EP0473025A1 - Pompe à engrenages internes pour fluide hydraulique - Google Patents

Pompe à engrenages internes pour fluide hydraulique Download PDF

Info

Publication number
EP0473025A1
EP0473025A1 EP91113738A EP91113738A EP0473025A1 EP 0473025 A1 EP0473025 A1 EP 0473025A1 EP 91113738 A EP91113738 A EP 91113738A EP 91113738 A EP91113738 A EP 91113738A EP 0473025 A1 EP0473025 A1 EP 0473025A1
Authority
EP
European Patent Office
Prior art keywords
eccentric
pump
wheel
radius
inner wheel
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
EP91113738A
Other languages
German (de)
English (en)
Other versions
EP0473025B1 (fr
Inventor
Siegfried Hertell
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.)
Barmag Luk Automobiltechnik GmbH and Co KG
Original Assignee
Barmag Luk Automobiltechnik GmbH 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 Barmag Luk Automobiltechnik GmbH and Co KG filed Critical Barmag Luk Automobiltechnik GmbH and Co KG
Priority to AT91113738T priority Critical patent/ATE96886T1/de
Publication of EP0473025A1 publication Critical patent/EP0473025A1/fr
Application granted granted Critical
Publication of EP0473025B1 publication Critical patent/EP0473025B1/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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps
    • F04C15/066—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type
    • F04C15/068—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type of the elastic type, e.g. reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0065—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes

Definitions

  • the invention relates to a gear pump according to the preamble of claim 1.
  • the inner wheel is mounted eccentrically in the recess of a rotor to the pump axis.
  • the rotor in turn is rotatably supported in the space formed by the outer wheel and is firmly connected to the pump shaft, which serves to drive the rotor.
  • the known pump has a circular-cylindrical inlet space located in an end wall and a channel system arranged in the rotor, which meshes with the circular-cylindrical insert space and is in permanent communication.
  • annular inlet space is covered by the rotating wheel so that the engagement zone on the pressure side has no connection to the inlet.
  • the deflection of the pump shaft cannot lead to a tilting of the inner wheel and thus to a leak in the pump and a reduction in its efficiency.
  • This advantage is particularly effective when the pump shaft is also used to drive other machine parts and / or when transverse forces are introduced into the pump shaft via the drive of the pump shaft, which can lead to misalignment.
  • the solution according to claim 2 serves the further purpose of avoiding static overdeterminations, since here the inner wheel is not positively fixed by the outer wheel with regard to its current axis of rotation.
  • the solution according to claim 3 achieves good cooling and lubrication of the eccentric, which is subjected to heat and wear due to the sliding bearings inside and outside.
  • the pump is advantageously operated with suction throttling, in which the inlet is throttled and a separate outlet valve is provided in the outlet for each cell formed by the toothing.
  • a separate outlet valve is provided in the outlet for each cell formed by the toothing.
  • the solution according to claim 5 has the advantage that the outer seals of the pump are not under pressure. A vacuum is only created when it is introduced into the pump.
  • the particular advantage of the design according to this invention results when used as a hydraulic pump for the hydraulic converter or the hydraulic clutch of an automatic motor vehicle transmission.
  • the pump according to the invention in its design and centering is independent of the design and centering of the hydraulic converter or the hydraulic clutch.
  • the loads on the pump and turbine wheel of the hydraulic converter cannot affect the hydraulic pump.
  • the compressive forces acting on the inner wheel and on the eccentric, as well as the force with which the clutch flap of the drive shaft engages in the eccentric substantially compensate and are aligned parallel to one another.
  • the driver pocket of the eccentric lies behind the plane of symmetry that passes through the pump axis.
  • the radial boundary wall of the driving pocket pointing in the direction of rotation lies essentially parallel to the secant of the inner wheel, which delimits the pressure zone on the inner wheel.
  • the pump housing is formed by the pump casing 1 and the end plates 2 and 3, which are stacked on top of one another.
  • the housing jacket 1 has a circular cylindrical interior, in the cylindrical inner jacket of which a circumferential groove 4 is pierced.
  • the outer wheel 6 is fastened on the webs 5 which remain to the side.
  • the entire package consisting of casing 1, end plates 2 and 3 and the outside wheel 6 is held together by a screw 7.
  • the screw connection 7 penetrates the outer wheel in the region of the tooth heads with holes 8.
  • the outer wheel has an internal toothing.
  • the interior of the pump is thus circumscribed by the internal toothing with tip circle 9 of the outer wheel.
  • a pin 10 is firmly inserted at one end.
  • the other end of the pin 10 projects into the interior of the pump.
  • an eccentric 11 is freely rotatable.
  • the axial width of the eccentric corresponds essentially to the axial width of the housing shell 1 and the outer wheel 6.
  • the eccentric has a circular cylindrical outer circumference, the central axis of which is indicated at 12 and which rotates with the eccentricity E about the axis 13 of the pin 10.
  • the inner wheel 14 is freely rotatably mounted on the eccentric 11.
  • the inner wheel 14 has external teeth.
  • the eccentricity E of the eccentric and the outer toothing of the inner wheel are dimensioned and the toothing is designed so that the outer toothing of the inner wheel meshes with the inner toothing of the outer wheel.
  • the top circles 9 and 15 of the toothing intersect in the circumferential intersections 21 and 22.
  • the teeth are designed so that the teeth of the outer and inner wheel between the intersections 21 and 22 of the tip circles 9 and 15 are in sealing engagement with their flanks. There are therefore several tooth cells between the intersections 21 and 22 in the engagement area, which are sealed by touching their flanks to one another and to the inner crescent space 23 facing away from the eccentricity.
  • the drive shaft 16 is used to drive the pump.
  • the drive shaft 16 is rotatably mounted concentrically to the central axis 13 of the pin 10 in the other end plate 2 and its end is essentially flush with the inside of the pump chamber.
  • the shaft 16 forms an end face on which a coupling tab 17 is attached eccentrically. This coupling tab 17 protrudes axially into a driving pocket 18 which is introduced into the adjacent end face of the eccentric 11 in the region of the eccentricity.
  • the pump has an essentially radial inlet channel 19 in the end plate 3.
  • the inlet channel opens into a distribution space 20 which concentrically surrounds the pin 10.
  • the distributor chamber is designed as a circular cylindrical recess in the end face of the end plate, which delimits the pump chamber. Their radius is smaller than the radius Fi of the root circle of the inner wheel.
  • a further circular cylindrical recess is made concentrically with the axis 13.
  • This recess serves as the inlet chamber 28.
  • the distributor chamber 20 and the inlet chamber 28 are connected to one another by channels which penetrate the eccentric axially. These channels are preferably formed as grooves of the inner bore of the eccentric and serve to lubricate the sliding bearing of the eccentric on the pin 10 and also to cool the eccentric 11.
  • the driving pocket 18 serves as such a channel, which therefore axially penetrates the eccentric 11 and with it outer edge revolves on a radius that is slightly larger than the radius of the shaft. Several such channels can also be provided.
  • the outer radius R of the inlet chamber 28, based on the axis 13 of the pin 10, has to be kept within certain limits according to the invention, which will be discussed later.
  • the dimensioning of the outer radius R of the inlet chamber 28 is such that the root circle Fi of the inner wheel or the circular area circumscribed by this root circle covers the inlet chamber 28 with the exception of a crescent-shaped inlet surface 27.
  • the inlet surface is also partially covered by the sides of the teeth of the inner wheel.
  • the inlet surface 27 runs on the side of the interior facing away from the eccentricity.
  • the inventive dimensioning of the outer radius R of the inlet chamber 28 on the one hand and the root circle Fi of the inner wheel on the other hand ensures that the crescent-shaped inlet surface 27 is never covered by one of the closed tooth cells of the engagement area. This avoids a dead travel of these tooth cells in the pressure range and the hydraulic efficiency ver improves.
  • the outlet channel 24 is located radially in the housing shell 2 and is connected to the circumferential groove 4 of the housing shell. This circumferential groove is limited on the inside by the outer circumference of the outer wheel and forms an outer chamber.
  • the outer wheel has at least one outlet bore 25 in the area of each tooth gap.
  • Fig. 1 it is shown that two outlet bores 25.1 and 25.2 are adjacent to each other in the axial direction per tooth gap.
  • the outlet bores are each arranged in parallel radial planes.
  • Each radial plane is covered by an elastic valve ring 26.1 and 26.2, which covers all the outlet bores of a normal plane and is thereby severed in an axial plane.
  • One end is e.g. held by a rivet, the other end is free to move.
  • These valve rings 26.1, 26.2 serve as check valves for each of the outlet bores.
  • the outer diameter of the inlet chamber 28 is now dimensioned such that the cells on the pressure side have no connection with the inlet chamber 28. Rather, the inlet chamber is in the pressure area from the end face of the inner wheel, i.e. covered by the area enclosed by the base circle and the tooth heads. Therefore, the width of the crescent-shaped inlet surface 27, which is delimited on the outside by the circumferential surface of the inlet chamber 28 and on the inside by the root circle of the inner wheel, may only be one division greater than the width of the crescent-shaped interior 23, which is delimited by the two root circles. The width of these crescent-shaped spaces and the division is measured in each case as a central angle about the central axis 13 of the pump.
  • the pump can preferably also be used as a suction-restricted pump.
  • the inlet duct 19 has a throttle 33.
  • This throttle only a limited amount of oil can be drawn in.
  • This time-limited suction quantity is only sufficient to completely fill the pump up to a certain speed.
  • the pump delivery rate is therefore proportional to the speed only up to this speed. If the speed increases, there is no further increase in the delivery rate. Therefore, increasing the speed is not associated with increased power consumption.
  • the pump is therefore particularly suitable for consumers in motor vehicles who have an oil requirement that is not dependent on the strongly fluctuating engine speed.
  • FIG. 3 schematically shows a hydraulic converter with an integrated hydraulic pump according to this invention.
  • a hydraulic converter is e.g. B. in the book “Dubbel”, Taschenbuch des Maschinenbau, pp. 904/905, 14.
  • the pump wheel 34 is driven by the pump shaft 35.
  • the output takes place via turbine wheel 36 and turbine shaft 37.
  • stator wheel 38 which is rotatably mounted on stator pin 10.
  • the pump wheel 34 is connected to a hollow cylindrical drive shaft 16 which concentrically surrounds the stator pin 10.
  • the stator pin 10 is fastened in the converter housing 39.
  • the hydraulic pump is fitted into a recess in the converter housing 39. It consists of end plate 2 and 3 and the outer wheel 6 fastened in between by screw 7.
  • the eccentric 11 On the stator pin 10, the eccentric 11 is freely rotatable by means of plain bearings.
  • the inner wheel 14 is freely rotatably mounted on the eccentric 11.
  • the eccentric 11 has an axially parallel recess (driver pocket 18) into which a coupling tab 17 of the drive shaft 16 engages.
  • a seal 40 is located between the end plate 3 and the drive shaft 16.
  • the inlet chamber 28 described above is delimited by this seal 40.
  • This circular cylindrical inlet chamber 28 is designed such that it only slightly projects beyond the root circle of the inner wheel 14 in the inlet area so that the throttling required for the suction throttle control results directly on the inner wheel. This in turn means that the inlet chamber 28 is under atmospheric pressure, so that the seal 40 is not under pressure.
  • the circular cylindrical distributor space 20 On the opposite side of the eccentric 11, the circular cylindrical distributor space 20 is formed in
  • a pressure chamber 4 is formed on the outer circumference of the outer wheel.
  • the outlet channels of the pressure cell formed by the toothing connect each cell formed between two teeth of the outer wheel to the pressure chamber 4.
  • a valve ring 26, which surrounds the outer circumference, serves as a check valve.
  • the pressure chamber 4 is delimited on the outside by the converter housing 39.
  • the pressure chamber 4 has a further outlet channel 29.
  • the plane of symmetry here denotes the axial plane of the eccentric, in which both the center of rotation of the eccentric, namely the pump axis 13, and the center of the circle 42 of the eccentric lie.
  • the driving pocket 18 is placed in such a way that the driving force which the coupling flap 17 exerts on the radial boundary wall of the driving pocket 18 runs essentially parallel to the resultant of the pressure forces which affect the inner wheel and the eccentric. It should be noted that this is a suction-restricted pump.
  • the most unfavorable load case for this pump lies in the lower speed range, in which all of the closed cells formed in the toothing are filled with oil and are therefore subjected to pressure in the pressure zone.
  • the front radial boundary wall of the driving pocket 18 is therefore essentially parallel to the secant which intersects the beginning and end of the pressure zone.
  • the beginning of the pressure zone lies in the plane of symmetry 41 and the end of the pressure zone lies where the tip circles of the inner wheel and the outer wheel intersect, i.e. H. where the last meshing of the inner wheel and outer wheel takes place.
  • this is preferably the case at the intersection of the tip circles.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP91113738A 1990-08-20 1991-08-16 Pompe à engrenages internes pour fluide hydraulique Expired - Lifetime EP0473025B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT91113738T ATE96886T1 (de) 1990-08-20 1991-08-16 Innenzahnradpumpe fuer hydraulikfluessigkeit.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4026261 1990-08-20
DE4026261 1990-08-20

Publications (2)

Publication Number Publication Date
EP0473025A1 true EP0473025A1 (fr) 1992-03-04
EP0473025B1 EP0473025B1 (fr) 1993-11-03

Family

ID=6412533

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91113738A Expired - Lifetime EP0473025B1 (fr) 1990-08-20 1991-08-16 Pompe à engrenages internes pour fluide hydraulique

Country Status (4)

Country Link
EP (1) EP0473025B1 (fr)
JP (1) JP3011797B2 (fr)
AT (1) ATE96886T1 (fr)
DE (1) DE59100553D1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2284638A (en) * 1993-11-18 1995-06-14 Barmag Luk Automobiltech An internal gear pump
WO2004044429A3 (fr) * 2002-11-14 2004-08-12 Luk Automobiltech Gmbh & Co Kg Pompe

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008251687A (ja) 2007-03-29 2008-10-16 Toshiba Corp プリント回路板、およびこれを備えた電子機器
DE102016217267A1 (de) 2016-09-09 2018-03-15 Mahle International Gmbh Anordnung für eine Kälteanlage mit einem Spiralverdichter
JP7886720B2 (ja) * 2022-03-30 2026-07-08 カヤバ株式会社 内接歯車ポンプおよび車高調整機能付き緩衝器
US12140141B1 (en) * 2024-04-30 2024-11-12 Hangzhou Quadrant Technology Co., Ltd. Electric oil pump including pump housing and eccentric assembly non-concentrically arranged with pump housing

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1099560A (fr) * 1954-02-15 1955-09-07 Perfectionnements aux machines à engrenages conjugués et leurs applications
GB2069609A (en) * 1980-02-15 1981-08-26 Zahnradfabrik Friedrichshafen Rotary positive-displacement fluidmachines
DE3444859A1 (de) * 1983-12-14 1985-06-27 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Rotationszellenpumpe fuer hydrauliksysteme
DE3504783A1 (de) * 1984-02-15 1985-10-24 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Zahnradpumpe mit innenverzahnung
EP0345978A1 (fr) * 1988-06-09 1989-12-13 Concentric Pumps Limited Pompe à engrènement interne

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2619062C2 (de) * 1976-05-03 1987-02-12 Robert Bosch Gmbh, 7000 Stuttgart Kraftstofförderaggregat bestehend aus Pumpe und Elektromotor
IT1180430B (it) 1984-02-17 1987-09-23 Continua Int Impianto di colata continua in curva di metalli in particolare d acciaio con dispositivo per ridurre in pezzi di rottame lo spezzone di coda della barra colata

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1099560A (fr) * 1954-02-15 1955-09-07 Perfectionnements aux machines à engrenages conjugués et leurs applications
GB2069609A (en) * 1980-02-15 1981-08-26 Zahnradfabrik Friedrichshafen Rotary positive-displacement fluidmachines
DE3444859A1 (de) * 1983-12-14 1985-06-27 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Rotationszellenpumpe fuer hydrauliksysteme
DE3504783A1 (de) * 1984-02-15 1985-10-24 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Zahnradpumpe mit innenverzahnung
EP0345978A1 (fr) * 1988-06-09 1989-12-13 Concentric Pumps Limited Pompe à engrènement interne

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2284638A (en) * 1993-11-18 1995-06-14 Barmag Luk Automobiltech An internal gear pump
GB2284638B (en) * 1993-11-18 1998-05-27 Barmag Luk Automobiltech An internal-geared pump
WO2004044429A3 (fr) * 2002-11-14 2004-08-12 Luk Automobiltech Gmbh & Co Kg Pompe

Also Published As

Publication number Publication date
DE59100553D1 (de) 1993-12-09
JPH04255585A (ja) 1992-09-10
EP0473025B1 (fr) 1993-11-03
ATE96886T1 (de) 1993-11-15
JP3011797B2 (ja) 2000-02-21

Similar Documents

Publication Publication Date Title
EP0682756B1 (fr) Boite de vitesses a pompe volumetrique
EP0362906B1 (fr) Pompe à engrènement interne
DE102011104324B4 (de) Hocheffiziente Konstantförderflügelzellenpumpe
DE3334919A1 (de) Fluegelradpumpe mit variabler foerderleistung
EP3929439A1 (fr) Décharge axiale de pression dans les paliers lisses des pompes
EP1141551A1 (fr) Ensemble de pompes comportant deux pompes hydrauliques
DE2939405A1 (de) Umlaufende hydraulische vorrichtung
DE102011108767B4 (de) Hocheffiziente Drehschieberkonstantpumpe
EP1019637A1 (fr) Moteur oscillant radial
EP0473025B1 (fr) Pompe à engrenages internes pour fluide hydraulique
EP0579981B1 (fr) Pompe à engrenages internes pour fluide hydraulique
DE102004021216B4 (de) Hochdruck-Innenzahnradmaschine mit mehrfacher hydrostatischer Lagerung pro Hohlrad
DE3841238C2 (fr)
EP0225338A1 (fr) Pompe a capacite variable.
EP0474001B1 (fr) Pompe à engrenages internes pour fluide hydraulique
EP0475109B1 (fr) Pompe à engrenages internes pour fluide hydraulique
DE3841329C2 (de) Flügelzellenvakuumpumpe
DE4008522C2 (fr)
DE10040711C2 (de) Flügelzellenpumpe
EP0381682B1 (fr) Compresseur cellulaire a piston rotatif
EP0315878B1 (fr) Pompe à engrènement interne
DE3737961A1 (de) Innenzahnradpumpe
DE3245974C2 (fr)
EP0320795A2 (fr) Pompe à vide avec palettes
DE3519741A1 (de) Fluegelzellenvakuumpumpe

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): AT DE FR GB IT SE

17P Request for examination filed

Effective date: 19920204

17Q First examination report despatched

Effective date: 19921211

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT DE FR GB IT SE

REF Corresponds to:

Ref document number: 96886

Country of ref document: AT

Date of ref document: 19931115

Kind code of ref document: T

REF Corresponds to:

Ref document number: 59100553

Country of ref document: DE

Date of ref document: 19931209

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

Effective date: 19940126

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
EAL Se: european patent in force in sweden

Ref document number: 91113738.8

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: AT

Payment date: 20040820

Year of fee payment: 14

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

Ref country code: AT

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

Effective date: 20050816

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

Ref country code: DE

Payment date: 20070904

Year of fee payment: 17

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

Ref country code: GB

Payment date: 20070723

Year of fee payment: 17

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

Ref country code: IT

Payment date: 20070823

Year of fee payment: 17

Ref country code: SE

Payment date: 20070820

Year of fee payment: 17

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

Ref country code: FR

Payment date: 20070821

Year of fee payment: 17

EUG Se: european patent has lapsed
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20080816

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20090430

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: 20090303

Ref country code: FR

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

Effective date: 20080901

Ref country code: IT

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

Effective date: 20080816

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: 20080816

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: 20080817