EP0240467A1 - Machine alternative à pistons rotatifs - Google Patents

Machine alternative à pistons rotatifs Download PDF

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Publication number
EP0240467A1
EP0240467A1 EP87810206A EP87810206A EP0240467A1 EP 0240467 A1 EP0240467 A1 EP 0240467A1 EP 87810206 A EP87810206 A EP 87810206A EP 87810206 A EP87810206 A EP 87810206A EP 0240467 A1 EP0240467 A1 EP 0240467A1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
movement
stroke
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP87810206A
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German (de)
English (en)
Other versions
EP0240467B1 (fr
Inventor
Iso Wyrsch
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Individual
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Individual
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Filing date
Publication date
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Priority to AT87810206T priority Critical patent/ATE68556T1/de
Publication of EP0240467A1 publication Critical patent/EP0240467A1/fr
Application granted granted Critical
Publication of EP0240467B1 publication Critical patent/EP0240467B1/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
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0079—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having pistons with rotary and reciprocating motion, i.e. spinning pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces
    • F01B3/06—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces by multi-turn helical surfaces and automatic reversal
    • F01B3/08—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces by multi-turn helical surfaces and automatic reversal the helices being arranged on the pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the key points of the rotary reciprocating piston machine are the simple conversion of the reciprocating motion of the piston into a rotary motion, which creates a rotary and reciprocating motion.
  • valves are superfluous, not only with 2-stroke but also with 4-stroke engines and pumps and compressors.
  • the lifting movement can also be converted electrically instead of mechanically and directly generate electrical energy (or vice versa).
  • the "rotary piston machine” is a reciprocating piston machine or a free piston machine, with additional rotary movement of the piston. If the stroke is mechanically limited, it is a reciprocating piston machine, otherwise (for example, when the piston movement is generated electrically according to claim 4) it is by definition a free-piston machine. However, since the typical main feature of the machine is the rotary stroke movement of the piston, the name “rotary piston machine” is chosen.
  • the piston rod can be rotatably connected (axial bearing) to the crosshead and the piston rod and piston can be rotated from the outside, or the piston can be rotated by a built-in additional drive (electric motor etc.) etc. etc.
  • Figure 2 shows a schematic example of this.
  • the rotary movement can be matched to the stroke movement. (See also claims 9, 10, 18, 19).
  • the rotary movement of the piston preferably takes place as a continuous rotation because of the inertia.
  • a rotary movement with a periodically alternating direction of rotation is also useful, which allows very large openings.
  • Lubrication See point 26.
  • the pre-compressor is fully integrated in the rotary piston machine.
  • the rotary reciprocating machine does not get bigger as a result.
  • Hardly any additional weight Almost all parts are already available.
  • the pre-compressor piston attached to the shaft is actually the only additional component.
  • Simple and cheap. The gas cushion in the pre-compressor improves the smooth running of the machine under certain conditions.
  • the outlet control via the rotary piston enables different systems to be fed with different pressure levels. (See also claim 16).
  • the rotary piston (item 2) rotates together with the through shaft (14) and the rotating piston (item 5).
  • the only rotating pistons (5) are firmly connected to the shaft (14).
  • the rotating rotary piston is forced by the cam track (item 3) to make an additional longitudinal (stroke) movement.
  • the rotary piston is therefore longitudinally displaceable on a shaft; however, it can still transmit a torque to the shaft (not visible in the picture, dealt with in claims 21, 22, 23).
  • the integrated pre-compressor mainly consists of the rotating pre-compressor piston (item 31). This is located in the inner cavity of the rotary piston (2). It is firmly connected to the shaft (14), so it does not make any lifting movement.
  • the oscillating stroke movement of the rotary piston (2) therefore causes the working medium located there to be compressed to the left and right of the pre-compressor piston.
  • a pump with slot control of the inlets and outlets with the rotary piston (for example according to claim 2) can be built with only one moving part: the rotary piston !!
  • the rotary piston machine works, for example, as an internal combustion engine.
  • the lifting forces on the pistons generate electrical energy.
  • the rotary motion is superimposed on the piston by the magnetic forces. Control of the gas exchange according to claim 1 or 2 is thus also possible.
  • the rotary movement can be generated in exactly the same way as with conventional electric motors (this also applies analogously to electrical generators). All known types with direct current, alternating current, three-phase current, single-pole, multi-pole or types as stepper motors, etc. can be used. Due to the shape of the armature, the rotary movement also results in the stroke movement of the piston: the stator guides the adjacent outer surface of the armature at one or more points by magnetic forces. See example in Figure 17: The top of the stator is where it guides the outer surface of the armature. At the bottom, the field of the stator is much wider axially. The axial movement of the outer surface of the armature is permitted there.
  • the possible axial force on the armature can be increased as follows:
  • the stator not only acts with axial forces on the outer surface of the armature where it guides the armature. It also supports the relative axial movement of the armature outer surface to the stator at other points by driving forces. These driving forces oscillate in accordance with the movement of the surface of the armature. Not only do they cause greater possible axial forces, they can also support the rotary movement.
  • Anchors made of magnetizable but not permanently magnetic material, without coils on the anchor :
  • the armature can be magnetized by the stator, but they migrate with magnetic poles on the anchor. Due to the special shape of the armature according to claim 4, such electric motors can be realized. See Figures 18 to 21. At at least one point, the stator acts with a strong field on the armature and magnetizes the armature. This creates a whole number of magnetic pole pairs on the armature, ie an even number of magnetic poles. The driving forces do not work in a purely tangential direction, as with a conventional electric motor.
  • NB The radial force component between the stator pole and armature is taken for granted and is therefore not mentioned here.
  • the driving forces of the stator act primarily in the axial direction. However, a tangential force component is also required to generate the rotary movement. Due to the shape of the anchor, this tangential force component is created automatically, unless the anchor is in a dead center of movement. For this reason, the machine in Figure 18 has, for example, an auxiliary winding (46) for starting the machine.
  • the machine in Figure 19 has a guide pole (44) and three points on the stator that drive the armature. The driving poles are controlled so that the armature continuously follows the attractive forces of the driving magnetic fields. As shown in Figures 20 and 21, two lifting cycles per revolution occur.
  • the shape of the anchor is shown in perspective in Figure 22.
  • Figure 20 we have two guide poles (44).
  • the relative movement of the armature outer surface to the stator has “nodes” at these points.
  • This machine also needs a starting device (not shown) for starting from the position shown.
  • Such machines with several (ideally min. 3) magnetic poles on the stator, which attract the armature with magnetic forces, can also be easily used to guide the armature in the radial direction:
  • the distance between armature and stator becomes electronic, for example regulated and kept constant by varying the magnetic forces.
  • this device also serves as a magnetic, practically frictionless magnet warehouse. With two such devices, the shaft or the piston is stored cleanly.
  • the stroke length and the form of movement can be varied by detaching the anchor from a guide point or by changing guide points. (This also applies to variant a with coils in the armature). By adjusting the stroke length of the piston, the delivery rate can be adjusted for pumps, for example. (See also claim 20).
  • the operation of the electric rotary reciprocating machine in the most common designs with the different types of current can be found in claim 9.
  • Alternative design The stator on the outside has the described functions and features of the armature. Similarly, the armature has the descriptive functions and features of the stator. This can be imagined as follows: If you exchange the words "stator" and "anchor" with each other, you get an analog but different design.
  • the outer surface of the armature is then to be understood analogously as the inner surface of the stator.
  • the external stator has the oblique or curved shape as described above for the armature.
  • the anchor guides and drifts with its magnet fields the stator so that the stator makes a rotary-lifting movement relative to the armature, etc. In most cases this is the less favorable design: the external stator is usually stationary relative to the surroundings. This makes it easier to supply power to the stator than to the rotating armature. - And this is a big advantage of this system with an anchor without coils.
  • a swashplate-like shaft and transmission element result in a torque from the lifting force or vice versa. So that the piston, the swash plate-like shaft and the guide element are not hindered in their movements, the connection between the transmission element and the cylinder is articulated.
  • the exact geometric requirements are described in claim 5.
  • Examples 1 and 6 show three examples of many possibilities.
  • the example in Figure 1 works without a ball joint with two interlocking joints. The inner joint only transmits radial forces and is axially displaceable. The outer joint with the axis of rotation perpendicular to the plane of the drawing also transfers axial forces. (NB: central shaft (14) see claims 21 and 22).
  • the swashplate-like shaft is molded into the piston.
  • the joint is designed as a ball joint.
  • Figures 6 a and b differ only in the different types of compensation for the longitudinal displacement of the joint point. In the positions shown, the pivot point is closest to the cylinder axis. After a quarter turn, the pivot point has moved a little away from the cylinder axis.
  • the arrangement of two such devices per rotary piston is also possible here. This can compensate for the eccentric application of force to the piston.
  • the cylinder part surrounding the hollow shaft and the hollow shaft are designed as an electric motor or an electric generator. (Claim 12) -
  • the rotation of the hollow shaft can be transmitted directly to the outside by, for example, the hollow shaft carrying a ring gear which is in engagement with another gear or a gear.
  • a spatial cam track (Fig. 9..11, item 3) is responsible for the piston movement, for example in the form of a cam disc or a circumferential groove, which is supported on guides (4), such as rollers or sliders.
  • the spatial cam track (item 3) is normally directly connected to the piston (2) and reproduces the stroke kinematics "program" stored in its cam shape with every turn.
  • the reverse arrangement is also conceivable, namely the guides on the piston and the cam track attached to the cylinder.
  • any integer number of lifting cycles per full revolution is possible - and any kinematics of the movement. If there are several lifting cycles per revolution, several guides can also be installed on the circumference. This prevents an eccentric force attack on the piston.
  • Claim 13 solves the following problem: Figure 13 clearly shows that the cam tapered and thickened again. This is due to a fixed attachment of the guide rollers. With a rocker (Fig. 12) the thickness of the cam remains constant over the entire circumference.
  • the classic crank mechanism in the reciprocating piston machine drives the piston in a temporally sinusoidal stroke movement with superimposed harmonics.
  • the piston thus remains somewhat longer in the area of bottom dead center than in the area of top dead center.
  • a different course of the piston movement ie a different stroke kinematics, would be desirable.
  • the lifting kinematics of the rotary reciprocating machine according to claims 4, 9, 7 and 13 can be chosen freely and match the application. In the other claims regarding the generation of the piston movement, the lifting kinematics can also be selected to a certain extent. Claim 18 mentions the geometric sizes with which the lifting kinematics of these systems are influenced. Application examples are also listed.
  • the purpose of changing the synchronization between piston rotation and the lifting movement can be, for example: - Adaptation of the control times to the operating point of the machine (speed, load etc.) - Switching the control times to reverse running for engines without a reverse gear (e.g. large marine diesel).
  • Stroke length adjustment devices are normally used to change the delivery volume of a pump or the displacement volume of a (hydraulic) motor, for example in hydrostatic transmissions.
  • the shaft takes part in the stroke movement of the piston and then compensate for the stroke movement of the shaft at another point, for example on the front of the machine.
  • the shaft is easily sealed, for example with rod seals (analogous to the piston rings on the reciprocating piston engine, but with an internal seal!).
  • Diaphragms or bellows can also transmit the torque with their torsional rigidity (and strength). They take up the stroke movement with their high elasticity in the axial direction. These designs are very cheap and practically frictionless.
  • Piston shapes according to Figure 5 c..e are suitable for this, for example. Piston shape and stroke length must be coordinated so that the pistons remain engaged with each other at every stroke position. In order to reduce the friction, the force can be transmitted indirectly via rolling elements instead of directly via sliding surfaces lie between the two piston surfaces.
  • the rotation of the piston on the cylinder wall can be used to achieve a hydrodynamic lubrication state (floating on the lubrication film).
  • Mixed friction usually occurs here with the conventional reciprocating piston engine. In addition, this increases the ability to absorb any lateral forces that may be present.
  • the conventional crank mechanism generates a transverse force on the piston, which changes in amount and direction with the crankshaft rotation (cause of the piston tipping). With the rotary reciprocating machine, it depends on the type of construction whether lateral forces occur at all: Shear forces are present on the machines with only one stroke cycle per revolution and only one device for generating movement per piston (exception: certain types of claim 4).
  • the eccentric force application creates a moment on the piston, which manifests itself as a pair of transverse forces.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Compressor (AREA)
  • Transmission Devices (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Massaging Devices (AREA)
EP87810206A 1986-04-04 1987-04-03 Machine alternative à pistons rotatifs Expired - Lifetime EP0240467B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87810206T ATE68556T1 (de) 1986-04-04 1987-04-03 Dreh-hubkolben-maschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH131686 1986-04-04
CH1316/86 1986-10-01

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP90100553.8 Division-Into 1987-04-03
EP90100552.0 Division-Into 1987-04-03

Publications (2)

Publication Number Publication Date
EP0240467A1 true EP0240467A1 (fr) 1987-10-07
EP0240467B1 EP0240467B1 (fr) 1991-10-16

Family

ID=4207589

Family Applications (3)

Application Number Title Priority Date Filing Date
EP90100553A Expired - Lifetime EP0369991B1 (fr) 1986-04-04 1987-04-03 Moteur alternatif à pistons tournant
EP90100552A Expired - Lifetime EP0369990B1 (fr) 1986-04-04 1987-04-03 Moteur alternatif à pistons tournant
EP87810206A Expired - Lifetime EP0240467B1 (fr) 1986-04-04 1987-04-03 Machine alternative à pistons rotatifs

Family Applications Before (2)

Application Number Title Priority Date Filing Date
EP90100553A Expired - Lifetime EP0369991B1 (fr) 1986-04-04 1987-04-03 Moteur alternatif à pistons tournant
EP90100552A Expired - Lifetime EP0369990B1 (fr) 1986-04-04 1987-04-03 Moteur alternatif à pistons tournant

Country Status (10)

Country Link
EP (3) EP0369991B1 (fr)
JP (1) JPH0794801B2 (fr)
KR (2) KR960000435B1 (fr)
AT (3) ATE68556T1 (fr)
AU (1) AU7209387A (fr)
CA (1) CA1308155C (fr)
DE (3) DE3788358D1 (fr)
ES (3) ES2026942T3 (fr)
GB (3) GB2198788B (fr)
WO (1) WO1987005964A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0461123A1 (fr) * 1989-01-24 1991-12-18 Mitchell Stirling Mach Syst Dispositif a cycle stirling.
WO1993023655A1 (fr) * 1992-05-12 1993-11-25 Hugh Edward Fisher Dispositifs comportant un piston et un cylindre
EP0680546A4 (fr) * 1991-10-15 1994-07-04 Mansour Almassi Moteur a combustion interne dote de pistons rotatifs.
EP0691467A1 (fr) * 1994-07-09 1996-01-10 Harald Hofmann Moteur à gaz chaud avec un dispositif à déplacement rotatif

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8907984D0 (en) * 1989-04-10 1989-05-24 Szyler Jan Rotary engine
NL9000078A (nl) * 1990-01-11 1991-08-01 Philips Nv Motor-compressor eenheid.
GB2280710A (en) * 1993-08-04 1995-02-08 Keith Andrew Maclaughan Rotating and reciprocating piston i.c. engine.
GB2287753B (en) * 1994-03-22 1997-12-10 Joanne Spinks Two stroke engine
CZ219997A3 (cs) * 1997-07-11 1999-01-13 Pavel Wenzel Motor s vnějším spalováním
EP0978932A1 (fr) * 1998-08-06 2000-02-09 S.C. NDR Management S.r.l. Appareil ayant un rotor et un stator
DE112008001613T5 (de) * 2007-06-18 2010-05-20 Cold Power Systems Inc., Calgary Energieüberführungsmaschine und Verfahren
RU2540025C2 (ru) 2009-07-02 2015-01-27 Хас-Мондомикс Б.В. Устройство и способ для нагнетания текучих масс
EA034460B1 (ru) 2014-08-25 2020-02-11 Басф Се Способ удаления сероводорода и диоксида углерода из потока текучей среды

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB282125A (en) * 1926-07-19 1927-12-19 Cecil Law Improvements in or relating to two-stroke cycle internal combustion engines
US2352396A (en) * 1942-02-20 1944-06-27 Kenneth R Maltby Internal-combustion engine
US2473936A (en) * 1947-10-18 1949-06-21 Burrough Joe Internal-combustion engine
DE3038673A1 (de) * 1980-10-14 1982-05-27 Wilfried 3176 Meinersen Schwant Antriebsmaschine, inbesondere brennkraftmaschine mit kurbelwellenfreier kraftuebertragung und schlitzgesteuertem ladungswechsel

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2532106A (en) * 1946-12-06 1950-11-28 Korsgren Theodore Yngve Multiple opposed piston engine
CH457070A (de) * 1965-11-19 1968-05-31 Polyprodukte Ag Rotierender Antrieb
DE2623234A1 (de) * 1976-05-24 1977-12-01 Alberto Kling Elektromagnetische antriebsvorrichtung
FR2510181A1 (fr) * 1981-07-21 1983-01-28 Bertin & Cie Convertisseur d'energie thermique en energie electrique a moteur stirling et generateur electrique integre

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB282125A (en) * 1926-07-19 1927-12-19 Cecil Law Improvements in or relating to two-stroke cycle internal combustion engines
US2352396A (en) * 1942-02-20 1944-06-27 Kenneth R Maltby Internal-combustion engine
US2473936A (en) * 1947-10-18 1949-06-21 Burrough Joe Internal-combustion engine
DE3038673A1 (de) * 1980-10-14 1982-05-27 Wilfried 3176 Meinersen Schwant Antriebsmaschine, inbesondere brennkraftmaschine mit kurbelwellenfreier kraftuebertragung und schlitzgesteuertem ladungswechsel

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0461123A1 (fr) * 1989-01-24 1991-12-18 Mitchell Stirling Mach Syst Dispositif a cycle stirling.
EP0461123A4 (en) * 1989-01-24 1992-03-11 Mitchell/Stirling Machines/Systems, Inc. Improved sibling cycle piston and valving method
EP0680546A4 (fr) * 1991-10-15 1994-07-04 Mansour Almassi Moteur a combustion interne dote de pistons rotatifs.
US5441018A (en) * 1991-10-15 1995-08-15 Almassi; Mansour Internal combustion rotary piston engine
EP0680546A1 (fr) * 1991-10-15 1995-11-08 ALMASSI, Mansour Moteur a combustion interne dote de pistons rotatifs
WO1993023655A1 (fr) * 1992-05-12 1993-11-25 Hugh Edward Fisher Dispositifs comportant un piston et un cylindre
GB2281354A (en) * 1992-05-12 1995-03-01 Hugh Edward Fisher Piston and cylinder devices
EP0691467A1 (fr) * 1994-07-09 1996-01-10 Harald Hofmann Moteur à gaz chaud avec un dispositif à déplacement rotatif

Also Published As

Publication number Publication date
GB8928578D0 (en) 1990-02-21
CA1308155C (fr) 1992-09-29
WO1987005964A1 (fr) 1987-10-08
ATE97992T1 (de) 1993-12-15
GB2226710B (en) 1990-12-05
KR960000435B1 (ko) 1996-01-06
EP0369990B1 (fr) 1993-12-01
GB8728277D0 (en) 1988-01-13
GB2226612B (en) 1990-12-05
ATE97991T1 (de) 1993-12-15
AU7209387A (en) 1987-10-20
EP0369991B1 (fr) 1993-12-01
GB2226710A (en) 1990-07-04
EP0240467B1 (fr) 1991-10-16
EP0369991A1 (fr) 1990-05-23
DE3788357D1 (de) 1994-01-13
ES2048328T3 (es) 1994-03-16
GB2198788A (en) 1988-06-22
KR960000436B1 (ko) 1996-01-06
JPS63502916A (ja) 1988-10-27
DE3773724D1 (de) 1991-11-21
GB2198788B (en) 1990-12-05
JPH0794801B2 (ja) 1995-10-11
ES2026942T3 (es) 1992-05-16
GB8928577D0 (en) 1990-02-21
ATE68556T1 (de) 1991-11-15
EP0369990A1 (fr) 1990-05-23
KR880701314A (ko) 1988-07-26
DE3788358D1 (de) 1994-01-13
GB2226612A (en) 1990-07-04
ES2048327T3 (es) 1994-03-16

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