EP0371321B1 - Accumulateur de fluide - Google Patents

Accumulateur de fluide Download PDF

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Publication number
EP0371321B1
EP0371321B1 EP89121122A EP89121122A EP0371321B1 EP 0371321 B1 EP0371321 B1 EP 0371321B1 EP 89121122 A EP89121122 A EP 89121122A EP 89121122 A EP89121122 A EP 89121122A EP 0371321 B1 EP0371321 B1 EP 0371321B1
Authority
EP
European Patent Office
Prior art keywords
accumulator
pressure chamber
accumulator according
piston
pressure
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
EP89121122A
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German (de)
English (en)
Other versions
EP0371321A1 (fr
Inventor
Wolfgang Forstner Siegfried Klett
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.)
Individual
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Individual
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 Individual filed Critical Individual
Priority to AT89121122T priority Critical patent/ATE76676T1/de
Publication of EP0371321A1 publication Critical patent/EP0371321A1/fr
Application granted granted Critical
Publication of EP0371321B1 publication Critical patent/EP0371321B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/20—Accumulator cushioning means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
    • F15B2201/312—Sealings therefor, e.g. piston rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/41—Liquid ports

Definitions

  • the invention relates to a fluidic pressure accumulator, with a movable wall, which is arranged between at least one resilient body providing a supporting force and a pressure chamber which can be acted upon by a fluid via a fluidic connection.
  • Such pressure accumulators are used in pneumatic and hydraulic systems and serve to absorb the fluid that expands, for example as a result of an increase in temperature, the pressure in the system being kept as constant as possible. This is particularly important in the case of liquid systems, since an increase in pressure could lead to leaks and destruction of individual components.
  • a so-called expansion tank is common in the chemical industry, which consists of a pressure vessel divided by a rubber membrane. This membrane is acted upon from one side with a chemical liquid and from the other side with air, which is closed in its half of the vessel. When the liquid expands, the membrane is deflected against the air cushion, which is compressed more and more with increasing deflection and exerts a counter pressure.
  • the main disadvantages here are the relatively short lifespan of the membrane in certain cases, the costs associated with the regularly required technical monitoring and the relatively low resistance to extreme temperatures and dependence on temperature fluctuations and mechanical influences. The relatively low aging and corrosion resistance also considerably narrows the area of application.
  • the object of the present invention is therefore to create a pressure accumulator in which the problems mentioned no longer occur and which has advantages over diaphragm or spring accumulators in that it is practically temperature-independent, responds easily at low pressures and absorbs high maximum pressures, and also guarantees a delayed reset for certain applications and is ultimately overload-proof and corrosion-resistant.
  • the resilient body is designed as a wire body which is molded from knitted and / or corrugated and / or rolled and / or interwoven and / or interwoven wire material.
  • Such a fluid pressure accumulator is characterized by a progressive response characteristic, which guarantees an extremely high maximum load capacity with excellent response behavior even at low pressure loads.
  • the working area of the pressure accumulator is consequently very large, and there is no need for complex storage of a large number of spring designs, since the pressure accumulator with one and the same wire body can be used both in cases of low and in cases of high or combined loads.
  • the dynamic load capacity is very good, it can be 5 to 10 times the maximum load possible with non-dynamic static load.
  • the pressure accumulator thus delays relaxation by releasing a stored volume over a longer period of time, which reduces the pulse energy and avoids the harmful or unpleasant effects of the switching shocks.
  • the wire body is insensitive to temperature and less susceptible to corrosion, so that the pressure accumulator is also used in the chemical industry, e.g. B. to the applications described above, can be used particularly advantageously.
  • a wire cushion is described in the magazine "Industriean accorder", No. 94 of November 24, 1982/104, pages 16 and 17. However, its use is limited to the damping of mechanical vibrations in connection with the storage of presses. The advantageous use of wire bodies of the type according to the invention in a fluid pressure accumulator is not taught.
  • a wire body made of stainless steel material has a particularly high resistance to all possible external influences.
  • the movable wall is designed as a movable piston in a corresponding cylinder or housing, which acts on a contact plate for the elastic wire body.
  • a counter contact plate is provided which is connected to the cylinder via at least one tension element and can be expediently adjusted with regard to its distance from the cylinder or the contact plate.
  • a bolt as a tension element which is guided centrally through the elastic wire body, a particularly compact arrangement can be achieved, the external dimensions of the pressure accumulator being hardly larger than those of the wire body itself.
  • the bolt is expediently screwed into the fluidic connection , whereby through holes and / or longitudinal grooves can be provided for supplying the fluid at least in the screw-in area of the bolt.
  • the pressure chamber of the pressure accumulator can also be designed as an edge-side piston bore on the fluidic device, so that a cylinder or housing can be dispensed with as a separate component, which brings about a further cost reduction.
  • Another advantage of the pressure accumulator according to the invention is that it causes a reduction in switching shocks or pressure peaks in valve controls or pumps connected to it. Switching shocks, which cause pressure waves, occur especially when changing the switching state of valves and can cause damage to fluidic devices. With the pressure accumulator according to the invention, the resulting pressure peaks can be damped very well, the damping advantageously being able to take place directly at the point of origin of the fault.
  • the fluid channel carrying the medium to be damped has a jump point and the pressure chamber of the pressure accumulator is connected to this jump point. This ensures that a pressure wave triggered by pressure fluctuations or the like does not run through in a straight line and passes unaffected by the pressure accumulator, but is briefly “jammed” so that the pressure accumulator can respond without problems.
  • a cylinder 10 is provided at one end with an axial, tubular threaded extension 11, which is provided with an external and an internal thread is and serves as a fluidic connection.
  • a bolt 13 is screwed into the threaded inner bore 12 and is provided with a thread at its two end regions.
  • the end region of the bolt 13 screwed into the threaded inner bore 12 has longitudinal grooves 14 on the edge, only one of which can be seen in the figure. These longitudinal grooves 14 extend beyond the threaded extension 11 into the interior of the cylinder 10 and thereby allow a fluid F, preferably a liquid, to flow into the cylinder.
  • a fluid F preferably a liquid
  • a piston 15 is slidably arranged on the pin 13.
  • This piston 15 is a sheet metal part by deep drawing, bulging, beading, pressing, flanging, stamping or the like. produced.
  • this piston 15 carries an outer piston seal 16 which is designed as an annular seal and which is held in a circumferential channel 17 which is U-shaped in cross section.
  • the piston 15 has a radially inwardly offset step 18, which engages in a corresponding indentation of a contact plate 19. This contact plate 19 protrudes radially over the cylinder 10 and rests against its open end.
  • an inner piston seal 21 is arranged, which seals the piston 15 to the bolt 13.
  • the piston 15 can be welded, soldered or pressed to the contact plate 19. However, it is also possible that the two parts are only inserted loosely into one another. In this case, the front end of the piston 15 must lie sealingly against the inner piston seal 21.
  • An elastic, cylindrical body 22 with an axial through opening 23 is formed as a body molded from wire material.
  • the wire material is knitted, corrugated, rolled, woven and / or intertwined. These types of structuring can be combined with one another in a variety of ways. Due to the compression and compression, the wire material lies close together and forms a compact, elastically reversibly deformable body. A very thin wire material is used, the wire thickness of which is preferably less than 1/50 of the diameter of the body.
  • This elastic body 22 is between an abutment surface of the abutment plate 19 and a facing abutment surface a correspondingly shaped counter plate 24 is held.
  • This counter abutment plate 24 is also pushed onto the bolt 13, the fixing being carried out by means of a washer 25 and two nuts 26 which are screwed onto the threaded end of the bolt 13.
  • the counter bearing plate 24 also has an indentation 27 in which the nuts 26 are arranged. The radial position is fixed by the indentations 27 and corresponding indentations in the elastic body 22.
  • a tubular stop body 28 is arranged in the through opening 23 of the elastic body 22 and limits the axial deformation of the elastic body 22. This stop body 28 is attached to the counter-contact plate 24.
  • the entire arrangement forming the pressure accumulator is screwed by means of the threaded extension 11 into a corresponding connection of a fluidic system, which is connected, for example, to a valve channel. If the fluid expands in this system, it gets there over the longitudinal grooves 14 in the cylinder 14 and moves the piston 15 to the right, whereby the contact plate 19 also moves to the right against the counter-contact plate 24, the distance to the cylinder 10 is fixed by means of the bolt 13. As a result, the elastic body 22 is compressed and moves the piston 15 to the left again as soon as the fluid contracts again. The displacement of the contact plate 19 is limited by the stop body 28.
  • a preload can be set, for example, which determines the release pressure for the movement of the piston 15.
  • a cylinder 30 is not designed here as a separate component, but as an edge-side bore in a solid housing 31 of a fluidic component.
  • a concentric, fluidic feed channel 32 opens into the front end of the cylinder 30 and is provided with an internal thread for receiving the bolt 13.
  • a piston 33 is solid and connected in one piece to a contact plate 34 for the elastic body 22. The piston 33 is in turn with an outer piston seal 35 in a circumferential groove and an inner piston seal 36 provided in an inner groove.
  • a counter-abutment plate 37 like the abutment plate 34, is designed as a solid, flat disc.
  • the bolt 13 is first screwed into the feed channel 32, after which the piston 33 is then pushed onto the bolt 13 and pushed into the cylinder 30. Now the elastic body 22 and the counter abutment plate 37 are pushed onto the bolt 13 and fixed by means of the nuts 26.
  • the remaining mode of operation corresponds to that of the first embodiment.
  • first exemplary embodiment can also be combined with elements of the second exemplary embodiment.
  • first exemplary embodiment can also be provided with a solid piston and / or one piece connected to the contact plate 19, while in the second exemplary embodiment an arrangement of the piston and contact plate corresponding to the first exemplary embodiment can be provided.
  • shoulders can be provided on the contact plate 34 and / or on the counter-contact plate 37 in order to fix the radial position of the elastic body 22.
  • the solid piston 33 can also be designed as a separate component with respect to the contact plate 34.
  • the piston seals shown can also be omitted if e.g. by an appropriate fit or by labyrinth seals or the like. an appropriate seal is guaranteed.
  • the dimensioning of the elastic body 22 can vary widely, e.g. the ratio of its length to its diameter.
  • the cylindrical shape can have a circular, oval, polygonal or similar cross section.
  • the central pin 13 can be omitted if the counter-contact plate is connected via external connecting means, e.g. a housing with which the cylinder 10 or the housing 31 is connected.
  • external connecting means e.g. a housing with which the cylinder 10 or the housing 31 is connected.
  • the pressure accumulators described are preferably suitable for high-pressure cleaners, tensioning systems, brake systems, valve arrangements or the like in which pressure peaks occur or pulsation damping appears to be necessary. Since no gas pressure accumulator is provided, monitoring by the TÜV is also not mandatory.
  • the elastic body is preferably made of stainless steel wire, but other types of wire can be used which have the necessary elastic properties.
  • the requirement for corrosion resistance depends not least on the aggressiveness of the environment or the fluid used.
  • the cylinder 30 is not designed as a separate component here, but is represented by an opening or recess of a housing 40 on the edge.
  • the latter is formed in the exemplary embodiment by a, for example, cuboid intermediate plate 41, or the like, between a valve arrangement 42 indicated by dashed lines and a base or distributor plate 43. is interposed.
  • the intermediate plate 41 for example, two fluid channels 44, 44 'designed as flow channels are provided, which can lead to consumers via the base plate or distributor plate 43 and which can be connected and controlled by means of the valve arrangement 42.
  • Each of the fluid channels 44, 44 ' is preferably in communication with an associated pressure chamber 46, which is the one axial Is assigned to the piston side, while on the other piston side, as already described above, there are elastic bodies 22. If pressure fluctuations occur in the fluid channels 44, 44 'on the part of the flow medium guided therein, the pressure accumulator effects a damping by means of the body 22.
  • the pressure accumulator according to the invention can be switched on.
  • the connection with channels supplying feed and / or control pressure is particularly advantageous. Pulsation damping of high efficiency can take place here, especially if the pressure is and / or gear pumps is supplied.
  • An intermediate plate construction according to FIG. 3 also allows effortless integration into existing systems. Any number of channels formed in the housing 40 can correspond to pressure accumulators 45 as required. It is of course also possible to connect pressure accumulators directly to the channels of a respective fluidic device, e.g. a valve to connect.
  • the pressure chambers 46 are expediently part of the respectively assigned fluid channel 44, 44 'and directly switched on in its channel path.
  • the pressure chambers 46 which are formed by the inner end portion of the associated housing opening 30, communicate with the fluid channel 44, 44 'in the region of a flow baffle 47, which coincides here with a flow deflection point.
  • This has the advantage that the pressure wave does not run past the pressure accumulator, but has an effect on the movable wall 48 formed by a piston in the exemplary embodiment and counteracts this supplied by the body 22 supporting force.
  • the arrangement is such that two channel branches of the fluid channel 44, 44 'from opposite connection surfaces 49 penetrate into the intermediate plate 41, being arranged parallel to one another, but offset by an amount from one another.
  • the ends of the channel branches arranged inside the plate are connected to one another by the pressure chamber 46, the associated housing opening containing the piston or the movable wall 48 extending transversely and preferably at right angles to the course of the fluid channel 44, 44 '.
  • the direction of movement of the movable wall is therefore preferably at right angles to a plane containing the two channel branches and indicated by the section plane IV-IV. It is advantageous here if the respective channel branches dip obliquely into the intermediate plate with reference to the associated connecting surface 49.
  • the counter-abutment surface 24, which has counter-abutment surface 50, is here a component of a hollow cylindrical cap-shaped body 51 which, with a threaded section 52 arranged at the open edge region, fits into a Extension of the housing opening is screwed in.
  • the contact plate 19 having the contact surface 53 is arranged axially displaceably in the cap-shaped body 51. It is expediently, as in the exemplary embodiment according to FIG. 2, formed in one piece with the piston 33 and together with it represents the movable wall 48.
  • two of the elastic bodies 22 are in the direction of movement of the wall 48 arranged in a row. This shows that if necessary, several elastic bodies 22 can be used per pressure accumulator, which can be connected in series and / or in parallel.
  • a step of the housing opening can serve as a stop for the contact plate 19.
  • the pressure accumulator according to the invention can therefore advantageously be used for reducing or damping switching shocks or pressure peaks in fluid channels or lines or other fluidic devices connected to valves, for example directional control valves such as shut-off valves. Also for damping so-called water hammer in In connection with water-carrying systems, for example in the household, and / or in connection with household appliances which work with water, for example washing machines, the pressure accumulator according to the invention can be used effectively.
  • the sandwich construction shown in FIGS. 3 and 4 is only a preferred embodiment.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Claims (12)

1. Accumulateur de pression pour fluide, comportant une cloison (15, 33) mobile qui est placée entre au moins un corps (22) élastique fournissant une force d'appui et une chambre de pression (46) recevant un fluide (F) par un raccord (12, 32) pour fluide, caractérisé en ce que le corps élastique est un corps en fil (22) moulé sous pression à partir d'un matériau en fil tricoté et/ou ondulé et/ou enroulé et/ou tissé et/ou tressé.
2. Accumulateur de pression selon la revendication 1, caractérisé en ce que le matériau en fil est de l'acier spécial.
3. Accumulateur de pression selon la revendication 1 ou 2, caractérisé en ce que l'épaisseur du fil est inférieure à 1/50 du diamètre du corps.
4. Accumulateur de pression selon l'une des revendications 1 à 3, caractérisé en ce que la cloison mobile est un piston (15, 33) se déplaçant dans la chambre de pression (46) et qui, pendant le fonctionnement de l'accumulateur de pression, ressort de la chambre de pression, par une partie de sa longueur et comprime, par une plaque d'application (19, 34), le corps en fil (22), situé à l'extérieur de la chambre de pression (46), s'appliquant par sa zone terminale opposée à la plaque d'application, contre une contre-plaque d'application (24, 37) reliée à l'enveloppe de la chambre de pression (10, 31) par au moins un élément de traction (13, 51).
5. Accumulateur de pression selon la revendication 4, caractérisé par un boulon central (13) servant d'élément de traction qui traverse le corps en fil (22) et le piston (15, 33) jusqu'à la paroi avant de la chambre de pression.
6. Accumulateur de pression selon la revendication 5, caractérisé en ce que le boulon (13), partant du côté de la chambre de pression, peut être vissé dans le raccord (12, 32) pour fluide de l'accumulateur de pression et est pourvu,dans la zone de vissage, de trous de passage et/ou de rainures longitudinales (14) permettant le passage du fluide.
7. Accumulateur de pression selon la revendication 5 ou 6, caractérisé en ce que le boulon (13) porte, sur le côté de la contre-plaque d'application (24, 37), opposé à la plaque d'application (19, 34), des éléments filetés (26) réglables servant de butée à la contre-plaque d'application (24, 37).
8. Accumulateur de pression selon l'une des revendications 5 à 7, caractérisé en ce qu'il est prévu entre la plaque d'application (19, 34) et la contre-plaque d'application (24, 37), un corps de butée (28) de préférence tubulaire, entourant le boulon (13), afin de limiter la déformation du corps en fil (22).
9. Accumulateur de pression selon l'une des revendications 4 à 8, caractérisé en ce que la chambre de pression (46) de l'accumulateur de pression est conçue sous la forme d'un alésage de piston (30) côté bordure, logeant le piston (30), pratiqué sur un dispositif (31) pour fluide, par exemple sous la forme d'une plaque de canal ou une plaque de raccord (41) reliée à une vanne (42).
10. Accumulateur de pression selon l'une des revendications 1 à 9 pour utilisation comme amortisseur afin de réduire les chocs de manoeuvre dans le cas de commandes de vanne ou pour réduire les pointes de pression dans le cas de pompes.
11. Accumulateur de pression selon la revendication 10, caractérisé en ce que le canal de fluide (40, 44′), acheminant le fluide d'amortissement, comporte un point de discontinuité (47) et la chambre de pression (46) de l'accumulateur de pression est raccordée à ce point de discontinuité (47).
12. Accumulateur de pression selon l'une des revendications 1 à 11, caractérisé en ce que pour produire la force d'appui il est prévu plusieurs corps en fil (22) montés les uns derrière les autres et/ou en parallèle.
EP89121122A 1988-11-30 1989-11-15 Accumulateur de fluide Expired - Lifetime EP0371321B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89121122T ATE76676T1 (de) 1988-11-30 1989-11-15 Fluidischer druckspeicher.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3840369 1988-11-30
DE3840369 1988-11-30
DE3916854 1989-05-24
DE3916854A DE3916854A1 (de) 1988-11-30 1989-05-24 Fluidischer druckspeicher

Publications (2)

Publication Number Publication Date
EP0371321A1 EP0371321A1 (fr) 1990-06-06
EP0371321B1 true EP0371321B1 (fr) 1992-05-27

Family

ID=25874692

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89121122A Expired - Lifetime EP0371321B1 (fr) 1988-11-30 1989-11-15 Accumulateur de fluide

Country Status (5)

Country Link
EP (1) EP0371321B1 (fr)
DE (2) DE3916854A1 (fr)
ES (1) ES2031338T3 (fr)
GR (1) GR3005051T3 (fr)
HU (1) HU210419B (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10334763A1 (de) * 2003-07-30 2005-03-17 Lucas Automotive Gmbh Druckspeicher für eine Fahrzeugbremsanlage und mit einem Druckspeicher ausgestattete Fahrzeugbremsanlage

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2105640A1 (de) * 1971-02-06 1972-08-17 Knorr-Bremse GmbH, 8000 München Federspeicherzylinder
DE3441484A1 (de) * 1983-11-30 1986-03-13 KUBOTA, Ltd., Osaka Fahrwerk fuer landfahrzeuge

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE94429C (fr) *
US3383853A (en) * 1966-05-17 1968-05-21 Fed Pacific Electric Co Energy storage mechanism for actuating circuit breakers and the like
FR2456238A1 (fr) * 1979-05-08 1980-12-05 Europ Propulsion Accumulateur d'energie
DE3622445A1 (de) * 1986-07-04 1988-01-21 Schubert Werner Von innen druckstossunempfindlicher hohlkoerper
DE3632988A1 (de) * 1986-09-04 1988-06-30 Schubert Werner Sonde zur minderung von druckstosswirkungen im inneren eines hohlkoerpers

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2105640A1 (de) * 1971-02-06 1972-08-17 Knorr-Bremse GmbH, 8000 München Federspeicherzylinder
DE3441484A1 (de) * 1983-11-30 1986-03-13 KUBOTA, Ltd., Osaka Fahrwerk fuer landfahrzeuge

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Zeitschrift "Industrieanzeiger", Nr. 94, 24.11.1982/104. Jg. Seiten 16 und 17 *

Also Published As

Publication number Publication date
HU896313D0 (en) 1990-02-28
EP0371321A1 (fr) 1990-06-06
GR3005051T3 (fr) 1993-05-24
HUT55873A (en) 1991-06-28
HU210419B (en) 1995-04-28
ES2031338T3 (es) 1992-12-01
DE58901541D1 (de) 1992-07-02
DE3916854A1 (de) 1989-09-28
DE3916854C2 (fr) 1991-02-21

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