EP0100334B1 - Vorrichtung zum verpressen rohrförmiger teile - Google Patents

Vorrichtung zum verpressen rohrförmiger teile Download PDF

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Publication number
EP0100334B1
EP0100334B1 EP83900555A EP83900555A EP0100334B1 EP 0100334 B1 EP0100334 B1 EP 0100334B1 EP 83900555 A EP83900555 A EP 83900555A EP 83900555 A EP83900555 A EP 83900555A EP 0100334 B1 EP0100334 B1 EP 0100334B1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
clamping jaws
area
annular
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
EP83900555A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0100334A1 (de
Inventor
Karl Sauder
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.)
Compat AG
Original Assignee
Compat AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Compat AG filed Critical Compat AG
Publication of EP0100334A1 publication Critical patent/EP0100334A1/de
Application granted granted Critical
Publication of EP0100334B1 publication Critical patent/EP0100334B1/de
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D39/00—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders
    • B21D39/04—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes with tubes; of tubes with rods
    • B21D39/046—Connecting tubes to tube-like fittings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/53—Means to assemble or disassemble
    • Y10T29/5367—Coupling to conduit

Definitions

  • the invention relates to a device for pressing tubular parts, with a plurality of spring-loaded clamping jaws, which can be adjusted in the radial direction, and a piston which acts on the clamping jaws and is annular in cross-section, on the inside of the end region facing the clamping jaws, on the inside of which is flared in the form of a piston, which is hydraulic in the direction of the clamping jaws is displaceable and can be returned to its rest position, the clamping jaws with their radially outer boundary surfaces bearing with a corresponding inclination angle on the conical extension of the piston, and the effective piston surface for the return of the double-acting piston only a fraction of the effective piston surface on the free, clamping jaws facing away and parallel to the bottom of the annular cylinder end of the piston for the feed thereof, and wherein the piston at its end forming the effective piston surface for the feed the largest cross-sectional area hey.
  • Such pipe connectors usually consist of two coaxially arranged tubular sections which are connected at one end to each other and the pipe connecting parts, for. B. thread sections, wear. An annular gap remains between the two tubular parts, the end of a hose being inserted into this gap.
  • a plurality of clamping jaws are arranged around an axis and located within a press-on element which has a conically tapering inner surface.
  • a cylindrical hydraulic piston is provided in order to move the pressing element against the clamping jaws, the clamping jaws being moved against one another in the radial direction by this displacement and the conical surfaces abutting one another.
  • the hose connection inserted between the clamping jaws is thereby pressed.
  • measuring devices which indicate whether the desired final outside diameter has been reached. For this purpose, the measuring device must be observed by the operator in order to stop the operation of the device at this moment. In such a device, relatively large hydraulic cylinders must be used in order to achieve the necessary contact pressure. If only a low operating pressure is available, there are still far more serious design problems since the device then becomes too bulky.
  • a piston is slidably mounted in a cylindrical housing with a stop collar, which is also provided with a stop collar which is directed outwards.
  • a cylinder space is created between the outer surface of the piston, the inner surface of the cylinder and the two mutually facing boundary surfaces of the stop collars, which can be acted upon hydraulically.
  • a pressing device which is actuated by a double-acting piston.
  • the pressing device is thus moved forward and backward by hydraulic force.
  • an inner and an outer cylindrical element are provided, two annular chambers being formed between these two elements.
  • the inner element acts as a hydraulic cylinder and the outer element as a hydraulic piston.
  • a correspondingly large piston area is required in order to be able to build up sufficient pressure for the pressing.
  • a correspondingly large, inwardly projecting collar must be provided to achieve the necessary piston area.
  • this piston since this piston must also form a cylinder wall, a large dimensioning is necessary at least in the transition area between this outer wall and the inwardly projecting collar.
  • a relatively thick design for the cylinder is required because the projecting collar has to absorb the enormous forces. There is no possibility of supporting from an opposite wall, since this collar is freely cantilevered.
  • a device of the type mentioned at the beginning has also become known (FR-A-2229479), in which spring-loaded clamping jaws, an annular piston with a conical extension and an adapted conical shape of the clamping jaws are provided.
  • the piston can be guided hydraulically into a pressing position and into a rest position, the piston area for the pressing position being larger than that for the return stroke.
  • An annular hydraulic cylinder is also provided, the rear of the piston being the effective piston surface for the press stroke and running parallel to the cylinder base.
  • the piston has its largest cross-sectional area on this rear side. This ensures that the required forces are matched, since a much larger piston area must be available during the pressing process than when the piston is returned to the rest position.
  • the hydraulic cylinder is designed as a one-piece part, and it is very difficult from a machining point of view to produce an annular fit exactly. However, an exact machining option is absolutely necessary, especially at the high pressures required here.
  • Another disadvantage of such a design is the one-sided loading of the clamping jaws, since the engagement end of the annular piston abuts a corner region of the radially displaceable clamping jaws, the well-provided radial guides for the clamping jaws not being sufficient due to the large force to be transmitted. Therefore, the clamping jaws very often jam and therefore damage the device and inaccurate pressing processes.
  • the annular hydraulic cylinder is formed by an outer cylinder sleeve and a coaxially inserted pipe piece, that a tapered ring is inserted axially coaxially with the piston on the free end of the outer cylinder sleeve facing away from the annular hydraulic cylinder, the inner boundary of which is widened conically towards the piston , wherein the outer boundaries of the clamping jaws, seen in the axial direction, taper conically towards both ends, and that the component formed from the pipe section and the cylinder base and the conical ring at the two ends of the outer cylinder sleeve by locking rings on the cylinder sleeve engaging in grooves in the cylinder sleeve Cylinder sleeve are fixed.
  • the measures according to the invention result in a significant improvement in the exact guidance of the clamping jaws when they are seen in the axial direction from both ends, this being only possible if an additional cone ring is used, on which the clamping jaws also rest. This eliminates the risk of canting, especially in the case of large power transmission when pressing the tubular parts.
  • this conical ring and the inner section of the hydraulic cylinder are held at the ends of the outer cylinder sleeve in a simple construction by locking rings has a special effect, especially since this outer cylinder not only forms part of the hydraulic cylinder, but also the outer one Housing and a complete cover of the parts arranged within the cylinder.
  • the fact that the attachment with such locking rings can be done is a significant improvement, especially since the accuracy of the mutual fit is not given in such a way as in the present invention by appropriate threads.
  • the individual parts can be fitted into each other in an exact fit and it is therefore only necessary to fix the position of these inserted parts within the outer cylinder sleeve due to the locking rings.
  • the measures according to the invention not only result in a very simple and precise machining option, but also in that the individual parts can be assembled without problems.
  • FIG. 1 shows an oblique view of the device
  • 2 shows a section through the device for pressing
  • Fig. 3 shows schematically an adjustable device for switching a hydraulic valve when a certain compression diameter is reached.
  • the device shown in Fig. 1 consists essentially of a cylinder body 1, in which the clamping jaws 2 and the actuators for the same are housed, and a housing 3 carrying this cylinder body 1.
  • a hydraulic valve is housed in the housing, via which the supply of the pressure medium can be regulated to the actuator. The necessary pressure can be achieved via a hand pump 4 or corresponding external connections.
  • an adjusting device 5 with an adjusting button 6 and a scale is provided. With this device, as will be explained in detail, the desired final diameter of the part to be pressed can be set.
  • An actuating handle 7 is also provided, by means of which the hydraulic valve can be switched over. As can already be seen from this Fig.
  • the device can be made in a very small but compact design, so that such a device is suitable for both stationary use and for individual use in any operation, at any location and at any location is.
  • an electrically operated pump can also be accommodated in the housing 3 in order to build up the necessary pressure.
  • the construction of the device can essentially be seen in the longitudinal section through the device according to FIG. 2.
  • a plurality of clamping jaws 2 adjoining one another in an approximately sector-like manner are provided, it being possible for different inserts to be fastened to the inner boundaries of these clamping jaws, depending on the desired end diameter range.
  • These jaws 2 are adjustable in the radial direction and spring-loaded against each other, with springs 8 being inserted into corresponding bores 9 between two jaws.
  • the clamping jaws are designed with conical lateral surfaces 10 and 11 falling towards the two ends.
  • the conical surface 11 is supported on a conical extension 12 of a cone ring 14 and the conical surface 10 on a conical extension 13 of the piston 15.
  • the piston 15 acts as an actuator for the jaws 2, so that when the piston 15 is displaced in the direction of the arrow 16, the jaws 2 are pushed against each other in the radial direction and are also slightly moved in the axial direction, since they have a uniform relative movement both to the piston 15 and also run to cone ring 14.
  • the piston 15 is of annular design and, in the exemplary embodiment shown, is inserted into an annular hydraulic cylinder.
  • the effective piston surface 18 for the advance of the piston 15 is formed on the free end of the piston 15 facing away from the clamping jaws 2 and runs parallel to the bottom 19 of the annular hydraulic cylinder 17.
  • the entire cross-sectional area of the piston 15 can thereby be utilized without additional stop webs or a correspondingly large stop collar should be provided to form a piston surface.
  • the effective piston surface 18 is thus attached to the area of the largest cross-sectional area of the piston 15. so that the structural dimensions of the piston 15 can be kept very small.
  • the ring-shaped hydraulic cylinder 17 can also be constructed very simply. This is formed by an outer cylinder sleeve 20 and a coaxially inserted tube piece, the cylinder base 19 being connected in one piece to the tube piece 21 used. This enables very simple production with turned parts.
  • the piston At its end facing the piston surface 18, the piston has a circumferential collar 22 with an outer diameter that is larger than the remaining area of the piston 15.
  • the outer boundary 23 of the hydraulic cylinder 17 is designed at least over the displacement range of the collar 22 with an enlarged inside diameter corresponding to the outside diameter of the collar 22.
  • An annular cylinder space is thereby created, which is enclosed on the one hand by the inner boundary 23 of the outer cylinder sleeve 20 and on the other hand the piston outer surface 24.
  • the boundary of the collar 22 facing away from the piston surface 18 forms a piston surface 25 which is only a fraction of the piston surface 18. With this very simple measure, not only can hydraulic compression take place, but also hydraulic return of the piston 15 to its rest position.
  • Groove-like depressions or bevels are provided on the outer edge of the base 19 of the hydraulic cylinder 17 and possibly also on the outer edge of the piston surface 18, which together form a circumferential annular channel when the piston 15 is in the rest position.
  • the supply line 34 for the pressure medium opens into this ring channel, so that even if the piston surface 18 lies directly on the base 19, the pressure medium can penetrate and cause the movement of the piston 15 in the direction of the arrow 16.
  • the supply line 35 for the pressure medium for resetting the piston 15 opens near the cylinder-side sealing ring 29 into the annular cylinder space 31, so that a proper supply for the pressure medium is possible even when the piston 15 is fully extended.
  • the described configuration also has a particular advantage in terms of construction in that no specially dimensioned screw connections are required.
  • the outer cylinder sleeve would have to have a substantially larger cross section and the other parts would also have to be correspondingly larger.
  • Grooves 37 are provided in the cylinder sleeve, into which locking rings 37 'engage. These locking rings have an L-shaped cross section, one leg abutting the inner wall of the cylinder sleeve 20 and the other leg engaging in the groove 37 on the same.
  • these locking rings 37 'into the grooves 37 are severed once or several times, seen in the circumferential direction thereof.
  • the separation surfaces of the locking rings run at an acute angle to a radial plane of the locking ring 37 'in order to thereby enable insertion.
  • the component 36 and the conical ring 14 are preferably offset at their outer edge regions over a length which corresponds to the leg of the locking ring 37 'resting on the cylinder sleeve by the thickness of this leg.
  • An adjustable switching device for switching a hydraulic valve also engages in the displacement area of the piston 15. This makes it possible, depending on the closed state of the clamping jaws 2 and thus in the exactly calculable position of the piston 15, to carry out a valve switchover so that the device operates automatically.
  • the piston surface 18 is thus acted upon up to the required compression diameter, whereupon the hydraulic valve is switched over after a previously adjustable displacement path of the piston 15, so that the annular space 31 is then acted upon and the piston 15 is returned to the rest position.
  • a control rod 38 engages in the displacement area of the piston 15, which can be brought into operative connection with a stop 40 ', which can be adjusted in its distance from the piston end on the clamping jaw side.
  • this control rod 38 is displaceably guided in a bore 39 of the fixed cone ring 14.
  • the switchover can take place by mechanical transmission or also by electrical switching means.
  • FIG. 3 By means of an adjusting knob 6, which is arranged on a threaded bolt 40, the stop 40 'for the control rod 38 can be adjusted in the axial direction, so that, depending on the desired end diameter, the piston 15 sooner or later abuts the free end of the control rod 38 and thus the stop 40 'is moved.
  • a scale 41 with a corresponding display element in order to make the adjustment visible from the outside.
  • a fine adjustment is possible, which can be regulated as a function of the thread pitch of the threaded bolt 40, so that, for example, with a corresponding thread pitch, the pressing diameter is changed by 1 mm when the adjusting knob is turned .
  • FIG. 3 A mechanical transmission of this switch can be seen in FIG. 3.
  • a control element 43 with an inclined run-up surface 44 is moved in the direction of the arrow 45 after the free end of the piston 15 abuts.
  • the bevel 46 on an actuating rod 47 can move it in the direction of arrow 48.
  • This actuating rod 47 stands with the actuating handle 7 or the connecting rod 49 connected to it in operative connection.
  • This connecting rod 49 leads to a lever 50, which causes the switching of the hydraulic valve 51.
  • the actuating rod 47 engages in a recess 60 on the bolt 52 of the connecting rod 49 and thus locks this connecting rod 49 in a position in which the hydraulic valve 51 is switched to the feed position for the piston 15.
  • the actuating rod 47 can again return to the position shown in FIG. 3, so that the connecting rod 49 or the bolt 52 in turn fixes the same becomes.
  • the control rod 38 could also be designed to be spring-loaded, so that it rests against the stop 40 'in its rest position.
  • a particular advantage of the design described is the relatively short overall length of the device, which is achieved by the special design of the double-acting piston. This eliminates the essential structural lengths, which are given, for example, by springs which are intended to cause a piston to return. The return can also be done hydraulically in a simple manner, so that these additional components can be omitted.
  • the device described also has a particular advantage in that the piston 15 can be moved relatively easily as long as there is no compression of a pipe connection. This is very easy because there are no special opposing forces.
  • This has made it possible to seal the storage tank for the pressure medium, which will usually be oil, in an airtight manner, so that a pressure can be built up within the storage tank. It is sufficient if compressed air is introduced into the free space of the storage tank so that the actual pressure medium is preloaded. There is therefore the possibility. without actuating a pump to supply the pressure medium solely through the pressure built up in the storage tank via the feed line 34, so that the piston 15 up to that starting position. in which it comes to the parts to be pressed, is advanced in a rapid gear.
  • the device described is practically insensitive to faults and thus also maintenance-free.
  • the parts in which there is a risk of damage are covered entirely or are not accessible from the outside when the parts to be pressed are inserted. It is thus also a very simple handling of this device.
  • the construction is simple and, in spite of the high pressures that can be achieved, can be carried out in a relatively small dimension, so that the device becomes very light and therefore also easy to transport.
  • the simple construction also results in an inexpensive construction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Earth Drilling (AREA)
  • Reduction Or Emphasis Of Bandwidth Of Signals (AREA)
  • Actuator (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
  • Medicines Containing Material From Animals Or Micro-Organisms (AREA)
  • Fats And Perfumes (AREA)
  • Clamps And Clips (AREA)
  • Shaping Of Tube Ends By Bending Or Straightening (AREA)
  • Surgical Instruments (AREA)
  • Quick-Acting Or Multi-Walled Pipe Joints (AREA)
  • Jellies, Jams, And Syrups (AREA)
  • Pipe Accessories (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)
  • Jigs For Machine Tools (AREA)
  • Pens And Brushes (AREA)
  • Forging (AREA)
  • Springs (AREA)
  • Investigating Or Analyzing Materials By The Use Of Ultrasonic Waves (AREA)
  • Control And Other Processes For Unpacking Of Materials (AREA)
  • Massaging Devices (AREA)
  • Manufacturing Of Electrical Connectors (AREA)
  • Making Paper Articles (AREA)
  • Processing Of Meat And Fish (AREA)
  • Measurement Of Radiation (AREA)
  • Magnetic Resonance Imaging Apparatus (AREA)
  • Analysing Materials By The Use Of Radiation (AREA)
  • Lining Or Joining Of Plastics Or The Like (AREA)
  • Automatic Assembly (AREA)
EP83900555A 1982-02-04 1983-02-01 Vorrichtung zum verpressen rohrförmiger teile Expired EP0100334B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0042482A AT376589B (de) 1982-02-04 1982-02-04 Vorrichtung zum verpressen rohrfoermiger teile
AT424/82 1982-02-04

Publications (2)

Publication Number Publication Date
EP0100334A1 EP0100334A1 (de) 1984-02-15
EP0100334B1 true EP0100334B1 (de) 1986-05-28

Family

ID=3490242

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83900555A Expired EP0100334B1 (de) 1982-02-04 1983-02-01 Vorrichtung zum verpressen rohrförmiger teile

Country Status (17)

Country Link
US (1) US4696085A (da)
EP (1) EP0100334B1 (da)
JP (1) JPS59500091A (da)
AT (2) AT376589B (da)
AU (1) AU561471B2 (da)
BR (1) BR8305746A (da)
CA (1) CA1207991A (da)
DE (1) DE3363630D1 (da)
DK (1) DK455983D0 (da)
ES (1) ES519509A0 (da)
FI (1) FI833575A7 (da)
HU (1) HUT36734A (da)
IT (1) IT1167313B (da)
NO (1) NO154185C (da)
NZ (1) NZ203168A (da)
WO (1) WO1983002737A1 (da)
ZA (1) ZA83745B (da)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3611253A1 (de) * 1986-04-04 1987-10-08 Peter Dipl Ing Schroeck Radialpresse
JPH0248092Y2 (da) * 1987-12-29 1990-12-18
WO2003057385A1 (en) * 2001-12-31 2003-07-17 Eaton Corporation Crimping apparatus for collars, method of crimping collars and a crimping kit
WO2004058601A1 (en) 2002-12-31 2004-07-15 Hellenic Environmental Systems Industry S.A. Waste container with swinging arms pivotally connected to the lid thereof
US6993953B2 (en) * 2003-02-04 2006-02-07 Interface Associates, Inc. Swaging die and method of use
EP1968686B1 (en) 2005-12-16 2019-05-08 Confluent Medical Technologies, Inc. Multi-layer balloons for medical applications
US20100229617A1 (en) * 2009-03-13 2010-09-16 Freudenberg-Nok General Partnership Swaging Operation For Relieving Stress From A Bushing Flange
US9283613B2 (en) * 2012-11-01 2016-03-15 Betaswage Pty Ltd Indexing die shoes in a swage press
CA2968508C (en) 2014-10-27 2023-08-08 Interface Associates, Inc. Methods of manufacturing nested balloons utilizing pressurized constrained annealing
CN114310180B (zh) * 2021-12-30 2024-01-05 辽宁美托科技股份有限公司 一种航空用新型35MPa轴向挤压管路连接件制造装配方法

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2999405A (en) * 1957-12-24 1961-09-12 Smith Corp A O Apparatus for radially compressing articles
US3370451A (en) * 1965-06-28 1968-02-27 Blaw Knox Co Apparatus and method for pointing tubes
US3977065A (en) * 1973-03-01 1976-08-31 Wyle Laboratories Crimping machine
US3879834A (en) * 1973-03-01 1975-04-29 Wyle Laboratories Crimping Machine
FR2229479A1 (en) * 1973-05-15 1974-12-13 Peeters Etude Realisat Eng Crimping machine for flexible tube end fittings - has hydraulic piston assembly and automatic stroke regulation
US3851514A (en) * 1973-07-18 1974-12-03 Weatherhead Co Swing-open crimper
US3972112A (en) * 1974-11-25 1976-08-03 Parker-Hannifin Corporation Method and apparatus for forming tube coupling joint
SE7513288L (sv) * 1975-01-27 1976-07-28 Wyle Laboratories Pressningsmaskin, foretredesvis for montering av ett beslag pa en slang eller liknande
GB1484515A (en) * 1975-04-16 1977-09-01 Imp Eastman Ltd Crimping apparatus
GB1569126A (en) * 1976-02-24 1980-06-11 Andrew Hydraulics Int Device for crimping tubular elements
DE2613240A1 (de) * 1976-03-27 1977-10-06 Schauz Ind Handel Gmbh Vorrichtung zum festpressen von armaturen auf schlauchenden
US4034593A (en) * 1976-04-09 1977-07-12 The Weatherhead Company Crimping machine with automatic swing open pushers
DE2844475C2 (de) * 1978-10-12 1983-09-29 Peter Ing.(grad.) 6380 Bad Homburg Schröck Radialpresse für Werkstücke mit zylindrischer Außenfläche
JPS55100835A (en) * 1979-01-29 1980-08-01 Matsutani Seisakusho:Kk Constantly loaded staking apparatus
US4314706A (en) * 1979-05-07 1982-02-09 Cushman Industries, Incorporated Chucks of constant jaw force
GB2059840B (en) * 1979-10-08 1983-03-02 Andrew Hydraulics Internatonal Crimping device
US4331019A (en) * 1979-10-12 1982-05-25 Andrew Hydraulics International Limited Device for crimping tubular elements
US4432559A (en) * 1981-12-16 1984-02-21 Robert Rasmussen Hydraulic chuck having ring collet

Also Published As

Publication number Publication date
DE3363630D1 (en) 1986-07-03
IT8367114A0 (it) 1983-02-03
JPS59500091A (ja) 1984-01-19
DK455983A (da) 1983-10-03
NZ203168A (en) 1986-01-24
AU1158683A (en) 1983-08-25
CA1207991A (en) 1986-07-22
EP0100334A1 (de) 1984-02-15
BR8305746A (pt) 1984-01-10
IT1167313B (it) 1987-05-13
FI833575A0 (fi) 1983-10-03
ES8402409A1 (es) 1984-02-01
ATE19967T1 (de) 1986-06-15
ES519509A0 (es) 1984-02-01
FI833575L (fi) 1983-10-03
NO833584L (no) 1983-10-03
IT8367114A1 (it) 1984-08-03
US4696085A (en) 1987-09-29
NO154185C (no) 1986-08-06
HUT36734A (en) 1985-10-28
ZA83745B (en) 1983-11-30
ATA42482A (de) 1984-05-15
WO1983002737A1 (fr) 1983-08-18
AT376589B (de) 1984-12-10
AU561471B2 (en) 1987-05-07
FI833575A7 (fi) 1983-10-03
NO154185B (no) 1986-04-28
DK455983D0 (da) 1983-10-03

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