EP0000777A1 - Regeleinrichtung für eine Axialkolbenpumpe - Google Patents

Regeleinrichtung für eine Axialkolbenpumpe Download PDF

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Publication number
EP0000777A1
EP0000777A1 EP78100590A EP78100590A EP0000777A1 EP 0000777 A1 EP0000777 A1 EP 0000777A1 EP 78100590 A EP78100590 A EP 78100590A EP 78100590 A EP78100590 A EP 78100590A EP 0000777 A1 EP0000777 A1 EP 0000777A1
Authority
EP
European Patent Office
Prior art keywords
control
piston
control device
axis
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP78100590A
Other languages
German (de)
English (en)
French (fr)
Inventor
Walter Heyl
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.)
Linde GmbH
Original Assignee
Linde 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 Linde GmbH filed Critical Linde GmbH
Publication of EP0000777A1 publication Critical patent/EP0000777A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F16H61/433—Pump capacity control by fluid pressure control means
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F16H61/431—Pump capacity control by electro-hydraulic control means, e.g. using solenoid valves
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D17/00—Control of torque; Control of mechanical power
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1203—Power on the axis

Definitions

  • the invention relates to a control device for the actuating device of an axial piston pump with an actuator and with an actuating piston connected to the actuator and designed as a differential piston, the small area of which is acted upon directly by the delivery pressure and the large area of which is acted upon by the delivery pressure via the control member, the regulating device also being used a control element (control slide) and is provided with an angle lever.
  • this configuration is not suitable for actuating or regulating devices in which the actuating piston has to cover a large piston stroke. This is particularly the case with pumps that are designed according to the swivel slide principle. In these, it also prepares constructive considerable difficulties that pressure-displacement measuring spring immediacy - bar with the control piston to connect as a spring for such a large spring travel is very large volume on the one hand and requires very large amount of space, but on the other hand, considerable effort to avoid kinking the spring.
  • a lever is arranged at least approximately parallel to the actuating piston, one end of the lever being connected in an articulated manner to the actuating piston and a spring being clamped between the other end of the lever and the actuating piston, and the lever with its side surface against the control slide presses.
  • the pivot point of the lever can be moved and a displacement of the actuating piston leads to lateral forces on the control slide (DT-OS 2 003 77 4 ).
  • a control device for the actuating device of an axial piston pump with an actuator and with an actuating piston configured as a differential piston the small area of which is acted upon directly by the delivery pressure and the large area of which is acted upon by the delivery pressure via the control member, is known with a control slide valve and with a Angle lever, the pivot axis of which is fixedly mounted on the housing, a force transmitter element being connected to the actuating piston and having a pressure body which bears perpendicularly to the axis of the actuating piston against one leg of the angle lever.
  • this pressure body is the control piston acted upon by the control pressure, the end of the angle lever against which the pressure body rests, is supported against a housing-fixed spring and the other end of the bell crank is connected to the control spool by a joint (DT-OS 2 017 656).
  • the control piston mounted in the control piston is structurally complex and here, too, both on the control piston and on the control piston occur very considerable on the control piston.
  • a lever system with a variable transmission ratio is used to transmit the forces.
  • the actuating piston is connected to a link which rests against the S l part and on the other hand rests against a lever, 1 one end of the lever is supported against a piston actuated by the delivery pressure and the second end is supported against the control slide supported by the spring ( DT-AS 620).
  • the pivot point of the two-armed lifting device is also movable here.
  • Another known control device also uses a lever system with variable transmission ratios.
  • a lever is provided see, the pivot point is displaceable and one end of which is supported against a spring.
  • the biasing force of the spring is variable depending on the position of the actuating piston and the other end of the lever acts on a pressure control valve.
  • the disadvantages of a movable lever joint described at the beginning occur (DT-OS 1 400 630 and DT-OS 1 425 756).
  • the invention has for its object to provide a control device which is suitable for machines with a large actuating piston stroke and which avoids the disadvantages mentioned.
  • the facility With such a facility, not only is the task accomplished, but the facility also has the advantage that one and the same device can be used for pumps of different sizes that are similar to one another and can be attached to them, since with a smaller actuating piston stroke only the distance that the pressure element travels relative to one arm of the angle lever becomes smaller.
  • the invention enables a controller in which the pressure-displacement measuring spring only makes a very small stroke, although the actuating piston makes a very large stroke. This means that the construction effort is relatively low.
  • a controller is created which is also suitable for pumps constructed according to the swivel slide principle and, moreover, does not significantly increase the installation space required for these pumps.
  • the use of a control device according to the invention in swing carriage machines represents a significant advance.
  • Damping devices can be provided to avoid vibrations of the controller.
  • One possibility for providing a damping device is between the pressure body and the actuating piston, in which a pressure space is provided between the two, which is reduced when the pressure body withdraws, the oil emerging from this pressure space through a throttle groove.
  • the space in front of the spring-side end face of the control slide can act as a damping be designed space that is connected to the interior via a throttle. This throttle point can be adjusted in a practical refinement in order to achieve such a damping with certainty, which guarantees freedom from vibrations, but on the other hand causes the controller to respond not too slowly.
  • the control piston and control spool on the one hand and the control piston can lie one behind the other in one plane. But they can also be arranged side by side in the direction of the machine shaft such that the axis of the control piston, the axis of the control slide and the angle lever lie in a plane which runs parallel to the axis of the actuating piston at a distance from it.
  • the direction of displacement of the pressure element is tangential to this axis in a plane lying at least approximately perpendicular to the axis of the actuating piston.
  • This has the consequence that the force exerted by the pressure body exerts a torque on the actuating body, which must be received on a corresponding support.
  • this arrangement has the advantage that much less space is required.
  • the same advantage is achieved if, as in the first case, the axes of the actuating piston, control piston and control slide lie in one plane, but this is perpendicular to the plane in which the shaft of the pump and the cylinder drum axis lie.
  • control piston and control spool can be arranged coaxially to one another. However, they can also be offset from one another in the plane in which the angle lever lies, so that a lever ratio between the control piston and the control slide is achieved.
  • the device can also be used as a control or regulating device for multiple pumps.
  • two or more control pistons can be arranged parallel to each other, each of which is acted upon by a pump.
  • the control piston can be designed as a step piston, with each step being acted upon by a pump.
  • the actuating piston is then connected to the various pumps, for example when the pumps are designed as swivel carriage pumps with the swivel carriage of the various pumps or with a swivel carriage common to all pumps.
  • the cylinder drum of the axial piston pump which is no longer shown in the drawing, is supported on the center pin 1 and bears against the control mirror 2 on the swivel slide 3, which in turn bears against the hollow cylindrical surface 4 of the housing base 5.
  • a guide hole 6 is provided in the swivel slide 3, into which the central pin 1 engages and into which the adjusting pin 8 engages with its spherical end part 7.
  • Control kidneys 9 are furthermore formed in the swivel slide 3 and are connected by the channels 10 to a channel 11 in the housing base 5. This channel 11 is connected to a cylinder chamber 12 in which the part 13 of small diameter of the actuating piston 13, 14 can be displaced.
  • the part 14 of large diameter is displaceable in the cylinder 15, which is closed by a cover 16.
  • an adjusting screw 17 is arranged, which can be fixed by a lock nut 18 and whose end face represents a stop for the displacement of the adjusting piston 13, 14 to the left in the drawing.
  • the screw 20, which can be fixed by a lock nut 19 forms an adjustable stop for the displacement path of the adjusting piston bens 13, 14 to the right in the drawing.
  • a bore 29 is provided in the adjusting pin 8, through which extends the guide part 21 of the pressure element, which rests against the surface 30 of the angle lever 31 by means of a ball 28.
  • a groove 22 is formed on the guide part 21 of the pressure body, which acts as a damping throttle for the liquid emerging from the bore 29 when the guide part 21 withdraws.
  • a first spring 26 is clamped between the adjusting pins 8 and the shoulder part 27 of the pressure body.
  • the angle lever 31 is easily rotatably supported on a journal 32.
  • a rolling bearing or a low-friction, wear-resistant slide bearing can be provided on the journal 32.
  • control piston 34 abuts and, on the other hand, the control slide 35 bears under the action of the force of the second spring 36, which on the one hand abuts directly against the control slide 35 and, on the other hand, is supported against a spring plate 37 whose position is determined by an adjusting screw 38 which is fixed by a nut 39.
  • the cylinder 12 is connected to the channel 11.
  • This channel 11 continues in the channel 40, which opens into the cylinder 41, in which the control piston 34 is displaceable.
  • a branch duct 61 branches off from the duct 40 and opens into the bore 42, in which the control slide 35 can be displaced.
  • the branch channel 61 opens into a region of the bore 42, which is always opposite an annular groove in the control slide 35, which in the drawing lies to the left of the collar 43, which in the position shown in the drawing exactly closes the annular space 44.
  • a channel 45 which leads to the cylinder 15, adjoins this annular space 44.
  • a drain line 46 opens into the bore 42.
  • the control piston 34 is provided with an extension 47 which can come to rest against an adjusting screw 48 which can be fixed by a nut 49.
  • the control piston 34 can be displaced by the adjusting screw 48 in such a way that the control slide 35 closes the annular groove 44 with its collar 43.
  • the screw 48 is then screwed back by a predetermined amount and thus releases the possible retraction path of the control piston 34.
  • the set screw 50 is provided with a conical end 51.
  • the path that the edge 52 of the control slide 35 can travel can be limited.
  • the largest possible free cross-section at the edge of the annular groove 44 between the latter and the collar 43 and thus the greatest possible actuating speed can be determined in both directions by the screws 50 and 48.
  • the screws 50 By screwing the screws 50 in such a way that the conical part protrudes into the bore 42, the movement of the edge of the control slide 35 opposite the edge 52 in the same annular groove can be further limited, so that, for example, when the control device is removed, it is prevented that the Control spool 35 is pressed out of the bore 42 by the second spring 36.
  • the screw 50 can be fixed by the lock nut 53.
  • the space vcr of the spring-side end face of the control slide 35 is connected to the housing interior 63 through the bore 62.
  • An adjustable throttle point is arranged in the bore. This provides adjustable damping. This throttle point is no longer shown in the drawing.
  • this surface of the angle lever 31, 33 against which the pressure body 27, 28 runs can be curved in a curve. This changes the characteristics. This is particularly useful for small capacities where the pump has to go through a large adjustment range. It can also be provided that differently curved cam tracks can be placed on one and the same angle lever 31, 33.
  • a thrust surface body is placed on the angle lever 31, 33, against the thrust surface of which the pressure element 27, 28 runs, this thrust body being connected to the angle lever 31, 33 in such a way that the position of the thrust surface relative to the angle lever is changed can, for example by means of an adjusting screw which is arranged approximately tangentially to the axis of the joint 32, the position of the end of the contact surface with respect to this arm 31 of the angle lever 31, 33 can be changed. Since the joint-side end of the contact surface lies directly on the angle lever 31, 33, the slope of the contact surface relative to the angle lever can be adjusted. It is particularly expedient if the adjusting screw mentioned is arranged in such a way that it is easily accessible through an opening in the housing which can be closed by means of a cover.
  • the embodiment according to FIG. 2 differs from that according to FIG. 1 in that, in place of the lever 31 mounted on the pivot pin 32, a lever 81 mounted on the pivot pin 32 is placed, on which a further lever 82 is mounted by means of the joint 80.
  • This lever 82 has a hyperbola-shaped surface 83 against which the pressing body 28, 27 bears.
  • the set screw 84 it is possible to adjust the position of the right end of the lever 82 in the drawing relative to the corresponding end of the lever 81.
  • the set screw 84 can be fixed in any position.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Reciprocating Pumps (AREA)
EP78100590A 1977-08-03 1978-08-03 Regeleinrichtung für eine Axialkolbenpumpe Withdrawn EP0000777A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2734933 1977-08-03
DE19772734933 DE2734933A1 (de) 1977-08-03 1977-08-03 Regeleinrichtung fuer eine axialkolbenpumpe

Publications (1)

Publication Number Publication Date
EP0000777A1 true EP0000777A1 (de) 1979-02-21

Family

ID=6015505

Family Applications (1)

Application Number Title Priority Date Filing Date
EP78100590A Withdrawn EP0000777A1 (de) 1977-08-03 1978-08-03 Regeleinrichtung für eine Axialkolbenpumpe

Country Status (7)

Country Link
US (1) US4273517A (it)
EP (1) EP0000777A1 (it)
JP (1) JPS5448303A (it)
BR (1) BR7804971A (it)
DE (1) DE2734933A1 (it)
IT (1) IT1097795B (it)
YU (1) YU186178A (it)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2558537A1 (fr) * 1984-01-19 1985-07-26 Linde Ag Regulateur de debit pour pompe hydrostatique, ou un piston de mesure de pression est charge par la pression de refoulement

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2930139A1 (de) * 1979-07-25 1981-02-12 Linde Ag Regeleinrichtung fuer ein hydrostatisches getriebe oder eine kolbenpumpe
US4375942A (en) * 1981-04-21 1983-03-08 Dynes/Rivett Inc. Tilting cam, rotating barrel pump
DE3207961A1 (de) * 1982-01-14 1983-07-21 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zum konstanthalten des produktes von foerderdruck und foerdervolumen einer verstellbaren pumpe
DE3323278C2 (de) * 1983-06-28 1986-05-22 Hydromatik GmbH, 7915 Elchingen Regelvorrichtung für mehrere aus hydrostatischen Getrieben bestehende Antriebsaggregate
US6099264A (en) * 1998-08-27 2000-08-08 Itt Manufacturing Enterprises, Inc. Pump controller
US6164924A (en) * 1998-09-01 2000-12-26 Oil-Rite Corporation Piston and drive assembly for use in a pump
US6257119B1 (en) * 1999-02-26 2001-07-10 Sauer-Danfoss Inc. Ball joint for servo piston actuation in a bent axis hydraulic unit
EP2174010A1 (de) * 2007-08-07 2010-04-14 Robert Bosch GmbH Hydrostatische maschine mit stellvorrichtung mit rückführelement zur ansteuerung eines regelventils
US20150345628A1 (en) * 2014-05-28 2015-12-03 Caterpillar Paving Products Inc. Power management system and method for power generation apparatus
DE102019205140A1 (de) * 2019-04-10 2020-10-15 Robert Bosch Gmbh Axialkolbenmaschine mit in die Anschlussplatte integrierten Ventilschiebern

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2971498A (en) * 1956-02-21 1961-02-14 Von Roll Ag Hydraulic control device for a hydrostatic drive
DE1154689B (de) * 1960-07-09 1963-09-19 Linde Eismasch Ag Einrichtung zum Steuern einer stufenlos regelbaren hydrostatischen Einheit
DE1528382A1 (de) * 1965-08-23 1969-06-26 Bosch Gmbh Robert Regel- und Steuereinrichtung
FR1588608A (it) * 1968-09-20 1970-04-17
DE1906983A1 (de) * 1969-02-07 1970-09-17 Bellows Valvair Kaemper Gmbh Vorrichtung zum Konstanthalten des Produktes aus Druck und Hubvolumen bei Verdraengerpumpen
DE1911695A1 (de) * 1969-03-03 1970-11-19 Mannesmann Meer Ag Leistungsregler fuer Hydraulikpumpen oder -motoren
DE2040205A1 (de) * 1970-08-13 1972-02-17 Bosch Gmbh Robert Steuer- und Regeleinrichtung fuer eine verstellbare Pumpe
DE1623779B1 (de) * 1967-12-14 1972-04-27 Bosch Gmbh Robert Funktionsgeber für Leistungsregler von Kolben-,vorzugsweise Axialkolbenpumpen
US3969896A (en) * 1975-05-08 1976-07-20 Sundstrand Corporation Transmission ratio control system
DE2501867A1 (de) * 1975-01-17 1976-07-22 Hydromatik Gmbh Axialkolbenmaschine in schraegachsen- bauweise mit schwenkbarer zylindertrommel

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1044620B (de) * 1957-11-22 1958-11-20 Brueninghaus Gmbh Stahlwerke Hydraulische Regelung fuer Pumpen, insbesondere Axialkolbenpumpen
DE1400630A1 (de) * 1961-05-17 1969-03-20 Conen Dipl Ing Helmut Leistungsregler fuer ein hydrostatisches Triebwerk
DE1425756A1 (de) * 1962-12-01 1969-04-10 Conen Dipl Ing Helmut Leistungsregler fuer ein hydrostatisches Triebwerk
DE1267092B (de) * 1964-10-16 1968-04-25 Bosch Gmbh Robert Leistungsregler fuer Kolbenpumpen und -motoren
DE1498288C3 (de) * 1965-06-19 1975-08-14 Robert Bosch Gmbh, 7000 Stuttgart Regelsystem für konstante hydraulische Leistung
DE1653385C3 (de) * 1967-08-25 1980-07-24 Volvo Hydraulikfabrik Gmbh, 1000 Berlin Vorrichtung zum Konstanthalten des Produktes aus Druck und Hubvolumen bei einer Verdrängerpumpe
DE2003774A1 (de) * 1970-01-23 1971-07-29 Bellows Valvair Deutschland Ni Vorrichtung zum Konstanthalten des Produktes aus Druck und Hubvolumen bei Verdraengerpumpen
US3669570A (en) * 1970-03-09 1972-06-13 Mannesmann Meer Ag Power regulation for fluid machines
DD98980A1 (it) * 1972-04-05 1973-07-12
SE373188B (it) * 1973-04-25 1975-01-27 Volvo Flygmotor Ab
GB1523588A (en) * 1974-11-18 1978-09-06 Massey Ferguson Services Nv Control systems for variable capacity hydraulic machines

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2971498A (en) * 1956-02-21 1961-02-14 Von Roll Ag Hydraulic control device for a hydrostatic drive
DE1154689B (de) * 1960-07-09 1963-09-19 Linde Eismasch Ag Einrichtung zum Steuern einer stufenlos regelbaren hydrostatischen Einheit
DE1528382A1 (de) * 1965-08-23 1969-06-26 Bosch Gmbh Robert Regel- und Steuereinrichtung
DE1623779B1 (de) * 1967-12-14 1972-04-27 Bosch Gmbh Robert Funktionsgeber für Leistungsregler von Kolben-,vorzugsweise Axialkolbenpumpen
FR1588608A (it) * 1968-09-20 1970-04-17
DE1906983A1 (de) * 1969-02-07 1970-09-17 Bellows Valvair Kaemper Gmbh Vorrichtung zum Konstanthalten des Produktes aus Druck und Hubvolumen bei Verdraengerpumpen
DE1911695A1 (de) * 1969-03-03 1970-11-19 Mannesmann Meer Ag Leistungsregler fuer Hydraulikpumpen oder -motoren
DE2040205A1 (de) * 1970-08-13 1972-02-17 Bosch Gmbh Robert Steuer- und Regeleinrichtung fuer eine verstellbare Pumpe
DE2501867A1 (de) * 1975-01-17 1976-07-22 Hydromatik Gmbh Axialkolbenmaschine in schraegachsen- bauweise mit schwenkbarer zylindertrommel
US3969896A (en) * 1975-05-08 1976-07-20 Sundstrand Corporation Transmission ratio control system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2558537A1 (fr) * 1984-01-19 1985-07-26 Linde Ag Regulateur de debit pour pompe hydrostatique, ou un piston de mesure de pression est charge par la pression de refoulement

Also Published As

Publication number Publication date
IT1097795B (it) 1985-08-31
IT7826225A0 (it) 1978-07-28
YU186178A (en) 1982-05-31
DE2734933A1 (de) 1979-02-15
BR7804971A (pt) 1979-05-22
JPS5448303A (en) 1979-04-16
JPS6347912B2 (it) 1988-09-26
US4273517A (en) 1981-06-16

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Inventor name: HEYL, WALTER