EP2078591A2 - Pressing tool - Google Patents

Abstract

The tool (1) e.g. crimping pliers (2), has crimping jaws (5) building a nest (45) for a connecting element. Hand levers (3, 4) manually apply crimping forces to move the jaws. The hand levers are located in a plane (50) that is aligned with a longitudinal axis (14) of the nest and divided into two half-planes (51, 53) by the longitudinal axis. A transfer/transmission unit transfers translational activation along the longitudinal axis in the force flow between the hand levers and the crimping jaws into rotational activation around the longitudinal axis.

Description

TECHNICAL FIELD OF THE INVENTION

The invention relates to a pressing tool, in particular a so-called pressing or crimping tool, for pressing connecting elements such as cable end sleeves, circular connectors, cable lugs or contact sockets on electrical conductors or for thin-walled pipe connections.

STATE OF THE ART

1. a) Für eine erste, bspw. in DE 195 07 347 C1 beschriebenen Variante werden Handhebel in einer Ebene einer Zange verschwenkt, in welcher sich auch ein abgeplatteter Zangenkopf erstreckt und sich Pressbacken des Presswerkzeuges bewegen. Das zu verpressende Verbindungselement, insbesondere mit dem in dieses eingelegten elektrischen Leiter, wird in vertikaler Richtung zu der vorgenannten Ebene in eine von den Pressbacken ausgebildete Aufnahme eingebracht. Mit einer Bewegung der Handhebel bewegen sich die Pressbacken in der zuvor erläuterten Ebene radial nach innen auf eine Längsachse des Verbindungselements zu. Anders gesagt ist für diese erste Variante die Ebene, in welcher die Handhebel bewegt werden, vertikal zu der Längsachse des Verbindungselements und der durch die Pressbacken geschaffenen Aufnahme für dieses orientiert.
2. b) Gemäß einer zweiten, bspw. in DE 4 026 332 C2 , DE 4 039 435 C1 und DE 198 18 482 C1 beschriebenen Variante erstrecken sich zwar sowohl die Handhebel als auch der abgeplattete Zangenkopf in einer Ebene entsprechend der ersten Variante. Allerdings wird für diese Variante das Verbindungselement nicht quer zu dieser Ebene in die durch die Pressbacken geschaffene Aufnahme eingeführt, sondern vielmehr stirnseitig in den Zangenkopf, wobei die Längsachse des Verbindungselements sowie die Einführrichtung in die durch die Pressbacken geschaffene Aufnahme in der zuvor erläuterten Ebene liegt. Somit fluchten die Längsachse der Aufnahme und des hierin angeordneten Verbindungselements mit einer Mittelachse zwischen den beiden Handhebeln.

Basically, two different types of actuation of pressing tools are known from the prior art:

1. a) For a first, eg in DE 195 07 347 C1 described variant hand lever are pivoted in a plane of a pair of pliers, in which also extends a flattened pliers head and move pressing jaws of the pressing tool. The connecting element to be pressed, in particular with the electrical conductor inserted in the latter, is introduced in a vertical direction to the aforementioned plane into a receptacle formed by the pressing jaws. With a movement of the hand lever, the pressing jaws move in the previously explained plane radially inwardly towards a longitudinal axis of the connecting element. In other words, for this first variant, the plane in which the hand levers are moved is oriented vertically to the longitudinal axis of the connecting element and the receptacle provided by the pressing jaws for this.
2. b) According to a second, for example DE 4 026 332 C2 . DE 4 039 435 C1 and DE 198 18 482 C1 Although described variant extend both the hand lever and the flattened pliers head in a plane corresponding to the first variant. However, for this variant, the connecting element is not introduced transversely to this plane in the receptacle provided by the pressing jaws, but rather frontally into the pliers head, wherein the longitudinal axis of the connecting element and the insertion direction is in the created by the pressing jaws recording in the previously explained level. Thus, the longitudinal axis of the receptacle and the connecting element arranged therein are aligned with a central axis between the two hand levers.

Due to the different power transmission mechanisms between the hand levers and the press jaws find a variety of pressing jaws use for pressing tongs according to variant a), in particular, the number of pressing jaws with the number of corners corresponds to be injected in the connecting element cross-sectional contour. On the other hand, the transmission mechanism of the pressing tongs according to variant b) requires the use of only two pressing jaws, in which case a pressing jaw must serve to specify a plurality of boundary surfaces of the cross-sectional contour to be formed in the connecting element. For example, pressing jaws with a trapezoidal contour of the pressing surfaces are used here.

From the publication US 3,201,969 is a gun-type pressing tool known with a housing with an L-shaped angled handle on which an operating knob is arranged according to the trigger of a gun. About the operation button, a valve can be actuated, which directs a pneumatic pressure on a piston. The actuation of the piston results in axial movement, which is converted via a toggle mechanism into a radial pressing movement of pressing elements, which act on a introduced into the "mouth of the gun" workpiece. The document also mentions that the pressing movement can be caused manually by pressing a finger on the actuating button instead of the pneumatic operation, without the document being explained in more detail how the required high forces can be generated by a single finger.

DE 42 41 224 C1 . DE 41 01 284 C2 and US 6,173,466 B1 also describe pistol-type pressing tools, in which, however, the workpiece to be pressed are to be introduced transversely to the "mouth" into the tool.

US 4,720,911 describes a tool which is similar to a tool for processing pop rivets and with which no radially acting on a workpiece pressing forces, but rather an axial compressive force is generated.

Further prior art is from the documents DE 101 40 270 B4 . DE 42 41 971 C1 and CH 402 099 known.

OBJECT OF THE INVENTION

• eine gegenüber dem Stand der Technik veränderte Lage oder Ausrichtung zwischen der Hand des Benutzers des Presswerkzeugs und dem Verbindungselement bzw. den Handhebeln und den Pressbacken
• veränderte Zugangsmöglichkeiten des Presswerkzeugs in besonderen Umgebungsbedingungen,
• veränderte Übertragungsmechanismen zwischen manuellen Betätigungskräften und den Pressbacken,
• eine veränderte Gehäusegestaltung und/oder
• eine veränderte Betätigungscharakteristik

ermöglicht.The invention has for its object to provide a new embodiment of a pressing tool for pressing fasteners, which

• a relation to the prior art changed position or alignment between the hand of the user of the pressing tool and the connecting element or the hand levers and the pressing jaws
• changed access possibilities of the pressing tool in special environmental conditions,
• changed transmission mechanisms between manual actuating forces and the pressing jaws,
• a modified housing design and / or
• a modified operating characteristic

allows.

SOLUTION

The object of the invention is achieved with the features of independent claim 1. Further embodiments of this inventive solution will become apparent according to the features of the dependent claims 2 to 13.

DESCRIPTION OF THE INVENTION

The present invention is u. a. caused by the knowledge that for the known from the prior art variants a) and b) the possibilities for a constructive specification of the relative position of the user's hand to the arrangement of the cable end or pipe or the connecting element and the relative orientation is limited to each other , With the present invention, new arrangements and relative positions between hand and connecting element in the pressing tool and / or alignments with each other are to be made possible. For this purpose, the invention proposes that the hand lever are arranged and movable in a plane in which the longitudinal axis of the connecting element is located. While this also applies to pressing tools of variant b), but for which the hand lever or a central axis of the hand lever are aligned to the longitudinal axis of the connecting element or the hand lever are arranged on both sides of the longitudinal axis, according to the invention, both hand lever on the same side of the longitudinal axis. In other words, the plane in which lies the longitudinal axis of the connecting element and in which the hand lever are arranged, divided by the longitudinal axis in two half-planes. Both hand levers are arranged according to the invention in the same half-plane. Such an arrangement opens up a new relative position and arrangement between the connecting element and the hand levers with improved operating options. On the other hand, this results in changed geometries and possible applications in cramped conditions. An orientation of the two hand lever in said half-plane can be arbitrary, with both hand lever or a hand lever can be oriented at an acute angle, a right angle or an obtuse angle to the longitudinal axis.

According to the invention, furthermore, in the force flow between hand levers and pressing jaws, a translatory loading is converted into a rotary application via a gear unit. (This transmission unit is also referred to below as "first transmission unit".)

While for the above-mentioned prior art, the hand lever are usually both pivotally mounted relative to a housing of the pressing tool, the invention proposes that a hand lever is movably arranged to the housing of the pressing tool, while the other hand lever is rigidly connected to the housing of the pressing tool. This may result in a simplified structure of the pressing tool, since two movable hand lever mandatory require a third part on which the movable hand lever are supported, while for a rigid hand lever this already can serve for storage of the movable hand lever. Alternatively or additionally, a rigid hand lever simplify the usability of the pressing tool, since with the rigid hand lever a fixation point fixed with respect to the housing is given with a possibly not varying position and orientation to the connecting element and any other parts arranged in the connecting element such as the conductor or a pipe.

In a further embodiment of the pressing tool according to the invention this has, in a first approximation, an outer shape of a "gun", which can already ensure an attractive design. In this case, the pressing jaws are arranged in the region of an "orifice" of the "gun", wherein the receptacle formed by the pressing jaws for the connecting element is oriented in the direction of the "mouth". For the arrangement of the pressing jaws in the area of the "mouth", an intuitive user guidance also results for a first-time use of the pistol-type pressing tool, since the user will intuitively introduce the connecting element into the "mouth" when aligned with it. Furthermore, for this embodiment, the hand lever rigidly connected to the housing is designed as a handle of the "pistol", while the hand lever movably connected to the housing forms a "trigger" of the "pistol", this "trigger" being quite slight or substantial with respect to a trigger a conventional gun can be extended. It is understood that such a hand lever as a kind of "trigger" can be pivoted or translationally movable.

Another aspect of the invention pays special attention to the shaping and force generation in the area of the pressing jaws. Here, the invention has recognized that it can be disadvantageous if a shaping takes place only with two pressing jaws, since this can lead to an uneven force development and / or shaping. In particular, in the event that a pressing with a cross-sectional contour is to take place with more than four corners or with complex outer geometry, a pressing with only two pressing jaws has proved to be disadvantageous. While for the known from the prior art pressing tongs according to variant b) was only intended to actuate two pressing jaws and / or actuation of more than two pressing jaws was not possible due to the transmission mechanism used, the invention proposes at least three pressing jaws , in particular four press jaws to provide, which can each move with an actuation of the hand lever radially inwardly on the longitudinal axis of the connecting element. Here you can the at least three press jaws have separate or coupled by the transmission mechanism degrees of freedom.

Further aspects of the invention are devoted to the transmission mechanism used between the hand levers and the pressing jaws:

For a first proposal, in the force flow between the hand levers and pressing jaws, a pivoting action is converted into a translatory loading via a further gear unit (hereinafter also referred to as "second gear unit"). For example, the pivoting action on a relative pivoting of the two hand lever can be brought about or exist directly in this. The second gear unit serves at least the purpose of converting the pivoting loading into a translatory loading. As a further alternative or cumulative effect of such a transmission unit, this can bring about a conversion of the direction of action of the application, whereby arbitrary orientations of the pivot axis of the pivoting action in the direction of action of the translatory loading by the gear unit can be made possible constructively.

For a particular embodiment of the invention, the second gear unit for converting the pivoting loading is formed in a translatory loading with a pivotable cam which is coupled, for example, in accordance with the movement of the lever pivot or rigid or rotationally fixed with fixed translation with a hand lever. At the pivotable cam is a translationally guided cam follower, in particular under the action of a spring, so that the cam follower can perform a translational movement, which is dependent on the pivoting of the cam. In this case, a relationship between the translational movement and the pivoting over the contour of the cam can be specified constructively, so that any desired linear or non-linear dependence can be achieved. On the other hand, via the contour of the cam, namely the distance of the contour from the pivot axis of the cam, the lever arm can be specified, with which an acting on the cam actuating torque is transmitted as an axial force on the cam follower.

Alternatively or cumulatively, for a further proposal of the invention, a transmission mechanism may comprise a first transmission unit via which a return of the translational movement of the cam follower or an element coupled thereto in a pivoting movement, wherein the pivot axis of this pivoting movement may deviate from the pivot axis of the cam, for example, may be rotated by 90 °. Preferably, the rotary application generated by the gear unit is an application about a pivot axis, which is oriented coaxially with the longitudinal axis of the connecting element.

In one embodiment of the pressing tool according to the invention, the first gear unit is formed with a rotatably mounted drive element. The drive element has a guide groove, which is inclined at least in regions relative to the longitudinal axis. The translatory loading is coupled with a translationally movable driver. The driver is, for example, with a pin thereof, slidably supported in the guide groove of the drive member to the guide groove. With a first gear unit formed in this way, a translational displacement of the driver on the one hand leads to a displacement of the driver along the guide groove. Due to the inclination of the guide groove relative to the longitudinal axis, this displacement also leads to a rotation of the drive element. The relationship between the translational displacement of the driver and the rotational movement of the drive element may be structurally determined by the contour of the guide groove, in particular its inclination relative to the longitudinal axis. If the guide groove has subregions in which it is oriented parallel to the longitudinal axis, the movement of the driver does not lead to any rotation of the drive element. As the inclination of the guide groove with respect to the longitudinal axis increases, the "transmission ratio" of the translational movement to the rotational movement can be increased. The guide groove can be designed arbitrarily, in particular at least in a partial area with or without play between the driver and guide, at least partially straight guide groove or arbitrarily curved guide.

For a further alternative or cumulative proposal, an inventive pressing tool in the power transmission mechanism has an additional gear unit (hereinafter "third gear unit") in the power flow between the hand levers and the pressing jaws a rotational loading, for example, the aforementioned drive element, in a radially inward direction converted oriented application of the pressing jaws.

A possible embodiment of such a third gear unit supports the pressing jaws in each case with respect to a housing-fixed pivot axis, which is oriented parallel to the longitudinal axis. The control of the pivoting of the pressing jaws about the pivot axis takes place in that a coupling between the drive element and the pressing jaws is provided eccentrically to the pivot axis, so that the rotational loading and movement of the drive element causes a movement of the pressing jaws results around the pivot axis ,

• eine Über- oder Untersetzung einer Antriebsbewegung und einer Antriebskraft bzw. eines Antriebsmomentes,
• eine Übertragung der Antriebsbewegung und einer Antriebskraft bzw. eines Antriebsmomentes von einem Ort zu einem anderen,
• eine Verlagerung von Übertragung der Antriebsbewegung und einer Antriebskraft bzw. eines Antriebsmomentes von einer Wirkrichtung zu einer anderen,

erfüllt. Während hierfür grundsätzlich sämtliche an sich bekannte Getriebeeinheiten im Rahmen der Erfindung einsetzbar sind, wird beispielhaft auf Ausgestaltungen der Getriebeeinheit als Getriebeeinheit mit

• mindestens einer kämmenden Zahnradstufe mit einer Stirnradverzahnung oder Kegelrädern,
• einem Spindeltrieb oder Schraubengetriebe,
• einem Planetengetriebe,
• einem Kurvengetriebe und/oder
• einem Vier- oder Mehrgelenktrieb oder Schubgelenkgetriebe

angesprochen. Vorteilhaft ist es, wenn über die Getriebeeinheit eine Übersetzung erfolgt, über die von der Hand des Benutzers aufgebrachte Kräfte bzw. Momente vergrößert werden können. Vorzugsweise finden die drei angesprochenen Vorschläge kumulativ mit beliebiger Hintereinanderschaltung der ersten, zweiten und dritten Getriebeeinheit Einsatz.A "transmission unit" in the sense of the present invention for the different embodiments explained above is understood to mean any unit which fulfills the purposes explained above, in particular

• an over or a reduction of a drive movement and a drive force or a drive torque,
• a transmission of the drive movement and a drive force or a drive torque from one location to another,
• a displacement of transmission of the drive movement and a drive force or a drive torque from one effective direction to another,

Fulfills. While this basically all known per se gear units are used in the invention, is exemplary of embodiments of the transmission unit as a transmission unit with

• at least one intermeshing gear stage with a spur gear or bevel gears,
• a spindle drive or screw gear,
• a planetary gear,
• a cam mechanism and / or
• a four- or multi-link drive or sliding joint transmission

addressed. It is advantageous if a translation takes place via the gear unit, via which forces or torques applied by the user's hand can be increased. Preferably, the three proposals mentioned cumulatively with any series connection of the first, second and third gear unit use.

A particularly compact, yet efficient embodiment results when the pressing jaws are rotatably mounted relative to a housing-fixed, the pivot axes predetermining sleeve. The sleeve has in this case the guide groove. The guide groove is inclined at least in a partial area in a projection in a longitudinal plane both with respect to the longitudinal axis and with respect to the circumferential direction of the sleeve. The drive element is arranged radially inward of the sleeve and pivotable here. The driver is formed in this case as radially outwardly oriented pin and extends in the guide. As a result of this "nested" training results in a particularly compact, but efficient transmission unit.

According to another proposal for a pressing tool, a spring element is interposed in the power flow between the hand lever and the pressing jaws. This spring element serves to influence the characteristics of the movement and force transmission and pressing jaws.

With the application of the hand lever can act on the return spring, which is supported with a spring base relative to the housing and with another spring base against a moving in the course of the application device. About such a return spring, a reset of the pressing tongs can be done after completion of a Teilpresshubs or completion of the entire pressing process, so that the hand lever and the pressing jaws need not be returned (alone) by mechanical actuation back to the starting position.

For a further proposal according to the invention a Zwangsgesperre is integrated in the pressing tool. Such Zwangsgesperre has distributed over the pressing stroke securing positions, locking or locking positions, which secure a once achieved pressing step with a reduction in the force applied to the lever operating force.

Advantageous developments of the invention will become apparent from the claims, the description and the drawings. The advantages mentioned in the introduction Features and combinations of several features are merely exemplary and may be effective alternatively or cumulatively, without the advantages of compelling embodiments of the invention must be achieved. Further features are the drawings - in particular the illustrated geometries and the relative dimensions of several components to each other and their relative arrangement and operative connection - refer. 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.

BRIEF DESCRIPTION OF THE FIGURES

Fig. 1

zeigt ein erfindungsgemäßes Presswerkzeug in einer Seitenansicht.

Fig. 2

zeigt das Presswerkzeug gemäß Fig. 1 in einem Längsschnitt in einer Ausgangsstellung mit geöffneten Handhebeln und geöffneten Pressbacken.

Fig. 3

zeigt das Presswerkzeug gemäß Fig. 1 und 2 in räumlicher Darstellung und teilweise demontiertem Zustand.

Fig.4

zeigt das Presswerkzeug gemäß Fig. 1 bis 3 in räumlicher Darstellung und teilweise demontiertem Zustand.

Fig. 5

zeigt das Presswerkzeug gemäß Fig. 1 bis 4 in räumlicher Darstellung und teilweise demontiertem Zustand.

Fig. 6

zeigt den Übertragungsmechanismus des Presswerkzeugs gemäß den Fig. 1 bis 5 in räumlicher Darstellung.

Fig. 7

zeigt das Presswerkzeug gem. den Fig. 1 bis 6 in einer Explosionsdarstellung.

Fig. 8

zeigt eine Hülse, welche Einsatz findet in einem Presswerkzeug gemäß Fig. 1 bis 7, in räumlicher Darstellung.

Fig.9

zeigt ein Antriebselement, welches Einsatz findet in einem Presswerkzeug gemäß Fig. 1 bis 7, in räumlicher Darstellung.

Fig. 10

zeigt zwei von vier Pressbacken für ein Presswerkzeug gemäß Fig. 1 bis 7 in räumlicher Darstellung.

Fig. 11

zeigt einen Schnitt XI-XI durch das Presswerkzeug gemäß Fig. 2.

Fig. 12

zeigt einen Schnitt XII-XII durch das Presswerkzeug gemäß Fig. 2.

Fig. 13

zeigt einen Schnitt XIII-XIII durch das Presswerkzeug gemäß Fig. 2.

Fig. 14

zeigt das Presswerkzeug gemäß Fig. 1 in einem Längsschnitt in einer Ausgangsstellung mit teilweise geschlossenen Handhebeln und Pressbacken.

Fig. 15

zeigt das Presswerkzeug gemäß Fig. 1 in einem Längsschnitt in einer Ausgangsstellung mit geschlossenen Handhebeln und Pressbacken.

Fig. 16

zeigt ein schematisches Blockschaltbild für den Übertragungsmechanismus für die Bewegung und die Beaufschlagung zwischen den Handhebeln und den Pressbacken mit mehreren zwischengeschalteten Getriebeeinheiten.

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

Fig. 1

shows a pressing tool according to the invention in a side view.

Fig. 2

shows the pressing tool according to Fig. 1 in a longitudinal section in a starting position with open hand levers and open pressing jaws.

Fig. 3

shows the pressing tool according to Fig. 1 and 2 in spatial representation and partially disassembled state.

Figure 4

shows the pressing tool according to Fig. 1 to 3 in spatial representation and partially disassembled state.

Fig. 5

shows the pressing tool according to Fig. 1 to 4 in spatial representation and partially disassembled state.

Fig. 6

shows the transmission mechanism of the pressing tool according to the Fig. 1 to 5 in spatial representation.

Fig. 7

shows the crimping tool acc. the Fig. 1 to 6 in an exploded view.

Fig. 8

shows a sleeve, which finds use in a pressing tool according to Fig. 1 to 7 , in spatial representation.

Figure 9

shows a drive element, which insert is used in a pressing tool according to Fig. 1 to 7 , in spatial representation.

Fig. 10

shows two of four pressing jaws for a pressing tool according to Fig. 1 to 7 in spatial representation.

Fig. 11

shows a section XI-XI by the pressing tool according to Fig. 2 ,

Fig. 12

shows a section XII-XII through the pressing tool according to Fig. 2 ,

Fig. 13

shows a section XIII-XIII by the pressing tool according to Fig. 2 ,

Fig. 14

shows the pressing tool according to Fig. 1 in a longitudinal section in a starting position with partially closed hand levers and pressing jaws.

Fig. 15

shows the pressing tool according to Fig. 1 in a longitudinal section in a starting position with closed hand levers and pressing jaws.

Fig. 16

shows a schematic block diagram of the transmission mechanism for the movement and the application between the hand levers and the pressing jaws with a plurality of intermediate gear units.

DESCRIPTION OF THE FIGURES

Fig. 1 to 15 show a pressing tool 1, which is designed as pressing tongs 2, or parts thereof. In the pressing tongs 2 via a transmission mechanism 7 is a transfer of an applied hand lever 3, 4 actuating force on pressing jaws 5. The hand lever 3 is movably mounted relative to a housing 6 of the pressing tongs 2, while the hand lever 4 is rigidly coupled to the housing 6 or part of it is. The hand lever 3, 4 can be enclosed by a user's hand. The hand lever 3 is pivotally mounted relative to the hand lever 4 and the housing 6 about a housing-fixed pivot axis 8, which is vertical to the plane according to Fig. 2 is oriented. For the illustrated embodiment, the pivot axis 8 is predetermined by a bearing pin 9, which passes through the hand lever and is rotatably supported on both sides of the hand lever 3 in aligned bores of the housing 6. On the side facing away from the hand lever 3 side of the pivot axis 8 and the bearing pin 9, a lever, extension or cam 10 is arranged, which is rigidly connected to the hand lever 3. Preferably, hand lever 3, bearing pin 9 and cam 10 are integrally formed with each other as an actuating element eleventh

The cam 10 spaced from the pivot axis 8 an actuating contact 12 with a cam follower 13, which is translationally displaceable in the direction of a longitudinal axis 14-14. The circular disc-shaped cam follower 13 for the illustrated embodiment is penetrated centrally without coupling in the direction of the longitudinal axis of a rod 16 which has a circular cross-section and is guided in the end facing away from the pressing jaws 5 in a bore 17 of the housing 6. The hand lever 3 has an angled in the direction of the pivot axis 8 or cranked area. This angled portion forms a right angle approximately to a main extension plane of the cam 10. The longitudinal axis of the hand lever 3 extends, at least in the in Fig. 2 The ratio of the length of the hand lever 3 to the pivot axis 8 to the distance of the actuating contact 12 from the pivot axis 8 is approximately 3 to 9, preferably 4 to 8 and in particular 5 to 6th

For the illustrated embodiment, the cam follower 13 is formed as an annular disc with a central through hole through which the cam follower 13 is slidably guided against a bore passing through the rod 16. Of the cam follower 13 of the power flow runs in the direction of the longitudinal axis 14-14 via a spring element 15 which is formed for the illustrated embodiment as a sleeve 18 made of an elastic material, preferably PE. The sleeve has an internal bore through which the rod 16 is passed under a clearance to permit displacement in the direction of the longitudinal axis 14-14. The spring element 15 is supported on the spring base point opposite the cam follower 13 on a support disk 19 which also has a spring base has central bore through which, while allowing a radial guidance, but a translational movement along the longitudinal axis 14-14, the rod 16 is passed.

From the support disk 19, the power flow is divided into at least one, here four, distributed in the circumferential direction return springs 20, of which one Federfußpunkt is supported on the support plate 19, while the other Federfußpunkt is fixed in the axial direction directly or indirectly relative to the housing 6 , Parallel to the return spring 20, the power flow extends over a driver 21, whose one end region in a blind hole receives the end region of the rod 16 while ensuring a translational degree of freedom and which is supported with an annular end face on the support disk 19. The driver 21 is translationally displaceable in the direction of the longitudinal axis 14-14, wherein this is prevented from rotating about the longitudinal axis 14-14. This can be ensured by a suitable guide between the driver 21 and the housing 6. Alternatively or cumulatively, the connection between the driver 21 to an adjacent component, in this case the support disk 19 and / or the rod 16, rotatably formed and this adjacent component rotatably about the longitudinal axis 14-14 relative to the housing 6 to be performed.

The driver 21 has in the Abstützscheibe 19 opposite end portion two transversely to the longitudinal axis 14-14 on the circumference of oppositely extending pins 22 which are moved translationally with the driver 21 in the direction of the longitudinal axis 14-14.

An in Fig. 9 as a single part spatially illustrated drive element 23 is cylindrical and has on the side facing away from the pressing jaws 5 a blind hole 55. In the area of the blind hole 55 an edge-closed guide groove 24 is introduced into the drive element 23. The guide groove 24 is formed in development of the lateral surface of the drive element 23 in a straight line, but inclined both with respect to the longitudinal axis 14-14 and with respect to the circumferential direction. The pins 22 of the associated end portion of the driver 21 extends into the blind hole of the drive member 23, wherein the pins 22 extend in the radial direction in the guide groove 24. To enable an assembly of driver 21 and drive member 23, the pins 22 can be connected to the driver 21 when it is inserted into the blind hole of the drive member 23. For example, the driver 21 may have a transverse bore into which the pins 22 or inserting a continuous pin under a transition fit or interference fit.

In the press jaws 5 facing end portion of the drive element 23 four coupling grooves 25 are frontally introduced, which are distributed uniformly over the circumference and extending from the longitudinal axis in the radial direction. The coupling grooves 25 are closed at the edge and have a groove bottom. Since the drive element 23 is fixed in the direction of the longitudinal axis 14-14, a movement of the driver along the longitudinal axis 14-14 causes the pins 22 to move in the guide groove 24, these forces acting transversely to the guide groove 24, via the one Twisting of the drive element 23 is effected.

The drive member 23 is under axial fixation, but allowing rotation about the longitudinal axis 14-14 in a Fig. 8 stored as a single item spatially illustrated sleeve 26. The sleeve is in a first approximation hollow cylinder-shaped with an annular inner collar 27 on which the drive element 23 rests in the direction of the pressing jaws 5 and is supported. On the side facing away from the pressing jaws 5 of the collar 27, the sleeve 26 has a support groove 28 which is oriented parallel to the longitudinal axis 14-14 and which is continuous, that is formed without a reason. The pins 22 extend radially outward from the drive element 23 into the support groove 28. The sleeve 26 is firmly supported relative to the housing 6. Thus, the support groove 28 ensures that the pins 22 and the driver 21 are guided in the direction of the longitudinal axis 14-14 without permitting a rotation about the longitudinal axis 14-14.

In the press jaws 5 end region facing the sleeve 26 has four end-side, uniformly distributed over the circumference bearing bores 29, which are partially formed by the collar 27 for the illustrated embodiment. Fig. 10 shows by reversing the line of sight towards the 8 and 9 two press jaws 5. The press jaws have 2 parallel to the longitudinal axis 14-14 extending cylindrical extensions 30, 31. The radially outwardly arranged extension 30 can be inserted into a bore 29 and secured in this via a fuse element such that a displacement of the Pressing jaw 5 in the direction of the longitudinal axis 14-14 is no longer possible, but a pivoting about a predetermined by the bearing bore 29 and the longitudinal axis of the extension 30 pivot axis 32 is possible. For the illustrated embodiment, the extensions 30 have a circumferential groove 33, in which inserted into the sleeve 26 state of the extension 30th a slot 34 of the sleeve 26 opens, in which a kind of locking plate, a locking pin or a U-shaped locking ring can be inserted so that this creates a positive connection in the direction of the longitudinal axis 14-14 connection between sleeve 26 and extension 30.

The position of the pressing jaw 5 is determined as a result of the housing-fixed sleeve 26 and for non-twisted drive element 23, since due to the connection of the extension 30 with the sleeve 26 only one pivoting degree of freedom remains about the pivot axis 32-32 and this pivoting degree of freedom is determined by the fact that the extension 31 comes to rest against the boundary of the support groove 28. By contrast, the rotation of the drive element 23 about the longitudinal axis 14-14 causes the coupling groove 25 entrains the extension 31, whereby a pivoting of the pressing jaw 5 about the pivot axis 32-32 goes along. Here, the dependence of the pivot angle of the pressing jaw 5 about the pivot axis 32 of the pivot angle of the drive element 23 by the geometric conditions, here the distances from the longitudinal axis 14-14, a longitudinal axis 54-54 of the extension 31 and the pivot axis 32, dependent. Since the distance between the longitudinal axis 54-54 of the extension 31 changes from the longitudinal axis 14-14 via the pivoting of the pressing jaw 5, the coupling groove 25 is not formed as a bore, but as an elongated groove.

The pressing jaws 5 each have pressing surfaces 35, which are formed by a plurality of pressure discs 36. The pressing discs 36 forming the pressing surface 35 are spaced from each other by a distance slightly larger than the thickness of the pressing discs 36. Thus, the pressing surface 35 is formed with individual broken bands. For adjacent press jaws 5, the press disks 36 are each offset in such a way that the press disks 35 of a press jaw 5 can enter the gaps between press disks 36 of an adjacent press jaw 5. This has the consequence that the pressure plates 36 of the adjacent pressing jaws can overlap each other, wherein the extent of the overlap depends on the pivoting of the pressing jaws 5 about the pivot axis 32-32. With a change in the overlap, the size of the pressing surface 35 and thus the contour of the compressed between the pressing jaws 5 connecting element and the cross-sectional area of the same changes.

The rod 16 is mounted in the end facing away from the pressing jaws 5 directly in the holes 17 of the housing 6. In the press jaws 5 facing end region, the rod 16 is indirectly supported radially relative to the housing 6, in particular below in the direction of the longitudinal axis 14-14, the rod 16 may be floatingly mounted or with one of the translationally in the direction of the longitudinal axis 14-14 moving components be coupled.

For the illustrated embodiment, the force flow in the pressing tongs 2 is as follows:

With an application of a force on the hand lever 3, 4, which is oriented towards a pivoting of the hand lever 3, 4 toward each other and on a pivoting of the hand lever 3 in Fig. 2 counterclockwise, there is a pivoting of the hand lever 3 about the pivot axis 8. This has the consequence that the cam 10 counterclockwise in Fig. 2 is pivoted, so that the actuating contact 12 is displaced in the direction of the longitudinal axis 14-14 and in the direction of the pressing jaws 5. The force generated in the region of the hand lever 3, 4 is translated according to the geometric conditions, ie the distance of the application of the force from the pivot axis and the distance of the actuating contact 12 from the pivot axis 8. The force acting in the actuating contact 12 force is transmitted via the spring element 15th transferred from the driver 21, the translational movement along the longitudinal axis 14-14 in a rotational movement of the drive member 23 by the coupling between the pins 22 described above Finally, the rotation of the drive element 23 due to the coupling of the coupling grooves 25 with the projections 31 to a pivoting of the pressing jaws 5 such that the pressing surfaces 35 in the direction of the longitudinal axis 14-14 move and a pressing force is generated in this direction. A translation of the pivoting of the drive element 23 to the pivoting of the pressing jaws 5 and ultimately the radial contact pressure of the pressing surfaces 35 results from the distances between the longitudinal axis 14-14, the longitudinal axis 54-54 of the extensions 31 and the pivot axes 32-32.

For the illustrated embodiment, further optional supplements are provided:

Finding a spring element 15 with a large, theoretically infinite stiffness use, this has the consequence that a fixed functional dependence between a pivoting of the hand lever 3 about the pivot axis 8 to the pivot angle of the pressing jaws 5 to the Swivel axis 32-32 can be specified. If, on the other hand, the spring element 15 has a disappearing stiffness in the other theoretical extreme case, the hand lever 3 can be pivoted without this resulting in the pivoting of the pressing jaws 5 and the generation of a radial pressing of the pressing jaws 5 on a connecting element. Depending on the action in the transmission mechanism 7, that is to say the pressing force in the region of the pressing jaws 5, stiffnesses between said extreme values result in different deformations of the spring element 15, which results in a change in the distance between the support disk 19 and the cam follower 13. Thus, the specification of the rigidity of the spring element 15, the operating characteristic of the pressing tongs 2 can be specified. In this case, a spring with an arbitrary characteristic, for example with a constant or dependent on the force or deformation spring constant can be used for the spring element 15. On the other hand, on the outer contour of the cam 10, the shape of the guide groove 24 and / or the coupling groove 25 also influence the operating characteristics, in particular a gear ratio between a force applied to the hand lever force and the force generated on the pressing jaws influence.

The guide rod 16 essentially serves to guide the elements which are displaceable relative to the latter. Of course, another guidance of the elements switched on in the transmission mechanism 7 can also take place. It is also conceivable that the rod 16 is rigidly coupled to the cam follower 13 and the end face acts directly on the drive member 13 or forms this. In this case, spring element 15 or sleeve 18 and support disk 19 are dispensable.

The return spring 20 is increasingly applied in the course of the closure of the hand lever 3, 4. If the pressing process is completed and the loading of the hand lever 3, 4 is eliminated, takes place via the return spring (s) 20, a return of the transmission mechanism 7 in the in Fig. 2 sketched position.

From the in Fig. 13 illustrated cross-section can be seen that for the illustrated embodiment, the cam 10 is formed with two parallel and rigidly coupled together cam plates 37, 38, which both abut the cam follower 13. By the intermediate space formed between the cams 37, 38, the rod 16 extends.

As a further optional detail, the pressing tongs 2 have a positive locking mechanism 39. For this purpose, the actuating element 11 preferably has a toothed segment 40 arranged concentrically to the pivot axis 8, adjacent to the pivot axis 8. A blocking element 41, which is acted upon by a spring 42, engages in this. The contact contours between the payment segment 40 and the blocking element 41 are such that, starting from the starting position of the pressing tongs 2 with increasing compression, the blocking element 41 can travel from tooth to tooth along the toothed segment 40, while the hand lever 3, 4 is blocked by the blocking element 41 , If the hand lever 3, 4 in its full closed position, the locking element 41 has left the toothed outer contour of the toothed segment 40 and pivots so that another contact surface of the locking member 41 engages the toothed segment 40 in operative connection, which allows a pivoting apart of the hand lever 3, 4 , For completely apart moving hand lever 3, 4 leaves the locking element 41 again the toothed outer contour of the toothed element 40, flips over, so that the locking element can be effective again as Zwangsgesperre 39. The Zwangsgesperre 39 serves to secure a once achieved by applying forces to the hand lever 3, 4 pressing position of the pressing jaws.

For the illustrated embodiment, the crimping tool 2 is formed to a first approximation in the manner of a pistol whose handle is formed with the hand lever 4, while the barrel of the pistol substantially includes the transmission mechanism 7. Handle and barrel of the pistol are formed approximately the same length. However, depending on the desired geometries of the pressing tongs, the "barrel" of the "gun" can be extended or shortened as required without necessarily requiring an altered transmission mechanism 7. The movable hand lever 3 is formed by the trigger of the pistol, the hand lever 3 being approximately as long as the hand lever 4. The hand lever 4 and the barrel essentially comprising the transmission mechanism 7 form an angle of approximately 90 to 130 °, in particular 100 to 120 °, while the hand lever 3, 4 in the in Fig. 1 illustrated starting position form an angle of 45 to 75 °, preferably 50 to 70 °. The bisecting central axis 52-52 between the hand levers 3, 4 is oriented approximately transversely to the longitudinal axis 14-14.

The housing 6 is formed for example as a hollow housing with a relatively small wall thickness and can be made as an injection molded part and, for example, made of metal or plastic. It is possible that the housing 6 as a split housing with a division plane parallel to the plane according to Fig. 1 is formed with two half-shells. For the illustrated embodiment, the housing 6, however, formed in the front region of the housing with a sleeve 43 which is formed substantially hollow cylindrical and in the region of the pressing jaws has a taper with an end opening 44, which forms a kind of "mouth" of the gun and through in that the connecting element can be inserted into the receptacle 45 of the crimping pliers which is limited by the pressing surfaces 35. By contrast, a rear part of the housing 6 is formed in a half-shell technique with a plane of separation of the half-shells parallel to the plane of the drawing FIG. 1 , wherein by means of production of the half shells in an injection molding process, a bore 17 for receiving the rod 16 and holes for the bearing pin can be formed already in the half shells. For the illustrated embodiment, the half shells in the region of the dividing plane of the hand lever 4 form an elongated opening into which the hand lever 3 can enter at the end of the pressing process.

16 shows a schematic representation of the transmission mechanism 7 of a pressing tongs according to the invention:

An actuating unit 46 initially generates an actuating force and / or actuating movement. This is fed to a gear unit 47 ("second gear unit"). For the illustrated embodiment of the pressing tongs 2, the gear unit 47 is formed with the actuating element 11, the cam 10 and the cam follower 13 and converts a relative movement of the hand lever 3, 4, here a pivoting of the hand lever 3, relative to the housing 6, in a translational movement , here of the cam follower 13 along the longitudinal axis 14-14 to. Without or with the interposition of a spring element 15, the output side converted actuating force and actuating movement of a transmission unit 48 ("first gear unit") is supplied. For the illustrated embodiment of the pressing tongs 2 is in the transmission unit 48 to the connection between driver 21 and drive element 23. The gear unit 48 converts a translational movement, here the movement of the driver 21 along the longitudinal axis 14-14, in a rotational movement, here of the drive member 23 about the longitudinal axis 14-14, to. The output side, once again converted actuating force and actuating movement of the transmission unit 48 is a further transmission unit 49 ("third gear unit") supplied. For the illustrated embodiment, the gear unit 49 is formed with the coupling of the drive element 23 with the pivotable pressing jaws 5. The gear unit 49 converts a rotational movement, here the movement of the drive member 23 to a radial movement of the Pressing jaws 5 in the direction of the longitudinal axis 14-14, which is ensured for the illustrated embodiment by the pivoting of the pressing jaws 5 about the pivot axes 32.

Finally, the pressing jaws act in the receptacle 45 for pressing on the lateral surface of the connecting element. The longitudinal axis of the receptacle 45 for the connecting element is oriented coaxially to the longitudinal axis 14-14 for the entire pressing movement. The connecting element is inserted in the direction of the longitudinal axis 14-14 in the receptacle 45 and removed therefrom after completion of the pressing operation.

In Fig. 2 the plane of the drawing forms a plane 50 in which the longitudinal axis 14-14 and the hand lever 3, 4 or their center axis 52-52 lie. The longitudinal axis 14-14 divides the plane 50 into an in Fig. 2 upper half-plane 53 and a lower half-plane 51. For the illustrated embodiment, both hand lever 3, 4 are arranged in the lower half-plane 51. Of course, the hand lever can also be arranged in any orientation, in deviation from the illustrated embodiment, in the half-plane 51, also with any opening angles. Preferably, the central axis 52-52 of the hand lever 3, 4 is oriented perpendicular to the longitudinal axis 14-14 in the half-plane 51. Also included in the subject matter of the application are embodiments in which, for example, a single cam disc is offset axially relative to the plane in which the hand levers are moved, acts on the cam follower and the longitudinal axis 14-14 and further components up to the receptacle 45 accordingly relative to the plane in which the hand lever are moved, is offset.

The housing 6 forms an interior 56, in which essential parts of the transmission mechanism 7 are arranged, in particular the pivot axis 8 and the bearing pin 9, the cam 10, the cam follower 13, the sleeve 18, the rod 16, the support disk 19, the driver 21st , the pins 22, the drive member 23, the sleeve 26 and the pressing jaws 5. Thus, the gear units 47-49 are arranged inside the housing. Only the hand lever 3 protrudes, at least in partial areas of its pivoting path, out of the housing 6.

It is also possible that the pressing tool is equipped with a set of interchangeable heads over which different pressing jaws 5, a different number of pressing jaws, different pressing cross sections and different pressing cross section sizes can be used. Different heads or components of the pressing tongs can be replaced be maintained while retaining other parts of the transmission mechanism, the housing, the hand lever and the like, so that such a set is compact and cost-effective for different applications suitable.

It is understood that deviating from the illustrated embodiment, a translational relative movement of the lever 3,4 can be generated and transmitted to the pressing jaws 5 via a transmission mechanism.

It is also possible that the hand lever 3, 4 are arranged only in a partial stroke both in a common half-plane 51, while moved for another partial stroke, a hand lever from said half-plane 51.

LIST OF REFERENCE NUMBERS

1

press tool

2

crimping pliers

3

Hand lever (movable)

4

Hand lever (rigid)

5

pressing jaw

6

casing

7

transmission mechanism

8th

swivel axis

9

bearing bolt

10

cam

11

actuator

12

operation Contact

13

cam follower

14

longitudinal axis

15

spring element

16

pole

17

drilling

18

shell

19

support disk

20

Return spring

21

takeaway

22

pen

23

driving element

24

guide

25

coupling groove

26

shell

27

Federation

28

Abstütznut

29

bearing bore

30

extension

31

extension

32

swivel axis

33

circumferential groove

34

slot

35

Press area

36

dummy block

37

cam

38

cam

39

Zwangsgesperre

40

toothed segment

41

blocking element

42

feather

43

shell

44

opening

45

admission

46

operating unit

47

gear unit

48

gear unit

49

gear unit

50

level

51

half-plane

52

central axis

53

half-plane

54

coupling axis

55

Proper hole

56

inner space

Claims (13)

Pressing tool (1) for pressing fasteners such. As cable end sleeves, circular connectors, cable lugs or contact sockets on electrical conductors or for thin-walled pipe connections, a) with pressing jaws (5), which are moved toward one another for the application of pressing forces acting radially to a longitudinal axis (14-14) of the connecting element in the radial direction, wherein b) the pressing forces and the movement of the pressing jaws (5) are caused by manual operation of hand levers (3, 4), c) the hand levers (3, 4) are arranged in a plane (50) in which lies the longitudinal axis (14-14) of the connecting element, d) the plane (50), in which the longitudinal axis (14-14) of the connecting element is located and in which the hand lever (3, 4) are arranged, divided by the Längsache (14-14) in two half-planes (51, 53) is and both hand lever (3, 4) in the same half-plane (51) are arranged, e) in the power flow between the hand levers (3, 4) and the pressing jaws (5) a translatory loading in the direction of the longitudinal axis (14-14) is converted by means of a gear unit (48) into a rotational loading about the longitudinal axis (14-14) , Press tool (1) according to claim 1, characterized in that a) a hand lever (3, 4) movable relative to a housing (6) of the pressing tool (1) is arranged and b) a hand lever (4) is rigidly connected to the housing (6) of the pressing tool (1). Press tool (1) according to claim 2, characterized in that the pressing tool has an outer shape, which corresponds to a first approximation of a "gun", wherein a) the pressing jaws (5) are arranged in the region of an "opening" of the "gun" and a receptacle (45) for the connecting element formed by the pressing jaws (5) is oriented in the direction of the "mouth", b) the rigidly connected to the housing (6) hand lever (4) forms the handle of the "gun" and c) the hand lever (3) movably connected to the housing (6) forms an elongated "trigger" of the "gun". Pressing tool (1) according to one of the preceding claims, characterized in that at least three pressing jaws (5), in particular four pressing jaws (5), are provided, which with an actuation of the hand lever (3, 4) in each case radially inwards on the longitudinal axis ( 14.14) of the connecting element to be acted upon. Pressing tool (1) according to one of the preceding claims, characterized in that in the power flow between the hand levers (3, 4) and the pressing jaws (5) a pivoting action on a transmission unit (47) is converted into a translatory loading. Pressing tool (1) according to claim 5, characterized in that the gear unit (47) with a pivotable cam (10), which is in particular pivoted with a hand lever (3), and a translationally guided cam follower (13) is formed. Pressing tool (1) according to claim 1, characterized in that the gear unit (48) is formed with a translationally movable driver (21) and a rotatably mounted drive element (23), which has a guide groove (24) inclined with respect to the longitudinal axis (14-14) ), wherein the driver (21) in the guide groove (24) of the drive element (23) is displaceably supported thereon. Pressing tool (1) according to one of the preceding claims, characterized in that in the power flow between the hand levers (3, 4) and the pressing jaws (5) a rotational loading, preferably of the drive element (23) according to claim 7, via a gear unit (49). is converted into a radially inwardly directed loading of the pressing jaws (5). Pressing tool (1) according to claim 8, characterized in that for a formation of the gear unit (49) a) the pressing jaws (5) in each case with respect to a housing-fixed, parallel to the longitudinal axis (14-14) oriented pivot axis (32) are rotatably mounted, and b) acting on the pivoting of the pressing jaws (5) about the pivot axis (32) via a coupling between the rotational loading of the drive element (23) and the pressing jaws (5) eccentrically to the pivot axis (32). Press tool (1) according to claim 9, characterized in that a) the pressing jaws (5) are rotatably mounted relative to a housing-fixed, the pivot axes (32) predetermining sleeve (26), b) the drive element (23) is pivotable radially inwards from the sleeve (26), c) the driver (21) is formed with a radially outwardly oriented pin which extends into the inclined guide groove (24), d) the drive element (23) is rotatably coupled in the region of a coupling axis (54) with a pressing jaw (5) and e) the radial distance of the coupling axis (54) from the pivot axis (32) or the longitudinal axis (14-14) is variable. Pressing tool (1) according to one of the preceding claims, characterized in that a spring element (15) is interposed in the force flow between the hand lever (3, 4) and pressing jaws (5). Pressing tool (1) according to one of the preceding claims, characterized in that the loading of the hand lever (3, 4) is accompanied by the application of a return spring (20), which a) with a spring base directly or indirectly relative to the housing (6) and b) with a different spring base relative to a component moved in the course of the application (support disk 19) is supported. Pressing tool (1) according to one of the preceding claims, characterized in that a Zwangsgesperre (39) is provided, via which with a reduction of the actuating force once reached a pressing stage can be ensured.

Images