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EP0232421B1 - Machine a vis - Google Patents

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Publication number
EP0232421B1
EP0232421B1 EP85905010A EP85905010A EP0232421B1 EP 0232421 B1 EP0232421 B1 EP 0232421B1 EP 85905010 A EP85905010 A EP 85905010A EP 85905010 A EP85905010 A EP 85905010A EP 0232421 B1 EP0232421 B1 EP 0232421B1
Authority
EP
European Patent Office
Prior art keywords
rotors
screw
mechanisms
group
stators
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
EP85905010A
Other languages
German (de)
English (en)
Other versions
EP0232421A4 (fr
EP0232421A1 (fr
Inventor
Dmitry Fedorovich Baldenko
Jury Vyacheslavovich Vadetsky
Moisei Timofeevich Gusman
Valery Igorievich Semenets
Valentina Alexeevna Khabetskaya
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.)
VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI
Original Assignee
VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI
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 VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI filed Critical VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI
Priority to AT85905010T priority Critical patent/ATE69485T1/de
Publication of EP0232421A1 publication Critical patent/EP0232421A1/fr
Publication of EP0232421A4 publication Critical patent/EP0232421A4/fr
Application granted granted Critical
Publication of EP0232421B1 publication Critical patent/EP0232421B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • 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
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/02—Fluid rotary type drives

Definitions

  • the invention relates to a screw machine with a plurality of screw mechanisms arranged one after the other, which have stators which are arranged coaxially and are rigidly connected to one another and rotors arranged therein and connected to one another by flexible shafts, the axes of the rotors being offset by the size of the eccentricity with respect to the central axis of the stators, and which are combined into groups and the groups into blocks, the axes of the rotors of the screw mechanisms of each group and in each block being arranged symmetrically to the central axis of the stators, and in each group the distances between the axes of the rotors of the adjacent screw mechanisms being the same.
  • Such a screw machine is known from GB-A-436 843.
  • the flexible shafts through which the rotors are connected serve to transmit the axial force as well as the torque.
  • torsions occur which do not guarantee a compensation of the inertial forces of the runners with one another, so that considerable torsional loads occur which have a negative effect on the service life of the screw machine.
  • the object of the invention is to improve a screw machine of the type mentioned in such a way that the torsional loads of the individual runners are almost balanced, but in any case are significantly reduced.
  • the presence of the connecting elements makes it possible to ensure that the predetermined alignment of all the rotors of the screw mechanisms relative to one another is ensured, that the sum of all the inertial forces acting in the screw machine is zero, since the vectors of the inertial forces which pass through the rotor axes are symmetrical to the central axis of the stators are arranged.
  • Each connecting element is designed as a crank, which is connected to the adjacent runners by means of bearings, the axis of which coincides with the axis of the respective rotor.
  • This structural design of the connecting element makes it possible to simplify the assembly of the screw machine.
  • the central angle of the symmetrical displacement of the rotor axis of each subsequent screw mechanism to the rotor axis of the previous screw mechanism is determined by the number of screw mechanisms in the group. In the same way, the angle of mutual displacement of the groups depends on their number in the block.
  • the inertial forces and their moments can be significantly reduced and fully compensated in most embodiments, which jumps the vibration level of stators, threaded sleeves and other machine elements allowed to lower.
  • the reduced vibration level of the screw machine increases the quality of the drilled borehole when a screw machine is used as the borehole sole motor and stabilizes the mode of operation during its operation.
  • connecting elements which increase the safety when aligning the rotors of the screw mechanisms, the use of additional procedural measures during the assembly of the motor, which are mandatory in the absence of connecting elements, is avoided.
  • cranks By using the cranks as connecting elements, the actual assembly is simplified and the assembly time is shortened.
  • a screw machine in an embodiment as a borehole sole motor contains an actuating device 1 (FIGS. 1a, 1a ') and a bearing element 2.
  • the actuating device 1 comprises a single block 3, the components of which are two groups 4 and 5.
  • the number of blocks 3 in the screw machine is determined by its output data (torque, speed, pressure drop) and can be increased if necessary.
  • the first group 4 comprises two screw mechanisms 6 and 7 arranged one after the other; the second group 5 accordingly contains screw mechanisms 8 and 9.
  • Each of the screw mechanisms 6, 7, 8, 9 includes a stator and a rotor housed therein.
  • the screw mechanism 6 it is the stator 10 and the rotor 11, in the mechanism 7 the stator 12 and the rotor 13, in the mechanism 8 the stator 14 and the rotor 15, in the mechanism 9 the stator 16 and the rotor 17.
  • the stators 10, 12, 14 and 16 of the actuating device 1 and the bearing element 2 are connected to one another by means of threaded sleeves 18 and have a common central axis 00 which corresponds to the axis of the screw motor.
  • the axes of the rotors 11, 13, 15 and 17 are offset from this common axis 00 by the size of the eccentricity "e".
  • the rotor 17 is connected to a shaft 19 of the bearing element 2 by means of a flexible shaft 20.
  • the axis of the shaft 19 also coincides with the axis 00.
  • a stone-destroying tool is attached to the output end of the shaft 19 (not shown in FIG. 1a, 1 a ').
  • the interacting rotors 11, 13, 15 and 17 and the stators 10, 12, 14 and 16 associated therewith form working chambers A which define the interior of the screw mechanisms 6, 7, 8 and 9 in Divide high and low pressure rooms.
  • the rotors 11 and 13, 13 and 15, 15 and 17 are each connected via a flexible shaft 21, 22 and 23, by means of which the transmission of the axial force from one rotor 11, 13 and 15 to the respectively adjacent rotor 13, 15 and 17 and the transmission of the largest share of torque is achieved.
  • the runners 11, 13, 15, 17 are connected to the flexible shafts 21, 22, 23 via smooth conical surfaces 24.
  • the runners 11 and 13, 13 and 15, 15 and 17 are also connected to each other to secure their symmetrical axis displacement by means of connecting elements 25 which transmit a certain residual torque.
  • the axes of the rotors 11, 13, 15 and 17 are offset with respect to one another along a circular line with a radius "e" equal to the eccentricity of the screw mechanisms and a center coinciding with the central axis 00.
  • the connecting elements 25 are designed as cranks 26, 27 and 28, the running surfaces 29 and 30 of which are supported in the respective runners 11, 13, 15 and 17 by means of bearings 31 and 32, so that the rotatability of the cranks 26, 27, 28 relative to the runners 11, 13, 15, 17 is made possible with the simultaneous transmission of a certain proportion of torque.
  • the predetermined axis position of the rotors 15 and 17 with respect to the common central axis 00 of the stators 14 and 16 is ensured by means of the crank 28, which is accommodated within a flexible shaft 23.
  • the actual groups 4, 5 are also aligned symmetrically with respect to one another by means of a similar connecting element 25, a crank 27, which is mounted between the runners 13 and 15 and arranged in the flexible shaft 22, which also on the smooth conical surfaces 24 with the runners 13 and 15 is connected.
  • the angle of the symmetrical displacement of the actual groups 4 and 5 in block 3 is also dependent on the number of groups in the block and is defined according to the axis position of the respective outer runners 11 and 15 or 13 and 17.
  • FIG. 4 shows a constructive connection variant for the rotors 33 and 34 of two screw mechanisms 35 and 36 arranged one after the other.
  • a flexible shaft 37 is accommodated within a crank 38.
  • the running surfaces 39 of the crank 38 are rotatably mounted in bearings 40 at the end sections of the runners 33 and 34 to be connected.
  • the stators 41 and 42 of the screw mechanisms 35 and 36 are connected to one another by means of a threaded sleeve 43 and, together with the runners 33 and 34 arranged inside, form a group 44.
  • the axis of the rotor 58 of the screw mechanism 52 in the group 47 is offset with respect to the axis of the rotor 56 of the screw mechanism 50 in the group 46.
  • the axes of the rotors 54, 55, 56, 57, 58, 59 of the screw mechanisms 48, 49, 50, 51, 52 53 are offset along a circular line with a radius "e", which corresponds to the eccentricity of the screw mechanisms 48, 49, 50 , 51, 52, 53 corresponds and is the same for all mechanisms 48, 49, 50, 51, 52, 53.
  • Fig. 8 shows the effect diagram of the inertial forces in the screw machine.
  • the inertial forces Fjs 4 and Fjss, Fjs ⁇ and Fjs 7 , Fjs 8 and Fjs 9 are the same size and also directed in pairs in opposite directions, whereby a complete compensation is guaranteed not only for the inertial forces but also for their moments.
  • This is achieved in that the axes of the rotors 54, 55, 56, 57, 58 and 59 are arranged symmetrically to the central axis 00 of the screw machine and the axial spacings of the rotors 54 and 55, 56 and 57, 58 and 59 are the same.
  • the block 61 of a screw machine (FIG. 9) comprises two groups 62 and 63, each of which consists of three screw mechanisms 64, 65 and 66 or 67, 68 and 69.
  • the axes of the rotors 70, 71 and 72 of the screw mechanisms 64, 65 and 66 are within the first group 62 (FIG.
  • the symmetrical axis displacement of the rotors 70, 71, 72 takes place along a circular line with a radius "e", which is the same as the eccentricity of the screw mechanisms 64, 65, 66, 67, 68, 69, which is the same for all mechanisms .
  • the center of this circular line coincides with the central axis 00 of the screw machine and all screw mechanisms 64, 65, 66, 67, 68, 69.
  • 12 shows the action diagram of the inertial forces in the screw machine in question. According to the size defined by the mass of the runners 70, 71, 72, 73, 74 and 75, they are the same.
  • the inertial forces (Fj 70 , Fj 71 , Fj 72 in the first group 62 and Fj 73 , Fj 74 and Fj 75 in the second group 63) are completely balanced, since their sum is zero.
  • the moments of inertial forces are just as completely balanced in that the axes of the rotors 70, 71, 72, 73, 74 and 75 are arranged symmetrically to the central axis 00 of the screw machine, the axial spacings of the rotors 70, 71 and 72 being the case with the first group 62 and the runners 73, 74 and 75 in the second group 63 are the same.
  • FIG. 13 shows a screw machine according to the invention as a pump.
  • the pump housing 76 receives a bearing element 77 and a drive shaft 78 which is connected to the rotor 80 of a screw mechanism 81 via an articulated connection 79.
  • the rotor 80 is located within a stator 82, which is connected to the pump housing se 76 is rigidly connected.
  • the stators 82, 83, 84 and 85 are connected to one another in a coaxial manner via threaded sleeves 86.
  • the rotors 80, 87, 88 and 89 are connected to one another in accordance with one of the variants considered above, namely by means of flexible shafts 90 and connecting elements 91 designed as crank 92.
  • the connecting elements 91 are rotatably accommodated in the respective runners 80, 87, 88, 89 by means of bearings 93.
  • the stators 82, 83, 84 and 85 and the rotor 80, 87, 88 and 89 respectively arranged therein form screw mechanisms 81, 94, 95 and 96 which are combined in pairs to form groups 97 and 98, which in the present modification only have one form a single block 99 of an actuating device 100.
  • the pump has an inlet space B and an outlet space C through which the working fluid or another liquid medium is supplied or discharged.
  • the screw machine shown in Fig. 14 is used as a compressor.
  • the compressor housing 101 accommodates an actuating device 102, which comprises a block 103 composed of screw mechanisms 104, 105, 106, and 107.
  • the screw mechanisms 104 and 105 and 106, 107 are combined in pairs to form groups 108 and 109.
  • the rotors 110, 111, 112 and 113 of the screw mechanisms 104, 105, 106 and 107 are connected to one another in an equiaxial manner via threaded sleeves 114.
  • the rotors 115, 116, 117 and 118 of these screw mechanisms 104, 105, 106, 107 are connected to one another in accordance with one of the arrangements considered above by means of flexible shafts 119 and connecting elements 120 designed as crank 121 in order to transmit the hydraulic axial force and the torque as well as the predetermined one To ensure axis displacement of the rotor 115, 116, 117 and 118.
  • the crank 121 is rotatably supported in the respective runners 115, 116, 117, 118 by means of bearings 122.
  • the outer rotor 118 of the screw mechanism 107 is rigidly connected to an articulated connection 123 and this is connected to a drive shaft 124.
  • the articulated connection 123 and the drive shaft 124 are arranged in a bearing element 125 which is rigidly connected to the housing 101, within which cooling spaces are arranged.
  • the compressor has an inlet E and an outlet space F, through which the gas medium to be conveyed is fed in or out.
  • the screw machine works as follows.
  • the flushing liquid is fed from the drill pipe cavity (not shown in FIG. 1 a, 1 a ') to the working chambers A of the first screw mechanism 6.
  • an active torque is generated on the rotor 11, which rotates it.
  • the rotation is transmitted from the rotor 11 via the flexible shafts 21, 22 and 23 successively to the rotor 13, 15 and 17, further to the bearing element 2 and then to the rock-destroying tool (not shown).
  • the torques created under the effect of the pressure gradient on the rotors 11, 13, 15 and 17 are summed and also transmitted to the stone-destroying tool via the shaft 19 of the bearing element 2.
  • the flushing liquid After the flushing liquid has flowed through the working chambers A of the screw mechanism 6, it enters the working chambers A of the screw mechanism 7 via the interior of the threaded sleeve 18. The pressure drop in the working chambers A of the screw mechanism 7 generates an additional torque on the rotor 13. The flushing liquid thus flows through the working chambers A of all screw mechanisms 7, 9 in succession and, via the bearing element 2, reaches the stone-destroying tool, through which it exits to the bottom of the borehole.
  • the principle of operation of the screw machines shown in FIGS. 13 and 14 has a single difference, which is only that the rotors 80, 87, 88 and 89, 115, 116, 117 and 118 are driven by a motor (not shown in the drawings) the drive shafts 78, 124 are driven and the working fluid (or the gas medium) from the room B (E) through the working chambers A of the screw mechanisms 81, 94, 95, 96, 104, 105, 106, 107 into the rooms C (F) is promoted.
  • the present invention can be used particularly effectively as a drive for rock-destroying tools when drilling oil and gas wells.
  • the invention can also be used as a borehole probe pump unit to extract water, petroleum or other mineral resources which are pumped around in liquid form.
  • the invention can also be used in reliable pump or compressor units with which liquid, gaseous or mixed media are to be pumped.

Landscapes

  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Physics & Mathematics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Valve Device For Special Equipments (AREA)
  • Permanent Magnet Type Synchronous Machine (AREA)
  • Extrusion Moulding Of Plastics Or The Like (AREA)
  • Earth Drilling (AREA)
  • Nitrogen And Oxygen Or Sulfur-Condensed Heterocyclic Ring Systems (AREA)
  • Mechanical Treatment Of Semiconductor (AREA)
  • Manipulator (AREA)
  • Drilling And Boring (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Formation And Processing Of Food Products (AREA)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)

Claims (1)

1. Machine à vis notamment pour entraînements de trous de forage, comprenant plusieurs mécanismes à vis (6, 7, 8, 9) disposés successivement, que comprennent des stators (10, 12, 14, 16) disposés coaxialement et reliés rigidement les uns aux autres et des rotors (11, 13, 15, 17) disposés dans ceux-ci et reliés les uns aux autres par des arbres flexibles (21, 22, 23), des axes des rotors (11, 13, 15, 17) étant décalés par rapport à l'axe central des stators (10, 12, 14, 16) de la grandeur de l'excentricité (e), et qui sont reliés pour former des groupes (4, 5) et les groupes (4, 5) sont réunis pour former des blocs (3), les axes des rotors (11, 12, 14, 16) des mécanismes à vis (6, 7, 8, 9) de chaque groupe (4, 5) étant disposés dans chaque bloc (3) symétriquement par rapport à l'axe central des stators (10, 12, 14, 16) et dans chaque groupe (4, 5) les écarts des axes des rotors (11, 13, 15, 17) des mécanismes à vis voisins (6, 7, 8, 9) étant identiques, caractérisés en ce que dans chaque bloc (3) et, de façon correspondante, dans chaque groupe (4, 5), entre les rotors (11, 13, 15, 17) des différents mécanismes à vis (6, 7, 8, 9) et, de plus, comme éléments de liaison supplémentaire, des manivelles (26, 27, 28) sont prévues pour maintenir la position axiale prédéterminée des rotors (11, 13, 15, 17), les uns par rapport aux autres, les éléments de liaison (25) étant montés rotatifs dans les rotors respectifs (11, 13, 15, 17) dans des paliers (31, 32).
EP85905010A 1985-07-22 1985-07-22 Machine a vis Expired - Lifetime EP0232421B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85905010T ATE69485T1 (de) 1985-07-22 1985-07-22 Schraubenvorrichtung.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/SU1985/000061 WO1987000571A1 (fr) 1985-07-22 1985-07-22 Machine a vis

Publications (3)

Publication Number Publication Date
EP0232421A1 EP0232421A1 (fr) 1987-08-19
EP0232421A4 EP0232421A4 (fr) 1989-02-07
EP0232421B1 true EP0232421B1 (fr) 1991-11-13

Family

ID=21616928

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85905010A Expired - Lifetime EP0232421B1 (fr) 1985-07-22 1985-07-22 Machine a vis

Country Status (9)

Country Link
US (1) US4764094A (fr)
EP (1) EP0232421B1 (fr)
JP (1) JPS63500315A (fr)
AT (1) ATE69485T1 (fr)
BR (1) BR8507248A (fr)
DE (1) DE3584677D1 (fr)
DK (1) DK141887A (fr)
NO (1) NO871171L (fr)
WO (1) WO1987000571A1 (fr)

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8708791D0 (en) * 1987-04-13 1987-05-20 Shell Int Research Assembly for directional drilling of boreholes
AT401089B (de) * 1988-09-30 1996-06-25 Gd Anker Gruber Duebel Anker G Exzenterschneckenpumpe
US5015162A (en) * 1989-11-28 1991-05-14 Heppner Terry D Attachment for an oil well screw pump system
GB2244518B (en) * 1990-05-31 1994-03-16 Mono Pumps Ltd Helical gear pump
US5090497A (en) * 1990-07-30 1992-02-25 Baker Hughes Incorporated Flexible coupling for progressive cavity downhole drilling motor
US5588818A (en) * 1995-04-20 1996-12-31 Horizon Directional Systems, Inc. Rotor-to-rotor coupling
US6173794B1 (en) 1997-06-30 2001-01-16 Intedyne, Llc Downhole mud motor transmission
US5911284A (en) * 1997-06-30 1999-06-15 Pegasus Drilling Technologies L.L.C. Downhole mud motor
US6241494B1 (en) * 1998-09-18 2001-06-05 Schlumberger Technology Company Non-elastomeric stator and downhole drilling motors incorporating same
DE60132936T2 (de) 2000-05-05 2009-02-26 Weatherford/Lamb, Inc., Houston Vorrichtung und Verfahren zur Herstellung einer Lateralbohrung
US9745799B2 (en) 2001-08-19 2017-08-29 Smart Drilling And Completion, Inc. Mud motor assembly
US9051781B2 (en) * 2009-08-13 2015-06-09 Smart Drilling And Completion, Inc. Mud motor assembly
ES2259070T3 (es) * 2002-07-17 2006-09-16 Elthom Enterprises Limited Atornillador rotatorio y metodo de transformar un movimiento en dicha maquina.
DE10245497C5 (de) * 2002-09-27 2009-02-19 Wilhelm Kächele GmbH Elastomertechnik Exzenterschneckenpumpe mit vergrößertem Temperaturbereich
RU2241855C1 (ru) * 2003-04-16 2004-12-10 ОАО НПО "Буровая техника" Скважинный гидроприводной винтовой насосный агрегат
AU2013390586C1 (en) 2013-05-23 2017-10-19 Cenovus Energy Inc. Progressive cavity pump and method for operating same in boreholes
WO2017210779A1 (fr) * 2016-06-10 2017-12-14 Activate Artificial Lift Inc. Pompe à cavité progressive et procédés de fonctionnement
US10385615B2 (en) 2016-11-10 2019-08-20 Baker Hughes, A Ge Company, Llc Vibrationless moineau system
CA2961629A1 (fr) 2017-03-22 2018-09-22 Infocus Energy Services Inc. Systemes, dispositifs, assemblages d'alesage et methodes d'utilisation associees
CN108533445B (zh) * 2018-02-05 2023-11-28 佛山科学技术学院 一种双浮子共振型远海波浪发电装置
RU200583U1 (ru) * 2020-05-18 2020-10-30 Открытое акционерное общество Научно-производственное объединение "Буровая техника" Винтовой забойный двигатель с вращающимся статором
CN118836113A (zh) * 2024-09-23 2024-10-25 西南石油大学 一种振动可控螺杆马达

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB436843A (en) * 1934-05-02 1935-10-18 Rene Joseph Louis Moineau Improvements in rotary pumps, compressors and motors
US3999901A (en) * 1973-11-14 1976-12-28 Smith International, Inc. Progressive cavity transducer
US4011917A (en) * 1974-08-19 1977-03-15 Wladimir Tiraspolsky Process and universal downhole motor for driving a tool
JPS593276B2 (ja) * 1975-04-11 1984-01-23 凸版印刷株式会社 レコ−ドセンタ−ラベルノ セイゾウホウホウ
JPS5758515A (en) * 1980-09-22 1982-04-08 Nissan Motor Co Ltd Alarm system for vehicle
JPS5758518A (en) * 1980-09-26 1982-04-08 Komatsu Ltd Speed0change controlling system for car rquipped with hydraulic transmission gear

Also Published As

Publication number Publication date
WO1987000571A1 (fr) 1987-01-29
EP0232421A4 (fr) 1989-02-07
DK141887A (da) 1987-04-03
BR8507248A (pt) 1987-10-27
DK141887D0 (da) 1987-03-19
JPS63500315A (ja) 1988-02-04
US4764094A (en) 1988-08-16
NO871171D0 (no) 1987-03-20
EP0232421A1 (fr) 1987-08-19
ATE69485T1 (de) 1991-11-15
DE3584677D1 (de) 1991-12-19
NO871171L (no) 1987-03-20

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