EP0547404A1 - Pompe à membrane actionnée hydrauliquement avec limitation du mouvement de la membrane - Google Patents

Pompe à membrane actionnée hydrauliquement avec limitation du mouvement de la membrane Download PDF

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Publication number
EP0547404A1
EP0547404A1 EP92119928A EP92119928A EP0547404A1 EP 0547404 A1 EP0547404 A1 EP 0547404A1 EP 92119928 A EP92119928 A EP 92119928A EP 92119928 A EP92119928 A EP 92119928A EP 0547404 A1 EP0547404 A1 EP 0547404A1
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EP
European Patent Office
Prior art keywords
diaphragm
membrane
valve
piston
control slide
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
EP92119928A
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German (de)
English (en)
Other versions
EP0547404B1 (fr
Inventor
Roland Dipl.-Ing. Hessenberger
Waldemar Dipl.-Ing. Horn
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.)
Lewa GmbH
Lewa Herbert Ott GmbH and Co KG
Original Assignee
Lewa GmbH
Lewa Herbert Ott GmbH and Co KG
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 Lewa GmbH, Lewa Herbert Ott GmbH and Co KG filed Critical Lewa GmbH
Publication of EP0547404A1 publication Critical patent/EP0547404A1/fr
Application granted granted Critical
Publication of EP0547404B1 publication Critical patent/EP0547404B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston

Definitions

  • the invention relates to a hydraulically driven diaphragm pump according to the preamble of claim 1.
  • a diaphragm system-controlled leakage supplement device is provided.
  • leakage supplement devices of diaphragm pumps are described in DE-PS 28 43 054 and in FR-PS 24 92 473.
  • Controlling the leak supplementation by means of the membrane system offers a number of other advantages compared to pressure-controlled leak supplementation with a snifting valve.
  • large suction heights can be overcome, the suction height being limited solely by the vapor pressure of the delivery fluid and hydraulic fluid.
  • overloading of the hydraulic space is excluded. Such pronounced vacuum peaks preferably occur in large high-pressure diaphragm pumps at the beginning of the suction phase when the liquid column in the suction line is accelerated suddenly when the suction valve is opened.
  • the membrane system-controlled leak supplement enables sniffing of hydraulic fluid at a low differential pressure of, for example less than 0.3 bar, ie the absolute pressure remains at around 0.7 bar.
  • the pressure-controlled leakage supplement requires a relatively high setting of the differential pressure at the snifting valve of, for example, 0.6 bar in order to ensure safe operation.
  • the resulting pressure drop in the hydraulic chamber during the sniffing process to, for example, 0.4 bar absolute pressure leads to increased gas formation. This results in a reduced delivery rate and delivery accuracy.
  • the manual positioning of the membrane before starting the pump is relatively complex. It is usually carried out in such a way that a connection between the hydraulic space and the storage space is created, which is done for example by removing the pressure relief valve.
  • the diaphragm is then pressed in the direction of its drive by applying overpressure on the suction side of the pump, which accordingly also acts on the diaphragm surface on the delivery chamber side. Then when the membrane is in the direction of its drive moved, hydraulic fluid is simultaneously displaced from the hydraulic space into the storage space.
  • the described complex yet necessary commissioning of the diaphragm pump has a particularly disadvantageous effect in modern triple diaphragm pumps, in which the initial diaphragm positioning has to be carried out on three pump heads.
  • This membrane positioning can be simplified with solenoid valves that are installed between the hydraulic space and the storage space.
  • the design and control engineering effort remains considerable in any case. It is also not always easy to provide the necessary overpressure on the suction side of the pump to push the membrane in the direction of its drive.
  • the invention has for its object to design the diaphragm pump of the generic type in such a way that the diaphragm stroke is functionally limited in both directions with simple means and that the pump is started up without manual preparatory work to influence the diaphragm system can be.
  • the invention is based on the idea of providing the devices for limiting the diaphragm stroke in both directions on the control slide of the leak-supplementing device which is already present. This results in an incredibly simple, yet functionally reliable design. At the same time, it is ensured that the pump can be put into operation without manual preparatory work having to be carried out to influence the membrane system.
  • the diaphragm pump designed according to the invention uses a double or combined principle with regard to the limitation of the diaphragm travel provided in both stroke directions.
  • This consists in that on the one hand the diaphragm stroke limitation in the suction stroke end position takes place in a purely mechanical way, namely by means of the almost gap-free support surface formed by the support plate and assigned pump body surface and adapted to the natural diaphragm geometry, while on the other hand the diaphragm stroke limitation in the pressure stroke limit position is effected purely hydraulically by the valve member provided on the piston-side end of the control slide interrupts the hydraulic connection from the piston working chamber to the membrane working chamber. In the latter case, excess hydraulic oil is then displaced into the hydraulic reservoir via the pressure relief valve provided.
  • the invention thus realizes the principle that on the basis of the diaphragm system-controlled leakage supplement that takes place by means of the control slide, a diaphragm system-controlled Path or stroke limitation of the membrane is effected both in the direction of the pressure stroke and in the direction of the suction stroke.
  • a diaphragm system-controlled Path or stroke limitation of the membrane is effected both in the direction of the pressure stroke and in the direction of the suction stroke.
  • the mechanical support surface is designed without holes, which has proven to be particularly advantageous when the invention is used for high-pressure diaphragm pumps.
  • the second control valve by means of which the hydraulic limitation of the diaphragm stroke takes place in the pressure stroke end position or limit position, is expediently designed as a plate valve, the valve plate of which, be it in the form of a plate washer, a plate shell or the like, in the pressure stroke end position, the connection channel or channels closes.
  • control slide of the leakage supplement device which has the support plate fixedly connected to it at its membrane-side end, can be configured such that the valve member of the second control valve provided on the piston-side end is also firmly connected to it.
  • valve member of the second control valve is fastened to one end of a valve tappet, which in turn is slidably guided in the control slide of the first control valve, coaxially with the latter, and rests with the other end under spring force of the diaphragm, so that it scans the membrane over the entire membrane stroke.
  • control slide of the first control valve is biased in the direction of the diaphragm by a spring that is stronger than the spring that biases the valve tappet of the second control valve. It is within the scope of the invention that the spring biasing the valve lifter of the second control valve is supported on the control slide itself.
  • the invention provides that the control slide has a stop at its piston-side end, which limits the displacement of the control slide in the direction of the diaphragm pressure stroke .
  • the control slide when the diaphragm moves from its suction stroke end position in the direction of the pressure stroke, the control slide only follows the diaphragm in a certain range, which is preferably 30-40% of the total diaphragm stroke. This means that the control spool, when the diaphragm returns from its pressure stroke end position to the suction stroke end position, is only actuated by the membrane to the last 30 - 40% of the suction stroke or pushed back against spring force.
  • the valve tappet of the valve plate scans the membrane over the entire membrane stroke.
  • the second control valve works completely independently of the first control valve, ie it still scans the membrane when the function of the first control valve is disturbed, for example by the effect of dirt.
  • the valve tappet runs along with it as it were.
  • the valve disk closes the connection channel or channels between the piston working room and the membrane working room. The hydraulic connection is thus interrupted so that the membrane cannot be deformed any further in the direction of the delivery chamber. Accordingly, the membrane is secured against overstretching. The excess hydraulic fluid in the piston working chamber is pushed back into the hydraulic reservoir via the pressure relief valve.
  • the invention thus not only results in a desirable protection of the diaphragm when the pump is started up, but also an additional improvement in the operational reliability of the pump is achieved due to the completely independent functioning of the two control valves. This is essential if the function of the first control valve is disturbed, for example by the effect of dirt, and remains in an open position continuously, so that an uncontrolled sniffing of hydraulic fluid would be possible. In this case, however, the second control valve reliably prevents membrane damage by preventing a pressure stroke of the membrane beyond the normal end position in the manner described. The excess hydraulic fluid is then drained back into the storage space. The pump only works with reduced power and the pressure relief valve responds.
  • Another advantage according to the invention results from the design of the control slide and the valve tappet which is displaceably guided therein.
  • the end faces of these two control elements together with the associated pump body surface form an almost gap-free mechanical support surface which is adapted to the natural membrane shape.
  • the diaphragm In its suction stroke end position, the diaphragm is mechanically supported by this contact surface and can be pressed on with the full delivery pressure without suffering any damage.
  • the invention therefore provides significant advantages, inter alia, achieved in that the commissioning of the pump can be carried out without manual preparatory work and that the diaphragm deflection is automatically limited by simple means both in the pressure stroke and in the suction stroke. This reliably prevents the membrane from overstretching or even bursting. For this reason, the diaphragm pump is also much easier to integrate into automated processes, which among other things. is based on the fact that there is no need for time-consuming manual preparatory work to influence the membrane system. Furthermore, the risk of membrane damage due to incorrect operation is eliminated. Costly downtimes can be avoided.
  • the diaphragm pump has a conventional diaphragm 1, in particular made of plastic. This is at its edge between a pump body 2 and a pump cover detachably attached to the end thereof 3 clamped and separates a delivery chamber 4 from a pressure chamber 5 filled with hydraulic fluid, which represents the piston working chamber.
  • the diaphragm pump has a hydraulic diaphragm drive in the form of an oscillating displacement piston 6, which can be displaced in a sealed manner in the pump body 2 between the piston working space 5 and a storage space 7 for the hydraulic fluid.
  • the piston working space 5 is connected via at least one axial bore 8 arranged in the pump body 2 to a diaphragm-side pressure space 9, which represents the diaphragm working space and together with the piston working space 5 forms the hydraulic space as a whole.
  • the diaphragm working space 9 is delimited on the one hand by the diaphragm 1 and on the other hand by a rear (piston-side) calotte 10.
  • This rear limitation cap 10 is formed by the appropriately designed end face of the pump body 2 and represents part of that - still to be described - mechanical support surface on which the membrane 1 bears at the end of the suction stroke (see FIG. 5).
  • a front limitation cap 11 formed by the end face of the pump cover 3 is formed in the delivery chamber 4.
  • the pump cover 3 is provided in the usual way with a spring-loaded inlet valve 12 (suction valve) and a spring-loaded outlet valve 13 (pressure valve). These two valves 12, 13 are connected via an inlet duct 14 and an outlet duct 15 to the delivery chamber 4 in such a way that the conveying medium during the suction stroke of the displacer 6 and thus the diaphragm 1 to the right according to FIG. 1 and thus the diaphragm 1 in the direction of the arrow via the suction valve 12 and the inlet channel 14 is sucked into the delivery chamber 4.
  • the conveyed medium is then metered in via the outlet channel 15 and the pressure valve 13 in the direction of the arrow discharged from the delivery room 4.
  • a leakage supplementation device In order to prevent the occurrence of cavitation at the end of the membrane suction stroke and to provide for the leakage supplementation required due to the leakage losses, a leakage supplementation device is provided.
  • This has a conventional spring-loaded sniffer valve 16, which is connected via a channel 17 to the storage space 7 and via a channel 18 and the connecting channel 8 on the one hand to the piston working space 5 and on the other hand to the diaphragm working space 9.
  • the leakage supplement is controlled by a first control valve which has a control slide 19.
  • This is axially displaceable with the displacement piston 6 in the area of the connecting channel 8 between the diaphragm working space 9 and the piston working space 5 in a corresponding bore of the pump body 2 and is under the action of a compression spring 23 (see FIG. 2).
  • the compression spring 23 is supported on the one hand in the pump body 2 and on the other hand on the diaphragm-side end of the control slide 19, so that the control slide 19 is biased in the direction of the diaphragm 1 and follows the movement of the diaphragm 1 from the suction stroke end position in the pressure stroke direction.
  • control slide 19 has a stop 28 at its piston-side end, for example in the form of a circlip, with a corresponding one in the piston working chamber 5 provided collar 29 cooperates and limits the displacement of the spool 19 in the direction of the diaphragm pressure stroke.
  • a circumferential groove 30 is provided which, in the suction stroke end position of the membrane 1 (FIG. 5), the connection between the snifting valve 16 of the leakage supplement device and the hydraulic chamber 5, 9 - via the channels 18, 8 - produces.
  • a second control valve 20 is provided at the piston-side end of the control slide 19.
  • this is designed as a poppet valve and has a shell-like valve disk 21, a valve tappet 22 connected to it and a compression spring 24, which is supported in the manner shown on the control slide 19 and the second control valve 20 in Biased towards membrane 1.
  • the valve tappet 22 is displaceable in the control slide 19, coaxially to the latter, and its membrane-side end is always in contact with the membrane 1 due to the action of its compression spring 24, so that it scans the membrane 1 over the entire membrane stroke.
  • the valve disk 21 is designed such that it closes the connection channel (s) 8 in the limit position of the membrane pressure stroke end position (see FIG. 4).
  • the diaphragm-side end of the control slide 19 is designed as a support plate 31. This is shaped so that its end face 10 'together with the associated end face 10 of the pump body 2 and the end face 10' 'of the diaphragm-side end of the valve lifter 22 forms an almost gap-free mechanical support surface for the diaphragm 1 in its suction stroke end position.
  • This support surface 10, 10 ', 10' ' is adapted to the natural membrane geometry, it being particularly important that it is designed to be completely bore-free.
  • the support plate 31 In the compressed position of the control slide 19, the support plate 31 is received in a corresponding bore 32 of the pump housing 2, but it is not necessary that the support plate 31 lies tightly against the seat formed by the bore 32. It is only necessary to ensure that the mechanical support surface described is provided by all of the end faces 10, 10 ′, 10 ′′ mentioned is formed for the membrane 1 in its suction stroke end position.
  • a pressure relief valve 27 is finally provided in the pump body 2, which is connected on the one hand via a channel 33 to the piston working chamber 5 and on the other hand via a channel 34 to the hydraulic reservoir 7.
  • the displacement piston 6 is moved to the right in order to carry out the suction stroke.
  • the mechanical support surface 10, 10 ′, 10 ′′ which is formed by the end faces of the pump body 2, the support plate 31 and the membrane-side end of the valve lifter 22, lies in the suction stroke end position .
  • the control slide 19 with its diaphragm-side support plate 31 and the valve tappet 22 are in the compressed position, in which the abovementioned end faces 10, 10 ', 10''are the described support surface adapted to the diaphragm shape form.
  • the membrane 1 is thus fully mechanically supported in its suction stroke end position and can be pressed on at the full delivery pressure without suffering any damage.
  • the circumferential groove 30 of the control slide 19 also establishes the connection, which serves to supplement the leak, between the hydraulic reservoir 7 and the hydraulic chamber 5, 9, specifically via the channel 17, the snifting valve 16, the channel 18 and the connection channel or channels 8.
  • the diaphragm 1 also carries out the pressure stroke due to the hydraulic medium acting on it in the hydraulic chamber 5, 9, to the end of the pressure stroke according to FIG. 3 corresponding to the normal position
  • the control slide 19 of the diaphragm 1, which is under the action of the compression spring 23, follows only over a distance which corresponds to approximately 30-40% of the total diaphragm pressure stroke, since the stop 28 of the control slide 19 then strikes the collar 29 on the housing and thus the displacement path of the Control spool 19 limited.
  • valve tappet 22 which is under the prestress of the compression spring 24, scans the membrane 1 over its entire pressure stroke.
  • the valve lifter 22 runs as it were, as long as the diaphragm 1 operates in its predetermined stroke range. This means that in the normal pressure stroke end position of the diaphragm 1, the valve tappet 22 has such a position that the valve disk 21 does not close the connecting channels 8 between the piston working space 5 and the diaphragm working space 9.
  • the membrane 1 If, however, the membrane 1, however, the intended work area by a certain amount, for example by 20% of the normal diaphragm stroke, in the direction of the delivery chamber 4 and thus assumes a limit position exceeding the normal position in its pressure stroke end position, results in a position according to FIG. 4, in which the valve disk 21 closes the connection channel or channels 8 between the piston work chamber 5 and the membrane work chamber 9 Has.
  • the excess hydraulic fluid present in the piston working space 5 is pushed back into the storage space 7 via the pressure limiting valve 27 and the channels 33, 34.
  • the process described in the introduction is then repeated by means of the displacement movement of the displacer 6 to the right until the membrane 1 abuts the support surface 10, 10 ', 10' 'in the suction stroke end position and is supported there mechanically.
  • the valve plate 21 closes the connecting channels 8 during the next pressure stroke of the diaphragm 1 in its pressure stroke limit position, so that it is thereby the hydraulic diaphragm travel limitation in the pressure stroke limit position results.
  • the excess hydraulic fluid is discharged from the piston working chamber 5 into the storage chamber 7 via the pressure limiting valve 27.
  • the malfunction described can be recognized easily and in good time due to the increased response of the pressure limiting valve 27 and due to the reduced pump output, so that the malfunction can be remedied immediately.
  • a vent hole 25 is provided in the pump housing 2, which runs from the geodetically highest point of the diaphragm working space 9 to the combined pressure limiting and gas discharge valve 27.
  • the vent hole 25 has a check valve 26. This is preloaded or arranged in such a way that it enables the desired ventilation of the membrane working space 9, i.e. a control from the membrane work space 9 to the gas discharge valve 27 permits.
  • the check valve 26 prevents a bypass flow from the piston working space 5 to the diaphragm working space 9 when the second control valve 20 is closed.
  • the further modified embodiment according to FIG. 8 represents a simplified design compared to the previously described construction, to the extent that the second control valve 20 consists only of the disk-shaped valve plate 21, that is to say, no separately guided in the control slide 19 under the action of a compression spring has standing valve lifter.
  • the valve plate 21 is fixedly connected to the piston-side end of the control slide 19 and is arranged or dimensioned such that it also closes the connecting channels 8 between the piston working chamber 5 and the membrane working chamber 9 in the end position of the diaphragm 1 corresponding to the stroke position.
  • the respective membrane system is only affected by the pressure spring 23 Control slide 19 or scanned by the support plate 31, otherwise the same advantageous effects result as in the previously described embodiments.
  • the leakage in the hydraulic chamber 5, 9 is effected via an axial bore 35 provided in the control slide 19, which on the one hand opens through the valve disk 21 into the piston working chamber 5 and on the other hand via a radially extending bore section 36 with the channel 18 or the sniffer valve 16 is connected.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP92119928A 1991-12-17 1992-11-23 Pompe à membrane actionnée hydrauliquement avec limitation du mouvement de la membrane Expired - Lifetime EP0547404B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4141670 1991-12-17
DE4141670A DE4141670C2 (de) 1991-12-17 1991-12-17 Hydraulisch angetriebene Membranpumpe mit Membranhubbegrenzung

Publications (2)

Publication Number Publication Date
EP0547404A1 true EP0547404A1 (fr) 1993-06-23
EP0547404B1 EP0547404B1 (fr) 1997-02-05

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EP92119928A Expired - Lifetime EP0547404B1 (fr) 1991-12-17 1992-11-23 Pompe à membrane actionnée hydrauliquement avec limitation du mouvement de la membrane

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US (1) US5246351A (fr)
EP (1) EP0547404B1 (fr)
JP (1) JPH05240162A (fr)
DE (2) DE4141670C2 (fr)

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EP1801417A1 (fr) 2005-12-20 2007-06-27 Milton Roy Europe Pompe à membrane à actionnement hydraulique avec dispositif de compensation des fuites
CN102352831A (zh) * 2011-10-24 2012-02-15 重庆水泵厂有限责任公司 隔膜泵自动补排油装置
DE102013105072A1 (de) 2013-05-16 2014-11-20 Prominent Gmbh Membranpumpe mit Lagensteuerung
CN114320847A (zh) * 2021-11-26 2022-04-12 嘉善边锋机械股份有限公司 一种实现自动憋压的气动计量泵

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JP4330323B2 (ja) * 2001-10-24 2009-09-16 株式会社タクミナ 往復動ポンプ
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DE102010039829A1 (de) * 2010-08-26 2012-03-01 Prominent Dosiertechnik Gmbh Membranpumpe mit trägheitsgesteuertem Leckergänzungsventil
CN103629088A (zh) * 2013-11-22 2014-03-12 德帕姆(杭州)泵业科技有限公司 一种新型均压限位补油的液压隔膜计量泵
CN104088777B (zh) * 2014-05-27 2016-09-28 德帕姆(杭州)泵业科技有限公司 一种隔膜定量压缩的计量泵
DE102014109801A1 (de) * 2014-07-11 2016-01-14 Prominent Gmbh Membranpumpe mit reduzierter Leckageergänzung im Überlastfall
WO2016077751A1 (fr) * 2014-11-14 2016-05-19 Checkpoint Fluidic Systems International, Ltd. Mécanisme de pompe à diaphragme sandwich métallique
CN105003424B (zh) * 2015-07-27 2017-03-01 杭州大泉泵业科技有限公司 一种高温液压式隔膜计量泵
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DE102017122270B4 (de) * 2017-09-26 2020-09-10 Prominent Gmbh Membranpumpe mit einer funktionssicheren Membranlagensteuerung
CN111989488B (zh) * 2018-04-18 2022-12-13 万纳工程公司 用于保护隔膜泵免受压差影响的装置
IT201800004722A1 (it) * 2018-04-19 2019-10-19 Pompa volumetrica a membrana
CN110425120A (zh) * 2019-08-13 2019-11-08 王建设 一种自动调压隔膜泵
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ES2946411T3 (es) * 2021-07-26 2023-07-18 Gea Mech Equipment Italia S P A Una bomba de pistón basada en membrana y un aparato de homogeneización que comprende la bomba de pistón basada en membrana
DE202021106223U1 (de) * 2021-11-15 2021-11-19 Feluwa Pumpen Gmbh Membrankolbenpumpe
CN115263708A (zh) * 2022-07-13 2022-11-01 德帕姆(杭州)泵业科技有限公司 一种高性能微量输送的计量泵
CN115182872B (zh) * 2022-08-05 2024-01-26 德帕姆(杭州)泵业科技有限公司 一种容积式活塞泵

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1801417A1 (fr) 2005-12-20 2007-06-27 Milton Roy Europe Pompe à membrane à actionnement hydraulique avec dispositif de compensation des fuites
CN102352831A (zh) * 2011-10-24 2012-02-15 重庆水泵厂有限责任公司 隔膜泵自动补排油装置
DE102013105072A1 (de) 2013-05-16 2014-11-20 Prominent Gmbh Membranpumpe mit Lagensteuerung
WO2014184125A1 (fr) 2013-05-16 2014-11-20 Prominent Gmbh Pompe à membrane dotée d'une commande de position
CN105209758A (zh) * 2013-05-16 2015-12-30 卓越有限公司 具有位置控件的隔膜泵
CN105209758B (zh) * 2013-05-16 2017-09-01 卓越有限公司 具有位置控件的隔膜泵
US9964105B2 (en) 2013-05-16 2018-05-08 Prominent Gmbh Diaphragm pump having position control
CN114320847A (zh) * 2021-11-26 2022-04-12 嘉善边锋机械股份有限公司 一种实现自动憋压的气动计量泵
CN114320847B (zh) * 2021-11-26 2023-11-14 嘉善边锋机械股份有限公司 一种实现自动憋压的气动计量泵

Also Published As

Publication number Publication date
EP0547404B1 (fr) 1997-02-05
US5246351A (en) 1993-09-21
JPH05240162A (ja) 1993-09-17
DE59208018D1 (de) 1997-03-20
DE4141670A1 (de) 1993-07-01
DE4141670C2 (de) 1994-09-29

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