EP0401408A1 - Machine à pistons radiaux - Google Patents

Machine à pistons radiaux Download PDF

Info

Publication number
EP0401408A1
EP0401408A1 EP89110348A EP89110348A EP0401408A1 EP 0401408 A1 EP0401408 A1 EP 0401408A1 EP 89110348 A EP89110348 A EP 89110348A EP 89110348 A EP89110348 A EP 89110348A EP 0401408 A1 EP0401408 A1 EP 0401408A1
Authority
EP
European Patent Office
Prior art keywords
piston
radial
machine according
cylinder
radial piston
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
EP89110348A
Other languages
German (de)
English (en)
Other versions
EP0401408B1 (fr
Inventor
Jürgen Dr.-Ing. Berbuer
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.)
LuK Fahrzeug Hydraulik GmbH and Co KG
Original Assignee
LuK Fahrzeug Hydraulik GmbH and Co KG
Vickers Systems 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 LuK Fahrzeug Hydraulik GmbH and Co KG, Vickers Systems GmbH filed Critical LuK Fahrzeug Hydraulik GmbH and Co KG
Priority to DE89110348T priority Critical patent/DE58906590D1/de
Priority to EP89110348A priority patent/EP0401408B1/fr
Priority to US07/534,674 priority patent/US5079994A/en
Priority to JP2148840A priority patent/JPH086682B2/ja
Publication of EP0401408A1 publication Critical patent/EP0401408A1/fr
Application granted granted Critical
Publication of EP0401408B1 publication Critical patent/EP0401408B1/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
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks
    • 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

Definitions

  • the invention relates to a radial piston machine and in particular radial piston pump for automobiles.
  • the invention has for its object to provide a radial piston machine (pump or motor) which is small compared to known radial piston machines of the same power, can be easily manufactured and works quietly. Furthermore, the construction principle should open up the possibility of changing the displacement volume of the machine with additional components.
  • the length of the respective cylinder bore is only slightly larger than the stroke of the associated piston. Furthermore, the supply and discharge of the fluid can save space through the central arranged control mirror pin take place, ie you can avoid inflow and outflow channels in radially outer housing parts.
  • the manufacture is inexpensive insofar as it is essentially a matter of rotationally symmetrical components, the pistons have a simple design and there are also no high demands on the manufacturing accuracy of the cylinder bores.
  • a special feature of the new radial piston machine is that the pistons are inclined when the cylinder star rotates. This means that pressure in the torque (and vice versa) is converted directly, so that the pistons are relieved of the lateral force.
  • the largest inclination angle ⁇ occurs at a piston position of 90 ° if the zero position in the main eccentricity plane is assumed.
  • a line seal by means of a piston ring is preferred, which can adapt to the changing shape between the ellipse and the circle and does not lead to excessive edge pressures.
  • the piston ring groove with its neck-side edge is arranged on the largest diameter of the piston head and the piston ring has a conical-spherical outer surface.
  • the basic shape of the piston ring is therefore conical, with the piston ring being revised spherically at the largest diameter.
  • the piston shoe which is preferably made in one piece with the piston neck and piston head, has a cylindrical bearing surface in order to engage with the
  • the cylindrical wing is connected asymmetrically to the piston head above the piston neck, the front wing part in the running direction being larger than the rear wing part. If the wings of the piston shoes are lubricated from the respective pump chamber via a hole in the piston, a symmetrical arrangement of the piston shoe and piston head can also be carried out. This type of lubrication also leads to hydrostatic relief of the pistons.
  • the fluid enclosed between the separating web and the cylinder space can be pre-compressed before it is connected to the actual pressure space. If the pre-compression at the time of connection corresponds exactly to the pressure in the pressure chamber, there is no structure-borne noise excitation. Therefore, the separator between low pressure and high pressure is widened in the direction of rotation of the pump by an amount that is suitable for producing a suitable pre-compression of the enclosed pressure fluid. Adjustments to different operating pressures can be made using pilot control notches.
  • the stroke ring of the radial piston machine is adjusted tangentially along a specially aligned guide, as a result of which the eccentricity of the stroke ring is spatially aligned in a certain way, which is noticeable like an adjustment of the advance angle between pump star and control pin.
  • the cam ring is tangential along a guide by a first amount of eccentricity adjustable, and the vertical distance of the guide from the axis of rotation of the cylindrical star is smaller by a second amount of eccentricity than the diameter of the cam ring.
  • the novel radial piston machine can be constructed with one or more disks, i. H. two or more cylinder stars arranged next to one another can be provided, which run on the same control mirror journal and are connected to one another via entrainment means.
  • a control mirror pin 2 is inserted in a sealed manner in a housing 1.
  • Inlet channels 3 and outlet channels 4 each lead to inlet grooves 5 and outlet grooves 6.
  • the grooves 5 and 6 are separated from one another by separating webs 7 and 8.
  • the control mirror pin 2 also has a central bore 9 through which a shaft 10 is passed in order to drive a further unit, not shown.
  • the shaft 10 is supported by bearings 11 in the housing 1 and drives a drive disk 12 via a spline 13 or the like.
  • the drive pulley 12 is connected to a cylindrical star 14, which is provided with a number of radially extending cylinder bores 15, which are each provided with a passage opening 17 on their base 16.
  • the number of cylinder bores 15 can be freely selected within a certain range, i. H. both even and odd numbered cylinders can be used.
  • a one-piece piston 20 is guided, which has a spherical piston head 21, a piston groove 22, a piston neck 23 and one Piston shoe 24 has.
  • the groove 22 is made along the largest diameter of the spherical piston head 21, namely the neck-side edge of the piston groove 22 coincides with the equator of the piston head 21.
  • the piston shoe 24 has a rectangular outline and a cylindrical wing, in which a front wing part 25 and a rear wing part 26 can be distinguished. The areas of these two wing parts are 58 and 42%, respectively.
  • the shoe 24 is connected asymmetrically to the piston neck 23 and piston head 22. This design is used for hydrodynamic lubrication since the lift on the rear wing part 26 is somewhat greater than on the front wing part 25.
  • the wing parts 25 and 26 can also be arranged symmetrically, as shown in FIGS. 5 and 6, which is particularly considered when a lubrication channel 27 leads from the pump chamber 17 to the wings 25, 26.
  • the wing parts 25, 26 can also be interrupted by an annular groove 28 which delimit a surface corresponding to the head 21 and are connected via a relief bore 29 with low pressure in order to provide hydrostatic relief.
  • a slotted piston ring 30 is inserted in the piston groove 22, the slot 31 of which can be seen in FIG. 2 and which enables a certain elastic change in shape of the piston ring 30, which is necessary because the piston head 21 can be inclined in the cylinder bore 15.
  • the piston ring 30 must therefore temporarily change from the circular shape to a weak elliptical shape, which also leads to displacements and swivels of the outer piston ring surface 32 to the cylinder wall.
  • the fluid pressure acts on the piston ring 30 from the outside and also from the inside, the piston groove 22, forth and in order to balance the fluid pressure on the piston ring, a trapezoidal cross-sectional shape of the piston ring 30 would be preferred.
  • the piston ring 30 is designed spherical in the region of its largest diameter 33, as can best be seen from FIG. 7 at 34.
  • the crowning radius can also be continued up to the smaller diameter of the piston ring.
  • the piston shoes 24 work together with a cam ring 35 (FIGS. 1 and 2) which has an inner running surface 36 and an outer surface 37.
  • the inner running surface 36 is arranged eccentrically to the cylinder star 14 and therefore transmits a stroke movement to the pistons 20 when the cylinder star rotates.
  • the return stroke is provided by hold-down rings 38 which engage on the inside of the piston shoes 24 in edge grooves formed there, so that overall positive guidance is achieved becomes.
  • the pump chamber 18 enclosed between the piston head 20 and the cylinder bore 15 widens at the inlet grooves 5 and narrows at the outlet grooves 6. As a result, the fluid is sucked in on the side 5 and displaced on the side 6, which results in the pump flow.
  • the separating webs 7 and 8 are each wider than the passage openings 17, namely that widening points in the angular range ⁇ are offset at least in each case in the direction of rotation of the cylindrical star 14. Accordingly, if the pumping spaces 18 move over the web 7 during their circulation, then the piston 20 already begins to compress the enclosed fluid before it comes into contact with the groove 6, in which the high pressure prevails. If this pre-compression corresponds exactly to the fluid pressure in the groove 6, there is no pressure release and thus no sound excitation. The aim is therefore to design the amount of pre-compression so that it corresponds to the desired pump pressure. Deviations can be compensated for by pre-tax notches in the range ⁇ as long as these deviations are not too large.
  • the dividers 7, 8 can also be arranged symmetrically to the plane 40-40, the widening points then being on both sides.
  • the radial piston pump described can also be designed as a control pump, as shown in FIG. 2.
  • the actuating system acts along an actuating plane 40 and has a small cylinder 41 with a small actuating piston 42 and a large actuating cylinder 43 with a large actuating piston 44 and a spring 45.
  • the small actuating piston 42 is constantly pressurized with the pump pressure and the large actuating piston 44 with control pressure which is less than the pump pressure. It can be regulated to a constant delivery volume or to a constant delivery pressure, which need not be described further. In general, however, this leads to adjusting movements of the cam ring 35 and thus to changed eccentricities e and changed pre-compression amounts, which would thus be mismatched with the system.
  • a guide 46 is provided in the housing 1 for the cam ring 35, against which the cam ring rests and is guided between different eccentric positions.
  • the vertical distance of the guide 46 from the axis of rotation 14a of the cylindrical star that is to say the distance 460-14a, is smaller than the radius of the outer surface 37 of the cam ring 35 with which it is supported on the guide 46.
  • the center 35a of the lifting ring does not coincide with the axis of rotation 14a of the cylindrical star, but takes up a distance c which represents a "constant" eccentricity.
  • the circumferential angle of the cylindrical star is designated by ⁇ .
  • the angle difference between the width of the web 7 and the width of the opening 17 is the separation angle ⁇ .
  • the piston 20 should cover a pre-compression path k when passing the angular range ⁇ , although the radial speed of the pistons 20 depends on the delivery volume and therefore different pre-compression paths seem to be the inevitable result.
  • the lead angle ⁇ is small for large delivery volumes and large for small delivery volumes.
  • the piston travel curve s crosses the separation angle ⁇ for large delivery volumes more in the range of an extreme value, while for small delivery volumes it is shifted more onto the flank of the piston travel curve s, as can be seen from the comparison of FIGS. 9 and 10.
  • an inclined contact surface (corresponding to the guide 46).
  • Such an inclined contact surface can be a straight or a curved guide.
  • the amount of constant eccentricity c is otherwise very small.
  • 11 and 12 show that the radial piston pump can also be designed for two or more cylinder stars 14.
  • the individual cylinder stars are coupled with one another in their rotational movement via driving claws 48 or the like, while a certain radial displacement between the cylinder stars remains possible.
  • two common suction connections 3 are provided, while the pressure connections 4a, 4b are separated for the two pump disks. It goes without saying that the bushing 9 is not absolutely required for the shaft 10 and this space could also be used for fluid channels.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
EP89110348A 1989-06-08 1989-06-08 Machine à pistons radiaux Expired - Lifetime EP0401408B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE89110348T DE58906590D1 (de) 1989-06-08 1989-06-08 Radialkolbenmaschine.
EP89110348A EP0401408B1 (fr) 1989-06-08 1989-06-08 Machine à pistons radiaux
US07/534,674 US5079994A (en) 1989-06-08 1990-06-07 Radial piston machine
JP2148840A JPH086682B2 (ja) 1989-06-08 1990-06-08 ラジアルピストン装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP89110348A EP0401408B1 (fr) 1989-06-08 1989-06-08 Machine à pistons radiaux

Publications (2)

Publication Number Publication Date
EP0401408A1 true EP0401408A1 (fr) 1990-12-12
EP0401408B1 EP0401408B1 (fr) 1993-12-29

Family

ID=8201475

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89110348A Expired - Lifetime EP0401408B1 (fr) 1989-06-08 1989-06-08 Machine à pistons radiaux

Country Status (4)

Country Link
US (1) US5079994A (fr)
EP (1) EP0401408B1 (fr)
JP (1) JPH086682B2 (fr)
DE (1) DE58906590D1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0687814A2 (fr) * 1994-05-25 1995-12-20 Sumitomo Electric Industries, Limited Pompe à plongeur
DE202010013078U1 (de) 2009-12-11 2011-02-24 Berbuer, Jürgen, Dr.-Ing. Hydrostatische Radialkolbenmaschine
DE102014215255A1 (de) 2013-08-07 2015-02-12 Schaeffler Technologies Gmbh & Co. Kg Radialkolbenmaschine
WO2020254501A1 (fr) * 2019-06-19 2020-12-24 Moog Gmbh Machine à pistons radiaux comprenant un piston à bille

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9525028D0 (en) * 1995-12-06 1996-02-07 Unipat Ag Hydrostatic piston machine
ITMO20040165A1 (it) * 2004-06-30 2004-09-30 Apparecchiature Idrauliche S P Macchina a fluido con cilindri radiali perfezionata.
US7484939B2 (en) * 2004-12-17 2009-02-03 Eaton Corporation Variable displacement radial piston pump
EP2206937B1 (fr) * 2009-01-13 2013-06-05 Sauer-Danfoss ApS Améliorations de ou associées aux segments de piston
US9188111B2 (en) 2009-01-20 2015-11-17 Eaton Corporation Displacement assembly for a fluid device
US9399984B2 (en) * 2012-06-25 2016-07-26 Bell Helicopter Textron Inc. Variable radial fluid device with counteracting cams
US9228571B2 (en) * 2012-06-25 2016-01-05 Bell Helicopter Textron Inc. Variable radial fluid device with differential piston control
US10683854B2 (en) * 2015-05-21 2020-06-16 Eaton Intelligent Power Limited Radial piston device with reduced pressure drop
JP6321700B2 (ja) * 2016-02-26 2018-05-09 三菱重工業株式会社 油圧機械および風力発電装置
DE102019205824A1 (de) * 2019-04-24 2020-10-29 Zf Friedrichshafen Ag Pumpe, insbesondere Ölpumpe für ein Getriebe
CN112112753A (zh) * 2020-10-09 2020-12-22 段井胜 一种液压马达
CN112177843B (zh) * 2020-10-09 2023-05-16 东莞市普林斯机电设备有限公司 一种内曲线径向柱塞液压马达
CN112253374B (zh) * 2020-10-09 2023-12-12 宁波真格液压科技有限公司 一种变量液压马达
KR102534467B1 (ko) * 2023-01-02 2023-05-30 하이드로텍(주) 다단 레이디얼 피스톤 펌프

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR862500A (fr) * 1938-12-21 1941-03-07 Aircraft Hydraulic Appliances Perfectionnements apportés aux pompes radiales à cylindres rotatifs
US3087437A (en) * 1959-10-12 1963-04-30 North American Aviation Inc High temperature variable displacement pump
DE1243520B (de) * 1958-09-04 1967-06-29 North American Aviation Inc Schmiereinrichtung an einem innenbeaufschlagten mehrteiligen Kolben einer Radialkolbenmaschine
DE2300681A1 (de) * 1972-01-07 1973-08-30 Karl Eickmann Rotor, kolben und kolbenschuhe und deren zuordnungen in radial-kolben-aggregaten
DE2460512A1 (de) * 1974-12-20 1976-06-24 Linde Ag Radialkolbenmaschine
GB1468658A (en) * 1974-03-06 1977-03-30 Lucas Ltd Piston for use in a radial piston pump or motor

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3084633A (en) * 1957-09-09 1963-04-09 North American Aviation Inc Hydraulic pump or motor
US3357362A (en) * 1966-06-17 1967-12-12 Allis Chalmers Mfg Co Hydrostatic power unit
JPS5559172U (fr) * 1978-10-16 1980-04-22
CH638590A5 (de) * 1979-02-26 1983-09-30 Sulzer Ag Hydrostatische kolbenmaschine.
JPS5999074A (ja) * 1982-11-29 1984-06-07 Hitachi Constr Mach Co Ltd ラジアルピストン式液圧回転機
JP2521481B2 (ja) * 1987-07-03 1996-08-07 川崎重工業株式会社 液圧ピストンポンプ・モ−タ
US4848213A (en) * 1988-01-11 1989-07-18 The Devilbiss Company Reciprocating piston compressor with offset cylinder

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR862500A (fr) * 1938-12-21 1941-03-07 Aircraft Hydraulic Appliances Perfectionnements apportés aux pompes radiales à cylindres rotatifs
DE1243520B (de) * 1958-09-04 1967-06-29 North American Aviation Inc Schmiereinrichtung an einem innenbeaufschlagten mehrteiligen Kolben einer Radialkolbenmaschine
US3087437A (en) * 1959-10-12 1963-04-30 North American Aviation Inc High temperature variable displacement pump
DE2300681A1 (de) * 1972-01-07 1973-08-30 Karl Eickmann Rotor, kolben und kolbenschuhe und deren zuordnungen in radial-kolben-aggregaten
GB1468658A (en) * 1974-03-06 1977-03-30 Lucas Ltd Piston for use in a radial piston pump or motor
DE2460512A1 (de) * 1974-12-20 1976-06-24 Linde Ag Radialkolbenmaschine

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0687814A2 (fr) * 1994-05-25 1995-12-20 Sumitomo Electric Industries, Limited Pompe à plongeur
EP0687814A3 (fr) * 1994-05-25 1996-05-15 Sumitomo Electric Industries Pompe à plongeur
DE202010013078U1 (de) 2009-12-11 2011-02-24 Berbuer, Jürgen, Dr.-Ing. Hydrostatische Radialkolbenmaschine
DE102009054548A1 (de) 2009-12-11 2011-06-16 Berbuer, Jürgen, Dr.-Ing. Hydrostatische Radialkolbenmaschine
WO2011070019A1 (fr) 2009-12-11 2011-06-16 Berbuer Juergen Machine hydrostatique à pistons radiaux
DE102014215255A1 (de) 2013-08-07 2015-02-12 Schaeffler Technologies Gmbh & Co. Kg Radialkolbenmaschine
WO2020254501A1 (fr) * 2019-06-19 2020-12-24 Moog Gmbh Machine à pistons radiaux comprenant un piston à bille

Also Published As

Publication number Publication date
DE58906590D1 (de) 1994-02-10
JPH086682B2 (ja) 1996-01-29
JPH03115782A (ja) 1991-05-16
EP0401408B1 (fr) 1993-12-29
US5079994A (en) 1992-01-14

Similar Documents

Publication Publication Date Title
EP0401408A1 (fr) Machine à pistons radiaux
DE3590198C2 (de) Ventilplatte für eine hydrostatische Axialkolbeneinheit
EP0044070A1 (fr) Pompe à pistons axiaux avec deux courants d'écoulement
EP0808421B1 (fr) Pompe hydrostatique ajustable
WO2007118624A1 (fr) Machine a piston hydrostatique avec disque de commande rotatif
DE3628479A1 (de) Mit einem druckmittel arbeitende, insbesondere hydraulische vorrichtung
DE3018711A1 (de) Axialkolbenpumpe mit pumpeneinlaufkranz
DE4011671C2 (de) Regelbare Flügelzellenpumpe
DE2527189A1 (de) Hydraulikpumpe mit taumelscheibe
DE3209640A1 (de) Hydraulikpumpe
EP0214164B1 (fr) Machine a deplacement positif, notamment pompe
DE2145056A1 (de) Kolbenmaschine
DE102017208755A1 (de) Hydrostatische unterstützungs- und schmierausnehmungen auf valv- segmentslauffläche
DE3242983A1 (de) Regelbare fluegelzellenpumpe
EP0383167B1 (fr) Moteur à pistons axiaux
DE2038086C3 (de) Axialkolbenmaschine
EP1700034B1 (fr) Machine a pistons axiaux pour realiser un acheminement independant dans plusieurs circuits hydrauliques
DE4135904A1 (de) Kolbenpumpe, insbesondere radialkolbenpumpe
DE2420542C2 (de) Radialkolbenmaschine
DE10347085B3 (de) Hydrostatische Kolbenmaschine mit zwei hydraulischen Kreisläufen
DE102021200205A1 (de) Axialkolbenmaschine mit hoher Antriebdrehzahl
DE1703210A1 (de) Als Pumpe oder Motor verwendbare Hydromaschine
DE510858C (de) Pumpe, insbesondere fuer Kunstseidespinnmaschinen, bei welcher die Kolben in radial angeordneten, rings verteilten zylindrischen Bohrungen eines Umlaufkoerpers gefuehrt sind
EP0474001A1 (fr) Pompe à engrenages internes pour fluide hydraulique
DE102022128195A1 (de) Hydraulische Radialkolbenmaschine

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 SE

17P Request for examination filed

Effective date: 19910302

17Q First examination report despatched

Effective date: 19920226

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: LUK FAHRZEUG-HYDRAULIK GMBH & CO. KG

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 SE

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

Ref country code: SE

Effective date: 19931229

REF Corresponds to:

Ref document number: 58906590

Country of ref document: DE

Date of ref document: 19940210

ITF It: translation for a ep patent filed

Owner name: BARZANO' E ZANARDO MILANO S.P.A.

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

Ref country code: GB

Payment date: 19940519

Year of fee payment: 6

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

Effective date: 19940427

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

Ref country code: GB

Effective date: 19950608

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

Effective date: 19950608

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

Ref country code: FR

Payment date: 19980508

Year of fee payment: 10

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

Ref country code: DE

Payment date: 19980604

Year of fee payment: 10

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

Ref country code: FR

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19990630

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: 20000503

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

Effective date: 20050608