EP0149787A2 - Dispositif de régulation de débit pour une pompe hydraulique réglable - Google Patents

Dispositif de régulation de débit pour une pompe hydraulique réglable Download PDF

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Publication number
EP0149787A2
EP0149787A2 EP84115198A EP84115198A EP0149787A2 EP 0149787 A2 EP0149787 A2 EP 0149787A2 EP 84115198 A EP84115198 A EP 84115198A EP 84115198 A EP84115198 A EP 84115198A EP 0149787 A2 EP0149787 A2 EP 0149787A2
Authority
EP
European Patent Office
Prior art keywords
valve
pump
pressure
torque
measuring spring
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
EP84115198A
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German (de)
English (en)
Other versions
EP0149787A3 (en
EP0149787B2 (fr
EP0149787B1 (fr
Inventor
Gerhard Beutler
Heinz Berthold
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.)
Brueninghaus Hydraulik GmbH
Original Assignee
Brueninghaus Hydraulik 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.)
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Publication date
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Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0149787A2 publication Critical patent/EP0149787A2/fr
Publication of EP0149787A3 publication Critical patent/EP0149787A3/de
Application granted granted Critical
Publication of EP0149787B1 publication Critical patent/EP0149787B1/fr
Publication of EP0149787B2 publication Critical patent/EP0149787B2/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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to a torque control device for an adjustable hydraulic pump with a hydraulic servo actuator for the stepless adjustment of the pump delivery rate, the delivery rate setting depending on the delivery pressure of the hydraulic pump and a pressure in an operating pressure control line, and in which the actuator is one the pump actuator in the direction of the maximum flow rate contains spring and has at least one piston acting on the pump actuator in the direction of a flow rate reduction, the piston surface of which can be acted upon by the delivery pressure or connected to the discharge via a hydraulically operated control valve, and the actuation of the control valve by the pressure in the operating pressure control line.
  • a torque controller is to keep the absorption torque of a hydraulic pump constant.
  • the relationship applies that the product of the operating pressure and the stroke volume of the pump must be constant.
  • a measure of the displacement of an H y DRO pump is the position of the pump delivery rate adjusting pump actuator.
  • a flow control device of the type mentioned which can also be combined with a torque control, is known for example from DE-AS 15 28 55o. It is an object of the invention to adjust a delivery rate device of the type mentioned in such a way that a torque control is additionally created.
  • a torque valve is provided, the closing force of which is determined by a measuring spring / measuring spring set which is connected to the pump actuator and is biased in dependence on the delivery rate setting and the torque valve Operating pressure control line depending on the pressure in the operating pressure control line and the bias of the measuring spring with the unpressurized drain.
  • the torque valve is followed by the control valve, which acts as a pressure compensator and primarily serves to adjust the delivery quantity.
  • the control valve acts as a pressure compensator and primarily serves to adjust the delivery quantity.
  • This has the advantage that the flow rate setting remains unaffected below the attractive torque control on the torque valve.
  • Another important advantage of the invention is that short swiveling times (setting times for the pump to the maximum delivery rate) are made possible because the actuating piston of the actuating device is directly connected to the process can. Nevertheless, there is a low-loss control, since in contrast to the prior art mentioned, DE-AS 2o 38 968, the torque characteristic is not determined by a throttle system by lowering the operating pressure, but only by changing the spring preload on the torque valve, i.e. by designing the Measuring spring or the measuring spring set.
  • the design and arrangement of the torque valve according to the invention in a flow rate control allows in a further embodiment of the invention that the torque valve can be attached to the hydraulic pump as a separate assembly and a driver pin of the pump actuator on the torque valve to change the bias of the measuring spring / measuring spring set depending on the flow rate setting attacks.
  • Such a torque valve can be used for pumps of different sizes and outputs, these pumps only having to match in the adjustment path for the pump actuator, that is to say, for example, in the swivel angle in the case of adjustable inclined-axis pumps.
  • An expedient embodiment of such a torque valve is characterized in claims 4 and 5.
  • the torque characteristic is determined solely by designing the characteristic of the measuring spring or the measuring spring set
  • a particularly expedient embodiment of the invention results if the stop for the measuring spring / measuring spring set can be adjusted from the outside by means of a handle in the torque valve. Due to the externally adjustable measuring spring or measuring spring set, any number of different torque characteristics can be preselected and also adjusted or adjusted during operation, which is particularly important when the pump torque is optimally adapted to the torque of the drive machine driving the pump Advantage is. A quick adaptation to any application is possible.
  • the stop in the torque valve can expediently be arranged on the end of the valve housing and be detachable for the exchange of the measuring spring / measuring spring set.
  • the torque control device is also suitable as a total control for two or more hydraulic pumps mechanically coupled on the drive side if, according to the invention, that the closing element of the torque valve of each pump depends on the sum of the pressure in the operating pressure control line of the individual pump and the pressure in the operating pressure line of the other pump / pumps and that each torque valve connects the operating pressure control line of its pump depending on the total operating pressure and the bias of its measuring spring with the unpressurized outlet.
  • the closing elements of the torque valves have a plurality of measuring surfaces which act in parallel and are each acted upon by the operating pressure of one of the pumps.
  • the hydraulic pump 1 is driven via the shaft 2 by a drive, not shown.
  • the pump actuator consists of a swivel element 3, the swivel angle ⁇ of which is proportional to the stroke volume of the hydraulic pump 1.
  • the servo actuator, not shown, for adjusting the swivel angle ⁇ comprises a spring 4 and a pressurizable actuating piston 5, the spring 4 adjusting the hydraulic pump 1 in the direction of the maximum swivel angle ⁇ , that is to say the maximum delivery volume.
  • An actuating piston 6 of the actuating device which can also be functionally combined with the piston 5, takes over the resetting function in the direction of a smaller swivel angle ⁇ .
  • the control pressure acting on the piston 6 in the line 7 is removed via a control valve 8 and the line 9 from the delivery pressure line 10 of the hydraulic pump 1.
  • a common pressure relief valve 11 is in series with the control valve 8.
  • the control valve 8 is designed as a pressure compensator and is acted upon on the one hand by the delivery pressure and on the other hand by a control pressure in the operating pressure control line 12, which controls the operating pressure of the hydraulic pump 1 behind a throttle 13 which limits the control flow the operating pressure line 14 decreases after an optionally adjustable flow restrictor 15.
  • a moment valve 16 is on the one hand acted upon by the pressure in the control line 12 and on the other hand by a measuring spring or Meßfedersatz 17 whose bias voltage is determined by the position of the piston 6 or the P umpenstellgliedes. 3
  • the torque valve 16 can connect the control line 12 to the unpressurized outlet 18.
  • the measuring spring 17 or the measuring spring set of the torque valve 16 is biased.
  • the spring characteristics of the measuring springs or the measuring spring set are designed such that, depending on the preload, an envelope curve is created in the theoretically desired power hyperbola.
  • a defined swivel angle ⁇ corresponds to a defined operating pressure in line 10.
  • FIG. 2 shows an embodiment of a torque valve 16 in its assignment to the pivotable pump actuator of an inclined-axis axial piston pump.
  • the pivotable actuator has a driver pin 20 projecting into the torque valve 16.
  • the torque valve 16 is designed as a seat valve arranged in a valve housing 21, with a valve cone 22 as a closing element, which opens from one the springs 23 and 24 formed measuring spring set 17 is acted upon.
  • the valve seat for the valve cone 22 is formed on a valve body 25 which is displaceably arranged in the valve housing 21 and on which the driver pin 20 of the pump actuator acts.
  • the valve body is acted upon by a spring 26 which is supported in the valve housing 21 and holds the valve body 25 in positive engagement with the driver pin 2o.
  • the spring 23 of the measuring spring set 17 is supported on a stop 27 and the spring 24 on an adjusting screw 28 in the stop 27.
  • the stop 27 is screwed into the end of the valve housing 21. Due to the rotational position of the stop 27, the preload of the measuring spring set 17 and thus the position of the desired torque characteristics and the response point of the torque valve 16 can be adjusted.
  • the stop 27 has a handle 29. The course of the torque characteristics or the spring characteristic can be done by changing the bias of the spring 24 with the help of the adjusting screw 28.
  • the pressure in the operating pressure control line 12 acts through the channel 3o in the valve body 25 on the closing member 22 against the force of the measuring spring set 17.
  • the width of the valve seat determines the effective measuring surface for the pressure in the line 12 on the closing member 22.
  • Exceeds the force exerted by the pressure in the line 12 on the measuring surface, the biasing force of the measuring spring set 17, the valve cone of the closing member 22 lifts off the valve seat in the valve body 25 and opens the control line, 32 for depressurized discharge, formed by the interior 31 of the fixed with the Hydraulic pump connected valve housing 21, wherein the interior 31 communicates with the unpressurized interior 32 of the hydraulic pump.
  • the driving pin 2o moves the valve body 25 in FIG. 2 to the right against the closing member 22 and thus increases the preload of the spring set 17 in accordance with the desired course of the torque characteristic.
  • FIG. 3 shows the control device according to the invention as a total torque control for two hydraulic pumps 33, 34, the drive shafts of which are driven directly or via a corresponding transfer gear 35 (only indicated schematically by a dash) by a common drive machine, not shown.
  • the control devices for the individual pumps correspond to the control device shown in FIG. The same parts are provided with the same reference numerals and are not explained again.
  • Only the torque valves denoted by 16 in FIG. 1 are designed here as total torque valves 36 and differ from the torque valve 16 in that the closing element 22 according to FIG. 4 has an additional measuring surface 37. The operating pressure of the other pump acts on this measuring surface 37 via a control line 38, 39.
  • the response that is, open the M omentenventile 36 for the control fluid in the lines 12 is performed to the pressureless outlet thus a function of the sum of the operating pressures.
  • Such regulations are necessary, for example, if two hydraulic pumps are driven by a common drive shaft or via a transfer case and the sum of the two absorption torques of the pumps must not exceed the drive torque.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
EP84115198A 1983-12-14 1984-12-12 Dispositif de régulation de débit pour une pompe hydraulique réglable Expired - Lifetime EP0149787B2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE8335902U DE8335902U1 (fr) 1983-12-14 1983-12-14
DE3345264 1983-12-14
DE19833345264 DE3345264A1 (de) 1983-12-14 1983-12-14 Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe

Publications (4)

Publication Number Publication Date
EP0149787A2 true EP0149787A2 (fr) 1985-07-31
EP0149787A3 EP0149787A3 (en) 1985-08-21
EP0149787B1 EP0149787B1 (fr) 1987-05-06
EP0149787B2 EP0149787B2 (fr) 1991-10-02

Family

ID=25816438

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84115198A Expired - Lifetime EP0149787B2 (fr) 1983-12-14 1984-12-12 Dispositif de régulation de débit pour une pompe hydraulique réglable

Country Status (4)

Country Link
US (1) US4668171A (fr)
EP (1) EP0149787B2 (fr)
JP (1) JPS60147588A (fr)
DE (2) DE8335902U1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0284989A2 (fr) * 1987-04-02 1988-10-05 BRUENINGHAUS HYDRAULIK GmbH Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune
EP0284988A2 (fr) * 1987-04-02 1988-10-05 BRUENINGHAUS HYDRAULIK GmbH Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune
EP0284987A2 (fr) * 1987-04-02 1988-10-05 BRUENINGHAUS HYDRAULIK GmbH Régulateur pour au moins deux machines hydrostatiques en relation par une conduite sous pression commune
WO1993012342A1 (fr) * 1991-12-13 1993-06-24 Putzmeister-Werk Maschinenfabrik Gmbh Regulateur de la pression initiale d'une pompe a cylindree variable
EP0554537A1 (fr) * 1992-01-30 1993-08-11 Brueninghaus Hydromatik Gmbh Machine à pistons axiaux, en particulier pompe hydraulique de type à plateau biais ou à axes inclinés, pourvue d'un dispositif de réglage du débit
EP0561153A1 (fr) * 1992-03-19 1993-09-22 Brueninghaus Hydromatik Gmbh Dispositif de réglage de puissance pour au moins deux pompes hydrostatiques à débit variable
EP0704623A1 (fr) * 1994-09-30 1996-04-03 Samsung Heavy Industries Co., Ltd Dispositif de contrÔle de refoulement pour des pompes hydrauliques
WO1996036813A1 (fr) * 1995-05-16 1996-11-21 Brueninghaus Hydromatik Gmbh Dispositif hydraulique coulissant de regulation de puissance et de couple
WO1998019069A1 (fr) 1996-10-31 1998-05-07 Brueninghaus Hydromatik Gmbh Systeme de regulation de puissance et de couple pour plusieurs pompes hydrauliques
EP1118771A2 (fr) 2000-01-18 2001-07-25 Brueninghaus Hydromatik Gmbh Dispositif de régulation de puissance
WO2005028863A1 (fr) * 2003-09-08 2005-03-31 Brueninghaus Hydromatik Gmbh Dispositif de regulation de puissance
DE102016123160A1 (de) * 2016-11-30 2018-05-30 Schwing Gmbh Großmanipulator mit schnell ein- und ausfaltbarem Knickmast

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3644769A1 (de) * 1986-12-30 1988-07-14 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer eine verstellbare hydrostatische maschine
JP2578371B2 (ja) * 1989-09-22 1997-02-05 株式会社小松製作所 可変容量ポンプの容量制御装置
DE4020325C2 (de) * 1990-06-26 1995-01-05 Hydrokraft Gmbh Regeleinrichtung für verstellbare Hydropumpen
DE4118869C2 (de) * 1991-06-07 1995-06-29 Hydromatik Gmbh Regelvorrichtung zur Regelung des Verdrängungsvolumens mehrerer hydrostatischer Maschinen
US5538401A (en) * 1994-07-05 1996-07-23 Denison Hydraulics Inc. Axial piston pump
JPH0986805A (ja) * 1995-09-25 1997-03-31 Kandenko Co Ltd ケーブルドラムの制動装置
DE19646687C1 (de) * 1996-10-31 1998-02-12 Brueninghaus Hydromatik Gmbh Leistungs- bzw. Momentenregeleinrichtung für mehrere Hydropumpen
DE19742157C2 (de) 1997-09-24 1999-07-01 Brueninghaus Hydromatik Gmbh Regeleinrichtung für eine verstellbare Hydropumpe mit mehreren Verbrauchern
DE19831587C2 (de) * 1998-07-14 2000-06-15 Brueninghaus Hydromatik Gmbh Leistungsregelvorrichtung zur Regelung der hydraulischen Leistung einer Hydropumpe
EP2049800B1 (fr) * 2006-08-21 2011-12-28 Joma-Polytec GmbH Pompe de circulation
US8647075B2 (en) * 2009-03-18 2014-02-11 Eaton Corporation Control valve for a variable displacement pump
US9086143B2 (en) 2010-11-23 2015-07-21 Caterpillar Inc. Hydraulic fan circuit having energy recovery
DE102017213458A1 (de) 2017-08-03 2019-02-07 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit Leistungsbegrenzung

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Publication number Priority date Publication date Assignee Title
FR1318661A (fr) * 1961-12-27 1963-02-22 Sciper Sa Dispositif de sécurité pour pompes volumétriques
FR2211054A5 (fr) * 1972-12-18 1974-07-12 Sperry Rand Corp
US3941513A (en) * 1974-09-05 1976-03-02 Parker-Hannifin Corporation Variable displacement pump control assembly
GB2104250A (en) * 1981-08-21 1983-03-02 Bosch Gmbh Robert An electrohydraulic adjusting device for an hydrostatic machine

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GB1126873A (en) * 1964-09-22 1968-09-11 Sperry Rand Corp Improvements in hydraulic supply and control systems
NL165340C (nl) * 1968-05-09 1981-03-16 Philips Nv Inrichting voor het opwekken van gestimuleerde infraroodemissie met een golflengte van ongeveer 10,6 mu bevattende middelen voor het instand houden van een elektrische ontlading in een gedeeltelijk uit kool- zuurgas bestaand gasmensel.
DE1921298B2 (de) * 1969-04-25 1973-08-23 Hydromatik Gmbh, 7900 Ulm Einrichtung zur regelung der foerdermenge verstellbarer axialkolbenpumpen
DE1922269A1 (de) * 1969-04-29 1970-11-12 Bellows Valvair Kaemper Gmbh Summenleistungsregler
BE757640A (fr) * 1969-10-16 1971-04-16 Borg Warner Systemes hydrauliques, notamment pour la regulation d'une pompea debit variable
US3669570A (en) * 1970-03-09 1972-06-13 Mannesmann Meer Ag Power regulation for fluid machines
US3768928A (en) * 1971-06-01 1973-10-30 Borg Warner Pump control system
DE2141722A1 (de) * 1971-08-20 1973-03-01 Bosch Gmbh Robert Druckregler fuer eine verstellbare pumpe
DD110684A1 (fr) * 1974-03-20 1975-01-05
US3935707A (en) * 1974-07-22 1976-02-03 General Signal Corporation Hydraulic control system
DE2461897A1 (de) * 1974-12-31 1976-07-08 Bosch Gmbh Robert Regeleinrichtung fuer eine pumpe
DE2551088C2 (de) * 1975-11-14 1984-06-28 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zur Mengen- und Druckregelung für Verstellpumpen
US4348159A (en) * 1980-01-07 1982-09-07 Rexnord Inc. Convertible pump servo-valve control
JPS57107407A (en) * 1980-12-25 1982-07-03 Daikin Ind Ltd Construction equipment such as power shovel

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1318661A (fr) * 1961-12-27 1963-02-22 Sciper Sa Dispositif de sécurité pour pompes volumétriques
FR2211054A5 (fr) * 1972-12-18 1974-07-12 Sperry Rand Corp
US3941513A (en) * 1974-09-05 1976-03-02 Parker-Hannifin Corporation Variable displacement pump control assembly
GB2104250A (en) * 1981-08-21 1983-03-02 Bosch Gmbh Robert An electrohydraulic adjusting device for an hydrostatic machine

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0284989A2 (fr) * 1987-04-02 1988-10-05 BRUENINGHAUS HYDRAULIK GmbH Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune
EP0284988A2 (fr) * 1987-04-02 1988-10-05 BRUENINGHAUS HYDRAULIK GmbH Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune
EP0284987A2 (fr) * 1987-04-02 1988-10-05 BRUENINGHAUS HYDRAULIK GmbH Régulateur pour au moins deux machines hydrostatiques en relation par une conduite sous pression commune
EP0284987A3 (en) * 1987-04-02 1989-12-27 Brueninghaus Hydraulik Gmbh Regulator for at least two hydrostatic machines linked to a common pressure pipe
EP0284989A3 (en) * 1987-04-02 1989-12-27 Brueninghaus Hydraulik Gmbh Regulator for at least two hydrostatic machines linked to a common pressure pipe
EP0284988A3 (en) * 1987-04-02 1989-12-27 Brueninghaus Hydraulik Gmbh Regulator for at least two hydrostatic machines linked to a common pressure pipe
US5586869A (en) * 1991-12-13 1996-12-24 Putzmeister-Werk Maschinenfabrik Gmbh Initial pressure governor for a variable displacement pump
WO1993012342A1 (fr) * 1991-12-13 1993-06-24 Putzmeister-Werk Maschinenfabrik Gmbh Regulateur de la pression initiale d'une pompe a cylindree variable
EP0554537A1 (fr) * 1992-01-30 1993-08-11 Brueninghaus Hydromatik Gmbh Machine à pistons axiaux, en particulier pompe hydraulique de type à plateau biais ou à axes inclinés, pourvue d'un dispositif de réglage du débit
EP0561153A1 (fr) * 1992-03-19 1993-09-22 Brueninghaus Hydromatik Gmbh Dispositif de réglage de puissance pour au moins deux pompes hydrostatiques à débit variable
EP0704623A1 (fr) * 1994-09-30 1996-04-03 Samsung Heavy Industries Co., Ltd Dispositif de contrÔle de refoulement pour des pompes hydrauliques
WO1996036813A1 (fr) * 1995-05-16 1996-11-21 Brueninghaus Hydromatik Gmbh Dispositif hydraulique coulissant de regulation de puissance et de couple
DE19517974A1 (de) * 1995-05-16 1996-11-21 Brueninghaus Hydromatik Gmbh Verschiebbare hydraulische Leistungs- bzw. Momentenregeleinrichtung
WO1998019069A1 (fr) 1996-10-31 1998-05-07 Brueninghaus Hydromatik Gmbh Systeme de regulation de puissance et de couple pour plusieurs pompes hydrauliques
EP1118771A2 (fr) 2000-01-18 2001-07-25 Brueninghaus Hydromatik Gmbh Dispositif de régulation de puissance
EP1118771A3 (fr) * 2000-01-18 2005-10-19 Brueninghaus Hydromatik Gmbh Dispositif de régulation de puissance
WO2005028863A1 (fr) * 2003-09-08 2005-03-31 Brueninghaus Hydromatik Gmbh Dispositif de regulation de puissance
DE102016123160A1 (de) * 2016-11-30 2018-05-30 Schwing Gmbh Großmanipulator mit schnell ein- und ausfaltbarem Knickmast

Also Published As

Publication number Publication date
US4668171A (en) 1987-05-26
EP0149787A3 (en) 1985-08-21
EP0149787B2 (fr) 1991-10-02
EP0149787B1 (fr) 1987-05-06
DE8335902U1 (fr) 1987-06-04
JPH0526955B2 (fr) 1993-04-19
DE3345264A1 (de) 1985-06-27
JPS60147588A (ja) 1985-08-03

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