EP3012924A1 - Jointing clamp - Google Patents

Abstract

The invention relates to a pressing tongs with two hand levers (3, 5) and two in the region of a pliers head (4) arranged actuating elements (9, 10) which actuate dies (12), between which a workpiece can be pressed. Between the hand levers (3, 5) and the actuating elements (9, 10) acts a toggle lever drive (33) with two toggle levers (34, 35), which form a knee angle (36). A toggle (34) is formed by a roller (23) which is rotatably mounted relative to the hand lever (5). The roller (23) rolls on a on the other hand lever (3) fixed cam track (24). A Zwangsgesperre (48) is formed with a Sperrverzahnungshebel (28) which is rotatably mounted relative to the roller (23). A lever part (30) of the pawl lever (28) is coupled via a sliding guide with the hand lever (3), while the other lever part (29) of the pawl lever (28) forms a locking toothing (31) of the Zwangsgesperres (48).

Description

TECHNICAL FIELD OF THE INVENTION

The invention relates to a pressing tongs for pressing a workpiece. This may be any pressing tongs, for example a pressing tongs for pressing pipe or pipe connections or a pressing tongs (which is also referred to as crimping tool) for pressing electrical line connections or plugs, sleeves or jacks with any electrical conductors. The crimping pliers may in principle have any of the various known constructional embodiments, wherein crimping with two or more dies or spikes (hereinafter collectively referred to as "dies") can take place during the pressing process. It is possible that the crimping tool is operated by external force, for example by means of an electric drive. Preferably, however, it is a hand-operated pressing tongs.

WAS STANDING OF THE TECHNOLOGY

During the pressing of a workpiece, the increasing plastic deformation of the workpiece between the dies causes a pressing force which increases during the pressing process. In known pressing tongs the translation of manually applied to hand lever of the pressing tongs hand forces to the dies by means of a drive mechanism is such that the required maximum pressing forces can be generated by manual operation of the hand lever.

From the pamphlets DE 197 13 580 C2 . DE 197 09 639 A1 . DE 199 24 086 C2 . DE 199 24 087 C2 . DE 199 63 097 C1 . DE 103 46 241 B3 . DE 10 2007 001 235 B4 . DE 10 2008 007 303 B4 Embodiments of pressing tongs are known in which the drive mechanism is formed with a toggle lever drive. Here, the pressing tongs may be formed with a C-shaped pliers head, in which pressing jaws on the toggle lever drive translationally to be moved, the pliers head "scissor-like" be formed with pivotally mounted to each other pressing jaws, wherein a toggle lever of the toggle lever is articulated. During the working stroke from an open position into a closed position of the pressing tongs, a knee angle formed between the knee levers in the area of a knee joint changes, with the approaching the closed position approaching the angle of the knee to an angle of 180 °. This kinematics of the toggle lever drive has the consequence that at the beginning of the power stroke smaller pressing forces are generated with a relatively large closing movement of the jaws with a partial stroke of the lever and at the end of the working great pressing forces are brought about with a small closing movement of the jaws with a corresponding partial stroke of the lever , Here, the selected lengths of the toggle and the articulation points of the toggle lever on the hand levers and jaws and thus the angular relationships determine the characteristics of the closing movement of the jaws and the pressing forces in response to the closing movement of the hand lever.

The publication of the design US 341,303 discloses a pressing tongs for the pressing of fittings for pipe joints. In this pressing tongs the jaws are pivotable about a common pivot against each other. A jaw is rigidly connected to a fixed hand lever, while the other jaw is coupled via a pivot joint with a movable hand lever. Here, a toggle lever mechanism is formed as follows with a principle "roller-curve": On the fixed hand lever, a roller is rotatably mounted about a roller axis. The movable hand lever carries a guide part, which forms a curved path. With movement of the hand lever toward each other, the movable hand lever with the curved path is supported on the roller mounted on the fixed hand lever. In this case, a toggle is formed with the roller, namely the material area of the roller, which extends between the contact point of the roller on the cam track and the roller axis. On the other hand, the other toggle lever is formed between the point of contact between roller and cam track on the one hand and the pivot axis, in the area in which the movable hand lever is articulated on the movable jaw. The "knee joint" is formed in this training by the rolling contact of the roller with the curved path, so this is not a "joint" in the classical sense. Rolls off during the closing movement of the hand lever the role of the curved path, changes depending on the contact point of the roller with the curved path, the length of the latter knee lever and the location of the knee joint on the cam track, so that by choosing the geometry of the cam track additional influence on the characteristics of the pressing tongs can be taken.

1. a) Mittels eines Zwangsgesperres soll gewährleistet werden, dass ein Öffnen der Handhebel und damit der Presszange erst dann möglich ist, wenn der Arbeitshub der Presszange vollständig durchlaufen ist und somit auch der Pressvorgang vollständig abgeschlossen worden ist.
2. b) Möglich ist, dass während des Durchlaufens des Arbeitshubs nach einem Teilhub die Betätigungskräfte, welche der Benutzer auf die Handhebel appliziert, reduziert werden. Dies ist beispielsweise der Fall für ein Unterbrechen des Pressvorgangs oder wenn der Benutzer die Presszange anders greifen möchte und somit umgreift. Würde es zu einer Reduzierung der Presskraft kommen, könnte es zu einer Verlagerung des Werkstücks gegenüber dem Gesenk kommen, was unerwünscht ist. Mittels des Zwangsgesperres wird eine einmal erreichte Teilpressstufe gesichert, so dass auch bei Reduktion oder Beseitigung der auf die Handhebel aufgebrachten Betätigungskräfte die Zangenbacken nicht oder nur in verringertem Umfang eine Öffnungsbewegung ausführen können.

In pressing tongs find so-called Zwangsgesperre use, which serve the following purposes:

1. a) By means of a Zwangsgesperres should be ensured that an opening of the hand lever and thus the pressing tongs is only possible when the working stroke of the pressing tongs has passed completely and thus the pressing process has been completed completely.
2. b) It is possible that during the passage of the power stroke after a partial stroke, the actuating forces which the user applies to the hand lever are reduced. This is for example the case for interrupting the pressing process or if the user wants to grip the pressing tongs differently and thus embraces. Would it come to a reduction of the pressing force, it could lead to a displacement of the workpiece relative to the die, which is undesirable. By means of Zwangsgesperres once achieved Teilpressstufe is secured so that even when reducing or eliminating the force applied to the hand lever actuating forces the jaws can not or only to a lesser extent perform an opening movement.

DE 10 2007 056 262 A1 discloses a crimping pliers, in which a toggle lever drive with the above-explained principle roller-curve is formed. In this forceps a compulsory detention is used. Here, a toothing of the Zwangsgesperres is arranged in the end region remote from the die of the movable jaw, while a spring-loaded pawl of Zwangsgesperres is rotatably mounted on the movable hand lever.

When forming the drive mechanism with a toggle lever drive without the use of the principle roller-curve is usually a toothing of a Zwangsgesperres formed by an extension of a knee lever also referred to as a pressure lever. This toothing interacts with a pawl, which is mounted under the action of a spring rotatable on the movable hand lever (see. EP 0 732 779 B1 ).

OBJECT OF THE INVENTION

The present invention has for its object to provide a pressing tongs with extended possibilities for the design of the characteristic with the simultaneous use of a Zwangsgesperres.

SOLUTION

The object of the invention is achieved with the features of the independent claim. Further preferred embodiments according to the invention can be found in the dependent claims.

DESCRIPTION OF THE INVENTION

The invention relates to a pressing tongs of any configuration, by means of which a pressing of a workpiece takes place. The pressing tongs have two drive elements, which are preferably manually operated hand lever. Furthermore, the pressing tongs have two actuating elements, which are arranged in the region of a pliers head. The actuators actuate dies, between which the workpiece can be pressed. It is possible that the actuators are designed directly as pliers jaws, which (one or more pieces) carry the dies. But it is also possible that the actuating elements are coupled by gearing with the dies. For example, according to EP 0 732 779 B1 the actuators are designed as a pivot ring and bearing plate, wherein a plurality of dies are pivotally mounted relative to the bearing plate and are guided in their end portions in grooves of the pivot ring, so that with relative pivoting of the pivot ring relative to the bearing plate, a common movement of the dies can be brought about by means of which a pressing of the workpiece takes place.

For the pressing tongs invention acts between the drive elements and the actuators a toggle lever drive. This has two toggle lever. The knee levers form a variable knee angle over the working stroke. In this case, the two toggle levers can be connected to each other in the area of a true knee joint. But it is also possible that a knee joint is formed in the region of a contact between a roller and a curved path.

By a suitable choice of the geometry of the curved path can u about the stroke. U. specifically a knee angle can be specified, which meets the requirements. For example, it can be attempted that, regardless of the workpiece to be pressed, the knee angle always remains within an angular range, for example from 130 ° to 190 °, in particular 145 ° to 180 °, due to the rolling movement of the roller relative to the curved path of the guide part.

1. a) die Rolle an dem festen Handhebel drehbar gelagert ist, während die Kurvenbahn fest mit dem beweglichen Handhebel verbunden ist, oder
2. b) die Rolle an dem beweglichen Handhebel drehbar gelagert ist, während die Kurvenbahn fest mit dem festen Handhebel verbunden ist.

For the embodiment of the invention, the principle role-curve is used. Here, a toggle lever is formed by a roller. The roller is rotatably mounted relative to a hand lever about a roller axis. The roller rolls on a firmly connected to the other hand lever cam track. It is possible that

1. a) the roller is rotatably mounted on the fixed hand lever, while the cam track is fixedly connected to the movable hand lever, or
2. b) the roller is rotatably mounted on the movable hand lever, while the cam track is fixedly connected to the fixed hand lever.

• Ein Sperrverzahnungshebel ist gegenüber dem Antriebselement, gegenüber welchem die Rolle drehbar gelagert ist, gelagert, Hierbei ist der Sperrverzahnungshebel sowohl relativ zu dem Antriebselement, gegenüber welchem die Rolle drehbar gelagert ist, als auch gegenüber der Rolle selber drehbar. Ein Hebelteil des Sperrverzahnungshebels ist über eine Gleitführung mit dem anderen Antriebselement gekoppelt. Das andere Hebelteil des Sperrverzahnungshebels bildet eine Sperrverzahnung des Zwangsgesperres aus.

According to the invention, a compulsory lock is formed as follows:

• A ratchet lever is mounted opposite to the drive element against which the roller is rotatably mounted. Here, the ratchet lever is rotatable both relative to the drive element against which the roller is rotatably mounted and to the roller itself. A lever part of the locking gear lever is coupled via a sliding guide with the other drive element. The other lever part of the locking gear lever forms a locking toothing of Zwangsgesperres.

According to the invention thus not the locking gear lever and the associated locking teeth of Zwangsgesperres are formed by a jaw or the actuating element. The Sperrverzahnungshebel is also not integrally formed with a toggle or pressure lever of the toggle lever drive. These inventively unrealized embodiments of the pawl lever have in particular the disadvantage that the movement of the pawl lever compellingly corresponds to the movement of the jaw or the toggle lever or the pressure lever. Rather, according to the invention, the extent of Movement of the jaw and the roller with the movement along the curved path deviate from the movement of the locking gear lever. Depending on the design of the sliding can be selectively influenced on the extent of movement of the locking gear lever, so that on the assumption of a fixed tooth width of the locking teeth on the slide can also influence the fineness of the operation of Zwangsgesperres and the number of securable partial pressing stages of the compulsory compound. Also for the geometric design of the locking teeth and the Sperrverzahnungshebels the invention solves the dependence on the circumstances for the forceps jaw and the toggle lever or pressure lever. The length of the locking gear lever, a circumferential extent of the locking teeth, any bending of the locking gear lever, the distance between the roller axis of the sliding guide and the geometry of the sliding guide can rather be freely determined by design.

In principle, the locking toothed lever can be rotatably mounted at any point of the drive element, against which the roller is rotatably mounted. A particularly compact embodiment of the pressing tongs according to the invention results when the locking toothed lever is mounted rotatably about the roller axis about which the roller is rotatable relative to the drive element.

The design of the slide can be arbitrary, for example, with one-sided or double-sided guideway. For a particularly simple embodiment of the invention, the sliding guide is formed with a slot along which a transversely to the extension of the slot play-free or at least in a partial area game-related leadership can be done. Here, the slot can be straight, curved or formed with kinks or heels.

A particularly compact embodiment of the pressing tongs according to the invention results when a bearing pin is used functionally by this one hand, for supporting the roller on this and on the other hand for supporting the locking gear lever on this serves.

It is also possible that another bearing pin is used multifunctionally by this one hand, the locking teeth lever relative to the sliding guide leads and on the other hand, the attachment of the cam track forming guide member is used.

• Von Vorteil ist, wenn eine Presszange nicht nur zum Verpressen von Werkstücken mit einer einzigen Geometrie, einer Materialsteifigkeit und/oder einer Querschnittsfläche (im Folgenden vereinfacht "Querschnittsfläche") eingesetzt werden kann, sondern multifunktional auch für unterschiedliche Werkstücke mit unterschiedlichen Querschnittsflächen. Ist aber bei starrer Ausgestaltung der Komponenten der Presszangen die Presszange ausgelegt für das Verpressen eines Werkstücks mit einer vorgegebenen Querschnittsfläche, hat der Einsatz der Presszange für ein Werkstück mit kleinerer Querschnittsfläche die Folge, dass bei diesem Einsatz die erforderlichen maximalen Presskräfte nicht erreicht werden, während bei Einsatz der Presszange für Werkstücke mit größerer Querschnittsfläche bereits nach einem Teilhub der Handhebel die maximalen Presskräfte erzeugt werden, so dass die vollständige Schließung der Handhebel zu übermäßigen Presskräften führen würde oder die vollständige Schließung der Handhebel durch manuelle Betätigungskräfte nicht möglich ist. Zur Abhilfe findet im Kraftfluss von den Handhebeln zu den Zangenbacken ein Kraft-Weg-Ausgleichselement Einsatz, welches bei einem Verpressen eines Werkstücks mit zu großer Querschnittsfläche infolge der Elastizität nicht (nur) zu einer plastischen Verformung des Werkstücks führt, sondern vielmehr zu einer Nachgiebigkeit führt, so dass im Idealfall ohne weitere plastische Verformung des Werkstücks die Handhebel allein unter elastischer Verformung des Kraft-Weg-Ausgleichselements geschlossen werden können. Beispiele für ein Kraft-Weg-Ausgleichselement, welches auch im Rahmen der vorliegenden Erfindung einsetzbar ist, sind beispielsweise
  • der Druckschrift EP 0 732 779 B1 , wo ein Abstützort des Kniehebeltriebs (somit im Rahmen der Erfindung die Rollenachse oder die Kurvenbahn) zur Bildung des KraftWeg-Ausgleichselements nachgiebig ausgebildet ist und/oder der Handhebel über eine Einschnürung elastisch ausgebildet ist,
  • den Druckschriften EP 0 158 611 B1 und DE 31 09 289 C2 , bei welchen ein Kniehebel elastisch abgestützt ist, oder
  • der nicht vorveröffentlichten europäischen Patentanmeldung EP 14 154 206.8 , wo ein Kniehebel oder Druckhebel selber nachgiebig ausgebildet ist,

zu entnehmen. Vorzugsweise ist das das Federelement bildende Kraft-Weg-Ausgleichselement aber abweichend zu den vorgenannten, aus dem Stand der Technik bekannten Ausführungsformen im Bereich des Zangenkopfes angeordnet: Möglich ist, dass das das Federelement bildende Kraft-Weg-Ausgleichselement im Kraftfluss zwischen dem Kniehebeltrieb und den Zangenbacken oder Betätigungselementen angeordnet ist, also dem Kniehebeltrieb nachgeordnet ist. Hierbei ist möglich, dass ein Federfußpunkt des das Kraft-Weg-Ausgleichselement bildenden Federelements an einem Betätigungselement, insbesondere einer Zangenbacke oder einem Schwenkring, befestigt oder angelenkt ist.As explained above, the use of the toggle lever drive, the use of the principle roller-curve and the described embodiment of the Zwangsgesperres constructive the characteristics of the pressing tongs can be influenced and the interaction with the Zwangsgesperre be specified. In addition, the behavior of the pressing tongs for an advantageous embodiment of the invention can be influenced via a force-displacement compensating element formed with a spring element. The use of a force-displacement compensating element in the pressing tongs is based on the following considerations:

• It is advantageous if a pressing tongs can be used not only for pressing workpieces with a single geometry, a material rigidity and / or a cross-sectional area (in the following simplified "cross-sectional area"), but also multifunctional for different workpieces with different cross-sectional areas. However, if the pressing tongs are designed for pressing a workpiece having a predetermined cross-sectional area in a rigid design of the components of the pressing tongs, the use of the pressing tongs for a workpiece with a smaller cross-sectional area has the consequence that the required maximum pressing forces are not achieved during this use, while Use of the crimping tool for workpieces with a larger cross-sectional area after a partial stroke of the lever, the maximum pressing forces are generated, so that the complete closure of the lever would lead to excessive pressing forces or the complete closure of the lever by manual operating forces is not possible. As a remedy, a force-displacement compensating element is used in the power flow from the hand levers to the jaws, which does not (only) lead to a plastic deformation of the workpiece when pressing a workpiece with too large a cross-sectional area due to the elasticity, but rather leads to a yielding so that ideally, without further plastic deformation of the workpiece, the hand lever can be closed solely by elastic deformation of the force-displacement compensating element. Examples of a force-displacement compensating element which can also be used in the context of the present invention are, for example
  • the publication EP 0 732 779 B1 where a Abstützort the toggle lever drive (thus in the invention, the roller shaft or the cam track) to form the KraftWeg-compensation element is resilient and / or the hand lever is formed elastically via a constriction,
  • the pamphlets EP 0 158 611 B1 and DE 31 09 289 C2 in which a toggle is elastically supported, or
  • the non-prepublished European patent application EP 14 154 206.8 where a toggle or pressure lever itself is compliant,

refer to. Preferably, however, the force-displacement compensating element forming the spring element is arranged in the region of the pliers head differently from the aforementioned embodiments known from the prior art. It is possible that the force-displacement compensating element forming the spring element in the force flow between the toggle lever drive and the Pliers jaws or actuators is arranged, so the knee lever drive is arranged downstream. It is possible that a spring base of the force-displacement compensating element forming spring element on an actuating element, in particular a pliers jaw or a pivot ring, is attached or articulated.

For the design of the force-displacement compensating element forming spring element, there are many possibilities. For a particular proposal of the invention, the spring element is designed as a bending beam. Here, the bending beam may have any geometry, for example, be formed straight or curved. By the choice of the course of the neutral fiber of the bending beam, the choice of material of the spring element and the bending stiffness, in particular the area moment of inertia of the bending beam, can be selectively taken influence on the elasticity of the spring element and the deformation behavior of the spring element.

In a particular embodiment of this idea, the spring element formed as a bending beam is designed in plate construction. This allows a particularly simple production of the spring element, wherein depending on the design of the individual plates of the spring element targeted and with high accuracy, the elastic behavior of the spring element can be specified. It is even possible that pressing tongs are provided with different characteristics of the force-displacement compensation element by a different number of otherwise identical plates is used for the different spring elements. Advantageous is a plate construction u. U. also when the spring element is formed integrally with another component of the pressing pliers, in particular an actuating element or the swivel ring, so that by means of the same plate and the manufacturing process used for this purpose can be carried out both a production of the spring element and the other component.

Another embodiment of the invention is dedicated to the integration of the spring element in the pliers head. For this embodiment, it is proposed that the spring element (at least partially) extends in the circumferential direction about a Gesenkachse. Here, the spring element with a circumferential direction of, for example, more than 90 °, more than 180 ° or even more than 270 ° extend around the Gesenkachse. It is possible that the spring element extends with a plurality of rectilinear, mutually inclined portions in the circumferential direction. But is also possible any curved course of the spring element in the circumferential direction.

In a preferred embodiment of the invention, the spring element is designed as circular arc spring or coil spring. For such a circular arc spring or coil spring results in a particularly favorable characteristic of the spring element, wherein u. U. also large spring travel are possible. It is also possible that on such a spring element an elasticity is brought about, which acts both in the circumferential direction about the Gesenkachse and in the radial direction to the Gesenkachse, which may be particularly advantageous for the integration of the spring element in the power flow between the drive elements, the drive mechanism and the actuators or dies.

In the embodiment of the spring element as a bending beam, the course of the flexural rigidity over the longitudinal axis of the bending beam can be arbitrary. In a preferred embodiment of the invention, the bending beam has a bending stiffness varying in the direction of its (rectilinear or curved) longitudinal axis. For a particular embodiment of the crimping tool, the area moment of inertia of the bending beam increases from the spring base point, which is acted on by the drive mechanism, to a circumferential cross-section of the bending beam opposite this spring base, which increase can be continuous or in steps. In a further embodiment of the pressing tongs according to the invention, the area moment of inertia of the bending beam is symmetrical to an axis of symmetry. The axis of symmetry runs approximately or exactly through the spring base on which the action by the drive mechanism takes place, and the cross section of the bending beam, which is opposite to this spring base in the circumferential direction. In this case, the die axis is preferably located on the said axis of symmetry. Such a configuration has proved to be particularly favorable for the design of the stresses in the bending beam and / or a symmetrical force generation on the coupled to the bending beam actuator.

As explained above, the dies can be fastened directly to an actuating element. For another embodiment of the invention, an actuating element on guides for the dies. The other actuator has actuating surfaces for the dies. In this case, relative movement of the actuators results in movement of the dies relative to the guides caused by the contact of the actuation surfaces with the dies. Preferably, in this context, both a sliding movement of the dies relative to the guides of the one actuating element as well as a sliding and / or rolling movement of the dies relative to the actuating surfaces of the other actuating element.

It is also possible that the actuating elements are pivoted relative to each other about the Gesenkachse, in which case, for example, an actuating element is designed as a pivot ring. In this case, the dies can be mounted pivotably relative to the guides, in particular by means of bearing bolts, which are held on the pliers head and store the dies with pliers head fixed bearing axis. The relative pivoting of the actuators has a pivoting of the dies relative to the guides result. This pivoting of the dies is caused by the contact of the actuating surfaces of the one actuating element with the dies.

In principle, the pressing tongs can also be used exclusively for a type, a geometry and / or a cross-sectional area of the workpiece. In a preferred embodiment of the invention are with the pressing tongs using the force-displacement compensation as a result of the force displacement compensating element and / or using the movement of the roller along the curved path with a change in the size and angular relationships of the toggle lever workpieces with different cross-sectional areas to be pressed compressible. In this case, the cross-sectional areas of the different workpieces, which are compressible with the same pressing tongs (without replacement of a replaceable head or replacement of dies), at least by a factor of 30 (in particular at least by a factor of 45, 50, 75, 100, 115 or even 200) before each other differ. By way of example only, workpieces having a cross-sectional area of 0.08 mm ² , 0.14 mm ² , 0.25 mm ² , 0.35 mm ² , 0.5 mm ² , 0.75 mm can be produced with the same crimping pliers ² , 1.0 mm ² , 1.5 mm ² , 2.5 mm ² , 4 mm ² , 6 mm ² , 10 mm ² and 16 mm ^{2 are} pressed.

In the open position of the pressing tongs form the dies a receptacle for the workpiece, which must be at least as large as the largest with the pressing tongs to be pressed workpiece. The smaller the workpiece that is inserted into the receptacle formed by the dies in the open position, then in fact, the greater the clearance and the worse is the guidance and fixation of the workpiece in the pliers head in the open position. In order to ensure a recording and exact alignment of the smaller workpiece in the pressing tongs before the start of the actual pressing operation, a partial closing movement would have to be brought about and fixation of the drive elements carried out in such a way that the receptacle formed by the dies is reduced to such an extent that the smaller workpiece fits precisely is included. The invention proposes alternatively or cumulatively that a positioning device can be arranged on the pliers head, by means of which a workpiece with a predetermined cross-sectional area in a receptacle (preferably also workpieces of different cross-sectional area in several receptacles) in a predetermined position and orientation on the Pliers head can be kept. In this case, the positioning device is preferably equipped only with suitable receptacles for a subset of the workpieces and cross-sectional areas to be pressed by the pressing tongs.

For a particular proposal of the invention it is proposed that the spring element is guided over a guide. This guide is preferably designed as an additional guide to other couplings of the spring element with the adjacent components of the pressing pliers, ie in particular in addition to the drive connection of the spring element with the actuating element and in addition to the coupling of the spring element in the region of the other Federfußpunktes with the drive element or lever. In this case, the additional guidance can be effected in the region of a spring base point or at any location of the spring element between the spring base points. The guide may be permanent or only temporary during part of the power stroke. By means of the guide, a guidance of the spring element in the circumferential direction about the Gesenkachse and / or radially to the Gesenkachse. It is also possible that in the guide, the spring element is acted upon by a bias against a projection or paragraph or in an end position. Only with overcoming the bias for passing through a portion of the power stroke of the pressing tongs can be done a solution of the spring element and thus a movement along the guide. For this embodiment, the spring element can be equipped with a targeted "nonlinearity", since with the solution of the spring element of the Projection or paragraph change the boundary conditions for the elastic deformation of the spring element. Here, the guide can be done for example by a housing or a cover plate of the pliers head. It is also entirely possible, however, for the guide of the spring element to be effected by a component of the pressing tongs moving in the course of the working stroke. About a particular embodiment of the invention, the leadership of a region of the spring element relative to another region of the spring element is effected.

Advantageous developments of the invention will become apparent from the claims, the description and the drawings. The advantages of features and of combinations of several features mentioned in the description are merely exemplary and can take effect alternatively or cumulatively, without the advantages having to be achieved by embodiments according to the invention. Without thereby altering the subject matter of the appended claims, as regards the disclosure of the original application documents and the patent, further features can be found in the drawings, in particular the illustrated geometries and the relative dimensions of several components and their relative arrangement and operative connection. The combination of features of different embodiments of the invention or of features of different claims is also possible deviating from the chosen relationships of the claims and is hereby stimulated. This also applies to those features which are shown in separate drawings or are mentioned in their description. These features can also be combined with features of different claims. Likewise, in the claims listed features for further embodiments of the invention can be omitted.

The features mentioned in the patent claims and the description are to be understood in terms of their number that exactly this number or a greater number than the said number is present, without requiring an explicit use of the adverb "at least". For example, when talking about an element, it should be understood that there is exactly one element, two elements or more elements. These features may be supplemented by other features or be the only characteristics that make up the product in question.

The reference numerals contained in the claims do not limit the scope of the objects protected by the claims. They are for the sole purpose of making the claims easier to understand.

BRIEF DESCRIPTION OF THE FIGURES

Fig. 1 bis 11

zeigen eine erste Ausführungsform der Presszange mit einer Öffnungsstellung (Fig. 1), einer Schließstellung (Fig. 2), Bestandteilen der Presszange in Explosionsdarstellung (Fig. 3 und 4), einem Führungsteil mit Kurvenbahnen in räumlicher Einzelteilzeichnung (Fig. 5), dem Kniewinkel der Presszange in Öffnungsstellung (Fig. 6) und Schließstellung (Fig. 7) sowie den Betätigungskraftverläufen für unterschiedliche Werkstücke (Fig. 8) und den Abmessungen des Federelements (Fig. 9 und 10) sowie den sich ergebenen Spannungsverläufen in dem Federelement (Fig. 11).

Fig. 12

zeigt eine weitere Ausführungsform der Presszange.

Fig. 13 und 14

zeigen eine weitere Ausführungsform der Presszange mit zusätzlicher Führung des Federelements.

In the following the invention will be further explained and described with reference to preferred embodiments shown in the figures.

Fig. 1 to 11

show a first embodiment of the pressing tongs with an open position ( Fig. 1 ), a closed position ( Fig. 2 ), Components of the crimping pliers in exploded view ( Fig. 3 and 4 ), a guide part with curved paths in a spatial part drawing ( Fig. 5 ), the knee angle of the pressing tongs in the open position ( Fig. 6 ) and closed position ( Fig. 7 ) and the Betätigungskraftverläufen for different workpieces ( Fig. 8 ) and the dimensions of the spring element ( Fig. 9 and 10 ) as well as the resulting voltage curves in the spring element ( Fig. 11 ).

Fig. 12

shows a further embodiment of the pressing tongs.

FIGS. 13 and 14

show a further embodiment of the pressing tongs with additional guidance of the spring element.

DESCRIPTION OF THE FIGURES

Fig. 1 shows a crimping pliers 1 in a representation in which one of two cover plates 2a, 2b, with which a solid hand lever 3 and a pliers head 4, in particular a kind of "housing" of the pliers head 4, is disassembled.

The pressing tongs 1 is formed with a fixed hand lever 3 and a movable hand lever 5. A pivoting of the hand lever 3, 5 towards each other (see transition from Fig. 1 to Fig. 2 ) Produces a drive mechanism 6 and a spring element 7, which forms a force-displacement compensating element 8, a relative movement of actuators 9, 10. Here, the actuator 9 is integral with the part of the cover plate 2, which in Area of the pliers head 4 extends, formed so that it is a fixed actuator 9 here. By contrast, the actuating element 10 is designed as a movable actuating element 10 in the form of a pivot ring 11, which relative to the fixed actuating element 9 to the vertical to the plane according to Fig. 1 oriented, given by dies 12 workpiece and die axis 13 is pivotable. The dies 12 are pivotable about axes, which are oriented parallel to the Gesenkachse 13, mounted opposite bearing pins 14, which are held on the actuating element 9 and the cover plate 2. The pivot pin 11 thus forms guides 15 for the dies 12. The pivot ring 11 forms radially inwardly in the region of grooves actuating surfaces 16 on which abutment surfaces 17 of the dies 12 abut such that a pivoting of the pivot ring 11 about the Gesenkachse 13 pivoting the dies 12 has around the bearing pin 14 result. This pivoting of the dies 12 in turn has the consequence that a die contour 18 formed by the dies 12, which is closed in the circumferential direction about the die axis 13 with the formation of minimal gaps between the adjacent dies 12, changes in size. For the illustrated embodiment, the die contour 18 is formed hexagonal regardless of the size thereof in the first approximation.

The spring element 7 is formed by an integral projection of the swivel ring 11, which extends in a circular arc or here in a spiral around the swage axis 13 in the circumferential direction. For the illustrated embodiment, the circumferential angle is approximately 360 °, wherein the formed in the connection region with the pivot ring 11 Federfußpunkt 19 and the outer Federfußpunkt 20 of the spring element 7 approximately in a 4:00 clock position with respect to the Gesenkachse 13 as shown in FIG Fig. 1 are arranged with horizontally oriented fixed lever 3. The Federfußpunkt 20 is pivotable, here via a bearing pin 21, hinged to the movable hand lever 5. On the movable hand lever 5, here via a bearing pin 22, a roller 23 is rotatably mounted. The roller 23 is located on a curved path 24 of a guide member 25. In the present case, the guide member 25 performs the roller 23 only on one side about the curved path 24, while for a different embodiment, a recording of the roller 23 between two curved paths can be done, which with a Game or no game can be the case. The guide member 25 is rigid, here via bearing pins 26, 27, fixed to the fixed hand lever 3. Opposite the bearing pin 22 is also pivotally mounted a Sperrverzahnungsheben 28, which is formed with lifting parts 29, 30. In the outer end region, the lever part 29 forms a locking toothing 31. The Lever part 30 has a radially oriented to the bearing pin 22 slot 32 through which the bearing pin 27 passes.

The drive mechanism 6 is designed as a toggle lever drive 33. This has a toggle lever 34, which corresponds to the connection between the contact point of the roller 23 with the guide track 24, and a second toggle 35, which corresponds to the connection between the bearing pins 21, 22 predetermined bearing axes. Between the toggle levers 34, 35 a knee angle 36 is formed.

For the working stroke of the pressing tongs 1 from the open position according to Fig. 1 according to the closed position Fig. 2 leads for disappearing pressing forces in a first partial stroke, the movement of the hand lever 3, 5 in support of the roller 23 on the curved path 24 of the guide member 25 to the fact that the bearing pin 21 and thus also the Federfußpunkt 20 of the spring element 7 in the circumferential direction 37 about the Gesenkachse 13th move. As a result of the vanishing pressing forces no elastic deformation of the spring element 7, so that a corresponding pivoting of the pivot ring 19 takes place, which in turn the pivoting of the dies 12 is connected and a reduction of the cross-sectional area of the die contour 18 is accompanied. However, since the point of contact of the roller 23 with the curved path 24 of the guide member 25 is not fixed, the roller 23 can roll on the cam track 24 during this partial stroke, which depending on the rolling movement of the roller 23 and the geometry of the curved path 24 also changed a knee angle 36 sets. This already complex kinematics is superimposed on an increasing elastic deformation of the spring element 7 with increase of the pressing forces in the region of the die with increasing closing movement. This is to be clarified on the basis of a theoretical limiting case, for which it is assumed that the workpiece after a first partial stroke, which is designed for example as idle stroke, and a second partial stroke, by means of which a pressing of the workpiece with plastic deformation thereof, during the last third Teilhubs is ideal rigid. Upon reaching this ideal rigid state of the workpiece, the position of the dies 12 and the pivot ring 11 and thus also the spring base point 19 is also fixed. Nevertheless, in the third partial stroke, a further closing movement of the hand lever 3, 5 take place, since with further loading of the hand lever 3, 5, the spring element 7 can be elastically deformed. On the one hand, a deformation of the spring base point 20 in the circumferential direction 37 can take place. It is also possible that the spring base point 20 is deformed in the radial direction 38 to the Gesenkachse 13. Thus, despite a rigid workpiece and fixed dies 12, fixed pivot ring 11 and fixed spring base 19 a rolling movement of the roller 23 along the guideway 24 done with transfer of the hand lever 3, 5 in the closed position. For realistic stiffnesses of the workpiece results in a superposition of a plastic deformation of the workpiece, but which becomes smaller and smaller with increasing pressing force, with an elastic deformation of the spring element 7, the proportion to the plastic deformation of the workpiece with increasing pressing force is always greater. This results in practice u. U. a superposition of the second partial stroke with the third partial stroke.

• Für ein großes Werkstück ist ein Leerhub als erster Teilhub (bspw. zwischen 0% und 15% des Arbeitshubs) sehr kurz ausgebildet und es erfolgt eine plastische Verformung des Werkstücks in einem zweiten Teilhub bspw. bereits am Anfang des Arbeitshubs (bspw. zwischen 15% und 60% des Arbeitshubs), während sich ein großer dritter Teilhub (bspw. zwischen 60% und 100% des Arbeitshubs) anschließt, in welchem vorrangig die Verformung des Federelements 7 erfolgt.
• Für ein kleineres Werkstück ist ein Leerhub als erster Teilhub (bspw. zwischen 0% und 30% des Arbeitshubs) länger ausgebildet und es erfolgt eine plastische Verformung des Werkstücks in einem zweiten Teilhub in einem späteren Bereich des Arbeitshubs (bspw. zwischen 30% und 80% des Arbeitshubs), während sich ein kleiner dritter Teilhub (bspw. zwischen 80% und 100% des Arbeitshubs) oder sogar kein dritter Teilhub anschließt, in welchem vorrangig die Verformung des Federelements 7 erfolgt.

Depending on the cross-sectional area of the workpiece to be pressed, the position of the different partial strokes changes over the working stroke of the pressing tongs 1:

• For a large workpiece, an idle stroke as a first partial stroke (eg. Between 0% and 15% of the working stroke) is very short and there is a plastic deformation of the workpiece in a second partial stroke, for example. Already at the beginning of the working stroke (eg. Between 15% and 60% of the working stroke), while a large third partial stroke (for example between 60% and 100% of the working stroke) follows, in which the deformation of the spring element 7 takes place with priority.
• For a smaller workpiece an idle stroke as a first partial stroke (eg. Between 0% and 30% of the working stroke) is formed longer and there is a plastic deformation of the workpiece in a second partial stroke in a later range of the power stroke (eg. Between 30% and 80 % of the working stroke), while a small third partial stroke (for example between 80% and 100% of the working stroke) or even no third partial stroke follows, in which the deformation of the spring element 7 takes place with priority.

With the pivoting of the hand lever 3, 5 toward each other, a pivoting of the locking toothed lever 28 is accompanied, during which a locking lug 39 of a pawl 40, which is also supported by a spring 93 pivotally mounted on the hand lever 5, ratchet-like along the ratchet teeth 31 slides. If the hand forces applied to the hand levers 3, 5 are temporarily reduced or eliminated, the engagement of the locking nose 39 in the locking toothing 31 blocks the opening movement of the hand levers 3, 5 and thus also the opening movement of the dies 12. Only when the hand levers 3, 5 completely close Have reached closed position, the locking lug 39 has the ratchet teeth 31 complete, with which the pawl 40 can fold down and ratchet-like slide during a then possible opening movement of the hand lever 3, 5 on the ratchet 31 back to their original position. With the Sperrverzahnungshebel 28 and acted upon by the spring 93 pawl 40 Zwangsgesperre 48 is formed.

With regard to the basic design of a pressing tongs 1 with a pivot ring 11 and the possibility of joint pivoting of six dies 12 here by relative rotation of the actuators 9, 10 is based on the relevant prior art, in particular EP 0 732 779 B1 and DE 10 140 270 B4 and DE 10 2005 003 615 B3 directed. In the present case, the hand lever 3, 5 drive elements 41, 42, on which the manual actuating forces are exerted. It is understood that the drive elements 41, 42 can also be acted upon by forces of an actuator such as an electric drive.

The spring element 7 is formed here as a kind of bending beam 43. In the region of the spring base point 20, force components in the circumferential direction 37 and / or in the radial direction 38 are introduced into this bending beam 43, which stresses the bending beam 43 about a bending axis which is vertical to the plane of the drawing Fig. 1 is oriented. It is also possible in principle to use a stress of the bending beam 43 with a compressive force on buckling. Preferably, however, the bending beam 43 is subjected to a tensile force in the circumferential direction 37. For the illustrated embodiment, the bending beam 43 is in accordance with a in the drawing plane Fig. 1 extending spiral spring or circular arc spring 44 is formed. Here, the spiral or circular arc spring extends in the circumferential direction 37 about the Gesenkachse 13.

The bending beam 43 in this case has a circular arc-shaped or spiral-shaped neutral fiber or longitudinal axis 45, along which the bending stiffness changes, in particular by a change in the area moment of inertia. For the illustrated embodiment, the design of the height of the cross section of the bending beam 43, which determines the area moment of inertia, symmetrical to an axis of symmetry, which passes through the Gesenkachse 13 and the Federfußpunkt 20. Accordingly, the height and the cross-sectional area of the spring element 7 is maximally in a cross-section 47, which is arranged centrally between the spring base points 19, 20 in the circumferential direction.

In the exploded view according to Fig. 3 it can be seen that the pressing tongs with two cover plates 2a, 2b is formed. The two cover plates 2a, 2b on the one hand form the fixed hand lever 3. On the other hand, the cover plates 2a, 2b form a kind of housing of the pliers head 4, between which the moving parts, namely the spring element 7, the pivot ring 11 and the dies 12 are accommodated. On the other hand, the bearing pins 14 of the dies 12 are received in bores 49 of the cover plates 2a, 2b.

It can be seen further in Fig. 3 in that the spring element 7 and the swivel ring 11 are formed in plate construction, here with four plates, wherein the individual plates for the swivel ring 11 and the spring element 7 are formed in one piece.

Notwithstanding the in Fig. 1 and 2 illustrated embodiment has according to Fig. 3 optionally, the spring element on its outer side a projection 50 in which a spring base 51 or a coupled with such a Federfußpunkt tappet another spring 52 is supported, the other Federfußpunkt 53 is supported on the cover plates 2a, 2b or the movable hand lever 5. By way of the further spring 52, the force relationships on the pressing tongs 1 can be influenced in addition to the spring element 7. Thus, the additional spring 52 can serve to influence the dependence of the generated pressing force on the pivoting angle of the hand lever and the actuating force applied to the hand lever. It is also possible that the contact pressure of the roller 23 on the guide track 24 of the guide member 25 is increased or ensured by the further spring 52.

Fig. 4 shows the assembled basic components of the pressing tongs 1 according to Fig. 3 before its assembly with the two hand levers 3, 5 associated with handles 54, 55th

According to Fig. 3 and 4 the pressing tongs 1 can have a positioning device 56. The positioning device 56 has three alternative receptacles 57a, 57b, 57c for workpieces with different cross-sectional areas for the illustrated embodiment. The positioning device 56 can be brought into different operating positions in which in each case a receptacle 57 a (57 b, 57 c) is arranged coaxially to the die axis 13. For the illustrated embodiment, the positioning device 56 is formed with a Positionierstrebe or positioning washer 58 which is pivotally mounted on the cover plates 2, here by means of a bearing pin 59. The Positionierstrebe or positioning washer 58 lies directly sliding on the outside of the cover plate 2b.

As in Fig. 5 is shown, the guide member 25 fork-shaped with the formation of a slot 60 between two legs 61 a, 61 b may be formed. Through the slot 60 of the guide member 25 extends to allow a relative pivotal movement of the locking teeth 28 (see also Fig. 3 ). In the outer end region, the legs 61a, 61b each have a bore 62a, 62b, through which the bearing pin 27 extends in the installed state. For reasons of weight, the legs 61 a, 61 b have recesses 63.

In Fig. 5 It can be seen that for the illustrated embodiment, two parallel cam tracks 24a, 24b are formed by the two legs 61a, 61b, on which then roll off two rollers 23a, 23b on both sides of the pawl lever 28. Furthermore, it can be seen that the cam tracks 24a, 24b for the illustrated embodiment have two concave portions 64, 65, between which a convex portion 66 is disposed. Here, the curved path 24 in the concave portion 65, which is traversed at the beginning of the power stroke, more inclined than other portions of the curved path 24th

• geeignete Formgebung der Kurvenbahn 24,
• Wahl der Kennlinie und Geometrie des Federelements sowie
• Auslegung des Antriebsmechanismus 6

der Kniewinkel 36 während des gesamten Arbeitshubs immer zwischen 130° und dem Streckwinkel von 180°.By suitable shaping of the curved path 24 it can be achieved that the knee angle 36 of the toggle lever drive 33 is relatively large during the entire working stroke. According to Fig. 6 the knee angle 36 is already at the beginning of the working stroke about 135 °, while this according to Fig. 7 at the end of the working stroke in the range of 160 to 185 °. Preferably lies through

• suitable shaping of the curved path 24,
• Choice of the characteristic and geometry of the spring element as well
• Design of the drive mechanism 6

the knee angle 36 always during the entire working stroke between 130 ° and the draft angle of 180 °.

In Fig. 8 the applied hand forces 67 are shown as a function of the actuation path 68 of the movable hand lever 5. Here, the curves 69 to 81 show the hand force curves for different cross sections of the workpieces, namely 0.08 mm ² (69), 0.14 mm ² (70), 0.25 mm ² (71), 0.35 mm ² (72 ), 0.5 mm ² (73), 0.75 mm ² (74), 1.0 mm ² (75), 1.5 mm ² (76) 2.5 mm ² (77), 4 mm ² ( 78), 6 mm ² (79), 10 mm ² (80) and 16 mm (81). It can be seen here that for smaller workpieces initially the initial first partial stroke is passed with vanishing press forces, while the actual hand forces must be applied only towards the end of the power stroke. As the size of the workpiece increases, the slope of the curves 69-81 is further displaced toward smaller actuation paths. It can be seen in Fig. 8 in that pressing of all of said workpieces with the same pressing tongs 1 is possible under controllable manual forces, which are preferably smaller than 300 N.

In Fig. 9 is shown for the spring element 7 an exemplary choice of dimensions. It can be seen here that the spring element extends in a spiral shape around the die axis 13 with a circumferential angle of approximately 360 °. The effective height 82 of the spring element 7 for influencing the area moment of inertia is symmetrical to the axis of symmetry 46 and increases from both Federfußpunkten 19, 20 to the same extent to the middle of the spring element 7 in the circumferential direction between the two Federfußpunkten 19, 20. While in Fig. 9 only discrete values of the height 82 of the spring element 7 are indicated, shows Fig. 10 the dependence of the height 82 from the circumferential angle 83, starting from the point centrally between the two spring base points 19, 20th

Figure 11 shows the stress distribution in the spring element 7, wherein the same gray levels are used for equal voltages here. By means of the symmetrical design of the spring element 7 and the choice of heights 82 according to Fig. 10 can be achieved that the maximum stresses in the spring element 7 along the circumference or the longitudinal axis 45 are constant.

Fig. 12 shows a further embodiment of the pressing tongs 1, which basically in the Fig. 1 to 11 illustrated embodiment corresponds. However, here the contour of the guideway 24 is selected such that it has exclusively concave portion 64, 65, which are connected to each other via a rectilinear portion 89.

Fig. 13 and 14 show a further embodiment of a pressing tongs, wherein Fig. 13 the pressing tongs in the open position with mounted cover plate shows and Fig. 14 the pressing tongs also in the open position, but without mounted cover plate shows. This embodiment basically corresponds to the embodiment of the pressing tongs 1 according to FIG Fig. 1 to 11 or Fig. 12 , However, the spring element 7 is guided with an additional guide 90. For the The guide 90 is formed by a spring pin 7 supported by the guide pin 91, which is guided in a guide groove or a slot 92 of the cover plates 2. Preferably, the slot 92 extends circumferentially around the die axis 13.

For the illustrated embodiments, the guide member 25 is fixed to the fixed hand lever 3, while the roller 23 is rotatably supported relative to the movable hand lever 5. But it is also possible that the guide member 25 is fixed to the movable hand lever 5, while the roller 23 is rotatably mounted relative to the fixed hand lever 3.

It is possible that for a hand-operated pressing tongs and a power-operated pressing tongs in the invention, the same basic structure is used, then be used in the manually operated pressing tongs as drive elements hand lever, while for the power-operated pressing tongs instead of the hand lever to an actuator deflected drive elements are used. To give just a simple non-limiting example, for an externally operated crimping tool, the fixed (hand) lever may also be shortened and supported on a fixed abutment, while on the movable (also shorter) (hand) Lever a connecting rod, a plunger o. Ä. Of the actuator is articulated. UU is a power-operated crimping pliers trained without Zwangsgesperre.

LIST OF REFERENCE NUMBERS

1

crimping pliers

2

cover plate

3

solid hand lever

4

pliers head

5

movable hand lever

6

drive mechanism

7

spring element

8th

Force-compensation element

9

fixed actuator

10

movable actuator

11

swivel

12

die

13

die axis

14

bearing bolt

15

guide

16

actuating surface

17

Counter-actuating surfaces

18

Gesenkkontur

19

spring base

20

spring base

21

bearing bolt

22

bearing bolt

23

role

24

cam track

25

guide part

26

bearing bolt

27

bearing bolt

28

Lock gear lever

29

lever part

30

lever part

31

locking teeth

32

Long hole

33

Knee lever drive

34

toggle

35

toggle

36

knee angle

37

circumferentially

38

radial direction

39

locking tab

40

lock blade

41

driving element

42

driving element

43

bending beam

44

Spiral or circular arc spring

45

longitudinal axis

46

axis of symmetry

47

cross-section

48

Zwangsgesperre

49

drilling

50

head Start

51

spring base

52

another spring

53

spring base

54

handle

55

handle

56

positioning

57

admission

58

positioning bar

59

bearing bolt

60

slot

61

leg

62

drilling

63

recess

64

concave subarea curved track

65

concave sub-area curved track

66

convex part of the curved path

67

manual force

68

actuating

69

Curve

70

Curve

71

Curve

72

Curve

73

Curve

74

Curve

75

Curve

76

Curve

77

Curve

78

Curve

79

Curve

80

Curve

81

Curve

82

height

83

pressure lever

84

knee

89

rectilinear section

90

guide

91

guide pin

92

Long hole

93

feather

Claims (14)

Pressing tongs (1) for pressing a workpiece with a) two drive elements (41, 42), b) two in the region of a pliers head (4) arranged actuating elements (9, 10) which actuate dies (12), between which the workpiece can be pressed, and c) a toggle lever drive (33) acting between the drive elements (41, 42) and the actuators (9, 10), ca) which has two toggle levers (34, 35), cb) wherein the toggle levers (34, 35) form a knee angle (36) which varies over the working stroke, d) wherein a toggle lever (34) of a roller (23) is formed, which da) relative to a drive element (42) is rotatably mounted about a roller axis and db) on a fixedly connected to the other drive element (41) curved cam track (24) rolls, characterized in that e) a Sperrverzahnungshebel (28) of a Zwangsgesperres (48) relative to rotate ea) the drive element (42) against which the roller (23) is rotatably mounted, and eb) of the roll (23) on the drive element (42), against which the roller (23) is rotatably mounted, is mounted, f) wherein a lever part (30) of the pawl lever (28) is coupled via a sliding guide with the other drive element (41) and g) another lever part (29) of the locking toothed lever (28) forms a locking toothing (31) of the positive locking mechanism (48). Crimping pliers (1) according to claim 1, characterized in that the locking toothed lever (28) is rotatably mounted about the roller axis with respect to the drive element (42) against which the roller (23) is rotatably mounted. Crimping pliers (1) according to claim 1 or 2, characterized in that the sliding guide is formed with a slot (32). Crimping pliers (1) according to claim 2 or claim 3 when appended to claim 2, characterized in that the roller (23) and the locking toothed lever (28) are mounted on a common bearing pin (22). Crimping pliers (1) according to one of the preceding claims, characterized in that a bearing pin (27) a) leads the Sperrverzahnungshebel (28) relative to the sliding guide and b) the attachment of a cam track (24) forming the guide member (25) is used. Crimping pliers (1) according to any one of the preceding claims, characterized in that a with a spring element (7) formed force-displacement compensating element (8) is provided. Crimping pliers (1) according to claim 6, characterized in that the spring element (7) is designed as a bending beam (43). Crimping pliers (1) according to claim 6 or 7, characterized in that the spring element (7) is formed in plate construction. Crimping pliers (1) according to claim 7 or 8, characterized in that the spring element (7) as a circular arc spring or coil spring (44) is formed. Crimping pliers (1) according to one of the preceding claims, characterized in that a) an actuating element (9) has guides (15) for dies (12) and b) an actuating element (10) has actuating surfaces (16) for the dies (12), c) wherein a relative movement of the actuating elements (9, 10), a movement of the dies (12) relative to the guides (15) result, which is caused by the contact of the actuating surfaces (16) with the dies (12). Crimping pliers (1) according to one of the preceding claims, characterized in that a) the actuating elements (9, 10) are pivoted relative to each other about the Gesenkachse (13), b) the dies (12) are mounted pivotably relative to the guides (15) and c) the relative pivoting of the actuating elements (9, 10) has a pivoting of the dies (12) relative to the guides (15) result, which is caused by the contact of the actuating surfaces (16) with the dies (12). Crimping pliers (1) according to one of the preceding claims, characterized in that they are in use with the crimping pliers (1) a) the force-displacement compensation as a result of the force-displacement compensating element (8) and / or b) the movement of the roller (23) along the curved path (24) of the guide part (25) with a change in the size and angular relationships of the toggle lever drive (33) Workpieces with different cross-sectional areas to be pressed can be pressed, wherein the cross-sectional areas deviate from one another by at least a factor of 30 for two different workpieces which can be pressed by the pressing tongs. Crimping pliers (1) according to one of the preceding claims, characterized in that a positioning device (56) for at least one workpiece is arranged on the pliers head (4). Crimping pliers according to one of claims 6 to 13, characterized in that the spring element (7) via a guide (90) is guided.

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