EP0195261B1 - Soupape magnétique, en particulier soupape de commande de quantité de combustible - Google Patents

Soupape magnétique, en particulier soupape de commande de quantité de combustible Download PDF

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Publication number
EP0195261B1
EP0195261B1 EP86102095A EP86102095A EP0195261B1 EP 0195261 B1 EP0195261 B1 EP 0195261B1 EP 86102095 A EP86102095 A EP 86102095A EP 86102095 A EP86102095 A EP 86102095A EP 0195261 B1 EP0195261 B1 EP 0195261B1
Authority
EP
European Patent Office
Prior art keywords
valve
stop
valve closing
solenoid valve
closing element
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
Application number
EP86102095A
Other languages
German (de)
English (en)
Other versions
EP0195261A3 (en
EP0195261A2 (fr
Inventor
Helmut Dipl.-Ing. Rembold
Walter Teegen
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to AT86102095T priority Critical patent/ATE45011T1/de
Publication of EP0195261A2 publication Critical patent/EP0195261A2/fr
Publication of EP0195261A3 publication Critical patent/EP0195261A3/de
Application granted granted Critical
Publication of EP0195261B1 publication Critical patent/EP0195261B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S239/00—Fluid sprinkling, spraying, and diffusing
    • Y10S239/90—Electromagnetically actuated fuel injector having ball and seat type valve

Definitions

  • the invention is based on a solenoid valve according to the preamble of the main claim.
  • a solenoid valve of this type has become known, in which the disk-shaped stop part of the valve closing member comes to rest upon opening on an annular bead of the fixed stop, which has a breakthrough coaxial with the annular bead.
  • the valve closing member strikes hard on the annular bead, so that rebounding disturbing the liquid flow occurs.
  • there are hydraulic adhesive forces which differ from valve to valve. Rebounders and adhesive forces have a very unfavorable effect on the switching times of the valves from stroke to stroke and from valve to valve. This is particularly disadvantageous when such a valve is used for the metering of fuel per injection stroke of a fuel injection pump or per fuel supply cycle and the metering accuracy required.
  • the solenoid valve according to the invention with the characterizing features of the main claim has the advantage that a squeezing flow in the opening gap between the damping chamber and the closing surface causes a damping of the opening movement of the valve closing member and that the adhesive forces when reopening the damping chamber are very low. Furthermore, it has been found to be advantageous that the function of the solenoid valve is far less temperature-dependent than in known solenoid valves due to the narrow stop surface of the damping chamber, since a turbulent squeezing flow occurs in the damping gap when the damping chamber is closed.
  • FIG. 1 shows a first exemplary embodiment of a solenoid valve in longitudinal section
  • FIGS. 2 and 3 show the part of a second and third exemplary embodiment essential to the invention in longitudinal section.
  • the solenoid valve has a valve housing 1, in which a core 2 made of ferromagnetic material is inserted, which carries a solenoid 3 between an inner cylinder 4 and an outer cylinder 5.
  • Inner cylinder 4 and outer cylinder 5 are connected to one another in a magnetically conductive manner by a yoke 6.
  • a magnetically conductive yoke plate 7 covers the outer cylinder 5 and the magnet coil 3.
  • the magnetic circuit interrupted between the inner cylinder 4 and the perforated plate 7 is bridged by an armature 10.
  • the armature 10 has a plate-shaped part 11 which merges into a hollow cylindrical connecting piece 12 which lies opposite the end face of the inner cylinder 4 and which engages through an opening 9 in the plate 7.
  • Two guide collars 18, 19 guide the valve closing part 15 in a cylinder bore 20 of a guide bushing 21.
  • the guide bushing 21 is part of a valve seat body 22 which has an inflow bore 23 in extension to the cylinder bore 20.
  • a cavity 24 is enclosed by the yoke 6 and valve seat body 22, from which drain bores 25 extend.
  • a conical valve seat 27 is formed in the valve seat body 22, with which a hemispherical closing body 28 of the valve closing part 15 cooperates.
  • Bores 29 in the guide bushing 21 connect the cavity 24 and the annular chamber 26.
  • the drain holes 25 lead via an intermediate chamber 30 to a return flow channel 31 in the valve housing 1.
  • a return spring 35 is supported, which with its upper end on Armature head 16 of the valve closing part 15 rests and, in the non-energized state of the solenoid 3, the valve closing part 15 lifts off the valve seat 27 and presses against a stop plate 36 arranged above the armature 10 and the plate 7, so that the solenoid valve is in the open position.
  • fluid for example liquid fuel
  • inflow bore 23 under high pressure, which is connected to the pressure chamber of a fuel delivery pump of a fuel injection system for internal combustion engines.
  • return flow channel 31 is connected to the low-pressure suction side of the fuel feed pump.
  • damping valve so that rebound is avoided, an open against the disc-shaped anchor head 16 damping chamber 40 is arranged on the stop plate 36.
  • the ceiling of the damping chamber 40 is formed by the plate itself and the side wall by an annular collar 41 projecting downward from the stop plate 36.
  • the thickness of the wall of the collar 41 is very small, so that the end-face, annular stop surface 42 for the anchor head 16 is very narrow.
  • the stop surface 42 is preferably spherical in order to keep the hydraulic adhesive forces low when the anchor head 16 is lifted off the stop surface 42.
  • this chamber 40 is through a throttle bore 43 in the stop plate 36 with the space 44 above it Stop plate 36 connected, which is also under low pressure.
  • the throttle bore 43 is dimensioned such that when the anchor head 16 strikes the stop surface 42 of the annular collar 41, the flow rate is negligible, so that a damping effect of the damping chamber 40 is present, but that fluid is removed from the chamber when the anchor head 16 is lifted off the annular collar 41 44 can flow into the damping chamber 40.
  • this throttle bore 43 a damping effect of the damping chamber 40 is ensured since the valve closing part 15 has a high speed before striking the annular collar 41, but has a low speed when it is lifted off.
  • a throttle in the form of a fine channel can be provided in the stop surface 42 of the annular collar 41 or in the surface of the anchor head 16 coming into contact therewith.
  • a plurality of openings 45 are arranged in the armature head 16, evenly distributed, through which displaced fluid can flow.
  • the arrangement of these openings 45 is preferably such that they coincide with the radially outer part of the stop surface 42 of the collar 41. This results in a further reduction in hydraulic gluing when lifting off the anchor head.
  • the solenoid valve opens again if the pressure in the pressure chamber of the connected fuel delivery pump is to be reduced.
  • the circuit to the magnetic coil 3 is interrupted again with the effect that the holding force of the core 2 is eliminated.
  • the valve closing part 15 is displaced upwards at a relatively high speed. In this case and in particular shortly before the anchor head 16 strikes the stop surface 42 of the annular collar 41, a squeezing flow from the damping chamber 40 and the space that overlaps with it occurs between the stop surface 42 and the ring region of the top side of the anchor head 16 that coincides therewith .
  • FIGS. 2 and 3 are modified compared to the one described above according to FIG. 1 only with regard to the damping device.
  • the same reference numerals are therefore used for parts that remain the same and have the same effect.
  • a check valve 50 is provided which allows fluid to flow from the upper space 44 into the damping chamber 40, but blocks in the opposite direction.
  • the check valve 50 consists of a recess 51 covering the damping chamber 40 and an opening 52 coaxial therewith with a smaller diameter and of a ball 53 in the recess 51 against the opening 52, which is supported by a conical compression spring 54 against the seat at the transition between rule the recess 51 to the opening 52.
  • the compression spring 54 is supported on a snap ring 55.
  • the check valve 50 has the advantage that when the anchor head 16 is lifted from the stop surface 42, fluid flows from the chamber 44 into the damping chamber 40 without resistance, whereas when the armature head 16 approaches when the solenoid valve is opened, no fluid flows from the damping chamber 40 into the chamber 44 can flow, but, as described above, displaced fluid is used to dampen the approach movement.
  • the damping chamber 40 is enlarged in that the valve closing part 15 has a blind bore 60 which is open at the top.
  • a throttle bore 61 is arranged in the lower part of the valve closing part 15, which connects the blind bore 60 with the annular chamber 26.
  • the damping chamber and its narrow stop surface can also be arranged on the valve closing part 15 or on its anchor head 16 instead of on the stop plate 36.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (10)

1. Soupape magnétique, en particulier soupape de commande de quantité de carburant pour des installations d'injection de carburant de moteurs à combustion interne, avec un électro-aimant (2, 3), un obturateur de soupape (15) mobile et actionné par cet électro-aimant, cet obturateur présentant à l'une de ses extrémités un élément de fermeture (28) et à l'autre de ses extrémités une pièce de butée (16), et avec une butée fixe (36), contre laquelle se trouve la pièce de butée dans la position d'ouverture de l'obturateur de soupape, caractérisée en ce que, contre la butée (36) ou la pièce de butée (16) de l'obturateur de soupape (15), une chambre d'amortissement (40) est disposée, ouverte d'un côté, ventilable et fermée lors du contact de la pièce de butée contre la butée (36), et en ce que la surface de butée (42) entourant l'ouverture de la chambre est réalisée étroite, de telle sorte qu'il se produit seulement de faibles forces hydrauliques d'adhérence.
2. Soupape magnétique selon la revendication 1, caractérisée en ce que la chambre d'amortissement (40) est constitué d'un anneau circulaire (41) dont les parois sont minces contre la butée (36).
3. Soupape magnétique selon la revendication 2, caractérisée en ce que la surface de butée (42) a une forme sphérique sur le côté frontal de l'anneau circulaire (41).
4. Soupape magnétique selon l'une des revendications 1 à 3, caractérisée en ce que la chambre d'amortissement (40) est ventilable par un alésage d'étranglement (43, 61).
5. Soupape magnétique selon la revendication 4, caractérisée en ce que l'alésage d'étranglement (43) est pratiqué dans la butée (36).
6. Soupape magnétique selon la revendication 4, caractérisée en ce que l'alésage d'étranglement (61) est pratiqué dans l'obturateur de soupape (15).
7. Soupape magnétique selon l'une des revendications 1 à 3, caractérisée en ce que la chambre d'amortissement (40) est ventilable par une soupape anti-retour (50).
8. Soupape magnétique selon la revendication 7, caractérisée en ce que la soupape anti-retour (50) est disposée dans la butée (36).
9. Soupape magnétique selon l'une des revendications 1 à 8, caractérisée en ce que la pièce de butée (16) de l'obturateur de soupape (15) à la forme d'une plaque et a des perçages (45) à l'extérieur de la zone de couverture avec la chambre (40).
10. Soupape magnétique selon la revendication 9, caractérisée en ce que les perçages (45) sont situés partiellement dans la partie de recouvrement avec la zone extérieure radiale de la surface de butée (42) de la chambre (40).
EP86102095A 1985-03-21 1986-02-18 Soupape magnétique, en particulier soupape de commande de quantité de combustible Expired EP0195261B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86102095T ATE45011T1 (de) 1985-03-21 1986-02-18 Magnetventil, insbesondere kraftstoffmengensteuerventil.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853510222 DE3510222A1 (de) 1985-03-21 1985-03-21 Magnetventil, insbesondere kraftstoffmengensteuerventil
DE3510222 1985-03-21

Publications (3)

Publication Number Publication Date
EP0195261A2 EP0195261A2 (fr) 1986-09-24
EP0195261A3 EP0195261A3 (en) 1988-03-16
EP0195261B1 true EP0195261B1 (fr) 1989-07-26

Family

ID=6265906

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86102095A Expired EP0195261B1 (fr) 1985-03-21 1986-02-18 Soupape magnétique, en particulier soupape de commande de quantité de combustible

Country Status (5)

Country Link
US (1) US4646976A (fr)
EP (1) EP0195261B1 (fr)
JP (1) JPH0816514B2 (fr)
AT (1) ATE45011T1 (fr)
DE (2) DE3510222A1 (fr)

Families Citing this family (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8719884D0 (en) * 1987-08-22 1987-09-30 Eaton Sa Monaco Electrically operated fluid valve
DE3741526A1 (de) * 1987-12-08 1989-06-22 Bosch Gmbh Robert Sitzventil
GB8729087D0 (en) * 1987-12-12 1988-01-27 Lucas Ind Plc Control valve
DE3834446A1 (de) * 1988-10-10 1990-04-12 Mesenich Gerhard Elektromagnetisches einspritzventil in patronenbauweise
US5190223A (en) * 1988-10-10 1993-03-02 Siemens Automotive L.P. Electromagnetic fuel injector with cartridge embodiment
GB8828160D0 (en) * 1988-12-02 1989-01-05 Lucas Ind Plc Fluid control valve
DE3841462C2 (de) * 1988-12-09 1996-05-30 Kloeckner Humboldt Deutz Ag Brennstoffeinspritzvorrichtung
DE4108758C2 (de) * 1991-03-18 2000-05-31 Deutz Ag Magnetventil für eine Kraftstoff-Einspritzvorrichtung
IT227711Y1 (it) * 1992-12-29 1997-12-15 Elasis Sistema Ricerca Fiat Valvola di dosaggio a comando elettromagnetico per un iniettore di combustibile
JP3197385B2 (ja) * 1993-03-24 2001-08-13 株式会社日本自動車部品総合研究所 燃料噴射弁
FR2717551B1 (fr) * 1994-03-17 1996-04-19 Eaton Sa Monaco Electrovanne à deux voies pour fluide.
IT1276503B1 (it) * 1995-07-14 1997-10-31 Elasis Sistema Ricerca Fiat Perfezionamenti ad una valvola di dosaggio a comando elettromagnetico, per un iniettore di combustibile.
EP0795881B1 (fr) * 1996-03-11 1999-06-09 Denso Corporation Dispositif électromagnétique à régulation de position pour stator
DE19616084A1 (de) * 1996-04-23 1997-10-30 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung
DE19650865A1 (de) * 1996-12-07 1998-06-10 Bosch Gmbh Robert Magnetventil
US5927614A (en) * 1997-08-22 1999-07-27 Touvelle; Matthew S. Modular control valve for a fuel injector having magnetic isolation features
US5878965A (en) * 1997-08-28 1999-03-09 Caterpillar Inc. Internally wetted cartridge control valve for a fuel injector
US5887799A (en) * 1997-09-11 1999-03-30 Impco Technoligies, Inc. Dual fuel injector
US5961052A (en) * 1997-09-25 1999-10-05 Caterpillar Inc. Control valve having a top mounted single pole solenoid for a fuel injector
GB2332476B (en) * 1997-12-19 2002-01-16 Caterpillar Inc Fuel injector with solenoid and terminal assemblies
US6036460A (en) * 1998-06-29 2000-03-14 Diesel Technology Company Flexible armature for fuel injection system control valve
DE19859484A1 (de) * 1998-12-22 2000-07-06 Bosch Gmbh Robert Kraftstoff-Einspritzventil für eine Hochdruckeinspritzung
DE19949814A1 (de) * 1999-10-15 2001-04-19 Bosch Gmbh Robert Druckregelventil für ein Speicherkraftstoffeinspritzsystem für Brennkraftmaschinen
DE19963922B4 (de) 1999-12-31 2007-12-13 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung mit sowohl laminar als auch turbulent gedämpftem Magnetventil
US6279843B1 (en) 2000-03-21 2001-08-28 Caterpillar Inc. Single pole solenoid assembly and fuel injector using same
DE10107115B4 (de) * 2001-02-14 2004-09-30 Robert Bosch Gmbh Drucksteuerventil
US6719224B2 (en) * 2001-12-18 2004-04-13 Nippon Soken, Inc. Fuel injector and fuel injection system
JP2004360748A (ja) * 2003-06-03 2004-12-24 Nissin Kogyo Co Ltd 常開型電磁弁
DE102004004095B3 (de) * 2004-01-27 2005-07-14 Siemens Ag Druckbegrenzungsvorrichtung
JP4866893B2 (ja) * 2008-10-30 2012-02-01 日立オートモティブシステムズ株式会社 電磁駆動型弁機構及びこれを用いた高圧燃料供給ポンプ
DE102010025370A1 (de) * 2010-06-28 2011-12-29 Schaeffler Technologies Gmbh & Co. Kg Fluidschaltventil, insbesondere Sitzventil
JP5563391B2 (ja) * 2010-07-05 2014-07-30 株式会社日本自動車部品総合研究所 電磁弁
DE102012214920A1 (de) * 2012-08-22 2014-02-27 Continental Automotive Gmbh Dämpfungsoberfläche an Ventilkomponenten
DE102014215774B4 (de) * 2014-08-08 2016-06-30 Continental Automotive Gmbh Vorrichtung für eine Hochdruckpumpe für ein Kraftfahrzeug
JP2019056419A (ja) * 2017-09-21 2019-04-11 日本電産トーソク株式会社 電磁弁
JP2019056421A (ja) * 2017-09-21 2019-04-11 日本電産トーソク株式会社 電磁弁
DE112021001012T5 (de) * 2020-02-13 2022-12-01 Padmini Vna Mechatronics Pvt. Ltd. Öl-Solenoid-Ventil mit Echtzeit-Überwachung der Kolbenposition
CN112901584B (zh) * 2021-03-10 2023-01-06 潍柴动力股份有限公司 一种电磁比例阀、流量阀及液压系统

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1459460A (en) * 1922-05-04 1923-06-19 Jenkins Brothers Valve
GB611619A (en) * 1944-11-25 1948-11-02 Bendix Aviat Corp Improvements in or relating to pressure regulating valves
DE1204485B (de) * 1963-10-05 1965-11-04 Danfoss As Magnetventil mit Abdichtung der Ventilteile gegen die Magnetteile durch einen Schlauch
DE1252319B (fr) * 1963-11-08
DE1301626B (de) * 1964-05-29 1969-08-21 Philips Patentverwaltung Magnetventil fuer eine Brennstoffeinspritzanlage fuer Brennkraftmaschinen
US3523676A (en) * 1969-02-26 1970-08-11 Monsanto Co Pulsed solenoid control valve
US3955795A (en) * 1973-11-15 1976-05-11 Refreshment Machinery Incorporated Valve
DE2658969A1 (de) * 1976-12-24 1978-07-06 Bosch Gmbh Robert Druckregelventil
DE3041018C2 (de) * 1980-10-31 1986-03-20 Daimler-Benz Ag, 7000 Stuttgart Kraftstoffeinspritzeinrichtung für eine luftverdichtende Einspritzbrennkraftmaschine
JPH0132724Y2 (fr) * 1981-03-12 1989-10-05
DE3139669A1 (de) * 1981-10-06 1983-04-21 Robert Bosch Gmbh, 7000 Stuttgart Magnetventil, insbesondere kraftstoffeinspritzventil
US4470545A (en) * 1982-02-19 1984-09-11 General Motors Corporation Electromagnetic unit fuel injector
DE3310021A1 (de) * 1983-03-19 1984-09-20 Otto 6762 Alsenz Gampper Jun. Magnetventil
DE3326840A1 (de) * 1983-07-26 1985-02-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
CH655371A5 (fr) * 1983-08-23 1986-04-15 Honeywell Lucifer Sa Valve hydraulique.

Also Published As

Publication number Publication date
EP0195261A3 (en) 1988-03-16
EP0195261A2 (fr) 1986-09-24
ATE45011T1 (de) 1989-08-15
JPS61218882A (ja) 1986-09-29
JPH0816514B2 (ja) 1996-02-21
DE3510222A1 (de) 1986-09-25
US4646976A (en) 1987-03-03
DE3664665D1 (en) 1989-08-31

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