EP0100334B1 - Apparatus for pressing tubular parts - Google Patents

Apparatus for pressing tubular parts 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
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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
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German (de)
French (fr)
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EP0100334A1 (en
Inventor
Karl Sauder
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Compat AG
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Compat AG
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Publication date
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Publication of EP0100334A1 publication Critical patent/EP0100334A1/en
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Publication of EP0100334B1 publication Critical patent/EP0100334B1/en
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    • 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.

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

Abstract

PCT No. PCT/EP83/00024 Sec. 371 Date Oct. 4, 1983 Sec. 102(e) Date Oct. 4, 1983 PCT Filed Feb. 1, 1983 PCT Pub. No. WO83/02737 PCT Pub. Date Aug. 18, 1983.An apparatus for pressing tubular parts, more particularly for pressing or forcing pipe-unions onto pipes, sleeves or hoses. The apparatus includes a plurality of spring loaded, radially adjustable jaws and an annular piston in operative communication with the jaws. The piston can move hydraulically towards the jaws and can be returned hydraulically to its neutral position. The effective area of the piston, by means of which it is returned to its neutral position, amounts to only a fraction of the piston-area which advances the piston. The end of the piston remote from the jaws engages in an annular hydraulic cylinder, the entire cross-section of the piston which is largest at this end, forming the effective piston-area which advances the piston.

Description

Die Erfindung betrifft eine Vorrichtung zum Verpressen rohrförmiger Teile, mit mehreren, in radialer Richtung verstellbaren, federbelasteten Klemmbacken und einem auf die Klemmbacken einwirkenden, im Querschnitt ringförmigen, an dem den Klemmbacken zugewandten Endbereich an seiner Innenseite kegelförmig erweiterten Kolben, welcher hydraulisch in Richtung der Klemmbacken verschiebbar und in seine Ruhestellung rückführbar ist, wobei die Klemmbacken mit ihren radial außenliegenden Begrenzungsflächen mit korrespondierendem Neigungswinkel an der kegelförmigen Erweiterung des Kolbens anliegen, und wobei die wirksame Kolbenfläche für die Rückstellung des doppelt wirkenden Kolbens nur einen Bruchteil der wirksamen kolbenfläche am freien, den Klemmbacken abgewandten und parallel zum Boden des ringförmigen Zylinders verlaufenden Ende des Kolbens für den Vorschub desselben beträgt, und wobei der Kolben an seinem die wirksame Kolbenfläche für den Vorschub bildenden Ende die größte Querschnittsfläche aufweist.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.

Es sind bereits einige Ausführungsformen solcher Vorrichtungen, welche im besonderen zum Aufpressen von Rohrverbindungsstücken auf die Enden von Hydraulikschläuchen eingesetzt werden, bekannt geworden. Solche Rohrverbindungsstücke bestehen in der Regel aus zwei koaxial zueinander angeordneten rohrförmigen Abschnitten, welche an ihrem einen Ende miteinander verbunden sind und die Rohrverbindungsteile, z. B. Gewindeabschnitte, tragen. Zwischen den beiden rohrförmigen Teilen verbleibt ein ringförmiger Spalt, wobei in diesen Spalt das Ende eines Schlauches eingeschoben wird.Some embodiments of such devices, which are used in particular for pressing pipe connectors onto the ends of hydraulic hoses, have already become known. 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.

Diese aufgesteckten Rohrverbindungsstücke werden dann zwischen die Klemmbacken der Vorrichtung eingeschoben und radial verpreßt, so daß das Ende des eingesetzten Schlauches fest zwischen den beiden rohrförmigen Abschnitten eingeklemmt wird.These attached pipe connectors are then inserted between the jaws of the device and pressed radially, so that the end of the hose used is firmly clamped between the two tubular sections.

Bei einer solchen bekannten Vorrichtung sind mehrere Klemmbacken um eine Achse herum angeordnet und innerhalb eines Aufpreßelementes gelegen, das eine sich konisch verjüngende Innenfläche aufweist. Es wird hier ein zylindrischer Hydraulikkolben vorgesehen, um das Aufpreßelement gegen die Klemmbacken zu verschieben, wobei durch diese Verschiebung und die aneinander anliegenden kegelförmigen Flächen die Klemmbacken in radialer Richtung gegeneinander bewegt werden. Die zwischen den Klemmbacken eingesetzte Schlauchverbindung wird dadurch gepreßt. Es sind ferner Meßeinrichtungen vorhanden, die anzeigen, ob der gewünschte End-Außendurchmesser erreicht worden ist. Zu diesem Zweck muß die Meßeinrichtung von der Bedienungsperson beobachtet werden, um den Betrieb der Vorrichtung in diesem Moment anzuhalten. Bei einer derartigen Vorrichtung müssen Hydraulikzylinder relativ großer Bauart verwendet werden, um den notwendigen Anpreßdruck zu erreichen. Falls nur ein niedriger Betriebsdruck zur Verfügung steht, ergeben sich noch weit schwerere Konstruktionsprobleme, da die Vorrichtung dann zu sperrig wird.In such a known device, a plurality of clamping jaws are arranged around an axis and located within a press-on element which has a conically tapering inner surface. Here, 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. There are also 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.

Es ist auch schon versucht worden, einen axial zur Klemmbackenachse ausgerichteten, großflächigen Kolben vorzusehen. Bei einer derartigen Ausführung ist jedoch die Vorrichtung nur von einer Seite her zugänglich, so daß nur Endrohrverbindungsstücke aufgepreßt werden können. Eine Muffenverbindung einer Schlauchleitung kann beispielsweise mit einer derartigen Anordnung nicht durchgeführt werden. Außerdem sind bei dieser Anordnung eine Vielzahl von federbelasteten Spindeln erforderlich, um das Betätigungsorgan für die Klemmbacken wiederum in die Ruhestellung zurückzuziehen. Dies bedingt wiederum eine aufwendige und kostspielige Konstruktion. Wenn diese Spindeln mit den Federn nicht angeordnet sind, besteht nur die Möglichkeit, eine Rückstellung durch das Eigengewicht des Betätigungsorgans und die federbelasteten Klemmbacken zu erreichen. Die Arbeitsgeschwindigkeit wird dadurch wesentlich herabgesetzt und außerdem sind dadurch Störungen im Arbeitsablauf gegeben.Attempts have also already been made to provide a large-area piston which is aligned axially with the clamping jaw axis. In such an embodiment, however, the device is only accessible from one side, so that only tailpipe connectors can be pressed on. A socket connection of a hose line, for example, cannot be carried out with such an arrangement. In addition, a plurality of spring-loaded spindles are required in this arrangement in order to retract the actuating member for the clamping jaws again into the rest position. This in turn requires an elaborate and costly construction. If these spindles are not arranged with the springs, there is only the possibility of resetting them through the weight of the actuating member and the spring-loaded jaws. The working speed is significantly reduced and there are also disruptions in the workflow.

Bei einer anderen bekannten Vorrichtung, bei welcher die Klemmbacken durch direkt radiale Einwirkung eines Druckmediums betätigt werden, ergeben sich Schwierigkeiten, da keinesfalls der notwendige Anpreßdruck erreicht werden kann. Es müßte dazu durch das Druckmedium ein Druck aufgebaut werden, welcher nur mit einem überdimensionalen Aufbau der Vorrichtung zu bewältigen wäre.In another known device, in which the clamping jaws are actuated by the direct radial action of a pressure medium, difficulties arise because the necessary contact pressure can never be achieved. For this purpose, a pressure would have to be built up by the pressure medium, which would only be manageable with an oversized design of the device.

Bei einer anderen bekannten Vorrichtung ist in einem zylindrischen Gehäuse mit einem Anschlagbund ein Kolben verschiebbar gelagert, welcher ebenfalls mit einem Anschlagbund versehen ist, welcher nach außen hin gerichtet wird. Zwischen der Außenfläche des Kolbens, der Innenfläche des Zylinders und den beiden einander zugewandten Begrenzungsflächen der Anschlagbunde wird ein Zylinderraum geschaffen, welcher hydraulisch beaufschlagt werden kann. Auch bei einer derartigen Anordnung ergeben sich Platzprobleme und somit entsprechend große Bauarten, da praktisch die eigentliche Kolben-Zylinder-Einheit seitlich außerhalb des als Kolben ausgebildeten Betätigungsteils für die Klemmbacken ausgeführt werden muß. Außerdem ist bei einer solchen bekannten Ausführung als nachteilig zu werten, daß eine Vielzahl von Federn vorgesehen werden muß, um nach einem Verpressen das Betätigungsorgan, also den Kolben, in seine Ruhestellung zurückzuführen. Einerseits bedeutet dies einen entsprechenden Materialaufwand und Platzaufwand, so daß die Konstruktion aufwendig wird und andererseits muß dadurch stets beim Verpressen diese zusätzliche Federkraft überwunden werden.In another known device, 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. Even with such an arrangement there are space problems and thus correspondingly large designs, since practically the actual piston-cylinder unit must be carried out laterally outside the actuating part designed as a piston for the clamping jaws. In addition, in such a known embodiment it is to be regarded as disadvantageous that a large number of springs must be provided in order to return the actuating member, that is to say the piston, to its rest position after pressing. On the one hand, this means a corresponding expenditure of material and space, so that the construction becomes complex, and on the other hand, this additional spring force must always be overcome when pressing.

Weiters ist eine Verpreßvorrichtung bekannt, welche von einem doppelt wirkenden Kolben betätigt wird. Die Preßvorrichtung wird also durch hydraulische Kraft sowohl nach vorne, als auch nach rückwärts bewegt. Dabei ist ein inneres und ein äußeres zylindrisches Element vorgesehen, wobei zwischen diesen beiden Elementen zwei ringförmige Kammern gebildet werden. Das innere Element wirkt dabei als hydraulischer Zylinder und das äußere Element als hydraulischer Kolben. Um hier für das Verpressen einen ausreichenden Druck aufbauen zu können, ist eine entsprechend große Kolbenfläche erforderlich. Es muß dazu ein entsprechend großer, nach innen vorspringender Bund vorgesehen werden, um die notwendige Kolbenfläche zu erzielen. Da aber dieser Kolben zugleich eine Zylinderwandung bilden muß, ist eine große Dimensionierung zumindest im Übergangsbereich zwischen dieser äußeren Wandung und dem nach innen vorspringenden Bund notwendig. Außerdem ist auch eine relativ dicke Bauweise für den Zylinder erforderlich, da der vorspringende Bund für sich die enormen Kräfte aufnehmen muß. Es ist keine Möglichkeit gegeben, eine Abstützung von einer gegenüberliegenden Wandung her zu erreichen, da dieser Bund frei auskragend ist.Furthermore, a pressing device is known which is actuated by a double-acting piston. The pressing device is thus moved forward and backward by hydraulic force. In this case, 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. But 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. In addition, 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.

Es ist auch bereits eine Vorrichtung der eingangs genannten Art bekannt geworden, (FR-A-2229479), bei welcher federbelastete Klemmbacken, ein ringförmiger Kolben mit kegelförmiger Erweiterung und eine daran angepaßte Kegelform der Klemmbacken vorgesehen sind. Der Kolben ist hydraulisch in eine Verpreßstellung und in eine Ruhestellung führbar, wobei die Kolbenfläche für die Verpreßstellung größer ist als jene für den Rückhub. Es ist ferner ein ringförmiger Hydraulikzylinder vorgesehen, wobei die Kolbenrückseite die wirksame Kolbenfläche für den Preßhub darstellt und parallel zum Zylinderboden verläuft. Der Kolben weist an dieser Rückseite seine größte Querschnittsfläche auf. Es ist dadurch eine Abstimmung auf die erforderlichen Kräfte gegeben, da ja beim Preßvorgang eine wesentlich größere Kolbenfläche zur Verfügung stehen muß als beim Rückführen des Kolbens in die Ruhestellung. Der Hydraulikzylinder ist als einstückiger Teil ausgeführt, wobei es bearbeitungstechnisch sehr schwierig ist, eine ringförmige Passung exakt herzustellen. Eine exakte Bearbeitungsmöglichkeit ist aber gerade bei den hier notwendigen hohen Drücken unbedingt erforderlich. Als weiterer Nachteil einer solchen Ausführung ist die einseitige Belastung der Klemmbacken anzusehen, da das Eingriffsende des ringförmigen Kolbens an einem Eckbereich der radial verschiebbaren Klemmbacken anstößt, wobei durch die zu übertragende große Kraft die wohl vorgesehenen radialen Führungen für die Klemmbacken nicht ausreichend sind. Es kommt daher sehr oft zu einem Verkanten der Klemmbacken und daher zur Beschädigung der Vorrichtung und zu ungenauen Verpreßvorgängen.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.

Aufgabe der vorliegenden Erfindung ist es daher, die Verkantungsgefahr der radial=bewegbaren Preßbacken zu verhindern und außerdem einen herstellungs- und montagemäßig einfachen Aufbau der Vorrichtung zu erreichen.It is therefore an object of the present invention to prevent the risk of canting of the radially movable press jaws and also to achieve a simple construction of the device in terms of manufacture and assembly.

Erfindungsgemäß gelingt dies dadurch, daß der ringförmige Hydraulikzylinder von einer äußeren Zylinderhülse und einem koaxial eingesetzten Rohrstück gebildet ist, daß achsgleich zum Kolben an dem den ringförmigen Hydraulikzylinder abgewandten freien Ende der äußeren Zylinderhülse ein Konusring fest eingesetzt ist, dessen Innenbegrenzung zum Kolben hin kegelförmig erweitert ist, wobei sich die Außenbegrenzungen der Klemmbacken in Achsrichtung gesehen nach beiden Enden hin kegelförmig verjüngen, und daß der aus dem Rohrstück und dem Zylinderboden gebildete Bauteil und der Konusring an den beiden Enden der äußeren Zylinderhülse durch in Nuten in der Zylinderhülse eingreifende Sperr-Ringe an der Zylinderhülse fixiert sind.According to the invention, this is achieved in that 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.

Die Bearbeitung eines auf die erfindungsgemäße Art zusammengesetzten ringförmigen Hydraulikzylinders ist sehr einfach durchzuführen, wobei auf exakte Genauigkeit gearbeitet werden kann. Die voneinander getrennten Teile, also die die äußere und die innere Zylinderwand bildenden Hülsen können getrennt gefertigt und daher in hoher Genauigkeit bearbeitet werden.The machining of an annular hydraulic cylinder assembled in the manner according to the invention is very easy to carry out, and it is possible to work with exact accuracy. The parts which are separate from one another, that is to say the sleeves which form the outer and the inner cylinder wall, can be produced separately and therefore machined with high accuracy.

Ferner ergibt sich durch die erfindungsgemäßen Maßnahmen eine wesentliche Verbesserung der exakten Führung der Klemmbacken, wenn diese in axialer Richtung gesehen von beiden Enden her erfaßt werden, wobei dies eben nur möglich ist, wenn ein zusätzlicher Konusring eingesetzt ist, an welchem die Klemmbacken ebenfalls anliegen. Es ist dadurch die Gefahr des Verkantens gerade bei der großen Kraftübertragung beim Verpressen der rohrförmigen Teile ausgeschaltet.Furthermore, 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.

Daß dieser Konusring und der innere Abschnitt des Hydraulikzylinders an den Enden der äußeren Zylinderhülse in einfacher konstruktiver Art durch Sperr-Ringe gehalten werden, bringt einen besonderen Effekt mit sich, zumal dieser äußere Zylinder nicht nur einen Teil des Hydraulikzylinders bildet, sondern auch zugleich das äußere Gehäuse und eine gänzliche Abdeckung der innerhalb des Zylinders angeordneten Teile. Daß die Befestigung mit solchen Sperr-Ringen erfolgen kann, bedeutet eine wesentliche Verbesserung, zumal durch entsprechende Gewinde die Genauigkeit der gegenseitigen Passung nicht in einer solchen Art wie bei der vorliegenden Erfindung gegeben ist. Die einzelnen Teile können in exakter Passung ineinandergefügt werden und es ist daher durch die Sperr-Ringe lediglich eine Lagefixierung dieser eingesetzten Teile innerhalb der äußeren Zylinderhülse notwendig.The fact that 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.

Es ergibt sich durch die erfindungsgemäßen Maßnahmen nicht nur eine sehr einfache und genaue Bearbeitungsmöglichkeit, sondern auch eine problemlose Montage der einzelnen Teile ist gewährleistet.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.

Weitere Merkmale und besondere Vorteile werden in der nachstehenden Beschreibung eines Ausführungsbeispieles der Erfindung anhand der Zeichnungen noch näher erläutert. Es zeigen : Fig. 1 Schrägsicht der Vorrichtung ; Fig. 2 einen Schnitt durch die Vorrichtung zum Verpressen ; Fig. 3 schematisch dargestellt eine verstellbare Einrichtung zum Umschalten eines Hydraulikventils bei Erreichen eines bestimmten Verpreßdurchmessers.Other features and special advantages are explained in more detail in the following description of an embodiment of the invention with reference to the drawings. 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.

Die in Fig. 1 dargestellte Vorrichtung besteht im wesentlichen aus einem Zylinderkörper 1, in welchem die Klemmbacken 2 und die Betätigungsorgane für dieselben untergebracht sind, sowie einem diesen Zylinderkörper 1 tragenden Gehäuse 3. Im Gehäuse ist ein Hydraulikventil untergebracht, über welches die Zufuhr des Druckmediums zu dem Betätigungsorgan geregelt werden kann. Der notwendige Druck kann über eine Handpumpe 4 oder entsprechende Außenanschlüsse erreicht werden. Ferner ist eine Einstellvorrichtung 5 mit einem Einstellknopf 6 und einer Maßskala vorgesehen. Mit dieser Einrichtung kann, wie noch eingehend erläutert wird, der gewünschte Enddurchmesser des zu verpressenden Teiles eingestellt werden. Ferner ist ein Betätigungsgriff 7 vorgesehen, über welchen das Hydraulikventil umgeschaltet werden kann. Wie schon aus dieser Fig. 1 ersichtlich, kann die Vorrichtung in einer sehr kleinen, jedoch kompakten Bauweise gefertigt werden, so daß eine derartige Vorrichtung sowohl zum stationären Einsatz als auch zu einem individuellen Einsatz in jedem Betrieb, an jedem Ort und an jeder Stelle geeignet ist. Anstelle eines Fremdanschlusses und zusätzlich zu einer Handpumpe kann auch eine elektrisch betätigbare Pumpe im gehäuse 3 untergebracht werden, um den notwendigen Druck aufzubauen.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. Furthermore, 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. 1, 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. Instead of a third-party connection and in addition to a hand pump, an electrically operated pump can also be accommodated in the housing 3 in order to build up the necessary pressure.

Der konstruktive Aufbau der Vorrichtung kann im wesentlichen dem Längsschnitt durch die Vorrichtung gemäß Fig. 2 entnommen werden. Es sind mehrere annähernd sektorförmig aneinander anschließende Klemmbacken 2 vorgesehen, wobei an den Innenbegrenzungen dieser Klemmbacken verschiedene Einsätze, je nach dem gewünschten Enddurchmesserbereich befestigt werden können. Diese Klemmbacken 2 sind in radialer Richtung verstellbar und gegeneinander federbelastet, wobei jeweils zwischen zwei Klemmbacken 2 Federn 8 in entsprechende Bohrungen 9 eingesetzt sind. An ihren Außenbegrenzungen sind die Klemmbacken mit nach den beiden Enden hin abfallenden Kegelmantelflächen 10 und 11 ausgeführt. Die Kegelmantelfläche 11 stützt sich dabei an einer kegelförmigen Erweiterung 12 eines Konusringes 14 und die Kegelmantelfläche 10 an einer kegelförmigen Erweiterung 13 des Kolbens 15 ab. Der Kolben 15 wirkt als Betätigungsorgan für die Klemmbacken 2, so daß bei einer Verschiebung des Kolbens 15 in Pfeilrichtung 16 die Klemmbacken 2 in radialer Richtung gegeneinander geschoben werden und auch in axialer Richtung geringfügig bewegt werden, da sie eine gleichmäßige Relativbewegung sowohl zum Kolben 15 als auch zum Konusring 14 ausführen.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. At their outer boundaries, 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.

Der Kolben 15 ist ringförmig ausgebildet und beim gezeigten Ausführungsbeispiel in einen ringförmigen Hydraulikzylinder eingesetzt. Die wirksame Kolbenfläche 18 für den Vorschub des Kolbens 15 ist am freien, den Klemmbacken 2 abgewandten Ende des Kolbens 15 ausgebildet und verläuft parallel zum Boden 19 des ringförmigen Hydraulikzylinders 17. Es kann dadurch die gesamte Querschnittsfläche des Kolbens 15 ausgenützt werden ohne daß zusätzliche Anschlagstege oder ein entsprechend großer Anschlagbund zur Bildung einer Kolbenfläche vorgesehen werden müßte. Die wirksame Kolbenfläche 18 ist also am Bereich der größten Querschnittsfläche des Kolbens 15 angebracht. so daß auch die baulichen Abmessungen des Kolbens 15 sehr klein gehalten werden können.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.

Der ringförmig ausgebildete Hydraulikzylinder 17 kann ebenfalls sehr einfach aufgebaut werden. Dieser wird von einer äußeren Zylinderhülse 20 sowie einem koaxial eingesetzten Rohrstück gebildet, wobei an dem eingesetzten Rohrstück 21 der Zylinderboden 19 einstückig anschließt. Es ist dadurch eine sehr einfache Fertigung mit Drehteilen möglich.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.

Der Kolben weist an seinem der Kolbenfläche 18 zugewandten Ende einen umlaufenden Bund 22 mit gegenüber dem restlichen Bereich des Kolbens 15 größeren Außendurchmesser auf. Die äußere Begrenzung 23 des Hydraulikzylinders 17 ist zumindest über den Verschiebebereich des Bundes 22 mit einem dem Außendurchmesser des Bundes 22 entsprechend vergrößerten Innendurchmesser ausgeführt. Es wird dadurch ein ringförmiger Zylinderraum geschaffen, welcher einerseits durch die innere Begrenzung 23 der äußeren Zylinderhülse 20 und andererseits der Kolbenaußenfläche 24 eingeschlossen ist. Die der Kolbenfläche 18 abgewandte Begrenzung des Bundes 22 bildet eine Kolbenfläche 25, welche nur einen Bruchteil der Kolbenfläche 18 beträgt. Es kann durch diese sehr einfache Maßnahme nicht nur eine hydraulische Verpressung erfolgen, sondern auch ein hydraulisches Rückführen des Kolbens 15 in seine Ruhestellung.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.

Es ist durchaus möglich, auch im Bereich der Innenbegrenzung 26 des Kolbens 15 einen nach innen abragenden Bund 27 vorzusehen, um dadurch eine relativ kurze Führungsfläche für den Kolben 15 innerhalb des Hydraulikzylinders 17 zu erreichen. Im Bereich dieser Bunde 22 und 27 werden Dichtringe 28 bzw. sonstige Dichtungselemente eingesetzt. Ein weiterer Dichtring 29 ist am Übergangsbereich zwischen der Innenbegrenzung 23 mit größerem Durchmesser und der Innenbegrenzung 30 mit kleinerem Durchmesser vorgesehen. Dieser Dichtring 29 bewirkt eine Abdichtung beim Rückführen des Kolbens 15 in die Ruhestellung. Durch den so gebildeten Zylinderraum 31 ergibt sich keine Schwächung der Zylinderhülse 20 oder des Kolbens 15, dieser Zylinderraum 31 reicht aber voll aus, um ein ordnungsgemäßes Zurückführen des Kolbens 15 zu ermöglichen.It is also possible to provide an inwardly projecting collar 27 in the area of the inner boundary 26 of the piston 15 in order to achieve a relatively short guide surface for the piston 15 within the hydraulic cylinder 17. In the area of these collars 22 and 27, sealing rings 28 or other sealing elements are used. Another sealing ring 29 is provided at the transition area between the inner boundary 23 with a larger diameter and the inner boundary 30 with a smaller diameter. This sealing ring 29 effects a seal when the piston 15 is returned to the rest position. The cylinder space 31 thus formed does not weaken the cylinder sleeve 20 or the piston 15, but this cylinder space 31 is sufficient to enable the piston 15 to be properly returned.

Am äußeren Rand des Bodens 19 des Hydraulikzylinders 17 und gegebenenfalls auch am äußeren Rand der Kolbenfläche 18 sind nutartige Vertiefungen oder Abschrägungen vorgesehen, welche bei der Ruhestellung des Kolbens 15 gemeinsam einen umlaufenden Ringkanal bilden. In diesen Ringkanal mündet die Zuführleitung 34 für das Druckmedium ein, so daß auch dann, wenn die Kolbenfläche 18 direkt auf dem Boden 19 aufliegt, das Druckmedium eindringen kann und die Bewegung des Kolbens 15 in Pfeilrichtung 16 hervorruft.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.

Die Zuführleitung 35 für das Druckmedium zum Rückstellen des Kolbens 15 mündet nahe des zylinderseitigen Dichtringes 29 in den ringförmigen Zylinderraum 31, so daß auch bei ganz ausgefahrenem Kolben 15 eine ordnungsgemäße Zuführung für das Druckmedium möglich ist.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.

Einen besonderen Vorteil in konstruktiver Hinsicht bringt die beschriebene Ausgestaltung noch insofern, als keine besonders dimensionierten Verschraubungen erforderlich sind. Bei Verschraubungen müßte die äußere Zylinderhülse einen wesentlich größeren Querschnitt aufweisen und auch die anderen Teile müßten entsprechend größer dimensioniert werden. Bei der beschriebenen Ausgestaltung ist es möglich, den Konusring 14 bzw. den das Rohrstück 21 und den Boden 19 bildenden Bauteil 36 ohne eine Verschraubung gegenseitig zu verbinden. Es werden hier in der Zylinderhülse Nuten 37 vorgesehen, in welche Sperr-Ringe 37' eingreifen. Diese Sperr-Ringe weisen einen L-förmigen Querschnitt auf, wobei der eine Schenkel an der Innenwandung der Zylinderhülse 20 anliegt und der andere Schenkel in die Nut 37 an derselben eingreift. Um diese Sperr-Ringe 37' in die Nuten 37 einbringen zu können, sind diese in deren Umfangsrichtung gesehen einmal oder mehrfach durchtrennt. Insbesondere dann, wenn nur eine Trennstelle vorgesehen ist, verlaufen die Trennflächen der Sperr-Ringe in einem spitzen Winkel zu einer Radialebene des Sperr-Ringes 37', um dadurch ein Einführen zu ermöglichen. Ferner ist noch vorgesehen, daß der Bauteil 36 und der Konusring 14 an ihren äußeren Randbereichen vorzugsweise über eine Länge, die dem an der Zylinderhülse anliegenden Schenkel des Sperr-Ringes 37' entspricht, um die Dicke dieses Schenkels abgesetzt sind.The described configuration also has a particular advantage in terms of construction in that no specially dimensioned screw connections are required. In the case of screw connections, the outer cylinder sleeve would have to have a substantially larger cross section and the other parts would also have to be correspondingly larger. In the embodiment described, it is possible to connect the conical ring 14 or the component 36 forming the pipe section 21 and the base 19 to one another without screwing. 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. In order to be able to introduce these locking rings 37 'into the grooves 37, these are severed once or several times, seen in the circumferential direction thereof. In particular, if only one separation point is provided, 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. Furthermore, it is also provided that 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.

Im Endzustand sind also die beiden Schenkel des Sperr-Ringes 37' zwischen der Zylinderhülse 20 und dem Konusring 14 bzw. dem Bauteil 36 eingespannt, so daß bei einer Belastung nur Scherkräfte auftreten können, jedoch keine Biegekräfte, wie dies beispielsweise beim Einsetzen eines Seegerringes der Fall wäre. Ferner kann bei einer derartigen Ausführung ein ebener Abschluß sämtlicher miteinander zu verbindender Teile ermöglicht werden und außerdem sind die Belastungsgrenzen sehr hoch. Selbstverständlich kann eine derartige Montage mit den erfindungsgemäßen Sperr-Ringen 37' nur dann erfolgen, wenn die zu arretierenden Bauteile (Konsuring 14 und Bauteil 36) vorerst entsprechend weit in eine Zylinderhülse 20 hineingeschoben werden können, damit der Sperr-Ring 37' in die Nut 37 eingelegt werden kann. Anschließend wird dann der entsprechende Bauteil wiederum nach außen gezogen, bis dieser am Sperr-Ring 37' anliegt. Durch diese Maßnahmen ist eine weit stärker belastbare Verbindung geschaffen, wie dies durch einzelne Schrauben möglich wäre. Es ist dadurch eine Konstruktion mit sehr kleinen Dimensionen möglich.In the final state, the two legs of the locking ring 37 'are clamped between the cylinder sleeve 20 and the conical ring 14 or the component 36, so that only shear forces can occur under load, but no bending forces, as is the case, for example, when a circlip is inserted Would be the case. Furthermore, with such a design, a level closure of all parts to be connected to one another can be made possible, and the load limits are also very high. Of course, such an assembly with the locking rings 37 'according to the invention can only take place if the components to be locked (retaining ring 14 and component 36) can initially be pushed correspondingly far into a cylinder sleeve 20 so that the locking ring 37' into the groove 37 can be inserted. The corresponding component is then again pulled outwards until it rests on the locking ring 37 '. These measures create a much more resilient connection than would be possible with individual screws. This enables a construction with very small dimensions.

Esgreift ferner in den Verschiebebereich des Kolbens 15 eine verstellbare Schalteinrichtung zum Umschalten eines Hydraulikventils ein. Dadurch ist es möglich, abhängig von dem Schließzustand der Klemmbacken 2 und somit in exakt berechenbarer Stellung des Kolbens 15 eine Ventilumschaltung vorzunehmen, damit die Vorrichtung selbsttätig arbeitet. Bis zum erforderlichen Verpreßdurchmesser wird also die Kolbenfläche 18 beaufschlagt, worauf nach einem vorher einstellbaren Verschiebeweg des Kolbens 15 ein Umschalten des Hydraulikventils erfolgt, so daß dann der Ringraum 31 beaufschlagt wird und eine Rückführung des Kolbens 15 in die Ruhestellung hervorgerufen wird.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.

Bei einem besonderen Ausführungsbeispiel ist vorgesehen, daß in den Verschiebebereich des Kolbens 15 eine Steuerstange 38 eingreift, welche mit einem Anschlag 40' in Wirkverbindung bringbar ist, welcher in seinem Abstand vom klemmbackenseitigen Kolbenende einstellbar ist. In konstruktiv einfacher Weise ist diese Steuerstange 38 in einer Bohrung 39 des feststehenden Konusringes 14 verschiebbar geführt. Die Umschaltung kann durch eine mechanische Übertragung oder auch durch elektrische Schaltmittel erfolgen. Eine einfache Ausführungsform kann der Fig. 3 entnommen werden. Mittels eines Einstellknopfes 6, welcher an einem Gewindebolzen 40 angeordnet ist, kann der Anschlag 40' für die Steuerstange 38 in axialer Richtung verstellt werden, so daß je nach gewünschtem Enddurchmesser der Kolben 15 früher oder später an das freie Ende der Steuerstange 38 anstößt und somit der Anschlag 40' verschoben wird. Es ist auch möglich, eine Skala 41 vorzusehen mit einem entsprechenden Anzeigeelement, um dadurch von außen sichtbar die Verstellung vorzunehmen. In diesem Zusammenhang ist es auch zweckmäßig, wenn eine Feineinstellung möglich ist, welche in Abhängigkeit von der Gewindesteigung des Gewindebolzens 40 geregelt werden kann, so daß beispielsweise bei einer entsprechenden Gewindesteigung erreicht wird, daß bei einer Umdrehung des Einstellknopfes der Verpreßdurchmesser um 1 mm geändert wird.In a special embodiment it is provided that 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. In a structurally simple manner, 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. A simple embodiment can be seen in 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. It is also possible to provide a scale 41 with a corresponding display element in order to make the adjustment visible from the outside. In this context, it is also expedient if 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 .

Der Fig. 3 kann eine mechanische Übertragung dieser Umschaltung entnommen werden. Bei Bewegung der Steuerstange 38 wird ein Steuerelement 43 mit einer schrägen Auflauffläche 44 nach dem Anstoßen des freien Endes des Kolbens 15 in Pfeilrichtung 45 bewegt. Durch die Abschrägung 46 an einer Betätigungsstange 47 kann diese in Pfeilrichtung 48 sich verschieben. Diese Betätigungsstange 47 steht mit dem Betätigungsgriff 7 bzw. der daran anschließenden Verbindungsstange 49 in Wirkverbindung. Diese Verbindungsstange 49 führt zu einem Hebel 50, welcher die Umschaltung des Hydraulikventils 51 bewirkt. Die Betätigungsstange 47 greift in eine Ausnehmung 60 an dem Bolzen 52 der Verbindungsstange 49 ein und arretiert somit diese Verbindungsstange 49 in einer Stellung, in welcher das Hydraulikventil 51 auf die Stellung Vorschub für den Kolben 15 geschaltet ist. Nach einem entsprechenden Zurückführen der Betätigungsstange 47 in Pfeilrichtung 48 wird der Bolzen 52 freigegeben, so daß durch das gegebenenfalls federbelastete Hydraulikventil 51 und/oder eine Feder 61 der Hebel 50 und somit auch die Verbindungsstange 49 in Pfeilrichtung 54 bewegt wird.A mechanical transmission of this switch can be seen in FIG. 3. When the control rod 38 moves, 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. After a corresponding return of the actuating rod 47 in the direction of the arrow 48, the bolt 52 is released, so that the lever 50 and / or the connecting rod 49 is moved in the direction of the arrow 54 by the possibly spring-loaded hydraulic valve 51 and / or a spring 61.

Sobald der Betätigungsgriff 7 wiederum entgegen der Pfeilrichtung 54 für einen neuen Arbeitsvorgang gedrückt oder beispielsweise von einem Magnet gezogen wird, kann die Betätigungsstange 47 wiederum in die in Fig. 3 dargestellte Lage zurückkehren, so daß die Verbindungsstange 49 bzw. der Bolzen 52 derselben wiederum fixiert wird. Dadurch werden infolge Einwirkung der Feder 62 der Gewindebolzen 40 und somit der Anschlag 40' wieder in ihre in Fig. 3 dargestellte Lage gebracht. Die Betätigungsstange 47 wird dadurch wieder verriegelt. Selbstverständlich könnte auch die Steuerstange 38 entsprechend federbelastet ausgeführt sein, so daß diese jeweils in ihrer Ruhestellung am Anschlag 40' anliegt.As soon as the actuating handle 7 is again pressed against the direction of the arrow 54 for a new operation or, for example, is pulled by a magnet, 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. As a result of the action of the spring 62, the threaded bolt 40 and thus the stop 40 'are brought back into their position shown in FIG. 3. The operating rod 47 is locked again. Of course, the control rod 38 could also be designed to be spring-loaded, so that it rests against the stop 40 'in its rest position.

Ein besonderer Vorteil der beschriebenen Ausgestaltung liegt noch in der relativ kurzen Baulänge der Vorrichtung, welche eben durch die besondere Ausgestaltung des doppeltwirkenden Kolbens erreicht wird. Es fallen dadurch wesentliche notwendige Baulängen weg, die beispielsweise durch Federn gegeben sind, die eine Rückführung eines Kolbens bewirken sollen. Die Rückführung kann aber in einfacher Weise ebenfalls hydraulisch erfolgen, so daß diese zusätzlichen Bauteile wegfallen können.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.

Anstelle der Anordnung eines ringförmigen Zylinders wäre es auch denkbar, das innere Rohrstück 21 des Bauteiles 36 wegzulassen, wobei dann ein entsprechendes Rohrstück 21 fest mit dem Kolben 15 verbunden wäre bzw. einstückig mit diesem ausgestaltet wäre. Eine solche Verlängerung des Kolbens müßte dann den Boden 19 des Bauteiles 36 entsprechend in Achsrichtung des Kolbens überragen, da bei einer solchen Ausführung das einen Teil des Kolbens 15 bildende Rohrstück 21 die innere Zylinderwandung bilden muß. Es ist dann noch eine entsprechende Abdichtung zwischen dem restlichen Bauteil 36 und dem mit dem Kolben 15 verbundenen bzw. einstükkigen Rohrstück 21 vorzusehen. Wesentlich günstiger ist jedoch die in der vorstehenden Beschreibung erläuterte Ausgestaltung, bei welcher sämtliche besonders bearbeiteten Teile der Vorrichtung abgedeckt und daher gegen Beschädigung geschützt sind.Instead of the arrangement of an annular cylinder, it would also be conceivable to omit the inner pipe section 21 of the component 36, in which case a corresponding pipe section 21 would be firmly connected to the piston 15 or would be designed in one piece with the latter. Such an extension of the piston would then have to project beyond the base 19 of the component 36 in the axial direction of the piston, since in such an embodiment the tube piece 21 forming part of the piston 15 must form the inner cylinder wall. It is then still necessary to provide a corresponding seal between the remaining component 36 and the one-piece pipe section 21 connected to the piston 15. However, the configuration explained in the above description, in which all specially machined parts of the device are covered and are therefore protected against damage, is considerably cheaper.

Einen besonderen Vorteil bietet die beschriebene Vorrichtung noch darin, daß der Kolben 15 relativ leicht bewegt werden kann, solange noch keine Pressung einer Rohrverbindung erfolgt. Dies geht eben dadurch sehr einfach, weil keine besonderen Gegenkräfte vorhanden sind. Dadurch ist es möglich geworden, den Vorratstank für das Druckmedium, welches in der Regel Öl sein wird, luftdicht abzuschließen, so daß ein Druck innerhalb des Vorratstankes aufgebaut werden kann. Es genügt dabei, wenn in dem freien Raum des Vorratstankes Druckluft eingeführt wird, so daß das eigentliche Druckmedium vorbelastet ist. Es besteht daher die Möglichkeit. ohne Betätigung einer Pumpe das Druckmedium allein durch den im Vorratstank aufgebauten Druck über die Zuführleitung 34 zuzuführen, so daß der Kolben 15 bis zu jener Ausgangslage. bei welcher er an die zu verpressenden Teile zur Anlage kommt, in einem Schnellgang vorgeschoben wird. Der Arbeitsablauf kann dadurch wesentlich beschleunigt werden, so daß es auch keiner zusätzlichen Maßnahmen zur Verringerung des Kolbenweges je nach Größe der zu verpressenden Teile bedarf. Durch diesen schnellen Vorwärtsgang, welcher nur durch die Leichtgängigkeit der beschriebenen Ausführung möglich ist, entfallen hier also zusätzliche Mittel, die die Rückstellbewegung des Kolbens begrenzen sollen.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 workflow can thereby be significantly accelerated, so that no additional measures to reduce the piston travel are required depending on the size of the parts to be pressed. This fast forward gear, which is only possible due to the smooth operation of the described embodiment, means that additional means are not required here which are intended to limit the return movement of the piston.

Es ist gerade dem Schnitt nach Fig. 2 zu entnehmen, daß die beschriebene Vorrichtung praktisch störungsunanfällig ist und somit auch wartungsfrei. Diejenigen Teile, bei denen die Gefahr einer Beschädigung gegeben wäre, sind zur Gänze abgedeckt bzw. von außen beim Einschieben der zu verpressenden Teile nicht zugänglich. Es ist somit auch eine einfachste Handhabung dieser Vorrichtung möglich. Die Konstruktion ist einfach und trotz erreichbarer hoher Drücke in einer relativ kleinen Dimension ausführbar, so daß die Vorrichtung sehr leicht wird und dadurch auch leicht transportabel. Durch den einfachen konstruktiven Aufbau ergibt sich selbstverständlich auch ein preisgünstiger Aufbau.It can be seen precisely from the section according to FIG. 2 that 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. Of course, the simple construction also results in an inexpensive construction.

Claims (10)

1. An apparatus for pressing tubular parts, having a plurality of spring-loaded clamping jaws (2) adjustable in the radial direction and a piston (15) which acts upon the clamping jaws (2) and is annular in cross-section and is enlarged in a tapered manner on its inside at the end region facing the clamping jaws (2) and which is displaceable towards the clamping jaws (2) and retractable into its rest position by hydraulic means, the clamping jaws (2) bearing with their boundary surfaces lying radially outwards at a corresponding angle of inclination on the tapered enlargement (13) of the piston (15), and the effective piston area (25) for the retraction of the double-acting piston (15) amounting only to a fraction of the effective piston area (18) on the free end - remote from the clamping jaws (2) and extending parallel to the base (19) of the annular cylinder (17) - of the piston (15) for the advance thereof, and the piston comprising at its end which forms the effective piston area (18) for the advance the greatest cross-sectional area. characterized in that the annular hydraulic cylinder (17) is formed by an outer cylinder sleeve (20) and a coaxially inserted tube member (21), a tapered ring (14), whose inner boundary (12) is enlarged in a tapered manner towards the piston (15), is securely inserted coaxially with the piston (15) at the free end of the outer cylinder sleeve (20) remote from the annular hydraulic cylinder (17), the outer boundaries of the clamping jaws (2) diminishing in a tapered manner towards both ends as viewed in the axial direction, and the structural component (36) formed by the tube member (21) and by the cylinder base (19) and the tapered ring (14) are fixed to the outer cylinder sleeve (20) at both ends of the cylinder sleeve (20) by locking rings (37') engaging in grooves (37) in the cylinder sleeve (20).
2. An apparatus according to Claim 1, characterized in that the cylinder base (19) is integrally joined to the tube member (21) inserted coaxially in the outer cylinder sleeve (20).
3. An apparatus according to Claim 1, characterized in that at its end remote from the clamping jaws (2) the piston (15) comprises at least on its outer boundary a continuous collar (22) of greater diameter, the outer boundary (23) of the cylinder (17) comprising at least over the displacement area of the collar (22) an inner diameter enlarged in accordance with the outer diameter of the collar (22).
4. An apparatus according to Claim 3, characterized in that the boundary of the collar (22) remote from the effective piston area (18) for the advance of the piston (15) forms the effective piston area (25) for the return movement of the piston (15), the annular cylinder space (31) being formed by the outer surface (24) of the piston, the inner boundary (23) of the outer cylinder sleeve (20), the piston area (25) and the end surface of the enlarged region of greater diameter.
5. An apparatus according to Claim 1, characterized in that a groove-like recess or bevel (33, 32) is provided in each case on the outer edge of the cylinder base (19) and on the outer edge area of the piston area (18) effective for the advance, the recesses or bevels (33, 32) jointly forming a circumferential annular channel when the piston (15) is in the rest position, and the feed line (34) for the pressure medium opens in the region of the annular channel.
6. An apparatus according to Claim 1, characterized in that the locking rings (37') have an L-shaped cross-section, one arm bearing on the inner wall of the cylinder sleeve (20) and the other arm engaging in the groove (37) in the latter.
7. An apparatus according to Claim 6, characterized in that the locking rings (37') are divided one or more times in their peripheral direction, the separation surfaces of the locking rings (37') extending at an acute angle to a radial plane of the locking ring (37').
8. An apparatus according to Claim 1, characterized in that on their outer edge regions the structural component (36) and the tapered ring (14) are offset preferably over a length which corresponds to the arm of the locking ring (37') bearing on the cylinder sleeve (20) by the thickness of the arm.
9. An apparatus according to Claim 1, characterized in that an adjustable switching device for reversing an hydraulic valve (51) engages in the displacement region of the piston (15).
10. An apparatus according to Claim 1, characterized in that the storage tank of the hydraulic medium is closed off hermetically and is connectable to a compressed-air line.
EP83900555A 1982-02-04 1983-02-01 Apparatus for pressing tubular parts Expired EP0100334B1 (en)

Applications Claiming Priority (2)

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AT424/82 1982-02-04
AT0042482A AT376589B (en) 1982-02-04 1982-02-04 DEVICE FOR COMPRESSING TUBULAR PARTS

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EP0100334B1 true EP0100334B1 (en) 1986-05-28

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EP (1) EP0100334B1 (en)
JP (1) JPS59500091A (en)
AT (2) AT376589B (en)
AU (1) AU561471B2 (en)
BR (1) BR8305746A (en)
CA (1) CA1207991A (en)
DE (1) DE3363630D1 (en)
DK (1) DK455983A (en)
ES (1) ES8402409A1 (en)
FI (1) FI833575A0 (en)
HU (1) HUT36734A (en)
IT (1) IT1167313B (en)
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CA1207991A (en) 1986-07-22
IT8367114A0 (en) 1983-02-03
FI833575A (en) 1983-10-03
ATA42482A (en) 1984-05-15
DK455983D0 (en) 1983-10-03
NO154185C (en) 1986-08-06
NZ203168A (en) 1986-01-24
AU561471B2 (en) 1987-05-07
IT1167313B (en) 1987-05-13
NO154185B (en) 1986-04-28
DK455983A (en) 1983-10-03
HUT36734A (en) 1985-10-28
US4696085A (en) 1987-09-29
JPS59500091A (en) 1984-01-19
ATE19967T1 (en) 1986-06-15
AT376589B (en) 1984-12-10
DE3363630D1 (en) 1986-07-03
FI833575A0 (en) 1983-10-03
BR8305746A (en) 1984-01-10
ES519509A0 (en) 1984-02-01
ES8402409A1 (en) 1984-02-01
ZA83745B (en) 1983-11-30
AU1158683A (en) 1983-08-25
WO1983002737A1 (en) 1983-08-18
NO833584L (en) 1983-10-03
EP0100334A1 (en) 1984-02-15

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