EP0004120A2 - Machine à engrenages avec des moyens de décompression du liquide dans l'espace entredents - Google Patents

Machine à engrenages avec des moyens de décompression du liquide dans l'espace entredents Download PDF

Info

Publication number
EP0004120A2
EP0004120A2 EP79200119A EP79200119A EP0004120A2 EP 0004120 A2 EP0004120 A2 EP 0004120A2 EP 79200119 A EP79200119 A EP 79200119A EP 79200119 A EP79200119 A EP 79200119A EP 0004120 A2 EP0004120 A2 EP 0004120A2
Authority
EP
European Patent Office
Prior art keywords
recesses
face
pressure chamber
suction chamber
helical
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
EP79200119A
Other languages
German (de)
English (en)
Other versions
EP0004120B1 (fr
EP0004120A3 (en
Inventor
Theodorus Henricus Korse
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.)
Korse Theodorus Henricus
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0004120A2 publication Critical patent/EP0004120A2/fr
Publication of EP0004120A3 publication Critical patent/EP0004120A3/de
Application granted granted Critical
Publication of EP0004120B1 publication Critical patent/EP0004120B1/fr
Expired 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
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement

Definitions

  • the invention relates to a gear machine (pump or motor) with helical gears meshing in external or internal engagement, the shafts of which are rotatably mounted in the housing and / or housing cover or in bearing bodies arranged in the housing, the engagement area on the side surfaces facing the gearwheels, i.e. in the Housing wall and / or housing cover or in the bearing bodies, recesses are formed, of which the recesses on the pressure chamber side are connected to the pressure chamber and the recesses on the suction chamber side are connected to the suction chamber.
  • the recess on the pressure chamber side and the suction chamber side in a side surface facing the gearwheels are separated from one another by a web of a certain width.
  • a backlash of zero or almost zero is aimed for in order to achieve a greatly reduced flow rate fluctuation and torque fluctuation.
  • Zero or almost zero means an backlash that is less than the usual backlash of e.g. Is 0.3 mm. This is achieved in that in the case of this straight toothing without or almost without backlash, the web width between the recess on the pressure chamber side and on the suction chamber side is reduced to half the value - compared to that of the same toothing with backlash. The problem of squeezing the hydraulic fluid and cavitation in an enclosed tooth gap occurs even more than in the case of a gear machine with backlash.
  • the invention has for its object to provide a gear machine of the type mentioned, in which the available squeezing areas are so large are that the hydraulic fluid can flow into the pinch oil chamber without squeezing or danger of cavitation and can flow out of it again.
  • the pressure chamber side and the suction chamber side recess on the leading end face of the helical toothing are thus offset by a distance V in the suction chamber side compared to the pressure chamber side and the suction chamber side recess on the trailing end side of the helical toothing.
  • the web width is unchanged from that of the comparable spur toothing of the same face cut.
  • the size of the displacement of the recesses is independent of whether there is backlash or not.
  • the technical progress achievable with the invention is based on several advantages.
  • the available squeezing surfaces of the recesses are significantly larger compared to the comparable straight toothing and can also flow into the pinch oil space and also flow out of it again via the.
  • the displacement process can take place undisturbed, the theoretical flow fluctuation is minimal and the pressure fluid can flow in or out of the enclosed tooth space undisturbed without the risk of crushing or cavitation.
  • the gear machine has a very low sound pressure level with little technical effort, i.e. compared to a known gear machine, the same flow rate can be achieved in the gear machine according to the invention at the same sound pressure level, the speed should be higher and the stroke volume smaller.
  • the gear machine according to FIGS. 1 to 3 has a housing 1 which is closed on both sides by housing covers 2 and 3.
  • the housing 1 has a continuous housing opening 4, which is formed by two intersecting bores 5 and 6.
  • the housing opening 4 has approximately the shape of an eight.
  • two bearing bodies 7 and 8 are arranged, in the bearing bores 9 and 10 of which a driving gear 11 is rotatably mounted.
  • two bearing bodies 12 and 13 are arranged in the bore 6, in whose bearing bores 14 and 15 the driven gear wheel 16 is rotatably mounted.
  • the gear machine according to Fig. La consists of a housing la with only one housing cover 2a.
  • the gears 11 and 16 are rotatably supported with their shafts directly in the housing la or in the housing cover 2a.
  • the driving gear 11 has right-hand teeth; the driven gear 16 has left-rising teeth.
  • the driving gear 11 is driven clockwise.
  • Fluctuation recesses 19, 20, 21, 22 attached so that when the volume of the enclosed tooth gap decreases, the enclosed tooth gap is connected to the pressure chamber D via the recesses 19 and 21 displaced by a distance V from one another, and that with increasing volume of the enclosed tooth gap the enclosed tooth gap is connected to the suction space S via the recesses 20 and 22 on the suction space side which are displaced by a distance V from one another.
  • Fig. 4 it is indicated for a helical toothing with backlash, how the recesses 19 to 22 are designed;
  • the center distance extends from the center M 1 of the driving helical gear 11 with right-hand teeth to the center M 2 of the driven helical gear 16 with left-hand teeth.
  • the pole P lies on the middle of the connecting line from M 1 to M 2.
  • the thin solid line 23 follows the contours of the toothing at the front trailing end Face 18 of the helical toothing.
  • the thin dash-dotted line 24 follows the contour of the toothing on the rear leading end face 17 of the helical toothing.
  • the thick line 25 represents the contour of the helical toothing in the center of the wheel.
  • the helical toothing is drawn for the position in which the enclosed tooth gap reaches its smallest volume or in which the hatched area of the enclosed tooth gap 26 reaches its minimum in the wheel center.
  • the pressure changeover process takes place at this very moment, ie the tooth gap is separated from the pressure chamber D and connected to the suction chamber S.
  • the recesses of the helical toothing with backlash are matched to this pressure changeover process.
  • the straight web edges 27 and 28 of the essentially rectangular recesses 19 and 20 of lines running parallel to M 1 , M 2 are at the rear leading end face 17 of the helical toothing through the two contact points 30 lying in this rear leading end face 17 on the engagement plane 29 and 31 formed.
  • the straight web edges 32 and 33 of the substantially rectangular recesses 21 and 22 of lines running parallel to M 1 , M 2 are through the two contact points 34 located in this front trailing end face 18 on the engagement plane 29 and 35 formed.
  • the line of symmetry 88 to the web edges 27, 28 is in the direction of the suction space S by a distance Y and the line of symmetry 89 to the Web edges 32, 33 is in the direction of pressure chamber D by a distance offset to the connecting line M 1 M 2 .
  • the recesses 19, 2 1 and 2 0 , 22 shifted by the distance V can be seen from FIG. 3.
  • the depth 36 of the recesses 19 to 22 is a few millimeters and the width 37 of the recesses 19 to 22 is approximately equal to the tooth height.
  • the recesses 19, 20 and 21, 22 on the pressure chamber side and suction chamber side, respectively, located on one end face of the toothing, are separated from one another by a web with the width 38.
  • the web width 38 is, compared to the web width 39 of the comparable straight toothing shown in FIG. 5 with the same face cut, unchanged.
  • the squeezing surfaces of the straight toothing available for a torsion angle ⁇ 1 are shown in FIG. 5 and the squeezing surfaces of the helical toothing available in FIG. 6.
  • the squeezing surface 40 is available on both end faces of the straight toothing.
  • the squeezing surface 41 is available on the leading end face 17 and the squeezing surface 42 is available on the trailing end face 18.
  • a squeezing surface with a gap 43 is available.
  • the recesses 19 to 22 on the two end faces 17, 18 of the helical toothing can also have a somewhat different shape.
  • the recesses must always be designed such that the enclosed tooth gap is connected to the pressure chamber D via the recesses 19, 21 on the pressure chamber side only with decreasing size of the area of the enclosed tooth gap in the wheel center and that only with increasing size of the area of the enclosed tooth gap in the wheel center the enclosed tooth gap is connected to the suction space S via the recesses 20, 22 on the suction space side.
  • notches 44, 45, 46, 47 are made, which are defined by the root circle 48, 49 and the root circle contour 50, 51, 52, 53 Tooth flank of the adjacent gearwheel is formed at an angle of rotation ⁇ 1 , at which the area of the enclosed tooth gap in the wheel center reaches its minimum.
  • the notches 44 to 47 according to the invention enlarge the available squeezing area even more.
  • the web width 77 is equal to the web width 54 of the comparable straight toothing without or almost without backlash, as can be seen from FIGS. 8 and 9.
  • the recesses are designed such that, with the volume of an enclosed tooth gap decreasing, the enclosed tooth gap via the recesses 55 and 56 with the pressure chamber D displaced by a distance V from one another is connected, and that as the volume of the enclosed tooth gap increases, the enclosed tooth gap is connected to the suction chamber S via the recesses 57 and 58 on the suction chamber side displaced by a distance V from one another.
  • the size of the area of the enclosed tooth gap in the center of the wheel becomes smaller and with increasing Volume of this enclosed tooth gap 59 the size of the area of the enclosed tooth gap 59 becomes larger in the center of the wheel, can be determined in the same way as for the helical toothing with backlash, for which angle of rotation 9 1 of the driving gear 11 this enclosed tooth gap reaches its smallest volume and when so the pressure reversal process must take place.
  • FIG. 9 for a helical toothing with the same face cut as the helical toothing according to FIG. 4, but without or almost without backlash, it is indicated how the recesses 55, 56, 57, 58 according to the invention are designed.
  • the thin solid line 60 follows the contours of the helical teeth on the front trailing face 61 of the helical teeth.
  • the thin dash-dotted line 62 follows the contours of the helical teeth on the rear leading end face 63 of the helical teeth.
  • the thick line 64 represents the contour of the helical toothing in the center of the wheel.
  • the helical toothing is drawn in the position in which an enclosed tooth gap reaches its smallest volume or in which the hatched area of the enclosed tooth gap 59 is smallest in the center of the wheel. At this very moment, the pressure changeover process must take place, ie the tooth gap is separated from the pressure chamber D and with Suction chamber S connected.
  • the recesses 55 to 58 of the helical toothing are matched to this pressure reversing process with no or almost no backlash.
  • the straight web edges 65 and 66 of the substantially rectangular recesses 56 and 58 of lines running parallel to M 1 M 2 on the rear leading end face 63 of the helical toothing become through the contact points 69 lying in this rear leading end face 63 on the engagement planes 68 and 67 or 70 formed.
  • the helical teeth are to the front trailing end face 61, the straight web edges 71 and 72 of substantially rectangular recesses 55 and 57 of paral- lel extending to M 1 M 2 lines by two in the front trailing end face 61 on the engagement planes 63 and 67 lying contact points 73 and 74 are formed.
  • the line of symmetry 90 to the web edges 65, 66 is in the direction of the suction space S by the distance and the line of symmetry 91 to the web edges 71, 72 is in the direction of the pressure space D by the same distance offset to the connecting line M 1 M 2 .
  • the depth 75 of the recesses 55 to 58 is a few millimeters.
  • the 3reide 76 of the recesses 55 to 58 is approximately equal to the tooth height.
  • the recesses 55, 58 and 55, 57 on the pressure chamber side and suction chamber side, respectively, located on the front face of the helical toothing, are separated from one another by a web with the width 77.
  • the land width 77 is compared with the land width 54 the manner shown in Fig. 8 ver G leichbaren Geradverzahnurg without or almost without any backlash with the same transverse section remained unchanged.
  • notches 78, 79, 80, 81, 82, 83, 84, 85 are made by the root circles 86, 87 and contours of the tooth flank of the adjacent gearwheel are formed at an angle of rotation ⁇ 1 at which the area of an enclosed M 1 or M 2 side tooth gap in the wheel center reaches its minimum.
  • These notches 78 to 85 increase the available squeezing area even more.
  • 11 and 12 show the construction of the notches 79, 81, 82 84 only for the angle of rotation ⁇ 1 , at which the area of the enclosed M 2 -side tooth space is at its minimum in the middle.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Gears, Cams (AREA)
EP79200119A 1978-03-10 1979-03-09 Machine à engrenages avec des moyens de décompression du liquide dans l'espace entredents Expired EP0004120B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2810563A DE2810563C2 (de) 1978-03-10 1978-03-10 Zahnradmaschine (Pumpe oder Motor)
DE2810563 1978-03-10

Publications (3)

Publication Number Publication Date
EP0004120A2 true EP0004120A2 (fr) 1979-09-19
EP0004120A3 EP0004120A3 (en) 1979-10-03
EP0004120B1 EP0004120B1 (fr) 1983-04-06

Family

ID=6034123

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79200119A Expired EP0004120B1 (fr) 1978-03-10 1979-03-09 Machine à engrenages avec des moyens de décompression du liquide dans l'espace entredents

Country Status (3)

Country Link
US (1) US4290739A (fr)
EP (1) EP0004120B1 (fr)
DE (1) DE2810563C2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2313627A (en) * 1996-05-29 1997-12-03 Roy William Masters Rotary engine
DE102020100241A1 (de) 2020-01-08 2021-07-08 Thyssenkrupp Ag Verfahren zur Herstellung von Phosphorsäure und Klinkerprozess-geeigneter Kalziumsulfatqualität zur kommerziellen und industriellen Verwertung von Kalziumsulfat

Families Citing this family (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59501514A (ja) * 1982-09-07 1984-08-23 フオ−ド　モ−タ−　カンパニ− はすば歯車ポンプ
US4824331A (en) * 1987-07-29 1989-04-25 Hydreco, Incorporated Variable discharge gear pump with energy recovery
DE4040409C1 (fr) * 1990-12-18 1992-05-14 Vse Schweisstechnik Gmbh, 5982 Neuenrade, De
US5131829A (en) * 1991-06-19 1992-07-21 Eaton Corporation Trapped volume vent means for meshing lobes of roots-type supercharger
US5733111A (en) * 1996-12-02 1998-03-31 Ford Global Technologies, Inc. Gerotor pump having inlet and outlet relief ports
US5865239A (en) * 1997-02-05 1999-02-02 Micropump, Inc. Method for making herringbone gears
US6544008B1 (en) * 1997-07-18 2003-04-08 John K. Apostolides Internal vent for reducing seal pressure in prelubrication pump assembly
US6708710B1 (en) * 1997-10-30 2004-03-23 Rpm Industries, Inc. Vehicle fluid change apparatus and method
US6988506B1 (en) 1997-10-30 2006-01-24 Rpm Industries, Inc. Fluid transfer system
US9062575B2 (en) * 1997-10-30 2015-06-23 RPM Industries, LLC Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
US7150286B2 (en) * 1997-10-30 2006-12-19 Rpm Industries, Inc. Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
US6042352A (en) * 1998-08-12 2000-03-28 Argo-Tech Corporation Bearing with pulsed bleed configuration
JP3830313B2 (ja) * 1999-09-06 2006-10-04 株式会社ジェイテクト ギヤポンプ
US6853954B2 (en) 2002-09-24 2005-02-08 John K. Apostolides Methods and systems for collecting and processing data in association with machine operation and maintenance
WO2006090495A1 (fr) * 2005-02-24 2006-08-31 Shimadzu Corporation Pompe a engrenage
US20070201989A1 (en) * 2005-10-14 2007-08-30 Parker-Hannifin Low ripple gear pump/motor
US20070178003A1 (en) * 2005-11-22 2007-08-02 Parker-Hannifin Corporation Gear pump with ripple chamber for low noise and pressure ripples
US20080063554A1 (en) * 2006-09-08 2008-03-13 Gifford Thomas K Precision flow gear pump
US20090089168A1 (en) * 2007-01-10 2009-04-02 Phyllis Adele Schneck ACE (Alternative Currency Exchange): Alternative Currency Tracking and Mapping System and Method
ITBO20070172A1 (it) * 2007-03-14 2008-09-15 Mario Antonio Morselli Apparecchiatura idraulica ad ingranaggi perfezionata
US7878781B2 (en) * 2007-12-11 2011-02-01 Hamilton Sundstrand Corporation Gear pump cavitation reduction
US8911222B2 (en) 2011-02-25 2014-12-16 Hamilton Sundstrand Corporation Input shaft assembly for gear pump
US8814547B2 (en) 2011-02-25 2014-08-26 Hamilton Sundstrand Corporation Seal retaining sleeve for gear pump
US8801410B2 (en) 2011-02-25 2014-08-12 Hamilton Sundstrand Corporation Coupling shaft for gear pump
US8992192B2 (en) 2011-02-25 2015-03-31 Hamilton Sundstrand Corporation Input shaft lubrication for gear pump
US9677559B2 (en) 2011-02-25 2017-06-13 Hamilton Sundstrand Corporation Bearing face geometry for gear pump
US9303644B2 (en) 2013-11-26 2016-04-05 Woodward, Inc. Gear pump bearing dam
DE102015201961A1 (de) 2015-02-04 2016-08-04 Volkswagen Aktiengesellschaft Verfahren zum Betrieb einer Verdrängerpumpe sowie eine hierfür bestimmte Verdrängerpumpe
US10563653B2 (en) 2016-01-12 2020-02-18 Hamilton Sundstrand Corporation Gear pump
US10443597B2 (en) 2016-01-12 2019-10-15 Hamilton Sundstrand Corporation Gears and gear pumps

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1634023A (en) * 1927-06-28 Ptjmp
US1129090A (en) * 1914-04-08 1915-02-23 American La France Fire Engine Company Inc Gear-pump.
US1233069A (en) * 1916-05-22 1917-07-10 Leonard Pump And Motor Co Pump and liquids.
US1706829A (en) * 1928-05-28 1929-03-26 Joseph Mercadante Pump
US2147405A (en) * 1935-01-05 1939-02-14 Trico Products Corp Motor vehicle power plant
US2136142A (en) * 1935-06-25 1938-11-08 American Viscose Corp Rayon-spinning pump
US2338065A (en) * 1940-06-13 1943-12-28 Joseph F Keller Gear pump
US2354992A (en) * 1941-11-11 1944-08-01 Westinghouse Electric & Mfg Co Gear pump
US2781730A (en) * 1952-10-22 1957-02-19 Thompson Prod Inc Implement pump
US2884864A (en) * 1955-04-14 1959-05-05 Borg Warner Pressure loaded pump, trapping grooves
CH399193A (de) * 1960-08-18 1966-03-31 Reiners & Wiggermann Verstell-Zahnradpumpe
FR1355756A (fr) * 1963-02-07 1964-03-20 Johannes Freres Pompe à engrenage perfectionnée destinée plus particulièrement aux engins de travaux publics
DE2249952C3 (de) * 1972-10-12 1975-03-27 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Hydraulische Zahnradmaschine
DE2623357A1 (de) * 1976-05-25 1977-12-15 Bosch Gmbh Robert Zahnradmaschine (pumpe oder motor)
DE2701303C3 (de) * 1977-01-14 1983-02-17 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Hydraulische Zahnradmaschine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2313627A (en) * 1996-05-29 1997-12-03 Roy William Masters Rotary engine
DE102020100241A1 (de) 2020-01-08 2021-07-08 Thyssenkrupp Ag Verfahren zur Herstellung von Phosphorsäure und Klinkerprozess-geeigneter Kalziumsulfatqualität zur kommerziellen und industriellen Verwertung von Kalziumsulfat
WO2021140074A1 (fr) 2020-01-08 2021-07-15 Thyssenkrupp Industrial Solutions Ag Procédé de production d'acide phosphorique et de sulfate de calcium de qualité appropriée pour un procédé de clinker en vue d'une utilisation commerciale et industrielle de sulfate de calcium

Also Published As

Publication number Publication date
DE2810563C2 (de) 1982-10-28
DE2810563A1 (de) 1979-09-13
US4290739A (en) 1981-09-22
EP0004120B1 (fr) 1983-04-06
EP0004120A3 (en) 1979-10-03

Similar Documents

Publication Publication Date Title
EP0004120B1 (fr) Machine à engrenages avec des moyens de décompression du liquide dans l'espace entredents
EP0994257B1 (fr) Pompe à engrenages externes avec limitation du débit
DE2554105C2 (de) Zahnradmaschine (Pumpe oder Motor)
DE19613833A1 (de) Innenzahnradmaschine, insbesondere Innenzahnradpumpe
DE2318753C2 (de) Zahnradmaschine
DE3249585C2 (de) Zahnradpumpe f}r inkompressible Medien
DE2510496C3 (de) Zahnradmaschine (Pumpe oder Motor)
DE2926566A1 (de) Stroemungsmesser mit positiver verdraengung
DE1806149A1 (de) Dichtung an Zahnradpumpen
DE69513142T2 (de) Innenzahnradpumpe mit radialen Zuführungsröhren
DE2848994A1 (de) Zahnradmaschine (pumpe oder hydromotor)
DE1403935A1 (de) Zahnradpumpe oder Zahnradmotor
DE2024339C2 (de) Zahnradverdrängermaschine für Flüssigkeiten, insbesondere Zahnradpumpe
EP0004119A2 (fr) Machine à engrenages avec des roues dentées décalées l'une par rapport à l'autre en direction circonférentielle
DE2249952A1 (de) Zahnradmaschine
DE2456387C2 (de) Dosiervorrichtung
WO2001002730A1 (fr) Machine a engrenage interne destinee au fonctionnement reversible dans un circuit hydraulique ferme
DE2517455A1 (de) Zahnradmaschine (pumpe oder motor)
DE2414760A1 (de) Zahnradpumpe
CH657434A5 (en) Rolling-contact mechanism and the use of the latter
EP2690252A1 (fr) Trochoid internal gear machine
EP0189560B1 (fr) Machine à engrenage (pompe ou moteur)
DE2701303C3 (de) Hydraulische Zahnradmaschine
DE2306065C3 (de) Zahnradpumpe oder -Motor mit im Außeneingriff stehenden Zahnrädern
DE2709913C2 (de) Zahnradpumpe

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

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): CH FR GB IT NL SE

AK Designated contracting states

Designated state(s): CH FR GB IT NL SE

17P Request for examination filed
RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: KORSE, THEODORUS HENRICUS

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

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): CH FR GB IT NL SE

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

Ref country code: NL

Effective date: 19830406

ET Fr: translation filed
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19840228

Year of fee payment: 6

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

Ref country code: FR

Payment date: 19840306

Year of fee payment: 6

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

Ref country code: SE

Payment date: 19840331

Year of fee payment: 6

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

Ref country code: SE

Effective date: 19870310

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

Ref country code: CH

Effective date: 19870331

GBPC Gb: european patent ceased through non-payment of renewal fee
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: 19871130

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: GB

Effective date: 19881117

EUG Se: european patent has lapsed

Ref document number: 79200119.0

Effective date: 19880215

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