EP0100627B1 - Pompe hélicoidale - Google Patents

Pompe hélicoidale Download PDF

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Publication number
EP0100627B1
EP0100627B1 EP83304217A EP83304217A EP0100627B1 EP 0100627 B1 EP0100627 B1 EP 0100627B1 EP 83304217 A EP83304217 A EP 83304217A EP 83304217 A EP83304217 A EP 83304217A EP 0100627 B1 EP0100627 B1 EP 0100627B1
Authority
EP
European Patent Office
Prior art keywords
casing
rotor
stator
pump
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
Application number
EP83304217A
Other languages
German (de)
English (en)
Other versions
EP0100627A1 (fr
Inventor
Stanley Ashbourne Eaton Payne
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.)
NOV Process and Flow Technologies UK Ltd
Original Assignee
Mono Pumps Ltd
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 Mono Pumps Ltd filed Critical Mono Pumps Ltd
Publication of EP0100627A1 publication Critical patent/EP0100627A1/fr
Application granted granted Critical
Publication of EP0100627B1 publication Critical patent/EP0100627B1/fr
Expired legal-status Critical Current

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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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • F04C2/1076—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member orbits or wobbles relative to the other member which rotates around a fixed axis
    • 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

Definitions

  • This invention relates to a helical gear pump.
  • helical gear pumps There are several different types of helical gear pumps. Each of these types includes an inner member, usually a rotor, and an outer member, which is usually in the form of a stator.
  • the rotor has an external helical gear form with n starts.
  • the stator has a complementary internal helical gear form with n ⁇ 1 starts.
  • One of said members, usually the stator, is of resilient material.
  • Such pumps are capable of delivering against high delivery pressures, and are suitable for borehole pumps. They require good sealing and hence adequate initial interference between inner and outer members, so that interference and hence sealing will not be lost completely when the resilient member deforms under pump delivery pressure. However, such adequate initial interference may result in a high starting torque being required. Such a high starting torque may be a drawback when the pump is to be hand- operated.
  • AU-A-111901 An example of such a pump is shown in AU-A-111901, in which the pump comprises a casing, an inlet to the casing, an outlet to the casing, a helical rotor mounted for rotation within said casing about its longitudinal axis, a stator of resilient material mounted within said casing and around said rotor, an end portion of the outer wall of the stator adjacent the end of the stator nearer said inlet being connected sealingly to the casing, the remainder of the outer wall of the stator being spaced from the casing so as to be unconstrained against radial movement.
  • This sort of pump of the so-called “self-compensating” type, has the pressure of the column of water in a rising main connected to the upper end of the casing acting on the exterior of the stator. If the pump is stopped, this pressure will cause a large interference between the stator and the rotor, so that a high starting torque will be required. Such pumps have therefore been unsuitable for manual operation.
  • the present invention is characterised in that the inlet to the casing is connected to a foot valve, in that at least two stators of resilient material are mounted within said casing, that said rotor is a single helical rotor of constant helical cross-section, said single rotor being associated with both stators such that the stators are operatively in series, in that an end portion of the outer wall of each of said stators is connected sealingly to said casing, in each instance adjacent to the end of the respective stator nearer said inlet of the casing, in that at least the stator nearer the inlet of the casing has the remainder of its inner wall spaced from said casing so as to be unconstrained against radial inward movement and in that the stator remote from the inlet of the casing has a radial interference with respect to the rotor within a predetermined tolerance to enable the starting torque requirement to be sufficiently small for the rotation of the rotor from standstill to be effected manually.
  • the pressure at the upper end of the lower stator is substantially equal to the pressure at the lower end thereof, when the pump is at a standstill. This has the effect of causing the pressure on the outside of the self-compensating lower stator to be substantially equal to the pressure on the inside thereof which means that the starting torque required to overcome the interference between the lower stator and its rotor is negligible and one therefore only has to overcome the radial interference of the upper stator or stators.
  • Both of the stators may have the remainder of their outer walls spaced from the casing so as to be unconstrained against radial inward movement along portions of their length, so that they are both of the self-compensating type but, alternatively, the upper stator may be of the moulded-in type.
  • the helical gear pump may be mounted in a borehole installation comprising a rising main with the pump at the lower end of the rising main which extends from a lower level upwardly to an upper level above the mouth of the borehole, a shaft inside the rising main being connected to and extending upwardly from the rotor to a level above the upper end of the rising main, the shaft having means above the outlet of the rising main to cause rotation and orbiting of the rotor within the stators, and to cause water to be pumped from the borehole for delivery out of the outlet opening.
  • the means to cause rotation may comprise manually-operable means which includes an arm operatively connected to the shaft, the arm having handle whereby the shaft may be rotated about its axis relative to the rising main.
  • the manually-operable means may include a pedestal mounted over and connected to the upper end of the rising main, the upper end of the pedestal supporting a bearing for the arm and having a clutch device to permit rotation of the arm in one direction only, about the rotational axis of the rotor.
  • the pedestal may have a water outlet below the level of the bearing, and a sealing gland below the bearing but above the water outlet, the shaft being adapted to pass sealingly through the sealing gland.
  • the water outlet may be in the form of a spout directed downwardly from the pedestal.
  • An upwardly directed baffle may be provided at the inner end of the spout.
  • the arm may be provided with gripping means for co-operating with the shaft, the gripping means including two bushes in a transverse bore intersected by a longitudinal bore to accommodate the shaft, and the two bushes in use being urged together by a bolt passing through them to grip the shaft where it intersects the transverse bore.
  • the means for causing rotation may be provided by a windmill-operated rotary drive having its output operatively connected to the shaft.
  • a borehole generally indicated by reference numeral 10. It has a borehole casing 12 within which a rising main 14 is centrally located by stabilizers 16 arranged at axially spaced intervals within the casing 12.
  • a helical gear pump 18, according to the invention, is mounted at the lower end of the rising main 14.
  • a foot valve and strainer 20 is provided below the pump 18.
  • the pump 18 has a shaft 22 located centrally within the rising main 14 by bobbin bearings 24. Rotary power is applied to the shaft 22 by means of manually-operable means in the form of a hand pump arm 26 of a hand pump head, generally indicated by reference numeral 27.
  • the hand pump arm 26 is rotatably mounted on pedestal 28 which is mounted by means of a base member 30 over the borehole 10.
  • the pedestal 28 has a delivery or outlet pipe 32 which is provided with a baffle 34 on the inside of the pedestal so as to prevent the introduction of foreign matter into the pedestal 28 from outside, via the outlet pipe 32.
  • the base member 30 is mounted on a concrete block 36 cast into the soil 38 around the mouth of the borehole 10.
  • the pump 18 comprises a cylindrical casing 40 connected to the lower end of the rising means 14 (not shown).
  • stators 42.1 and 42.2 are mounted sealingly in tandem around the rotor 44.
  • the ring 45 is arranged at the suction end of the stator 42.2.
  • the rotor 44 is connected to the lower end of the shaft 22.
  • the stator 42.1 is moulded into casing 42.11 which is attached to the casing 40.
  • the stator 42.2 is moulded into ring 45 which is attached to the casing.
  • a clearance space 48 is provided around the upper end of the stator 42.2.
  • the rotor 44 will be arranged to have conventional radial interference with the stator 42.1, and little radial interference with the stator 42.2.
  • the stators 42.1 and 42.2 are also arranged in timed relationship with each other relative to the rotor 44 and are held in position in the casing 40. Under no load, the radial interference between the rotor 44 and the inner surface of the stator 42.2 will be less than the radial interference between the rotor 44 and the inner surface of the stator 42.1.
  • the shaft 22 is sufficiently flexible to take up the eccentricity of the rotor orbiting within the stator. It is therefore not necessary to have flexible connectors, such as universal joints and so on, in line with shaft 22.
  • the shaft 22 is made up of a number of sections joined end-to-end.
  • stator 42.3 is also sealingly mounted in similar fashion to the stator 42.2 within the casing 40.
  • Rotor 44 and stator 42.2 of Figure 3 operate in the same way as described for the stator 42.2 and the rotor 44 of Figure 2.
  • the stators 42.2 and 42.3 of Figure 3 are also arranged in timed relationship relative to each other and relative to the rotor 44, and are held in position in the casing 40.
  • the delivery pressure at the outlet from the stator 42.3 will act on the outside of the stator in the clearance space 48 and will balance to some degree the internal pressure inside the stator 42.3. Thus, sealing interference between the stator 42.3 and the rotor 44 will be substantially maintained so that delivery can take place even under a high head.
  • a hand pump head 27 which includes the pedestal 28 rotatably supporting the arm 26 via anti-friction bearing 60.
  • the arm 26 has a ratchet device 62 to prevent it from being turned in the wrong direction.
  • the teeth for the ratchet device 62 and bearing 60 are mounted in a plug 64 which is located in the upper end of the pedestal 28.
  • the shaft 22 passes. through seals 66 which engage sealingly with the shaft 22 along its outer surface.
  • the shaft 22 is locked in relation to the arm 26 by gripping means which includes bushes 68 and 70 urged together by a bolt 72 passing with clearance through them.
  • the bushes have faces 68.1 and 70.1 urged into gripping relationship with the shaft 22 by means of the bolt 72.
  • the bushes are located axially in a bore 74 which is intersected by the shaft 22. If desired, the ends of the bore 72 are closed off by plugs 76 and 78 to prevent tampering with the locking arrangement on the shaft 22.
  • the bolt 72 is provided with a socket head 72.1, further to discourage tampering if the cover 76 should be removed. In Figure 4 the plug 78 is shown removed.
  • the stator has three starts and the rotor has two starts.
  • the lower ends of the casing is conveniently threaded to engage with a foot valve or a foot valve and strainer 20.
  • the direction of rotation of the rotor is arranged to take place in such a direction that water will be pumped upwardly.
  • the upper ends of the stators 42.2 will be subjected to partial delivery pressure.
  • the upper ends of the stators 42.1 and 42.3 will, on the other hand, be subjected to full delivery pressure. This is the pressure which is applied to the clearance spaces 48.
  • the interference between the rotor and the stators 42.2 and 42.3 can be minimal.
  • pressure builds up however, a tendency for the stators to expand under internal pressure can be cancelled or counteracted or compensated for by the external pressure around the outside of the stators, in the clearance spaces mentioned. It is thus possible to start with minimal interference between the rotor and the stators, yet without the danger of losing necessary sealing interference, as pressure builds up inside the stators.
  • compensating stators 42.2 and 42.3 Because of the compensating effect which the delivery pressure has on the outer surfaces of the stators 42.2 and 42.3, they may for brevity be referred to as compensating stators.
  • the hand pump embodiment shown in the drawings shows the handle connected directly to the pump shaft without an intermediate gear ratio. It is possible to have the pump shaft driven via a step-down or step-up drive to drive it slower or faster than the handle. Such a drive may be provided by chain and sprockets, V-belts and pulleys, or a gear drive with toothed gearwheels.
  • the pump shaft may also be driven by a rotary windmill-driven shaft directly or via a step-up or step-down drive.
  • a pump according to the invention having the stator nearer the inlet as a compensating stator, also has advantages in pumping hot liquids or in pumping cold liquids which later become hot.
  • the moulded-to metal stator 42.1 In order to allow for temperature, the moulded-to metal stator 42.1 must have greater initial clearance at low temperature.
  • stator 42.2 ensures adequate performance in the cold condition. As temperature rises, so the stator 42.1 expands, thereby taking up the greater initial clearance and providing required interference and hence good sealing at the final operating temperature.
  • helical gear pumps having stators arranged in series in accordance with the invention, have low starting torques in practice yet have adequate deliveries even at high heads and at low speeds, without excessive torque requirements.
  • helical gear pumps are very suitable for use as hand pumps on boreholes.
  • a pump having a series mounting of compensating stators has an increased efficiency over a pump having a single compensating stator of a length equivalent to the series- mounted compensating stators.

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  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (8)

1. Pompe à engrenages hélicoïdaux pour forage comportant un tubage (40), une entrée (20) de tubage, une sortie de tubage, un rotor hélicoïdal (44) monté pour pouvoir tourner à l'intérieur dudit tubage autour de son axe longitudinal, un stator (42) en matériau élastique monté à l'intérieur dudit tubage et autour dudit rotor, une portion d'extrémité de la paroi extérieure du stator près de l'extrémité du stator la plus proche de ladite entrée (20) étant connectée de façon étanche au tubage, le reste de la paroi extérieure du stator se trouvant à une certaine distance du tubage de façon à ce qu'un déplacement radial ne lui soit pas interdit, caractérisée en ce que l'entrée (20) du tubage est reliée à une soupape de pied (20); en ce qu'au moins deux stators en matériau élastique sont montés à l'intérieur dudit tubage; en ce que ledit rotor (44) est un rotor hélicoïdal unique de section droite hélicoïdale constante, ledit rotor unique étant associé avec deux stators de façon que les stators fonctionnent en série; en ce qu'une portion d'extrémité de la paroi extérieure de chacun desdits stators (42) est reliée de façon étanché au dit tubage (40), dans chaque cas prés de l'extrémité du stator respectif la plus proche de ladite entrée du tubage; en ce qu'au moins le stator (42.2) le plus proche de l'entrée (20) du tubage a la reste de sa paroi extérieure qui se trouve à une certaine distance (en 48) dudit tubage (40) de façon à ce qu'un déplacement radial intérieur ne lui soit pas interdit; et en ce que le stator (42.1, 42.3) éloigné de l'entrée (20) du tubage présente une interférence radiale par rapport au rotor en restant dans une tolérance prédéterminée pour permettre que le couple de démarrage demandé reste suffisamment faible pour que la mise en rotation du rotor à partir de la position d'arrêt puisse se faire manuellement.
2. Pompe selon la revendication 1, caractérisée en ce que l'un et l'autre desdits stators (42.3, 42.2) ont le reste de leurs parois extérieures espacées (en 48) dudit tubage (40) de façon à ce qu'un déplacement radial intérieur sur des portions de leur longueur ne leur soit pas interdit.
3. Pompe selon la revendication 1 ou 2, caractérisée en ce qu'elle est montée dans une installation de pompage de forage comportant une colonne montante (14) qui s'étend, depuis un niveau inférieur, vers le haut, jusqu'à un niveau situé au-dessus de l'embouchure du forage, la pompe se trouvant à l'extrémité inférieure de la colonne montante; en ce qu'un arbre (22) situé à l'intérieur de la colonne montante est relié au rotor et s'étend vers le haut, depuis le rotor, jusqu'à un niveau situé au-dessus de l'extrémité supérieure de la colonne montante; en ce que l'arbre présente, à un niveau situé au-dessus de l'ouverture de sortie (32), des moyens (26) pour entraîner l'arbre en rotation, ce par quoi, en service, le rotor est amené à tourner, en mouvement orbital, à l'intérieur des stators pour pomper l'eau depuis le forage jusqu'à l'ouverture de sortie.
4. Pompe selon la revendication 3, caractérisée en ce que le moyen de mise en rotation consiste en un dispositif manoeuvré manuellement comprenant un bras relié à un arbre, ledit bras présentant une poignée (26.1) par laquelle l'arbre peut être tourné manuellement autour de son axe.
5. Pompe selon la revendication 4, caractérisée en ce que les moyens de manoeuvre manuelle comportent une chaise (28) montée sur l'extrémité supérieure de la colonne montante (14) et reliée à cette extrémité, l'extrémité supérieure de la chaise supportant un palier (60); et en ce qu'il est prévu un cliquet (62) pour ne permettre la rotation du bras autour de l'axe de rotation de l'arbre que dans un seul sens.
6. Pompe selon la revendication 5, caractérisée en ce que la chaise (28) comporte la sortie d'eau (32) en-dessous du niveau du palier (60).
7. Pompe selon la revendication 6, caractérisée en ce que la chaise (28) comporte une garniture d'étanchéité (66) en-dessous du palier (60) mais au-dessus de la sortie d'eau (32), ledit arbre étant prévu pour traverser de façon étanche la garniture d'étanchéité.
8. Pompe selon la revendication 6 ou 7, caractérisée en ce que la sortie d'eau a la forme d'une buse dirigée vers le bas depuis la chaise; et en ce qu'un déflecteur (34) s'étend vers le haut à l'extrémité intérieure de la buse.
EP83304217A 1982-07-20 1983-07-20 Pompe hélicoidale Expired EP0100627B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ZA825185 1982-07-20
ZA825185 1982-07-20

Publications (2)

Publication Number Publication Date
EP0100627A1 EP0100627A1 (fr) 1984-02-15
EP0100627B1 true EP0100627B1 (fr) 1987-05-20

Family

ID=25576174

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83304217A Expired EP0100627B1 (fr) 1982-07-20 1983-07-20 Pompe hélicoidale

Country Status (10)

Country Link
EP (1) EP0100627B1 (fr)
JP (1) JPS5974385A (fr)
AU (1) AU554747B2 (fr)
BR (1) BR8303901A (fr)
DE (1) DE3371674D1 (fr)
ES (1) ES524252A0 (fr)
GB (1) GB2124305B (fr)
MW (1) MW3283A1 (fr)
NZ (1) NZ204931A (fr)
ZW (1) ZW16083A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3345233C2 (de) * 1983-12-14 1985-10-31 Joh. Heinrich Bornemann GmbH & Co KG, 3063 Obernkirchen Exzenterschneckenpumpe zum Fördern von Flüssigkeiten aus Bohrlöchern, insbesondere aus Erdöl-Bohrlöchern
FR2696792B1 (fr) * 1992-10-13 1994-12-09 Inst Francais Du Petrole Système de pompage comportant une pompe volumétrique à grand débit.
US5820354A (en) * 1996-11-08 1998-10-13 Robbins & Myers, Inc. Cascaded progressing cavity pump system
GB2338268A (en) * 1998-02-24 1999-12-15 Orbit Pumps Ltd Stator assembly
RU2247264C2 (ru) * 2003-03-24 2005-02-27 Брот Александр Робертович Погружная насосная установка
RU2249726C2 (ru) * 2003-03-24 2005-04-10 Брот Александр Робертович Погружная насосная установка
US7214042B2 (en) * 2004-09-23 2007-05-08 Moyno, Inc. Progressing cavity pump with dual material stator
WO2009040442A1 (fr) * 2007-09-28 2009-04-02 Shell Internationale Research Maatschappij B.V. Procédé pour améliorer une récupération d'un fluide d'hydrocarbures
EP3050520A1 (fr) 2015-01-27 2016-08-03 Michael Zhadkevich Dispositifs et techniques de compression vasculaire
CN109763978A (zh) * 2019-03-12 2019-05-17 北京雷神博峰信息技术有限责任公司 一种车载电动手摇一体泵
CN114320884B (zh) * 2021-11-10 2024-06-14 浙江环誉泵业科技有限公司 一种航空航天用高速高温高效燃油泵

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1728143A1 (de) * 1968-08-30 1972-03-30 Max Streicher Exzenterschneckenpumpe

Family Cites Families (12)

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Publication number Priority date Publication date Assignee Title
GB446291A (en) * 1933-10-30 1936-04-27 Alfred Lanser Improvements in rotary pumps
US2408109A (en) * 1945-03-13 1946-09-24 Alden Speare S Sons Co Pump
US2621605A (en) * 1945-10-12 1952-12-16 Clayton Mark & Company Pump
US2826152A (en) * 1955-08-30 1958-03-11 Robbins & Myers Helical gear pump with bellows stator
GB1067014A (en) * 1964-10-30 1967-04-26 Unitex Ltd Improvements in helical gear pumps
US3347169A (en) * 1966-09-26 1967-10-17 Sargent Industries Rotary well pump
US3982858A (en) * 1973-11-14 1976-09-28 Smith International Corporation, Inc. Segmented stator for progressive cavity transducer
US3999901A (en) * 1973-11-14 1976-12-28 Smith International, Inc. Progressive cavity transducer
DE2418967C2 (de) * 1974-04-19 1982-09-09 Netzsch-Mohnopumpen Gmbh, 8672 Selb Exzenterschneckenpumpe
CH616487A5 (fr) * 1977-03-30 1980-03-31 Peter F Roth
DE2817280A1 (de) * 1978-04-20 1979-10-25 Streicher Foerdertech Stator fuer exzenterschneckenpumpen
FR2463299A1 (fr) * 1979-08-13 1981-02-20 Michel Durand Pompe verticale a traction manuelle, eolienne, a moteur ou autre pour pompe a grande profondeur

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1728143A1 (de) * 1968-08-30 1972-03-30 Max Streicher Exzenterschneckenpumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PUMPING MANUEL, 6th edition, 1979, pp. 67-70 *

Also Published As

Publication number Publication date
JPS5974385A (ja) 1984-04-26
GB2124305A (en) 1984-02-15
DE3371674D1 (en) 1987-06-25
AU1692783A (en) 1984-01-26
BR8303901A (pt) 1984-02-28
ES8405901A1 (es) 1984-06-16
EP0100627A1 (fr) 1984-02-15
ZW16083A1 (en) 1984-02-08
GB2124305B (en) 1985-08-29
AU554747B2 (en) 1986-09-04
MW3283A1 (en) 1985-02-13
GB8319576D0 (en) 1983-08-24
NZ204931A (en) 1986-06-11
ES524252A0 (es) 1984-06-16

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