EP0819832B1 - Tiefbohrvorrichtung, Tiefbohrpumpenvorrichtung und Verwendung eines hydrodynamischen Retarders zur Kompensation der vom Antriebssystem ausgelösten Rückstellmomente - Google Patents
Tiefbohrvorrichtung, Tiefbohrpumpenvorrichtung und Verwendung eines hydrodynamischen Retarders zur Kompensation der vom Antriebssystem ausgelösten Rückstellmomente Download PDFInfo
- Publication number
- EP0819832B1 EP0819832B1 EP97111621A EP97111621A EP0819832B1 EP 0819832 B1 EP0819832 B1 EP 0819832B1 EP 97111621 A EP97111621 A EP 97111621A EP 97111621 A EP97111621 A EP 97111621A EP 0819832 B1 EP0819832 B1 EP 0819832B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- deep
- blade wheel
- well pump
- rotor
- deep drilling
- 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
Links
- 238000005553 drilling Methods 0.000 title claims description 51
- 238000005086 pumping Methods 0.000 title description 2
- 238000001816 cooling Methods 0.000 claims description 6
- 238000000926 separation method Methods 0.000 claims 1
- 230000008719 thickening Effects 0.000 claims 1
- 230000001960 triggered effect Effects 0.000 claims 1
- 230000000694 effects Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 239000007788 liquid Substances 0.000 description 2
- 241000656145 Thyrsites atun Species 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000012432 intermediate storage Methods 0.000 description 1
- 230000002427 irreversible effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 238000009987 spinning Methods 0.000 description 1
Images
Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
- E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
- E21B43/121—Lifting well fluids
- E21B43/126—Adaptations of down-hole pump systems powered by drives outside the borehole, e.g. by a rotary or oscillating drive
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B3/00—Rotary drilling
- E21B3/02—Surface drives for rotary drilling
Definitions
- the invention relates to a deep drilling device, in particular with the Features from the preamble of claim 1; a Deep drilling pump device, in detail with the features from the Preamble of claim 7; also a general purpose a hydrodynamic retarder to compensate for the downforce in the Restoring torques introduced into the drive train.
- Deep drilling devices and deep drilling pump devices are in a variety known from executions. They have in common that by means of a Drive machine with a extending over a longer distance Drilling spindle or the pump rotor coupled linkage is driven.
- the first-mentioned device serves to provide the borehole, in which the rotor and stator are then one Deep drilling pump device for the purpose of pumping oil, for example can be introduced. In such systems, it occurs due to the Length of the rotating components, i.e. the drill pipe or the rotor, both Rotation for the occurrence of torsional forces which occur in these components are stored as restoring forces along their length.
- the twist in Circumferential direction or the torsional stress of the driven rotating components leads when the power flow is interrupted by the Drive machine for output, for example when the Drive machine or in the event of an accident to trigger a restoring torque due to the rotatingly drivable components that are in the drive, in particular the drive machine and the components downstream of it, for example, effective in the transmission downstream of the drive machine becomes.
- This can result in significant irreversible damage as well Lead size of the restoring torque.
- a electric drive motor can be driven backwards and thus be harmed.
- the drive systems are usually not designed for such high shock loads.
- the invention is therefore based on the object of a deep drilling device and to further develop a deep drilling pump device such that the Damage due to the rotating output parts Interruption of the power flow occurring restoring moments with little constructive effort and inexpensive to be avoided.
- the solution of the task according to the invention is for the deep drilling device by the features of claim 1 and for the Deep drilling pump device by the features of claim 8 characterized.
- Advantageous configurations are in the subclaims played.
- the object is achieved in that in a Deep drilling device and in the deep drilling pump device between the Drive machine and the linkage or the rotatingly driven Output parts, which can extend over a longer distance hydrodynamic retarder is arranged.
- the hydrodynamic retarder includes a rotor impeller and a stator impeller, which are together form a toroidal work space, the blading, as such known, is executed obliquely.
- the blade direction related to the Installation position is chosen such that the rotor blade wheel in Normal operation of the deep drilling and deep drilling pump device, i.e. in the Drilling or production operation, "fleeing" works, i.e. that the rotor paddle wheel works with rotation with freewheel effect.
- Such a device is essentially characterized in that due to the inclined blades, the rotor blade wheel despite Filling the retarder in constant drive connection with the Drive machine and stand on a separate freewheel device Decoupling of the rotor blade wheel from the drive can be dispensed with, while only a small portion of the prime mover itself Drive power for the operation of the rotor blade wheel are applied got to.
- the hydrodynamic retarder can therefore be used throughout Remain filled, i.e. an external inlet and outlet for filling for the case of an interruption of the power flow can be omitted.
- the device is characterized by a low design effort and is therefore very inexpensive.
- the retarder is preferably self-controlling.
- a closed circuit for the operating fluid is assigned to the toroidal working space between the rotor and stator impeller. This serves to lead possibly heated equipment out of the toroidal work space and to feed it back in after cooling, or possibly to lead it via a heat exchanger (not shown here in detail) and to feed it back to the hydrodynamic retarder.
- the exit from the toroidal work space is made possible by slots in the blade base of the stator blade wheel.
- the equipment is supplied via appropriate devices in the stator impeller. These devices can be designed, for example, as so-called filling slots, which form a filling channel.
- the blading of the stator impeller is preferably carried out in such a way that the blades carrying the filling slots do not run parallel with respect to their front and back.
- the blades are made tapering from the blade base to the blade end - here from the blade base to the blade end.
- the blade carrying the filling slot has a thickness that makes it possible to integrate the entire filling slot in the blade from the cross section. From the bottom of the blade to the end of the blade, the blade thickness becomes increasingly smaller.
- Such a design of the filling channels makes it possible to generate an undisturbed meridian flow between the rotor and stator vane wheel in the so-called spitting operation, ie when the restoring force applied by the drilling spindle or by the pump rotor is cushioned.
- filling channels are also conceivable, for example in In the form of filling cams or in a scoop thickened over the entire width incorporated slits.
- An equipment container is integrated in the closed circuit. This is located above the retarder in the installed position. This makes possible es, possible leakage losses quickly through supply to the work area compensate.
- a hydrodynamic retarder 2 is provided, i.e. between Drive machine and linkage and / or drilling spindle and pump rotor.
- the hydrodynamic retarder 2 comprises a rotor blade wheel 3 and a Stator impeller 4, which together form a toroidal working space 5 form.
- the hydrodynamic retarder, in particular the stator impeller 4, is stored in a housing 6.
- the rotor paddle wheel 3 is constantly at least indirectly in drive connection with the drive machine. It can not rotatably at least indirectly with one here in detail shown drive shaft or the output components can be coupled. In the version shown it is a with the drilling spindle the deep drilling device or the pump rotor Deep drilling pump device rotatably coupled component 7.
- the rotor blade wheel 3 and the stator blade wheel 4 have an oblique angle Blading 8 or 9, i.e. the blades are opposite the Parting plane E between the rotor 3 - and the stator vane 4 inclined arranged.
- the blade direction i.e. the inclination of the individual blades opposite the respective blade base - for the stator blade wheel with 10, designated for the rotor blade wheel with 11 - towards the respective blade end - for the rotor blade wheel with 12 and the stator blade wheel with 13 designated, in the direction of the parting plane E is chosen such that in Normal operation, i.e.
- Rotor blade wheel 3 when driving the drilling spindle or with it rotatably connected component 7 or the pump rotor or with this rotatably coupled component 7 via the engine Rotor blade wheel 3 is carried continuously, but due to the oblique Blading is not a closed cycle of equipment between the rotor and stator impeller can arise. How the Rotor blade wheel 3 in this operating state can be "fleeing" against the stator impeller. The resource remains essentially between the two adjacent to each other Blading the blades 9 of the rotor blade wheel 3. It does not find any Circulation in the direction of the stator vane 4 instead that a Braking reaction torque is generated.
- the hydrodynamic retarder 2 thus works in normal operation of the drive system with the Effect of a freewheel. When designing the drive system is only which for rotation of the rotor blade wheel 3 and thus for the circulation of the Resource by the rotor blade wheel 3 low power required to consider.
- the rotor blade wheel 3 of the hydrodynamic retarder 2 is at Reset of the drilling spindle or the pump rotor due to the at least indirectly non-rotatable connection with this or this or one with this or this connected component 7 against the Direction of rotation in normal operation - normal operation is designated II here the opposite direction of rotation with I - moves. Because of the sloping Blading the hydrodynamic retarder works like when resetting a hydrodynamic brake, i.e. in the so-called "pike" operation.
- the toroidal working space 5 between the rotor and stator impeller a closed circuit for the operating fluid assigned, which here with 14 is designated.
- the closed circuit 14 serves to heat Lead resources out of the toroidal work space 5 and feed it again after cooling down or possibly via a here to perform the heat exchanger, not shown in detail, and the feed hydrodynamic retarders again.
- the exit from the Toroidal working space is via slots 15 in the blade base 10 of the Stator impeller 4 allows.
- the equipment is supplied after cooling has taken place via appropriate devices in the stator impeller 4. These devices can be used, for example, as so-called filling slots 16 be executed, which form the filling channel.
- the Blading of the stator blade wheel as shown in Figure 2, such that the filling slots carrying blades with respect to their front 20th - And rear 21 not parallel.
- the The scoop base has a thickness for the scoop carrying the filling slot on, which makes it possible to cross-section the entire filling slot in the Integrate shovel. From the blade base 10 to the blade end 13, here the front edge of the blade, the blade thickness becomes increasingly smaller.
- a device for cooling for example in the form of a heat exchanger.
- the closed circuit 14 can also be designed such that due to its length or the possibility of intermediate storage of the Equipment is already cooled. On an external cooling circuit can therefore be dispensed with.
- hydrodynamic Retarders For the design and integration of the hydrodynamic Retarders have a variety of options. Is essential to the invention however, an arrangement of a hydrodynamic retarder in one Deep drilling device between the drive machine and the drilling spindle, and in one Deep drilling pump device between the engine and the Pump rotor.
Landscapes
- Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Physics & Mathematics (AREA)
- Environmental & Geological Engineering (AREA)
- Fluid Mechanics (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
- Transmission Of Braking Force In Braking Systems (AREA)
Description
Dem torusförmigen Arbeitsraum zwischen Rotor- und Statorschaufelrad ist ein geschlossener Kreislauf für das Betriebsfluid zugeordnet. Dieser dient dazu, evt. erwärmtes Betriebsmittel aus dem torusförmigen Arbeitsraum herauszuführen und diesem nach Abkühlung direkt wieder zuzuführen oder eventuell über einen hier, im einzelnen nicht dargestellten Wärmetauscher zu führen und dem hydrodynamischen Retarder wieder zuzuführen. Der Austritt aus dem torusförmigen Arbeitsraum wird über Schlitze im Schaufelgrund des Statorschaufelrades ermöglicht. Die Zufuhr des Betriebsmittels erfolgt über entsprechende Einrichtungen im Statorschaufelrad. Diese Einrichtungen können beispielsweise als sogenannte Füllschlitze ausgeführt sein, die einen Füllkanal bilden. Zu diesem Zweck ist die Beschaufelung des Statorschaufelrades vorzugsweise derart ausgeführt, daß die Füllschlitze tragenden Schaufeln bezüglich ihrer Vorder - und Rückseite nicht parallel verlaufen. Im besonderen werden die Schaufeln vom Schaufelgrund ausgehend zum Schaufelende - hier also vom Schaufelgrund zum Schaufelende - hin, verjüngend ausgeführt. Im Schaufelgrund weist dabei die den Füllschlitz tragende Schaufel eine Stärke auf, die es ermöglicht, den gesamten Füllschlitz vom Querschnitt her in der Schaufel zu integrieren. Vom Schaufelgrund zum Schaufelende hin, verkleinert sich die Schaufeldicke zunehmend. Lediglich im Bereich des sich im wesentlichen vom Schaufelgrund zur Schaufelvorderkante hin erstreckenden Füllkanales erfolgt entsprechend der Kontur bzw. der Größe des Füllschlitzes bzw. des Füllkanales eine örtliche Ausbuchtung bzw. Auswölbung an der Schaufel. Diese bleibt jedoch im wesentlichen im Bereich des Schaufelendes bzw. der Schaufelvorderkante angeordnet. Die Anzahl und die Größe der Füllschlitze sowie deren Ausführung richtet sich im wesentlichen nach der gewünschten Zeit zum Füllen des Retarderkreislaufes und dem geforderten Flüssigkeitsdurchsatz zur Abfuhr der entwickelten Wärme. Eine derartige Ausführung der Füllkanäle ermöglicht es, im sogenannten spießenden Betrieb, d.h. beim Abfedern der von der Bohrspindel oder vom Pumpenrotor aufgebrachten Rückstellkraft, eine ungestörte Meridianströmung zwischen Rotor- und Statorschaufelrad zu erzeugen.
- Fig. 1
- einen Ausschnitt aus einem Antriebssystem, einsetzbar sowohl für eine Tiefbohrvorrichtung als auch eine Tiefbohrpumpenvorrichtung in Einbaulage;
- Fig. 2
- eine Ansicht A-A gemäß Fig. 1 auf ein Statorschaufelrad.
Claims (8)
- Tiefbohr- oder Tiefbohrpumpenvorrichtung, umfassend1.1 eine Antriebsmaschine;1.2 ein von der Antriebsmaschine wenigstens mittelbar antreibbares Bauteil (7);1.3 das antreibbare Bauteil (7) ist entweder eine Bohrspindel oder ein Gestänge mit einem wenigstens mittelbar angekoppelten und antreibbaren Pumpenrotor;1.4 eine zwischen Antriebsmaschine und dem antreibbaren Bauteil (7) angeordnete Einrichtung zur Kompensation der bei Änderung des Betriebszustandes möglichen auftretenden Rückstellmomente am antreibbaren Bauteil (7);
gekennzeichnet durch die folgenden Merkmale:1.5 die Einrichtung ist als hydrodynamischer Retarder (2), umfassend ein Rotor (3)- und ein Statorschaufelrad (4), ausgeführt;1.6 Rotorschaufelrad (3) und Statorschaufelrad (4) bilden miteinander einen torusförmigen Arbeitsraum (5), welcher bei Betrieb der Tiefbohr- oder Tiefbohrpumpenvorrichtung stets befüllt ist;1.7 das Rotorschaufelrad (3) steht wenigstens mittelbar mit der Antriebsmaschine in ständiger Triebverbindung;1.8 die Beschaufelung (8, 9) von Rotor (3) - und Statorschaufelrad (4) ist derart geneigt gegenüber einer Trennebene zwischen dem Rotor (3)- und dem Statorschaufelrad (4) ausgeführt, daß aufgrund der Schaufelrichtung (10, 11)1.8.1 in der Betriebsweise des Antriebes des antreibbaren Bauteiles (7) das Rotorschaufelrad (3) im wesentlichen im Freilauf rotiert, und1.8.2 im Fall der Unterbrechung des Kraftflusses beim Auftreten von Rückstellmomenten am antreibbaren Bauteil (7) zwischen Rotorschaufelrad (3) und Statorschaufelrad (4) ein Bremsmoment erzeugt wird. - Tiefbohr- oder Tiefbohrpumpenvorrichtung nach Anspruch 1, gekennzeichnet durch die folgenden Merkmale:2.1 das Statorschaufelrad (4) weist im Schaufelgrund (10) schlitzförmige Öffnungen (15) auf;2.2 der Beschaufelung (8) des Statorschaufelrades (4) sind Einrichtungen zur Befüllung des hydrodynamischen Retarders (2) zugeordnet;2.3 die schlitzförmigen Öffnungen (15) und die Einrichtungen zur Befüllung sind miteinander über einen Kreislauf gekoppelt.
- Tiefbohr- oder Tiefbohrpumpenvorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Kreislauf als geschlossener Kreislauf ausgeführt ist.
- Tiefbohr- oder Tiefbohrpumpenvorrichtung nach einem der Ansprüche 2 oder 3, dadurch gekennzeichnet, daß der Retarder frei von einem externen Kühlkreislauf ist.
- Tiefbohr- oder Tiefbohrpumpenvorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß im geschlossenen Kreislauf ein Wärmetauscher vorgesehen ist.
- Tiefbohr- oder Tiefbohrpumpenvorrichtung nach einem der Ansprüche 2 bis 5, gekennzeichnet durch die folgenden Merkmale:6.1 in der Beschaufelung (8) des Statorschaufelrades (4) sind Füllkanäle (16) integriert;6.2 die Füllkanäle (16) tragenden Schaufeln sind vom Schaufelgrund (10) bis hin zur Schaufelvorderkante (13) verjüngend ausgeführt;6.3 im Bereich der Schaufelvorderkante (13) ist in der Rückseite der Schaufel eine örtliche Verdickung für den Füllkanal (16) vorgesehen.
- Tiefbohr- oder Tiefbohrpumpenvorrichtung nach einem der Ansprüche 2 bis 6, dadurch gekennzeichnet, daß bezogen auf die Einbaulage des hydrodynamischen Retarders (2) im Kreislauf ein Hochbehälter vorgesehen ist, welcher einen bestimmten Betriebsmittelspiegel aufweist.
- Verwendung eines hydrodynamischen Retarders (2) in einer Tiefbohr- oder Tiefbohrpumpenvorrichtung zwischen einer Antriebsmaschine und einem rotierend antreibbaren Abtrieb zur Kompensation vom Abtrieb im Fall der Unterbrechung des Kraftflusses im Antriebssystem (1) ausgelöster Rückstellmomente.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19628950A DE19628950C2 (de) | 1996-07-18 | 1996-07-18 | Tiefbohrvorrichtung, Tiefbohrpumpenvorrichtung und Verwendung eines hydrodynamischen Retarders zur Kompensation von im Antriebssystem vom Abtrieb ausgelöster Rückstellmomente |
DE19628950 | 1996-07-18 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0819832A2 EP0819832A2 (de) | 1998-01-21 |
EP0819832A3 EP0819832A3 (de) | 1999-03-31 |
EP0819832B1 true EP0819832B1 (de) | 2004-10-20 |
Family
ID=7800147
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97111621A Expired - Lifetime EP0819832B1 (de) | 1996-07-18 | 1997-07-09 | Tiefbohrvorrichtung, Tiefbohrpumpenvorrichtung und Verwendung eines hydrodynamischen Retarders zur Kompensation der vom Antriebssystem ausgelösten Rückstellmomente |
Country Status (4)
Country | Link |
---|---|
US (1) | US6092595A (de) |
EP (1) | EP0819832B1 (de) |
CA (1) | CA2210421C (de) |
DE (2) | DE19628950C2 (de) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19748907C1 (de) * | 1997-11-05 | 1999-05-12 | Netzsch Mohnopumpen Gmbh | Antriebskopf für ein drehantreibbares Gestänge, insbesonders zum Antreiben einer Bohrlochpumpe |
DE19849756C2 (de) * | 1998-10-28 | 2002-05-29 | Netzsch Mohnopumpen Gmbh | Antriebskopf für ein drehantreibbares Gestänge, insbes. zum Antreiben einer Bohrlochpumpe |
US6579077B1 (en) | 2001-12-27 | 2003-06-17 | Emerson Electric Company | Deep well submersible pump |
US8708072B2 (en) | 2011-02-15 | 2014-04-29 | Deere And Company | Modulated vehicle retardation system and method |
US8733489B2 (en) | 2011-02-15 | 2014-05-27 | Deere & Company | Vehicle overspeed protection system |
US8662186B2 (en) * | 2011-03-15 | 2014-03-04 | Weatherford/Lamb, Inc. | Downhole backspin retarder for progressive cavity pump |
CN102424043B (zh) * | 2012-01-09 | 2013-07-31 | 谢陵波 | 一种同轴式液压缓速制动装置 |
AR085241A1 (es) * | 2012-02-15 | 2013-09-18 | Ener Tools Sa | Disposicion de frenado para cabezales de bombeo |
CN109644587A (zh) * | 2017-10-10 | 2019-04-19 | 金荣宽 | 便携式挖掘机 |
WO2020236430A1 (en) * | 2019-05-21 | 2020-11-26 | Schlumberger Technology Corporation | Biased control unit |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3572480A (en) * | 1969-04-14 | 1971-03-30 | William S Nagel | Transmission-driven retarder with fluid-operated blocker and inlet valve |
US4043434A (en) * | 1974-08-29 | 1977-08-23 | Parmac, Inc. | Mechanically adjustable dual pocket hydromatic brake |
AU514850B2 (en) * | 1976-04-13 | 1981-03-05 | Paemac, Inc | Hydromatic brake |
US4324387A (en) * | 1980-01-30 | 1982-04-13 | Twin Disc, Incorporated | Power delivery system having a pressure modulated hydrodynamic retarder for controlling a load |
JPH01150031A (ja) * | 1987-12-03 | 1989-06-13 | Daikin Mfg Co Ltd | 流体式リターダ |
DE4010970C2 (de) * | 1990-04-05 | 1996-05-30 | Voith Turbo Kg | Hydrodynamischer Retarder |
CA2074013A1 (en) * | 1992-07-16 | 1994-01-17 | Robert A. R. Mills | Brake assembly for rotating rod |
DE9302767U1 (de) * | 1993-02-25 | 1993-05-27 | Zweiweg Schneider GmbH & Co. KG, 8200 Rosenheim | Retarder-Baugruppe für den Einsatz in Mehrwege-Fahrzeugen |
DE4324460C1 (de) * | 1993-07-21 | 1994-11-24 | Daimler Benz Ag | Zahnräderwechselgetriebe für Kraftfahrzeuge mit einer Dauerbremse (Sekundärretarder) |
US5551510A (en) * | 1995-03-08 | 1996-09-03 | Kudu Industries Inc. | Safety coupling for rotary down hole pump |
GB2299849A (en) * | 1995-04-10 | 1996-10-16 | Mono Pumps Ltd | Downhole pump drive head assembly with hydrodynamic retarder |
US5749416A (en) * | 1995-04-10 | 1998-05-12 | Mono Pumps Limited | Downhole pump drive head assembly |
-
1996
- 1996-07-18 DE DE19628950A patent/DE19628950C2/de not_active Expired - Fee Related
-
1997
- 1997-07-09 EP EP97111621A patent/EP0819832B1/de not_active Expired - Lifetime
- 1997-07-09 DE DE59712022T patent/DE59712022D1/de not_active Expired - Lifetime
- 1997-07-11 US US08/893,442 patent/US6092595A/en not_active Expired - Lifetime
- 1997-07-15 CA CA002210421A patent/CA2210421C/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
CA2210421A1 (en) | 1998-01-18 |
DE19628950A1 (de) | 1997-05-15 |
US6092595A (en) | 2000-07-25 |
EP0819832A2 (de) | 1998-01-21 |
DE59712022D1 (de) | 2004-11-25 |
CA2210421C (en) | 2007-10-02 |
EP0819832A3 (de) | 1999-03-31 |
DE19628950C2 (de) | 1999-09-23 |
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