EP0669469A1 - Actionneur fluidique rotatif - Google Patents

Actionneur fluidique rotatif Download PDF

Info

Publication number
EP0669469A1
EP0669469A1 EP94118946A EP94118946A EP0669469A1 EP 0669469 A1 EP0669469 A1 EP 0669469A1 EP 94118946 A EP94118946 A EP 94118946A EP 94118946 A EP94118946 A EP 94118946A EP 0669469 A1 EP0669469 A1 EP 0669469A1
Authority
EP
European Patent Office
Prior art keywords
piston
rotary drive
housing
drive
space
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
EP94118946A
Other languages
German (de)
English (en)
Other versions
EP0669469B1 (fr
Inventor
Kurt Dipl.-Ing. Dr. Stoll
Jörg Alexander Bitzer
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.)
Festo SE and Co KG
Original Assignee
Festo SE and Co KG
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 Festo SE and Co KG filed Critical Festo SE and Co KG
Publication of EP0669469A1 publication Critical patent/EP0669469A1/fr
Application granted granted Critical
Publication of EP0669469B1 publication Critical patent/EP0669469B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/072—Combined pneumatic-hydraulic systems
    • F15B11/076—Combined pneumatic-hydraulic systems with pneumatic drive or displacement and speed control or stopping by hydraulic braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type

Definitions

  • the invention relates to a fluid-actuated rotary drive, with a drive swivel piston arranged in a housing, which can be driven for a swiveling movement by means of a fluidic pressure medium such as compressed air, and which is in drive connection with an output shaft which taps off one of the swiveling movement of the drive.
  • a fluidic pressure medium such as compressed air
  • a rotary drive of this type referred to as a pivoting piston engine, can be found in DE 39 41 255 A1. It has a housing with a housing space in which a pivoting piston equipped with a radially projecting wing is arranged. An output shaft which is connected to the swivel piston in a rotationally fixed connection is led out of the housing. By supplying a fluidic pressure medium into the housing space, the pivoting piston can be driven to perform a reciprocating pivoting movement, so that a reciprocating rotary movement can be picked up on the output shaft and can be used to drive any component.
  • the object of the present invention is to provide a rotary drive of the type mentioned which, even with slow rotary movements, allows extremely uniform rotary movements to be tapped from the output shaft.
  • the pivoting movement of the pivoting piston driving the output shaft is influenced by a fluid brake device constructed in the manner of a fluidically actuatable rotary drive.
  • This has no self-function in terms of work performance. Rather, its task is to ensure that a constant swiveling speed is maintained and / or to brake the movement of the drive swiveling piston in order to maintain the desired quality of the rotary movement that can be tapped.
  • the brake piston When the drive pivoting piston is pivoted, the brake piston is pivoted, in particular synchronously, and the latter pushes hydraulic fluid out of a partial space of the displacement space, a certain counterpressure being generated in the said partial space via the outflow cross-section provided, which influences the pivoting speed of the brake piston and in particular reduced, which also has an immediate effect on the swivel speed of the drive swivel piston.
  • Hydraulic fluid brake cylinders are known as such, for example from the specialist book "Pneumatic controls", W. Deppert / K. Stoll, Vogel-Verlag, 4th ed. 1977, pp. 75 - 78.
  • the brake piston used there performs linear movements, so that the fluid brake cylinder has relatively large dimensions overall.
  • the configuration according to the invention allows the most compact dimensions of the entire rotary drive to be maintained, the fluid brake device being able to be integrated into the overall arrangement without any problems if required.
  • the exemplary fluidically actuable rotary drive comprises a drive device 1 and a hydraulic fluid brake device 2 mechanically coupled to it in motion.
  • These two devices 1, 2 each contain, as an essential component, a swivel unit 3, 3 ', the structure of which preferably corresponds to that of the swivel unit of the in DE 39 41 255 A1 described swing piston engine is realized.
  • a swivel unit 3, 3 ' the structure of which preferably corresponds to that of the swivel unit of the in DE 39 41 255 A1 described swing piston engine is realized.
  • the two swivel units 3, 3 ' are accommodated in a common block-like housing 4, whereby they are arranged coaxially next to one another with a small distance. In this way, there is a compact unit.
  • An output shaft 5 is rotatably mounted in the housing 4. Corresponding bearing points are indicated at 6, 6 '.
  • the output shaft 5 can be driven via the drive device 1 to a reciprocating rotary movement about its longitudinal axis 7 in the exemplary embodiment, which can be tapped at an end section 8 of the output shaft 5 protruding from the housing 4. In this way, objects or tools can be rotated.
  • the fluid brake device 2 working with a hydraulic medium is also coupled to the output shaft 5. It ensures that the rotary movement that can be tapped is extremely uniform even with slow rotary movements, and at the same time it can serve to specify the desired rotational speed.
  • Each swivel unit 3, 3 ' has a swivel piston 12, which is differentiated in the case of the drive device 1 as the drive swivel piston 13 and in the case of the fluid brake device 2 as the swiveling brake piston or brake swivel piston 14.
  • Each pivoting piston 12 is accommodated in a housing chamber 15 formed in the housing 4, which is referred to as the housing space 16 in the case of the drive device 1 and as the displacement space 17 in the case of the fluid brake device 2.
  • the pivoting pistons 12 can be pivoted in the associated housing chamber 15 about a respective pivot axis 18, 18 ', which in the exemplary embodiment coincide with the longitudinal axis 7 forming the axis of rotation of the output shaft 5.
  • the output shaft 5 passes through both the housing space 16 and the displacement space 17.
  • a respective pivoting piston 12 has a bushing-like bearing section 22, which can be seen clearly in FIG. Starting from the bearing section 22, at least one wing 23 projects radially. By interacting with mating surfaces 24 fixed to the housing, a respective pivoting piston 12 in the associated housing chamber 15 tightly separates two subspaces 26, 27 which follow one another in the pivoting direction 25. The tightness is expediently ensured by a sealing arrangement 28 which the respective pivoting piston 12 carries and which bears against the counter surfaces 24 and can slide along them.
  • a fluid channel 32 opens into each sub-space 26, 27 of the two swivel units.
  • pneumatic pressure medium is alternately fed and discharged via the fluid channels 32 of the drive device 1, so that the drive swivel piston 13 has a reciprocating swivel movement according to swivel direction 25 executes the pivot axis 18 as the center.
  • the maximum swivel angle in the exemplary embodiment is approximately 300 °. Larger swivel angles prevent, as is also the case with the swivel unit 3 'of the fluid brake device 2, a partition 33 fixed to the housing, which projects into the swivel path of the wing 23 and contributes to the department of the respective two subspaces 26, 27 by interaction with the bearing section 22. If necessary, the partition 33 can be used directly as a mechanical stop to limit the pivoting angle.
  • the fluid channels 32 expediently open into the subspaces 26, 27 in the immediate vicinity of the partition 33.
  • the housing space 16 and the displacement space 17 in the exemplary embodiment are designed as originally circular chambers, into which the partition 33 is inserted as a separate part at one point on the circumference in such a way that on the one hand they are provided with the lateral surface of the bearing section 22 or one provided there Seal and on the other hand cooperates sealingly with the inner surface of the housing space 16 or the displacement space 17.
  • the partition 33 thus has the function of a piston space divider.
  • the radial extent of the partition 33 essentially corresponds to that of the respective wing 23.
  • connection openings which enable the connection of pressure medium lines via which the compressed air required to drive the rotary drive is supplied and discharged.
  • the housing space 16 and the displacement space 17 lie separately from one another in a coaxial orientation in the interior of the housing 4.
  • An intermediate wall 34 extends axially between them and is penetrated by the output shaft 5 in a sealed manner.
  • the housing 4 is expediently constructed in several parts and, in the exemplary embodiment, comprises three parts, namely an intermediate piece 35 which forms the intermediate wall 34 and two end covers 36, 36 'which form the outer end walls of the two housing chambers 15. In the separated state, there is an axial half of the associated housing chamber 15 in each end cover 36, 36 ', while the intermediate piece 35 forms the other axial half of the associated housing chamber 15 on opposite axial sides.
  • the aforementioned housing parts 35, 36, 36 ' can easily be stacked on top of one another and tightly connected to one another by fastening means 37, for example screws.
  • a device can be provided there if necessary with which the angle of rotation of the output shaft 5 can be set within the maximum values predetermined by the pivoting range of the pivoting piston 12.
  • both pivot pistons 12 are in a rotationally fixed connection with the output shaft 5
  • the brake piston 14 is mechanically coupled to the drive pivot piston 13 in such a way that it synchronizes with its pivoting movements and is driven by the drive pivot piston 13 to pivot.
  • the orientation of the pivoting piston 12 with respect to the output shaft 5 is expediently such that the wings 23 are axially aligned and there is no angular offset in the pivoting direction 25. Nevertheless, such an arrangement would also be possible in principle.
  • the fluid brake device 2 also contains an equalization space 38 which is formed separately from the displacement space 17. It can be an integral part of the housing 4, but is preferably located as shown in an expansion tank 43 designed as a separate component, which is attached to the outer surface of the housing 4, for. B. is fastened by means of screws 44.
  • the compensation space 38 is preferably assigned to the two subspaces 26, 27 of the displacement space 17 together, and communicates with each of these subspaces 26, 27 via at least one fluid channel 45, 46 of the fluid channels 32 already mentioned.
  • the compensation chamber 38 forms with the fluid channels 45, 46 and the two sub-chambers 26, 27 of the displacement chamber 17 a closed hydraulic system which is completely filled with a hydraulic medium, preferably with oil.
  • the minimum overflow cross section determines the swiveling speed of the brake piston 14 as a function of the pressure of the drive medium acting on the drive swivel piston 13.
  • the rotational speed which can be tapped off at the output shaft 5 can thus be influenced via the brake piston 14.
  • the fluid channels 45, 46 in the exemplary embodiment each have a throttle point 47 at which the flow cross section is reduced in comparison to the other sections of the fluid channels 45, 46.
  • the throttling intensity can preferably be adjusted from the outside as required, so that it can be easily adapted to the respective circumstances without having to replace the rotary drive.
  • the respective adjustable throttle point 47 is part of a throttle check valve 48 known as such, in which the throttle point 47 and a check valve 49 connected in parallel with it are combined. Such a throttle check valve 48 is switched on in the course of each fluid channel 45, 46.
  • the arrangement is such that the respective check valve 49 with a flow from the Displacement chamber 17 blocks in the direction of the compensation chamber 38, so that the hydraulic fluid must flow via the throttle point 47. If the flow direction is opposite, the hydraulic fluid can pass the check valve 49 without throttling. In this way, throttling preferably takes place only in the case of the displaced hydraulic fluid, while the hydraulic fluid flowing into the other sub-space can flow in unhindered.
  • the check valve 49 is expediently a lip check valve which has a flexible annular sealing lip.
  • the two throttle check valves 48 are mounted in the embodiment in a wall 50 of the surge tank 43.
  • a respective fluid channel 45, 46 has a first channel section 54, which on the one hand opens into one of the partial spaces 26, 27 and on the other hand on an outer surface 53 of the housing 4.
  • the outer surface is adjoined by a second channel section 55 provided in the expansion tank 43, which extends to a receiving section 56, which is open to an outer surface 58 of the expansion tank 43.
  • the throttle check valve 48 is inserted and in particular screwed into the receiving section 56 via this open side.
  • a third and last channel section 57 extending transversely from the receiving section 56 opens into the compensation space 38 arranged below the wall 50. This fluid channel course applies to both fluid channels 45, 46 communicating with the subspaces 26, 27.
  • a section of the wall delimiting the compensation space 38 is preferably formed by a movable compensation piston 59. It is under constant pretension due to a spring arrangement 60 acting on it and is acted upon in the sense of a volume reduction of the compensation space 38.
  • the biasing piston 59 is always held in such a way that in spite of any leakage losses or temperature-related expansions no air entry is possible in the hydraulic circuit mentioned.
  • the compensating piston 59 is guided in a linearly movable manner in the interior of the compensating container 43, the spring arrangement 60 acting in the direction of the wall 50 mentioned and being supported between the compensating piston 59 and a further container wall 51 present on the side opposite the wall 50.
  • the stroke of the compensating piston 59 in the sense of compression of the spring arrangement 60 can, if required, be predetermined by a stop element 63 which is connected in parallel with the spring arrangement 60.
  • a lip sealing ring 64 is expediently provided for sealing between the output shaft 5 and the intermediate wall 34.
  • a corresponding lip sealing ring 64 ' is located in the axially opposite region between the end cover 36' and the output shaft 5 penetrating it outwards.
  • the prevailing oil and air pressure in the fluid brake device, which preferably works with oil, and in the drive device, preferably works with air, can be practically the same, so that good controllability is achieved. Since both swivel wings sit on a common axis, there is no need for complex couplings.
  • the rotary drive according to the invention can be installed like a conventional rotary drive which does not have a fluid brake device.
  • the rotary drive is very well suited for generating slow, constant rotary movements, with no hydraulic pump required.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Hydraulic Motors (AREA)
  • Braking Arrangements (AREA)
EP94118946A 1994-02-26 1994-12-01 Actionneur fluidique rotatif Expired - Lifetime EP0669469B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4406376A DE4406376A1 (de) 1994-02-26 1994-02-26 Fluidisch betätigbarer Drehantrieb
DE4406376 1994-02-26

Publications (2)

Publication Number Publication Date
EP0669469A1 true EP0669469A1 (fr) 1995-08-30
EP0669469B1 EP0669469B1 (fr) 1997-09-24

Family

ID=6511330

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94118946A Expired - Lifetime EP0669469B1 (fr) 1994-02-26 1994-12-01 Actionneur fluidique rotatif

Country Status (2)

Country Link
EP (1) EP0669469B1 (fr)
DE (2) DE4406376A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10458441B2 (en) 2013-02-27 2019-10-29 Woodward, Inc. Rotary piston actuator anti-rotation configurations

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19847983C1 (de) 1998-10-17 2000-05-25 Daimler Chrysler Ag Mehrteiliges, versenkbares Fahrzeugverdeck
FI108076B (fi) * 1999-08-17 2001-11-15 Esko Raikamo Voimaelin venttiilien tms. asettamiseksi haluttuun asentoon
DE202008003944U1 (de) 2008-03-20 2008-06-05 Festo Ag & Co Fluidbetätigter Drehantrieb
EP2420682B1 (fr) * 2010-08-21 2012-06-06 FESTO AG & Co. KG Dispositif d'entraînement rotatif hydraulique
US9816537B2 (en) 2013-02-27 2017-11-14 Woodward, Inc. Rotary piston type actuator with a central actuation assembly
US9234535B2 (en) 2013-02-27 2016-01-12 Woodward, Inc. Rotary piston type actuator
EP3194794B1 (fr) * 2014-09-19 2018-12-05 Woodward, Inc. Configuration pour verin rotatif
US11199248B2 (en) 2019-04-30 2021-12-14 Woodward, Inc. Compact linear to rotary actuator
EP4133186A1 (fr) 2020-04-08 2023-02-15 Woodward, Inc. Actionneur du type à piston rotatif, doté d'ensemble d'actionnement central

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2066901A (en) * 1979-12-21 1981-07-15 Tovarne Strojarskej Tech Rotary positive-displacement fluid-machines
GB2239053A (en) * 1989-12-14 1991-06-19 Festo Kg Motor of the oscillating-piston type
EP0481692A2 (fr) * 1990-10-15 1992-04-22 C & C MANUFACTURING INC. Dispositif à axes multiples
EP0564950A1 (fr) * 1992-04-10 1993-10-13 UNIVER S.p.A. Vérin rotatif programmable

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2066901A (en) * 1979-12-21 1981-07-15 Tovarne Strojarskej Tech Rotary positive-displacement fluid-machines
GB2239053A (en) * 1989-12-14 1991-06-19 Festo Kg Motor of the oscillating-piston type
EP0481692A2 (fr) * 1990-10-15 1992-04-22 C & C MANUFACTURING INC. Dispositif à axes multiples
EP0564950A1 (fr) * 1992-04-10 1993-10-13 UNIVER S.p.A. Vérin rotatif programmable

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10458441B2 (en) 2013-02-27 2019-10-29 Woodward, Inc. Rotary piston actuator anti-rotation configurations

Also Published As

Publication number Publication date
DE59404164D1 (de) 1997-10-30
EP0669469B1 (fr) 1997-09-24
DE4406376A1 (de) 1995-08-31

Similar Documents

Publication Publication Date Title
EP1212517A1 (fr) Dispositif de reglage d'un arbre a cames destine a des moteurs a combustion interne
EP0669469B1 (fr) Actionneur fluidique rotatif
DE2253575A1 (de) Steuergeraet fuer lenkeinrichtungen o.dgl
EP1249619B1 (fr) Unité de soupapes à clapet anti-retour piloté et actionneur à fluide équipé d'une telle unité
EP0886036A2 (fr) Moteur à pistons à air comprimé
EP0937206B1 (fr) Moteur de positionnement pneumatique ou hydraulique muni d'un dispositif de desenclenchement
EP0737610A2 (fr) Direction à crémaillère hydraulique
DE1914723C3 (de) Steuerventil für hydraulische Antriebe
DE2156696C2 (de) Steuervorrichtung mit einer Meßspindel und einem Mitlaufteil
WO2010084002A2 (fr) Ensemble machine hydraulique
DE2516154A1 (de) Impulsgeber
DE2161459C3 (de) Hydrostatisch angetriebene Doppelpumpe
DE19543237A1 (de) Hydraulische Stellvorrichtung, insbesondere Schwenkantrieb
DE19757157C2 (de) Hydraulischer Linearantrieb
EP0280745B1 (fr) Pompe à membrane à piston
DE3825453C2 (fr)
DE3841382C1 (fr)
DE2825790C2 (de) Stellmotor mit Nachlaufsteuerung
DE2806929C2 (de) Fluidbetätigter Servomotor mit Nachlaufsteuerung
DE1243519B (de) Drehschieber fuer eine schnellaufende mehrzylindrige Druckfluessigkeits-Schubkolbenmaschine (Pumpe oder Motor)
DE2944471A1 (de) Pneumatisches antriebselement
DE2251999C3 (de) Einrichtung zur Anzeige der Endstellungen des Arbeitskolbens eines doppeltwirkenden druckmittelbetätigten Stellmotors
DE68903307T2 (de) Ramme fuer schwenkrollengetriebe.
DE19806980C2 (de) Zweistufiger hydraulischer Kurzhublinearantrieb
EP0089568A1 (fr) Dispositif d'actionnement rotatif à fluide sous pression

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: 19950303

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

17Q First examination report despatched

Effective date: 19970128

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

ITF It: translation for a ep patent filed

Owner name: MANZONI & MANZONI

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19970924

REF Corresponds to:

Ref document number: 59404164

Country of ref document: DE

Date of ref document: 19971030

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: FESTO AG & CO

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

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

Ref country code: SE

Payment date: 20021216

Year of fee payment: 9

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

Ref country code: FR

Payment date: 20031027

Year of fee payment: 10

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

Ref country code: GB

Payment date: 20031126

Year of fee payment: 10

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

Ref country code: SE

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

Effective date: 20031202

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

Ref country code: DE

Payment date: 20031219

Year of fee payment: 10

EUG Se: european patent has lapsed
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: 20041201

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: 20050701

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

Effective date: 20041201

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: 20050831

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051201