EP0580196B1 - Pump comprising a partially hollow piston - Google Patents

Pump comprising a partially hollow piston Download PDF

Info

Publication number
EP0580196B1
EP0580196B1 EP93201766A EP93201766A EP0580196B1 EP 0580196 B1 EP0580196 B1 EP 0580196B1 EP 93201766 A EP93201766 A EP 93201766A EP 93201766 A EP93201766 A EP 93201766A EP 0580196 B1 EP0580196 B1 EP 0580196B1
Authority
EP
European Patent Office
Prior art keywords
fluid
piston
chamber
high pressure
valve
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.)
Expired - Lifetime
Application number
EP93201766A
Other languages
German (de)
French (fr)
Other versions
EP0580196A1 (en
Inventor
Paul Buisine
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.)
Sofitech NV
Original Assignee
Sofitech NV
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 Sofitech NV filed Critical Sofitech NV
Publication of EP0580196A1 publication Critical patent/EP0580196A1/en
Application granted granted Critical
Publication of EP0580196B1 publication Critical patent/EP0580196B1/en
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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves

Definitions

  • the present invention relates to the technical domain of pumps and, especially, of high pressure or very high pressure pumps.
  • Such pumps are met, among other activities, in petroleum and related industries and in industrial cleaning industry and in civil engineering. These pumps are characterized in that their powers are very high, usually about 373 000 to 746 000 or 895 200 Joules/s (say, 500 to 1000 or 1200 CV) and in that they must convey very corrosive fluids (such as highly acid fluids) or very abrasive fluids (such as cement slurries for oil well cementing) or also special fluids such as fracturation gels in the petroleum industry, charged with propping agent (sand), and other particular fluids.
  • very corrosive fluids such as highly acid fluids
  • very abrasive fluids such as cement slurries for oil well cementing
  • special fluids such as fracturation gels in the petroleum industry, charged with propping agent (sand), and other particular fluids.
  • a pump of this type schematically consists of a "power end" and a “fluid end".
  • the power end comprises all the elements which are necessary for the piston displacements, and the piston.
  • the fluid end is a very high pressure end which schematically consists of a body forming the piston chamber, with its inlet valve and outlet valve, and a fluid discharge element.
  • the chamber comprises one (or several) inlet valve and one (or several) outlet valve.
  • valves are placed at the end of the chamber opposite to the free end of the piston.
  • the present invention is a determining improvement of such a type of "in line" fluid end.
  • the Fig. 1 shows prior art "in line” fluid ends.
  • the Fig. 2 shows a preferred embodiment of the invention.
  • the "in line” pump according to the prior art (Fig. 1) comprises a high pressure body (9), a high pressure chamber (2) and a solid piston (8).
  • the body and the piston have a filler joint (7) which must be submitted to the high pressure of the chamber (2).
  • the fluid end comprises an inlet valve (1) in form of a ring assembled on the return spring (5), at the chamber end which is nearest the piston, and an outlet valve (3) also assembled on a return spring (4).
  • the outlet valve is placed at the other end of the chamber (2) and can tightly close this end.
  • the inlet pipes (6) When the piston displaces in the direction (A) of the inlet, the fluid is drawed by suction in a known manner by the inlet pipes (6). These pipes comprise a tore for symmetrically distributing the fluid.
  • the valve (1) is pushed back and does not oppose the fluid inlet.
  • the chamber (2) When the piston arrives on the thrust, the chamber (2) is then filled with the fluid, which is retained by the valve (3) pushed on its seat (10) by the spring (4).
  • the joint (7) may not resist, or in badly manner, to the high pressure, which is a serious problem.
  • the fluid circulation at the inlet in the pipes (6) is as a high abrasion and a risk of mechanical rupture especially at the zone (12) occur.
  • the piston is itself modified and co-operates with a "in line" fluid end (Fig. 2).
  • the equipment according to the invention comprises a high pressure fluid end body (21), a low pressure body (22) delimiting with the piston (16) a low pressure chamber (24), a fluid inlet pipe (26) and a discharge pipe (20).
  • the high pressure body (21) delimites with the piston (16) a high pressure chamber (13).
  • the piston (16) is partially hollow at its extension (17) placed in front of the discharge pipe (20) (free end of the piston).
  • the said extension (17) determines in the body of the piston a high pressure chamber (19) which, to the rear, opens with an opening (or several) in the low pressure chamber (24), and, to the head (i.e. to the discharge pipe) comprises an inlet valve (15).
  • the inlet valve (26) opens in the low pressure chamber (24) and the discharge pipe (20) has an outlet valve (14).
  • a high pressure joint (23) makes the area between the high pressure chamber (13) and the low pressure chamber (24) around the piston tight.
  • a low pressure joint (25) makes the low pressure chamber (24) tight.
  • a known phenomenon implies a depression in the high pressure chamber (13).
  • the valve (15) becomes opened, the valve (14) becomes closed, and the fluid circulates from the low pressure chamber (24) to the chamber (19) through the opening or port (18) and, finally, to the chamber (13).
  • valve (15) When the piston pushes back in the direction (D), the valve (15) becomes closed, the fluid is compressed in the chamber (13) by the piston formed by the extension (17) filled with the fluid and closed by the valve (15), the valve (14) becomes opened and the fluid is ejected through the discharge pipe (20).
  • the present invention provides several advantages, all are very important and even decisive.
  • the dead volume may be lowered up to a very low volume, substantially equal to zero. This obviously has a positive effect on the volumetric efficiency of the high pressure pump.
  • the pipe (26)/chamber (24)/chamber (19)/chamber (13)/discharge (20) fluid circulation is substantially ideal from the point of view of the fluid hydrodynamic. Especially, the fluid has not to radically change its flow direction. This will obviously decrease the cavitation which especially occurs with viscosified fluids, and with high flow rates, as well as the abrasion process.
  • one or several pipes (26) may exist, including pipes with an annulus injection or a multi-point injection, as well as one or several openings (18) having an appropriate form.
  • the applications relate to especially all the high pressure pumps in all industries.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Compressor (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Reciprocating Pumps (AREA)

Description

  • The present invention relates to the technical domain of pumps and, especially, of high pressure or very high pressure pumps.
  • Such pumps are met, among other activities, in petroleum and related industries and in industrial cleaning industry and in civil engineering. These pumps are characterized in that their powers are very high, usually about 373 000 to 746 000 or 895 200 Joules/s (say, 500 to 1000 or 1200 CV) and in that they must convey very corrosive fluids (such as highly acid fluids) or very abrasive fluids (such as cement slurries for oil well cementing) or also special fluids such as fracturation gels in the petroleum industry, charged with propping agent (sand), and other particular fluids.
  • Moreover, petroleum industry requires very strict dimension and weight specifications, which obviously are contradictory to mechanical strength, power, and to wearing and abrasion resistance which are also required for such pumps.
  • It has been known up to now numerous pumps which must be improved.
  • A pump of this type schematically consists of a "power end" and a "fluid end". The power end comprises all the elements which are necessary for the piston displacements, and the piston.
  • The fluid end is a very high pressure end which schematically consists of a body forming the piston chamber, with its inlet valve and outlet valve, and a fluid discharge element.
  • In conventional pumps, the chamber comprises one (or several) inlet valve and one (or several) outlet valve.
  • Generally, these valves are placed at the end of the chamber opposite to the free end of the piston.
  • The structure and the operation of such pumps have been very well known in the art.
  • It has been also known an agencement called "in line". The present invention is a determining improvement of such a type of "in line" fluid end.
  • The Fig. 1 shows prior art "in line" fluid ends.
  • The Fig. 2 shows a preferred embodiment of the invention.
  • The "in line" pump according to the prior art (Fig. 1) comprises a high pressure body (9), a high pressure chamber (2) and a solid piston (8). The body and the piston have a filler joint (7) which must be submitted to the high pressure of the chamber (2).
  • In order to simplify, the power end of the pump is not shown.
  • The fluid end comprises an inlet valve (1) in form of a ring assembled on the return spring (5), at the chamber end which is nearest the piston, and an outlet valve (3) also assembled on a return spring (4). The outlet valve is placed at the other end of the chamber (2) and can tightly close this end.
  • When the piston displaces in the direction (A) of the inlet, the fluid is drawed by suction in a known manner by the inlet pipes (6). These pipes comprise a tore for symmetrically distributing the fluid. The valve (1) is pushed back and does not oppose the fluid inlet. When the piston arrives on the thrust, the chamber (2) is then filled with the fluid, which is retained by the valve (3) pushed on its seat (10) by the spring (4).
  • When the piston pushes back in the direction (D), the valve (1) becomes closed, the fluid is compressed into the chamber (2), the valve (3) becomes opered end the fluid is ejected through the discharge pipe (11).
  • This type of "in line" fluid end has two disadvantages.
  • On one hand, the joint (7) may not resist, or in badly manner, to the high pressure, which is a serious problem.
  • On the other hand, the fluid circulation at the inlet in the pipes (6) is as a high abrasion and a risk of mechanical rupture especially at the zone (12) occur.
  • Finally, the fluid is admitted in the direction (A) and is ejected in the opposite direction (D) which is prejudicial to the pump performances. According to the present invention, the piston is itself modified and co-operates with a "in line" fluid end (Fig. 2).
  • The equipment according to the invention comprises a high pressure fluid end body (21), a low pressure body (22) delimiting with the piston (16) a low pressure chamber (24), a fluid inlet pipe (26) and a discharge pipe (20).
  • The high pressure body (21) delimites with the piston (16) a high pressure chamber (13).
  • The piston (16) is partially hollow at its extension (17) placed in front of the discharge pipe (20) (free end of the piston).
  • The said extension (17) determines in the body of the piston a high pressure chamber (19) which, to the rear, opens with an opening (or several) in the low pressure chamber (24), and, to the head (i.e. to the discharge pipe) comprises an inlet valve (15).
  • Finally, the inlet valve (26) opens in the low pressure chamber (24) and the discharge pipe (20) has an outlet valve (14).
  • A high pressure joint (23) makes the area between the high pressure chamber (13) and the low pressure chamber (24) around the piston tight.
  • A low pressure joint (25) makes the low pressure chamber (24) tight.
  • The return springs of the valves (15) and (14) are not shown in order to simplify ; furthermore, their agencement is conventional and obvious when reading the below operating mode.
  • When the piston displaces in the inlet direction (A), a known phenomenon implies a depression in the high pressure chamber (13). The valve (15) becomes opened, the valve (14) becomes closed, and the fluid circulates from the low pressure chamber (24) to the chamber (19) through the opening or port (18) and, finally, to the chamber (13).
  • When operating, all of the chambers are obviously permanently filled with fluid.
  • When the piston pushes back in the direction (D), the valve (15) becomes closed, the fluid is compressed in the chamber (13) by the piston formed by the extension (17) filled with the fluid and closed by the valve (15), the valve (14) becomes opened and the fluid is ejected through the discharge pipe (20).
  • The present invention provides several advantages, all are very important and even decisive.
  • It must be appreciated that the dead volume may be lowered up to a very low volume, substantially equal to zero. This obviously has a positive effect on the volumetric efficiency of the high pressure pump.
  • In the case - which often occurs with the present techniques as it has been above described - the high pressure joint (23) would not correctly make the tightness, this would have only weak consequences because the fluid loss would be easily recuperated in the chamber (24) without any pollution (this factor becomes decisive substantially on all the oil field). As far as the low pressure joint is concerned, the present techniques easily assume a leak absence and then remove any pollution risk, and moreover, the maintenance of such an atmospheric/low pressure joint is easy.
  • The pipe (26)/chamber (24)/chamber (19)/chamber (13)/discharge (20) fluid circulation is substantially ideal from the point of view of the fluid hydrodynamic. Especially, the fluid has not to radically change its flow direction. This will obviously decrease the cavitation which especially occurs with viscosified fluids, and with high flow rates, as well as the abrasion process.
  • The inertial forces produced by the piston will co-operate with the aperture and the closure of the inlet valve exactly at the time which is the more efficiency. This advantage tends to maintain the volumetric efficiency at a high value and also prevents the cavitation.
  • Finally, the high pressure element symmetry with regard to the axle implies to lower the stress concentration process and then allows a substantial matter decrease and then a weight decrease which is another important parameter in the considered industries.
  • Obviously, one or several pipes (26) may exist, including pipes with an annulus injection or a multi-point injection, as well as one or several openings (18) having an appropriate form.
  • The number of pistons is unimportant though tri - piston pumps have been specially used up to now.
  • The applications relate to especially all the high pressure pumps in all industries.

Claims (3)

  1. In line pump comprising at least one piston (16) having one end displaced by a power-end outside the pumping fluid and a free end displaced within a fluid-end which comprises a fluid inlet (26), a piston chamber with inlet valve and outlet valve and a fluid discharge element, a filler joint (25) being provided between the piston and the fluid end, characterized in that each piston (16) comprises a hollow chamber (19) in communication, through at least one opening (18), with a low pressure chamber (24), and through an inlet valve (15), with a high pressure chamber (13) closed by an outlet valve (14) opening into a discharge element (20), whereby a high pressure joint (23) is provided between the high pressure chamber (13) and the low pressure chamber (24), the filler joint (25) being therefore a low pressure joint.
  2. Application of the pump according to claim 1 to high pressure pumps used in the petroleum and related industries, in industrial cleaning or in civil engineering.
  3. Application according to claim 2 to the pumping of abrasive fluids such as cement slurry.
EP93201766A 1992-07-20 1993-06-18 Pump comprising a partially hollow piston Expired - Lifetime EP0580196B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9209022A FR2693771B1 (en) 1992-07-20 1992-07-20 Pump comprising a partially hollow piston, and its applications in particular in the petroleum industry.
FR9209022 1992-07-20

Publications (2)

Publication Number Publication Date
EP0580196A1 EP0580196A1 (en) 1994-01-26
EP0580196B1 true EP0580196B1 (en) 1996-08-14

Family

ID=9432125

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93201766A Expired - Lifetime EP0580196B1 (en) 1992-07-20 1993-06-18 Pump comprising a partially hollow piston

Country Status (6)

Country Link
EP (1) EP0580196B1 (en)
JP (1) JPH06167277A (en)
CA (1) CA2100837A1 (en)
DE (1) DE69304002T2 (en)
FR (1) FR2693771B1 (en)
NO (1) NO306223B1 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD691180S1 (en) 2012-04-27 2013-10-08 S.P.M. Flow Control, Inc. Center portion of a fluid cylinder for a pump
US8662865B2 (en) 2010-12-09 2014-03-04 S.P.M. Flow Control, Inc. Offset valve bore in a reciprocating pump
USD705817S1 (en) 2012-06-21 2014-05-27 S.P.M. Flow Control, Inc. Center portion of a fluid cylinder for a pump
USD706832S1 (en) 2012-06-15 2014-06-10 S.P.M. Flow Control, Inc. Fluid cylinder for a pump
WO2018183154A1 (en) * 2017-03-27 2018-10-04 Karcher North America, Inc. Hollow piston pump

Families Citing this family (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002018801A1 (en) * 2000-08-25 2002-03-07 Rosenthal Stephen A Method and apparatus for joining seams
US6568925B2 (en) 2001-03-28 2003-05-27 Eric Gunderson Abrasive liquid pump apparatus and method
KR100442379B1 (en) * 2001-10-15 2004-07-30 엘지전자 주식회사 Apparatus for sucking gas in linear compressor
JP2006329007A (en) * 2005-05-24 2006-12-07 Meika Ryu Current control reciprocating fluid pressure feeding unit
JP5107651B2 (en) * 2007-10-02 2012-12-26 タクボエンジニアリング株式会社 Syringe for paint supply
US8590614B2 (en) 2011-05-03 2013-11-26 Halliburton Energy Services, Inc. High pressure stimulation pump
USD687125S1 (en) 2011-08-19 2013-07-30 S.P.M. Flow Control, Inc. Fluid end
CN103161725A (en) * 2011-12-16 2013-06-19 东台兴业股份有限公司 Piston-type pressure pump
WO2013116535A1 (en) 2012-02-01 2013-08-08 S.P.M. Flow Control, Inc. Pump fluid end with integrated web portion
CN102777373A (en) * 2012-07-10 2012-11-14 镇江长城注浆设备有限公司 Double-liquid synchronous grouting pump
CN104696185A (en) * 2015-03-20 2015-06-10 丹阳琦瑞机械有限公司 Vertical electrolyte filling pump
US11578710B2 (en) 2019-05-02 2023-02-14 Kerr Machine Co. Fracturing pump with in-line fluid end
US11560888B2 (en) 2019-05-14 2023-01-24 Halliburton Energy Services, Inc. Easy change pump plunger
US11739748B2 (en) 2019-05-14 2023-08-29 Halliburton Energy Services, Inc. Pump fluid end with easy access suction valve
US11231111B2 (en) 2019-05-14 2022-01-25 Halliburton Energy Services, Inc. Pump valve seat with supplemental retention
US10808846B1 (en) 2019-05-14 2020-10-20 Halliburton Energy Services, Inc. Pump plunger with wrench features
US11105327B2 (en) 2019-05-14 2021-08-31 Halliburton Energy Services, Inc. Valve assembly for a fluid end with limited access
US11441687B2 (en) 2019-05-14 2022-09-13 Halliburton Energy Services, Inc. Pump fluid end with positional indifference for maintenance
US11965503B2 (en) 2019-05-14 2024-04-23 Halliburton Energy Services, Inc. Flexible manifold for reciprocating pump
US11261863B2 (en) 2019-05-14 2022-03-01 Halliburton Energy Services, Inc. Flexible manifold for reciprocating pump
US11280326B2 (en) 2019-06-10 2022-03-22 Halliburton Energy Services, Inc. Pump fluid end with suction valve closure assist
US10808851B1 (en) 2019-06-10 2020-10-20 Halliburton Energy Services, Inc. Multi-material frac valve poppet
US10941766B2 (en) 2019-06-10 2021-03-09 Halliburton Energy Sendees, Inc. Multi-layer coating for plunger and/or packing sleeve
US10989188B2 (en) 2019-07-26 2021-04-27 Halliburton Energy Services, Inc. Oil field pumps with reduced maintenance
US10677380B1 (en) 2019-07-26 2020-06-09 Halliburton Energy Services, Inc. Fail safe suction hose for significantly moving suction port
US11530750B2 (en) 2019-12-24 2022-12-20 Halliburton Energy Services, Inc. Horizontal balanced guided valve
US11073144B1 (en) 2020-02-14 2021-07-27 Halliburton Energy Services, Inc. Pump valve assembly
US11002120B1 (en) 2020-02-28 2021-05-11 Halliburton Energy Services, Inc. Dynamic packing seal compression system for pumps
US10947967B1 (en) 2020-03-11 2021-03-16 Halliburton Energy Services, Inc. Discharge valve disabler and pressure pulse generator therefrom

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR599965A (en) * 1925-06-20 1926-01-27 C I Ingg Audoli Bertola Ab Low flow pump for domestic installations
CH257522A (en) * 1943-12-27 1948-10-15 Anonyme Messier Societe Hydraulic pump.
GB672173A (en) * 1949-08-06 1952-05-14 Siam Improvements in or relating to reciprocating pumps

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8662865B2 (en) 2010-12-09 2014-03-04 S.P.M. Flow Control, Inc. Offset valve bore in a reciprocating pump
US8662864B2 (en) 2010-12-09 2014-03-04 S.P.M. Flow Control, Inc. Offset valve bore in a reciprocating pump
US8668470B2 (en) 2010-12-09 2014-03-11 S.P.M. Flow Control, Inc. Offset valve bore for a reciprocating pump
USD691180S1 (en) 2012-04-27 2013-10-08 S.P.M. Flow Control, Inc. Center portion of a fluid cylinder for a pump
USD706832S1 (en) 2012-06-15 2014-06-10 S.P.M. Flow Control, Inc. Fluid cylinder for a pump
USD705817S1 (en) 2012-06-21 2014-05-27 S.P.M. Flow Control, Inc. Center portion of a fluid cylinder for a pump
WO2018183154A1 (en) * 2017-03-27 2018-10-04 Karcher North America, Inc. Hollow piston pump

Also Published As

Publication number Publication date
FR2693771A1 (en) 1994-01-21
CA2100837A1 (en) 1994-01-21
DE69304002D1 (en) 1996-09-19
JPH06167277A (en) 1994-06-14
FR2693771B1 (en) 1994-09-23
NO932609D0 (en) 1993-07-19
DE69304002T2 (en) 1997-03-13
NO932609L (en) 1994-01-21
EP0580196A1 (en) 1994-01-26
NO306223B1 (en) 1999-10-04

Similar Documents

Publication Publication Date Title
EP0580196B1 (en) Pump comprising a partially hollow piston
US11614079B2 (en) Suction bore cover and seal arrangement
US20200400000A1 (en) Frac system with hydraulic energy transfer system
EP0512594B1 (en) Suction valve for high pressure slurry pump
US9945210B2 (en) Pressure exchanger system with integral pressure balancing system
US10995738B2 (en) Fluid end and center feed suction manifold
US9284953B2 (en) Multiple port discharge manifold fluid end
US3801234A (en) Fluid end for a plunger pump
US20140271266A1 (en) Fluid end with protected flow passages and kit for same
US20200355182A1 (en) Fluid end crossbore
US5382057A (en) Manifold for a front-discharge fluid end reciprocating pump
US11421792B2 (en) Valve configuration
US2811925A (en) Device for transmitting pressure and pumping fluids
US5064354A (en) High pressure fluid pump
US11384856B2 (en) Spherical pump valve
US20220397107A1 (en) Fluid end assembly
US4102611A (en) Plunger pump
US2038155A (en) Pump
CN208900338U (en) A kind of piston type reciprocating booster pump
US2943577A (en) Pump
CN216198924U (en) Fracturing unit truck hydraulic end assembly with long integral service life
CN214838487U (en) Universal valve body
US20230127613A1 (en) Compresser for pumping fluid having check valves aligned with fluid ports
US20230313890A1 (en) Fluid end valve
CA2202521C (en) Valve arrangement in a hydraulic percussive rock drill

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 DK GB IT NL

17P Request for examination filed

Effective date: 19940722

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

Owner name: SOFITECH N.V.

17Q First examination report despatched

Effective date: 19950516

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE DK GB IT NL

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

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19960814

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRE;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.SCRIBED TIME-LIMIT

Effective date: 19960814

Ref country code: DK

Effective date: 19960814

REF Corresponds to:

Ref document number: 69304002

Country of ref document: DE

Date of ref document: 19960919

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
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: GB

Payment date: 20020612

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: 20020626

Year of fee payment: 10

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: 20030618

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: 20040101

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

Effective date: 20030618