US4492481A (en) Thrust bearing starter apparatus
US4033239A (en) Radial piston machine
FI74072B (fi) Glidskoarrangemang foer boejningskompenserad vals.
US3177734A (en) Variable-speed transmissions utilizing belts and pulleys
US4033237A (en) Hydrostatic piston machine having small clearances between bearing surfaces
US5127660A (en) Support mechanism for fluid film seals

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

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT NL

17P Request for examination filed

Effective date: 19930623

17Q First examination report despatched

Effective date: 19940331

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT NL

REF Corresponds to:

Ref document number: 69211238

Country of ref document: DE

Date of ref document: 19960711

ITF It: translation for a ep patent filed
ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

REG Reference to a national code

Ref country code: FR

Ref legal event code: CD

Ref country code: FR

Ref legal event code: TP

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20090312 AND 20090318

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

Ref country code: NL

Payment date: 20090630

Year of fee payment: 18

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

Ref country code: IT

Payment date: 20090710

Year of fee payment: 18

REG Reference to a national code

Ref country code: NL

Ref legal event code: V1

Effective date: 20110101

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: 20100620

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

Ref country code: NL

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

Effective date: 20110101

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

Ref country code: FR

Payment date: 20110620

Year of fee payment: 20

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

Ref country code: GB

Payment date: 20110613

Year of fee payment: 20

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

Ref country code: DE

Payment date: 20110609

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 69211238

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 69211238

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20120619

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 EXPIRATION OF PROTECTION

Effective date: 20120621

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 EXPIRATION OF PROTECTION

Effective date: 20120619