EP0184484A1 - Drehkolbenmaschine und mit der Kurbel gekoppelter Ring - Google Patents

Drehkolbenmaschine und mit der Kurbel gekoppelter Ring Download PDF

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Publication number
EP0184484A1
EP0184484A1 EP85402172A EP85402172A EP0184484A1 EP 0184484 A1 EP0184484 A1 EP 0184484A1 EP 85402172 A EP85402172 A EP 85402172A EP 85402172 A EP85402172 A EP 85402172A EP 0184484 A1 EP0184484 A1 EP 0184484A1
Authority
EP
European Patent Office
Prior art keywords
piston
crank
crown
axis
angle
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
EP85402172A
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English (en)
French (fr)
Other versions
EP0184484B1 (de
Inventor
Jean Claude Janicki
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.)
Sanofi SA
Original Assignee
TECNALOR SA
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 TECNALOR SA filed Critical TECNALOR SA
Priority to AT85402172T priority Critical patent/ATE41695T1/de
Publication of EP0184484A1 publication Critical patent/EP0184484A1/de
Application granted granted Critical
Publication of EP0184484B1 publication Critical patent/EP0184484B1/de
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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement

Definitions

  • the present invention relates to rotary piston machines, in particular to rotary piston compressors, comprising a cylindrical chamber, in which are arranged an eccentric or crank part of a shaft coaxial with said chamber, an annular rotary piston being able to roll in contact. of the chamber wall and a piston drive ring mounted with clearance inside thereof, the timing of the piston on its raceway being ensured by elastic means.
  • French patent 2280808 only delaying the detachment of the piston while maintaining the angle formed between the line connecting the center of the chamber to the center of the piston with the line connecting the latter center to the center of the eccentric to a optimum value between 20 ° and 40 °.
  • the rotor is constituted by a cylindrical jacket freely mounted in the chamber around the shaft and kept in contact with the wall of said chamber thanks to a rolling device with movable mounting, which consists of a lever wedged on the shaft and carrying at one end a roller and at the other end an arm ending in a roller, a spring being provided to separate the arm from the lever.
  • French patent 2223570 recommending the mounting of the rotary piston on an eccentric drive ring secured to the eccentric of the shaft, the angle made by the straight line connecting the axis of the shaft to the axis of the eccentric part with the straight line which connects the latter axis to the central axis of the eccentric crown is between 70 ° and 1100, in such a way that the piston rolls while being applied on the interior wall of the casing and that, once a certain release pressure is reached, the piston moves away from the wall of the casing.
  • Such a compressor does not perform mechanical setting of the piston in operation, but only drives the piston by means of the eccentric ring.
  • the present invention relates to a machine in which one realizes both a good drive of the piston and its setting on the bore of the chamber, while preventing its detachment in the high pressure zone, without this embodiment comprising the mounting mechanical with adjustment of the eccentric or mounting on ball bearings directly on the eccentric, necessarily requiring costly precision in terms of machining and assembly of the machine.
  • the rotary piston machine in particular rotary piston compressor, comprising a cylindrical chamber, in which are arranged an eccentric or crank part of a shaft coaxial with said chamber, an annular rotary piston being able to roll in contact with the wall of the chamber and a coaxial crown for driving the piston mounted inside the latter, so as to be able to slide relative to the piston, the timing of the piston on its raceway being ensured by elastic compensation means bearing on the crank or the shaft and on the bore of the crown, further comprising a flap dividing the free space around the piston into two variable volume compartments is characterized in that the crown is driven in rotation by means of a coupling member of the crank and the crown, so that it can pivot around a common axis.
  • the coupling member is a pin mounted in a yoke.
  • the journal is mounted in a bore of the crank and in a yoke secured to the crown.
  • a clevis secured to the crank and a bore made in the crown.
  • the timing of the piston on its raceway can be ensured by elastic means of compensation with various progressive adjustment.
  • a spring is mounted transversely upstream of the point of contact of the piston and of the wall of the chamber with respect to the direction of rotation, bearing on the crown and on the crank, so that the straight line d he action of the spring passes through the axis of the shaft and is perpendicular to the right connecting the center of the piston and the center of the journal.
  • the spring is housed between a centering stud fixed to the crown and a cylindrical housing with counterbore made in the crank, the bottom of the housing being parallel to the right connecting the centers of the piston and the crank.
  • the compressor of a refrigeration machine according to the invention shown in FIGS. 1 and 2 comprises a central body of compressor 2 provided with two front external flanges 11 and rear 12, crossed by a motor shaft 4 with axis 0 1 .
  • the body 2 contains a coaxial cylindrical chamber of the shaft 4, the internal wall 10 of which constitutes the raceway of the piston.
  • the shaft 4 is made integral with an eccentric or crank 3.
  • a rotary piston 5 of axis 0 2 of diameter smaller than that of the chamber is placed inside of the latter, so as to be able to roll in contact with the wall of the chamber, while a movable drive ring 6 is mounted inside the piston 5, so as to be able to slide relative to the piston according to the sliding surface 7.
  • the crown 6 is provided with a clevis 8, 9 and the end of the crank 3 has a bore 24, so as to be able to couple the crown 6 and the crank 3 by means of a pin 0 3 axis which can freely rotate in bore 24.
  • the virtual piston drive rod 5 is represented by the right connecting the center of the crown and of the piston 0 2 to the center of the journal 0 3 .
  • the body of the compressor 2 contains, under the cylinder head 34 provided with the cylinder head gasket 37, the usual members, such as suction and discharge pipes, the latter provided with two valves 17, HP outputs 41,42, as well as a flap separation 15 tilting about its axis 16 and provided with sealing segments 54.
  • the flap 16 separates the interior of the cylinder in HP chamber 13 and BP chamber 14, the point of contact of the end of the flap and of the piston 5 being effected by means of the bearing surface 29 of the bevel cut flap, in the central axis of the cylinder at point G.
  • the usual equipment of a compressor includes a lubricant reservoir 38 with its level control plug 39.
  • the motor shaft 4 rests in bearings 43,44, it is provided with rotary seals 31 and a bubbling spoon 32 and a balancing weight 33.
  • Centering feet 35 equip the rear and front flanges of the stator.
  • Spider legs 40 serve to lubricate the plain bearing of the movable crown and of the piston.
  • the lateral sealing of the piston 5 is ensured by circular segments 36.
  • the wedging means used to take up the initial mounting clearance and the wear clearance consist, according to FIGS. 2 and 3, of a spring 30 of compensation working in compression, whose axis of action 23 (FIG. 11) is perpendicular to the line connecting the center of the crown 0 2 and the center of the pin 0 3 .
  • One of the ends of the spring 30 is supported on a centering shoe 52, integral with the crown 6 and the other in a centering counterbore 53 present on the motor shaft 4.
  • the piston 5 is mounted on a needle bearing 22 and the compensation device comprises a pair of wedges with conical slopes 55 biased by a locking spring 57 with an axis 61, the outer surface 60 of the wedge 55 of rounded shape taking support on a contact shoe 59 secured to the crown (see FIG. 14).
  • a line 01E can be drawn connecting the center 0 1 of the tree at point E. It is with respect to this line that we define the wedging angle ⁇ 1 , between the line 0 1 E and the line 0 1 0 3 connecting the center 0 1 of the tree in the center of the trunnion.
  • the angle ⁇ 1 is therefore the angle by which the axis of the journal 0 3 is offset, relative to the line 01E in the direction of rotation of the shaft.
  • this angle must be carefully chosen. Indeed, the angle ⁇ 1 is mathematically linked to the value of the clearance J between the piston and the wall of the chamber. This clearance J is calculated and measured when, the effects produced by elastic compensation means being canceled, the axis of the piston 0 2 is located in alignment with the axes 0, and 0 3 of the shaft and the journal, on the line of alignment of these axes.
  • the graph in FIG. 5 represents a curve 48 giving the variation of the clearance J in 10 -1 mm as a function of the angle ⁇ 1 in radians. We see that the variation is almost linear for values of J greater than 1 mm.
  • the values of J and ⁇ 1 are mathematically linked and can be calculated for given dimensions of the chamber, the crank arm and other parameters of the construction.
  • FIG. 4 represents, for a clearance of 2.5 mm corresponding to an angle Ux of approximately 36 °, a variation of the reaction force Re expressed in decanewton at the sliding contact point E of the piston on the wall of the chamber in function of the crank angle w in radians, i.e. the instantaneous angular position of the straight line 0 1 E.
  • This curve shows an equilibrium point 45 for a crank angle value w 1 to which the force diagram of FIG. 10 corresponds, where the reaction force Re at the point of contact E is zero.
  • the curve has a maximum at 46 corresponding to a value of the crank angle w located between 0 ° and w 1 for which the reaction force Re at the contact point E is maximum.
  • This negative reaction force Re has a minimum at 47, the effect of which must be combated by the use of elastic compensation means, such as springs or a combination of shims and springs (see the force diagram, FIG. 11).
  • FIG. 6 presents a curve 49 of variations in the compression efficiency in percent as a function of the setting angle ⁇ 1 in radians.
  • the ascending part of the curve corresponds to the low values of ⁇ 1 which should theoretically be chosen.
  • the reaction force Re the variations of which as a function of the crank angle w are shown in FIG. 4, can reach prohibitive values incompatible with the tolerable forces that can be imposed on the materials due to their resistance. to break and wear quickly.
  • the reaction on the motor shaft is too strong and as a result of the increase in mechanical forces the efficiency decreases.
  • the smaller ⁇ 1 the greater the forces exerted on the piston and the journal which generate energy losses by transformation into friction heat.
  • FIGS. 7 and 8 show the curves 50 and 51 showing the variations of the forces Re expressed in decanewton as a function of the value of the clearance J in 10 -1 mm, corresponding respectively to the maximum reaction force at the contact point E ( point 46 of the curve according to FIG. 4) and at the maximum negative reaction force (point 47 of the same curve).
  • the positive reaction force Re decreases when the clearance J increases. This force tends towards infinity for a zero clearance, which would direct the constructor towards the largest possible clearance.
  • a range of angles ⁇ 1 is chosen in FIG. 5 corresponding to the desired efficiency. For reasons of resistance of the materials mentioned above, we will choose greater than 20 °, or better, greater than 30 °. To know the positive and negative reactive forces to which the materials will be subjected, we will draw force diagrams, according to Figure 4 for each of the chosen values of the angle ⁇ 1 .
  • Figures 9, 10 and 11 show the force diagrams for different crank angles w exerted in a compressor, where the setting angle ⁇ 1 is 32 ° 64 ′ and the play of 5 mm. These diagrams correspond, respectively, with regard to FIG. 9, to any crank angle w between 0 ° and w 1 (FIG. 4), that is to say where the force Re is positive, with regard to the figure 10, at an equilibrium angle w 1 (point 45, figure 4) just before the detachment of the piston from its raceway and, as regards figure 11, at an angle between w 1 and w 2 ( point 47, figure 4) in the separation zone where the negative Re force is maximum.
  • FIG. 4 any crank angle w between 0 ° and w 1
  • FIG. 4 any crank angle w 1 (point 45, figure 4) just before the detachment of the piston from its raceway and, as regards figure 11, at an angle between w 1 and w 2 ( point 47, figure 4) in the separation zone where the negative Re force is maximum.
  • Rc represents the circle described by the radius of the cylinder Rc having its center 0 1 ,
  • the piston is in equilibrium for a crank angle w between 0 ° and w 1 ( Figure 4). It is subjected to a torque resulting from the positive PPc force which represents the pressure force prevailing in the HP chamber and passing through the center of the piston 02.
  • the letter a designates the arm of the lever which makes it possible to calculate the torque acting on the axis 0 3 of the journal and which keeps the piston applied in its path bearing for a rotation of the crankshaft corresponding to an angle of 0 ° to w 1 in radians.
  • FIG. 10 represents the piston in equilibrium for an angle w equal to w 1, that is to say just before the detachment of the piston.
  • FIG. 11 represents a force diagram for an angle w comprised between w 1 and w 23, that is to say in the separation zone.
  • the force Re becomes negative and reaches its maximum for an angle w 2 .
  • This force is exerted via the lever arm b and forms a torque tending to detach the piston from its point of contact E with the cylinder.
  • the effect of the negative force Re is compensated by the action of one or more springs 30 ( Figures 11 and 12), whose torque FR x 0 1 0 3 cos ⁇ 3 is equal to the pair Re x b.
  • the bearing face 62 of the spring 30 on the crown is parallel to the straight line 25 connecting the centers of the piston 0 2 and of the journal 0 3 and its line of action 23 passing through the center 0 1 of the shaft is perpendicular to the right 25.
  • the calculation of the spring force must take into account several factors, such as the working pressure in the HP chamber and the dimensions of the chamber and the piston.
  • the spring 30 is disposed upstream of the contact point E with respect to the direction of the piston bearing (FIG. 2), its axis 67 passes through the axis 0 1 of the shaft and is perpendicular to the straight line 25. It is housed between a centering stud 65 fixed to the crown and a cylindrical housing with counterbore 64 formed in the crank and the bottom 66 of which is parallel to the straight line 25 (FIG. 12).
  • the device using one or more springs to keep the piston applied on its raceway and to compensate for the negative force Re represents a first solution for setting the piston.
  • Other compensation and setting means consist in using wedges with conical slopes urged by one or more springs and allow a progressive setting of setting.
  • a concave housing formed by two inclined longitudinal flats 58 to accommodate a pair of wedges 55 with conical slopes 58 of opposite direction.
  • the crank block has two slopes at the location of the housing, the angle of orientation of each corresponding to the slope of the wedge which is housed there.
  • the conical slopes of the housing and shims are inclined at an angle ⁇ 4 relative to the axis 0 1 of the shaft 4. At the two transverse ends of the housing are housed the shims 55.
  • the faces of shims opposite the sides with a slope of angle ⁇ 4 and bearing on a flat 62 or shoe which the crown 6 has at this location are convex and rounded, so that the shims are supported on their hooves according to a generatrix designated by K.
  • the longitudinal plane of symmetry 63 of wedges passes through the center 0 1 .
  • the two wedges 55 are biased in opposite directions by a spring 57 working under compression, the centering axis 61 of which is housed at the two ends in the wedges.
  • the thrust of the wedges 55 exerted against the shoe 62 of the crown is perpendicular to the right connecting the axis of the piston 0 2 and the axis of the journal 0 3 .
  • FIG. 15 and 16 Another embodiment of shims is shown in Figures 15 and 16. Instead of being oriented at an angle ⁇ 4 relative to the axis O 1 of the shaft 4, the slope 71 of the shim 70 is inclined transversely by with respect to the axis 0 1 and in particular of an angle ⁇ 5 with respect to the straight line connecting the center 0 3 of the journal and the center 0 2 of the piston. To this end, the housing provided for the shim is between the longitudinal flat 71 of the crank 3 and the flat 72 that has the bore of the crown 6.
  • the shim 70 one longitudinal face of which has a slope of angle ⁇ 5 , is pierced on a lateral face of the two blind housings 73 to accommodate the ends of the two springs 74 working under compression, the opposite ends of which are retained by centering studs 75 placed on a flat part of the crown 6.
  • wedges The action of wedges is exerted along a transverse straight line with respect to the axis of the shaft 4 and has the effect of pushing the crown 6 of the crank in the direction perpendicular to said straight line.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)
  • Compressor (AREA)
  • Hydraulic Motors (AREA)
  • Transmission Devices (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Acyclic And Carbocyclic Compounds In Medicinal Compositions (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
EP85402172A 1984-11-13 1985-11-12 Drehkolbenmaschine und mit der Kurbel gekoppelter Ring Expired EP0184484B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85402172T ATE41695T1 (de) 1984-11-13 1985-11-12 Drehkolbenmaschine und mit der kurbel gekoppelter ring.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8417307A FR2573137B1 (fr) 1984-11-13 1984-11-13 Machine a piston rotatif et couronne accouplee a la manivelle.
FR8417307 1984-11-13

Publications (2)

Publication Number Publication Date
EP0184484A1 true EP0184484A1 (de) 1986-06-11
EP0184484B1 EP0184484B1 (de) 1989-03-22

Family

ID=9309551

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85402172A Expired EP0184484B1 (de) 1984-11-13 1985-11-12 Drehkolbenmaschine und mit der Kurbel gekoppelter Ring

Country Status (12)

Country Link
US (1) US4759697A (de)
EP (1) EP0184484B1 (de)
JP (1) JPS61126391A (de)
KR (1) KR920001968B1 (de)
CN (1) CN1005074B (de)
AT (1) ATE41695T1 (de)
BR (1) BR8505704A (de)
DE (1) DE3569011D1 (de)
ES (1) ES8706906A1 (de)
FR (1) FR2573137B1 (de)
IE (1) IE56884B1 (de)
PT (1) PT81477B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3164737A1 (fr) * 2024-07-22 2026-01-23 Valeo Japan Co., Ltd. Compresseur a piston roulant

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JPH03113527A (ja) * 1989-09-27 1991-05-14 Yokogawa Electric Corp 回転磁気メモリの制御装置
JPH0744427A (ja) * 1993-07-30 1995-02-14 Nec Corp ディスクのデータ整列方式
CN1267792A (zh) * 1999-03-22 2000-09-27 彭力丰 滚动转子式压缩机
CN100441871C (zh) * 2003-06-17 2008-12-10 乐金电子(天津)电器有限公司 密封旋转式压缩机的偏心活塞装置
CN104074762A (zh) * 2014-06-12 2014-10-01 珠海凌达压缩机有限公司 旋转式压缩机的泵体结构及旋转式压缩机
CN105604982A (zh) * 2016-01-29 2016-05-25 南通广兴气动设备有限公司 一种旋压高压气泵
CN105545739A (zh) * 2016-01-29 2016-05-04 南通广兴气动设备有限公司 一种旋压真空泵
RU2664727C2 (ru) * 2017-02-07 2018-08-22 Общество с ограниченной ответственностью Научно-производственное предприятие "Норд-инжиниринг" (ООО НПП "Норд-инжиниринг") Роторно-поршневой двигатель
CN112983816B (zh) * 2021-03-05 2023-05-09 珠海格力节能环保制冷技术研究中心有限公司 压缩机
CN113339429B (zh) * 2021-07-09 2025-01-10 绍兴铁安汽配制造有限公司 一种制动器的楔块总成

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR655802A (fr) * 1927-05-11 1929-04-24 Vacuum Compressor Ab Dispositif au moyen duquel on obtient un contact étanche entre le piston et les parties fixes d'une machine rotative telle qu'un compresseur, une pompe, ou un moteur
GB380313A (en) * 1931-12-11 1932-09-15 John Ekeloef Improvements in rotary pumps or compressors
FR2232674A1 (de) * 1973-06-11 1975-01-03 Little Inc A
DE2853915A1 (de) * 1978-12-14 1980-06-19 Erich Becker Rollkolbenpumpe
EP0078148A1 (de) * 1981-10-20 1983-05-04 Sanden Corporation Vorgespannte Antriebseinrichtung für kreisendes, fluidverdrängendes Maschinenteil

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR582267A (fr) * 1924-05-23 1924-12-15 Dispositif de compresseur d'air, rotatif, à piston cylindrique
US1692639A (en) * 1926-12-11 1928-11-20 Henry L Elsner Pump
FR1256125A (fr) * 1960-02-05 1961-03-17 Perfectionnement apporté aux machines rotatives à rotor excentré
DE2437559A1 (de) * 1974-08-03 1976-02-19 Bosch Gmbh Robert Kompressor
DE2509536A1 (de) * 1975-03-05 1976-09-16 Bosch Gmbh Robert Kompressor mit einem zu seiner antriebswelle exzentrischen rollkolben
JPS5392914A (en) * 1977-01-25 1978-08-15 Nippon Air Brake Co Eccentric driving mechanism of rotary piston type compressor
DE2944198A1 (de) * 1979-11-02 1981-05-07 Bitzer Kühlmaschinenbau GmbH & Co KG, 7032 Sindelfingen Rollkolbenverdichter
DE2946906C2 (de) * 1979-11-21 1985-02-14 Bitzer Kühlmaschinenbau GmbH & Co KG, 7032 Sindelfingen Rollkolbenverdichter

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR655802A (fr) * 1927-05-11 1929-04-24 Vacuum Compressor Ab Dispositif au moyen duquel on obtient un contact étanche entre le piston et les parties fixes d'une machine rotative telle qu'un compresseur, une pompe, ou un moteur
GB380313A (en) * 1931-12-11 1932-09-15 John Ekeloef Improvements in rotary pumps or compressors
FR2232674A1 (de) * 1973-06-11 1975-01-03 Little Inc A
DE2853915A1 (de) * 1978-12-14 1980-06-19 Erich Becker Rollkolbenpumpe
EP0078148A1 (de) * 1981-10-20 1983-05-04 Sanden Corporation Vorgespannte Antriebseinrichtung für kreisendes, fluidverdrängendes Maschinenteil

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3164737A1 (fr) * 2024-07-22 2026-01-23 Valeo Japan Co., Ltd. Compresseur a piston roulant
EP4685352A1 (de) * 2024-07-22 2026-01-28 Valeo Japan Co., Ltd. Rollkolbenkompressor

Also Published As

Publication number Publication date
ES548747A0 (es) 1987-07-01
JPS61126391A (ja) 1986-06-13
ES8706906A1 (es) 1987-07-01
KR860004245A (ko) 1986-06-18
IE852819L (en) 1986-05-13
PT81477B (pt) 1991-05-22
DE3569011D1 (en) 1989-04-27
EP0184484B1 (de) 1989-03-22
BR8505704A (pt) 1986-08-12
IE56884B1 (en) 1992-01-15
PT81477A (fr) 1985-12-01
US4759697A (en) 1988-07-26
KR920001968B1 (ko) 1992-03-07
FR2573137A1 (fr) 1986-05-16
FR2573137B1 (fr) 1987-02-13
ATE41695T1 (de) 1989-04-15
CN85108179A (zh) 1986-08-27
CN1005074B (zh) 1989-08-30

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