EP0230529A2 - Configuration de valves pour accumulateur hydraulique - Google Patents

Configuration de valves pour accumulateur hydraulique Download PDF

Info

Publication number
EP0230529A2
EP0230529A2 EP86114822A EP86114822A EP0230529A2 EP 0230529 A2 EP0230529 A2 EP 0230529A2 EP 86114822 A EP86114822 A EP 86114822A EP 86114822 A EP86114822 A EP 86114822A EP 0230529 A2 EP0230529 A2 EP 0230529A2
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
shut
control
arrangement according
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
EP86114822A
Other languages
German (de)
English (en)
Other versions
EP0230529B1 (fr
EP0230529A3 (en
Inventor
Gerald Lexen
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.)
MAN Truck and Bus SE
Original Assignee
MAN Nutzfahrzeuge AG
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 MAN Nutzfahrzeuge AG filed Critical MAN Nutzfahrzeuge AG
Priority to AT86114822T priority Critical patent/ATE72693T1/de
Publication of EP0230529A2 publication Critical patent/EP0230529A2/fr
Publication of EP0230529A3 publication Critical patent/EP0230529A3/de
Application granted granted Critical
Publication of EP0230529B1 publication Critical patent/EP0230529B1/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
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B2013/0428—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with switchable internal or external pilot pressure source
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87193—Pilot-actuated
    • Y10T137/87209—Electric

Definitions

  • the invention relates to a valve arrangement for connecting a hydraulic pressure accumulator to a hydraulic pump or hydraulic working machine.
  • shut-off valve is arranged, which must be completely leak-tight, in order to prevent the hydraulic machine from being accidentally pressurized and starting, in particular when the hydraulic machine is based on the displacement principle works because a leaking shut-off valve could build up enough pressure over a long period of time to start this machine.
  • the shut-off valve was previously designed as a manually operated shut-off valve that had to be opened and closed as required.
  • shut-off valve In order to achieve an even better use of the excess energy in stationary systems or vehicles, especially if there are frequent changes in the operating state, it is necessary to integrate the shut-off valve in a control or regulating system and no longer by hand, but by Control signals. As tests by the applicant have shown, the coupling of a servomotor with a conventional shut-off valve leads to inadequate results because either the actuating forces become impermissibly high or the switching time of the shut-off valve is too long.
  • the invention has for its object to further develop the known valve arrangement mentioned at the outset such that it can be controlled by means of a control signal without impairing operational safety and is capable of responding quickly to this control signal.
  • shut-off valve arranged in a working line is not actuated directly, but rather by means of a leak-free control valve, the actuation of which requires only relatively small forces.
  • controlled a hydraulic control circuit which in turn provides the actuating forces required to operate the shut-off valve.
  • the shut-off valve has a control cylinder in which an actuating piston is slidably received.
  • This actuating piston carries a valve body that can be hermetically sealed against a valve seat and always seals leak-free even against extremely high pressure drops, provided that a sufficiently high control pressure acts on the actuating piston, because the pressure prevailing on both sides of the valve seat seeks to actuate the actuating piston in this way to move the valve body up from the valve seat.
  • the two outputs of the shut-off valve according to the invention are connected on both sides of the valve seat to a shuttle valve, the third connection of which is connected to the control cylinder of the shut-off valve.
  • the pressure drop that drives the shuttle valve corresponds to the pressure drop across the shut-off valve, with the higher pressure applied to it being applied by the shuttle valve to the control cylinder, so that the pressure on the control piston is always sufficient to ensure that the valve body is sufficient press firmly against the valve seat.
  • the control piston is leak-free sealing in the control cylinder according to a preferred embodiment of the invention, however, that connection of the shut-off valve which is separated from the interior of the control cylinder only by the control piston is connected to the pressure accumulator; as long as the shut-off valve is closed, in particular during those times when the device equipped with the valve arrangement according to the invention is not used, there is therefore no pressure drop across the actuating piston, so that the shut-off valve can also shut off leak-tight over an arbitrary long period of time, as was the case with the previously used manual shut-off valves.
  • shut-off valve To open the shut-off valve there is a leak-free, remotely operated control valve between its control cylinder and the shuttle valve arranged, which in its rest position establishes the connection between the shuttle valve and the control cylinder, on the other hand shuts off the shuttle valve in the working position and relieves the control cylinder against a tank or reservoir.
  • a throttle is arranged between the control cylinder and the control valve or this and the tank or the storage container, which ensures that the control cylinder, in which the above-mentioned high pressure of over 400 bar can prevail, is not approximately is released explosively, which could lead to damage in the control valve, in the lines and also in the shut-off valve.
  • the shut-off valve is designed as a 2/2-way valve in a cartridge design; such a standard valve fulfills all of the above requirements for the shut-off valve according to the invention, forms a ready-to-install unit and can be replaced with another, similar valve with little effort if necessary, e.g. if Safety regulations should prescribe the regular replacement of the shut-off valve.
  • control valve is designed as a directional seat valve, which preferably has an electromagnetic drive.
  • a valve has a valve seat which, when the valve is at rest, hermetically seals its connection to the tank seals so that the control pressure transmitted by the control valve in this operating state cannot escape to the tank.
  • the control valve is also designed so that any pressure forces that occur are directed perpendicular to the movement of its valve body, so that only relatively small actuating forces are required. Because of the small, required channel cross section, the valve body of the control valve only has to travel a relatively short switching distance, so that an electromagnet as an actuator for the control valve is completely sufficient.
  • a pressure measuring point with a pressure sensor or for receiving such a valve is arranged on both sides of the shut-off valve, preferably in the respective control line to the shuttle valve; Via these two pressure measuring points, every pressure relevant for operation and operational safety can be taken off, e.g. the supply pressure in the accumulator, the delivery pressure of the hydraulic machine working as a pump and the like. More. When the shut-off valve is closed, the pressure drop measured must remain constant. If this is not the case, then there is a fault.
  • the two measuring points can be equipped with a device which takes remedial measures in the event of such a fault and / or triggers an alarm.
  • a shut-off throttle is arranged between the pressure accumulator and the tank, which can optionally be provided with a servomotor.
  • This shut-off throttle is used to safely relieve the pressure in the reservoir towards the tank, which is necessary, for example, when repair or maintenance work on the pressure reservoir or on the valve arrangement has to be carried out. It is also possible to connect a servomotor assigned to the shut-off throttle to a monitoring device which is connected to the two measuring points mentioned above, so that the pressure accumulator is automatically emptied when a fault occurs.
  • valves and throttles of the arrangement according to the invention is accommodated in a common block.
  • This block preferably accommodates all elements of the arrangement according to the invention.
  • the various working and control lines of the arrangement according to the invention are thus formed by bores, so that the risk of damage to a connecting line is excluded.
  • This block can advantageously be flanged directly to the pressure accumulator; however, it is equally possible to attach this block wherever this is particularly advantageous for spatial reasons.
  • the block does not have to be easily accessible from the outside, as was the case with the manually operated shut-off valve of the known arrangement mentioned at the beginning.
  • a pressure limiting valve is preferably also arranged, which connects the pressure accumulator to the tank and has the purpose of automatically lowering this excess pressure to a permissible value in the event of an unacceptable excess pressure in the pressure accumulator.
  • Such an impermissible excess pressure can be brought about, for example, by mechanical deformation of the pressure accumulator or its heating. It is thus possible to mount the pressure accumulator together with the valve arrangement according to the invention in a vehicle even at locations where it is exposed to the sun's rays or other heating. Furthermore, the latter configuration ensures that the pressure accumulator does not burst in the event of an accident.
  • the invention thus creates a compact shut-off block with safety functions for hydraulic accumulators with a blocking position, a continuous position and the possibility of emptying the accumulator directly into the oil tank via a blocking throttle.
  • the control pressure for controlling the actual shut-off valve which is preferably designed as a 2/2-way valve in a cartridge construction, is directly derived from the connections for the accumulator or the connected hydraulic unit taken, the higher of the two pressures being selected in order to achieve a reliable holding effect. Furthermore, measuring connections for regulation, control or monitoring are provided.
  • Both the 2/2-way valve in cartridge design and the directional seat valve controlling this are each absolutely sealed when closed, so that any pressure drop due to leakage is reliably avoided even over a long period of time.
  • the shut-off block according to the invention is thus very compact and simple, can be attached to the pressure vessel as well as anywhere in a vehicle, and the valve can be operated remotely, so that the shut-off block according to the invention can be used for the electro-hydraulic control of the accumulator hydraulics is suitable.
  • the simple structure also guarantees safe operation.
  • shut-off block according to the invention is shown schematically.
  • the shut-off block 5 shown has three hydraulic connections, namely the connection P for a hydraulic unit designed either as a pump or working machine, the connection S for a high-pressure or low-pressure accumulator and the connection T for a tank or reservoir.
  • a 2/2-way valve C in a cartridge design is arranged, which has a control cylinder 6.
  • an actuating piston 9 is arranged in a sealing and movable manner and carries a valve body 10 on its side facing away from the pressure chamber of the control cylinder 6.
  • This valve body 10 is set up in the end position shown in the drawing opposite a valve seat 11 seal leak-free.
  • the valve seat 11 divided into the interior of the valve C into a first space 7 with a connection B adjacent to the actuating piston 9 and a second space 8 with a connection A.
  • the connection B is connected to the storage connection S by a working line 3 during the connection A is connected via a working line 4 to the connection P for the hydraulic unit.
  • a spring is preferably provided in valve C, which presses the actuating piston 9 and thus the valve body 10 in abutment against the valve seat 11.
  • the working line 4 is connected via a control line 1 to the one input of a shuttle valve WV, the other input of which is connected to the working line 3 via a control line 2.
  • the two control lines 1 and 2 and thus also the respective working line 4 and 3 are each formed with a measuring connection M 'or M ⁇ , on which a pressure sensor is arranged.
  • the output of the shuttle valve WV is connected to the control cylinder 6 of the valve C via a further control line 10.
  • the shuttle valve WV has a valve body, which blocks that of the two inputs of the valve WV, which has the lower pressure of both inputs, so that the control cylinder 6 can always be connected to that working line 3 or 4, in each of which the higher one Pressure prevails. Provision is therefore always made that when the control cylinder 6 is pressurized, it is so high that the valve body 10 of the valve C remains pressed against the valve seat 11 in a sealing manner.
  • the directional seat valve W connects the two branches of the control line 10, between which the directional seat valve W is arranged.
  • a discharge line 11 which connects the directional seat valve W to the connection T for the reservoir, is blocked off leak-free by an absolutely tight valve seat seal.
  • control cylinder 6 is emptied via the port T and is therefore free of pressure, so that only the pressure prevailing in the interior spaces 7 and 8 of the valve C of the valve C acts on it, displacing this control piston 9 in the drawing and thus the Valve body 10 lifts off the valve seat 11, as a result of which the interiors 7 and 8 and thus the connections B and A of the valve are connected to one another and hydraulic work fluid can flow unhindered between the connections S and P via the working lines 3 and 4.
  • a first throttle DR ' is provided, and between this and the tank port T, a second throttle DR ⁇ is provided in line 11.
  • These two throttles are designed to prevent the explosion-like pressure drop in the control cylinder 6 of the shut-off valve C and to enable the controlled but rapid opening of the shut-off valve C at a predetermined speed or in a predetermined opening time.
  • the shut-off block preferably also has a pressure relief valve DB, which the working line 3 with the relief line 11 and thus the connections S and T with each other.
  • This pressure relief valve DB relieves any pressure increases caused by external influences (e.g. temperature, deformation, etc.), which can occur particularly in the event of an accident. If the increase in pressure in the pressure accumulator cannot take on a critical value due to external influences, the valve DB can be omitted.
  • a shut-off throttle D is arranged, through the opening of which the working line 3 can also be connected to the discharge line 11 and thus the connection S for the pressure accumulator to the connection T for the storage container. It is thus possible to lower the pressure accumulator by opening the shut-off throttle D and to make it pressure-free. This is necessary, for example, if repairs or a change in the hydraulic oil have to be carried out.
  • the shut-off throttle D can be operated remotely and can be coupled to a monitoring device or a sensor. For example, it is possible to couple the shut-off throttle D with a cover closing the arrangement in such a way that when the cover is removed, the pressure accumulator is emptied for safety reasons. It is also possible to provide the shut-off throttle D with an easily accessible handle, via which e.g. the pressure accumulator can be released after an accident.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Valve Device For Special Equipments (AREA)
  • Safety Valves (AREA)
EP86114822A 1986-01-27 1986-10-24 Configuration de valves pour accumulateur hydraulique Expired - Lifetime EP0230529B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86114822T ATE72693T1 (de) 1986-01-27 1986-10-24 Ventilanordnung fuer einen hydraulischen druckspeicher.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863602362 DE3602362A1 (de) 1986-01-27 1986-01-27 Ventilanordnung fuer einen hydraulischen druckspeicher
DE3602362 1986-01-27

Publications (3)

Publication Number Publication Date
EP0230529A2 true EP0230529A2 (fr) 1987-08-05
EP0230529A3 EP0230529A3 (en) 1989-04-26
EP0230529B1 EP0230529B1 (fr) 1992-02-19

Family

ID=6292702

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86114822A Expired - Lifetime EP0230529B1 (fr) 1986-01-27 1986-10-24 Configuration de valves pour accumulateur hydraulique

Country Status (5)

Country Link
US (1) US4706930A (fr)
EP (1) EP0230529B1 (fr)
AT (1) ATE72693T1 (fr)
DE (2) DE3602362A1 (fr)
DK (1) DK166551B1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4223389A1 (de) * 1992-07-16 1994-01-20 Rexroth Mannesmann Gmbh Steueranordnung für mindestens einen hydraulischen Verbraucher
DE4438899C1 (de) * 1994-10-31 1995-09-07 Hydac Technology Gmbh Energierückgewinnungsvorrichtung
US5477677A (en) * 1991-12-04 1995-12-26 Hydac Technology Gmbh Energy recovery device
DE19638837A1 (de) * 1996-09-21 1998-03-26 Wabco Gmbh Anordnung zur Steuerung eines Druckes
EP2603705A1 (fr) * 2010-08-09 2013-06-19 Parker Hannifin Manufacturing Sweden AB Système de commande hydraulique

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5116188A (en) * 1987-09-16 1992-05-26 Kabushiki Kaisha Kobe Seiko Sho Vibration suppressing device for wheeled construction equipment
FR2630788A2 (fr) * 1988-02-05 1989-11-03 Bendix France Dispositif de fuite pour vidange d'un accumulateur a membrane
DE3815873A1 (de) * 1988-05-09 1989-11-23 Rexroth Mannesmann Gmbh Hydrostatischer antrieb
US5325668A (en) * 1988-06-10 1994-07-05 S.I.T.I. Societa Impianti Termoelettrici Industriali S.P.A. Method and apparatus for hydraulic pressing
DE3920030A1 (de) * 1988-06-25 1989-12-28 Zahnradfabrik Friedrichshafen Hydraulische energiespeicheranlage
DE3922553C2 (de) * 1989-07-08 2002-03-14 Mannesmann Rexroth Ag Vorrichtung zur Entlastung eines unter hohem Druck stehenden mit Hydraulikflüssigkeit gefüllten Arbeitsraumes
DE4004931C2 (de) * 1990-02-16 1995-02-23 Rexroth Mannesmann Gmbh Vorgesteuertes Druckabschaltventil
DE4112065C2 (de) * 1991-04-12 1995-06-29 Rexroth Mannesmann Gmbh Vorgesteuertes Druckabschaltventil mit einstellbarer Schaltdruckdifferenz
DE4129509C2 (de) * 1991-09-05 1994-06-16 Rexroth Mannesmann Gmbh Hydraulische Steueranordnung für Baumaschinen
DE4219552C2 (de) * 1992-06-15 1996-03-07 Rexroth Mannesmann Gmbh Vorgesteuertes Zwei-Wegeventil mit einstellbarer, druckunabhängiger Schließzeit
US5375619A (en) * 1993-04-28 1994-12-27 Foster; Raymond K. Protective circuit for pressure and return
JPH10169805A (ja) * 1996-12-05 1998-06-26 Smc Corp パイロット式切換弁
US6427967B1 (en) * 1997-07-15 2002-08-06 Rowland Frank Evans Valve, unit, assembly and system
US6575164B1 (en) * 1998-10-15 2003-06-10 Ntc Technology, Inc. Reliability-enhanced apparatus operation for re-breathing and methods of effecting same
US6408876B1 (en) * 1998-12-01 2002-06-25 Hitachi Construction Machinery Co., Ltd. Control valve
US8597849B2 (en) * 2005-08-30 2013-12-03 GM Global Technology Operations LLC Pressure activated shut-off valve
KR101445729B1 (ko) * 2007-07-02 2014-10-07 파커 하니핀 매뉴팩쳐링 스웨덴 아베 유체 밸브 장치
CN108502083B (zh) * 2018-04-20 2024-06-04 重庆大学 一种适合多坡地形的蓄能液压自行车
DE102018006380A1 (de) * 2018-08-11 2020-02-13 Hydac Fluidtechnik Gmbh System zum Laden und Entladen mindestens eines Hydrospeichers

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US2683966A (en) * 1953-06-08 1954-07-20 Oilgear Co Hydraulic press
US3533434A (en) * 1968-01-22 1970-10-13 Rotax Ltd Fluid flow controlling valves
FR2381192A1 (fr) * 1977-02-16 1978-09-15 Frank Roger Bloc de regulation de l'alimentation d'une unite de travail alimentee en derivation a partir d'une centrale hydraulique commune a d'autres unites
US4149565A (en) * 1977-02-02 1979-04-17 International Harvester Company Pilot controlled poppet valve assembly
US4340086A (en) * 1979-04-19 1982-07-20 Sperry Vickers, Division Of Sperry Gmbh Hydraulic control valve unit
DE3113933A1 (de) * 1981-04-07 1982-10-28 Robert Bosch Gmbh, 7000 Stuttgart "hydraulische steuereinrichtung"

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US2925984A (en) * 1956-11-28 1960-02-23 Marotta Valve Corp Solenoid-operated poppet-type shut-off valve
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JPS5138135B2 (fr) * 1971-09-17 1976-10-20
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US4463818A (en) * 1982-09-07 1984-08-07 Applied Power Inc. Tilt cab truck in which the cab is partially supported by the tilting cylinder while in the drive position

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2683966A (en) * 1953-06-08 1954-07-20 Oilgear Co Hydraulic press
US3533434A (en) * 1968-01-22 1970-10-13 Rotax Ltd Fluid flow controlling valves
US4149565A (en) * 1977-02-02 1979-04-17 International Harvester Company Pilot controlled poppet valve assembly
FR2381192A1 (fr) * 1977-02-16 1978-09-15 Frank Roger Bloc de regulation de l'alimentation d'une unite de travail alimentee en derivation a partir d'une centrale hydraulique commune a d'autres unites
US4340086A (en) * 1979-04-19 1982-07-20 Sperry Vickers, Division Of Sperry Gmbh Hydraulic control valve unit
DE3113933A1 (de) * 1981-04-07 1982-10-28 Robert Bosch Gmbh, 7000 Stuttgart "hydraulische steuereinrichtung"

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Title
Fachveröffentlichung "Hydrobus", technischer Schlussbericht - hydrostatische Bremsenergierückgewinnung für Stadtlinienbusse - April 1983, S. 41 und 286 *

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5477677A (en) * 1991-12-04 1995-12-26 Hydac Technology Gmbh Energy recovery device
DE4223389A1 (de) * 1992-07-16 1994-01-20 Rexroth Mannesmann Gmbh Steueranordnung für mindestens einen hydraulischen Verbraucher
US5558004A (en) * 1992-07-16 1996-09-24 Mannesmann Rexroth Gmbh Control arrangement for at least one hydraulic consumer
DE4223389C2 (de) * 1992-07-16 2001-01-04 Mannesmann Rexroth Ag Steueranordnung für mindestens einen hydraulischen Verbraucher
DE4438899C1 (de) * 1994-10-31 1995-09-07 Hydac Technology Gmbh Energierückgewinnungsvorrichtung
DE19638837A1 (de) * 1996-09-21 1998-03-26 Wabco Gmbh Anordnung zur Steuerung eines Druckes
DE19638837B4 (de) * 1996-09-21 2006-06-14 Wabco Gmbh & Co.Ohg Anordnung zur Steuerung eines Druckes
EP2603705A1 (fr) * 2010-08-09 2013-06-19 Parker Hannifin Manufacturing Sweden AB Système de commande hydraulique
EP2603705A4 (fr) * 2010-08-09 2017-04-05 Parker Hannifin Manufacturing Sweden AB Système de commande hydraulique

Also Published As

Publication number Publication date
ATE72693T1 (de) 1992-03-15
DK578386A (da) 1987-07-28
DK578386D0 (da) 1986-12-02
DE3602362A1 (de) 1987-07-30
EP0230529B1 (fr) 1992-02-19
DK166551B1 (da) 1993-06-07
DE3683933D1 (de) 1992-03-26
EP0230529A3 (en) 1989-04-26
US4706930A (en) 1987-11-17

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