Press pliers

Abstract

Crimping tool (1) in particular for crimping cable lugs or the like onto electrical conductors, with two crimping jaws (2, 3) pivotable relative to each other, wherein in each crimping jaw (2, 3) a crimping die (23, 24) rotatably mounted having several different crimping recesses (27, 28) extending over a circumference with respect to an axis of rotation (y), characterized in that a position corresponding to a working position of a crimping recess (27, 28) is secured by positive locking and that the crimping die (23, 24) is movable transversely to its axis of rotation (y) to release the positive locking position.

Description

[0001] The invention relates to a crimping tool, in particular for crimping cable lugs or the like onto electrical conductors, with two crimping jaws that can pivot relative to each other, wherein in each crimping jaw a crimping die is rotatably mounted, the latter having several different crimping recesses formed over a circumference with respect to an axis of rotation.

[0002] Crimping pliers of the type in question are known, both as hand-operated and motor-driven tools. These are used, for example, to attach cable lugs to electrical conductors. For this purpose, a workpiece, particularly a tubular one, is pressed between the two crimping jaws, which have, for example, hexagonal crimping recesses in the crimping dies. A different crimping profile, i.e., a different opening cross-section of the crimping recesses of both crimping dies, is generally required for each cable cross-section. In known pliers, the crimping dies are adjusted accordingly by rotating them around their axis of rotation, whereby the crimping recesses of both dies must be aligned to ensure proper crimping of the workpiece.

[0003] Such a crimping tool is known, for example, from DE 19 628 752 B4. US 4 825 682 A discloses a crimping device designed as a stationary unit, in which one crimping die is movable relative to the other crimping die in a slide-like manner, and the movable crimping die can be actuated via a toggle lever. One of the crimping dies must be released for rotation by pulling out a retaining axle. The other crimping die must be retracted far enough to release the positive locking mechanism, allowing it to be rotated if necessary. US 2 838 970 A discloses a crimping tool in which a nut must be loosened to release a crimping die so that it can then be rotated. Afterward, it must be reinserted and the nut tightened again.From US patent 7,536,896 B1, a crimping tool is known in which adjusting wheels are provided for the crimping dies, which are arranged on the same axis of rotation as the crimping die and are directly connected to the crimping die. An adjusting wheel and the crimping die have the same axis of rotation.

[0004] Based on a prior art according to DE 19 628 752 B4, the invention aims to provide an advantageous embodiment of a crimping tool.

[0005] This problem is initially solved with regard to the subject matter of claim 1, wherein the focus is on the fact that a position corresponding to a working position of a press trough is secured by positive locking and that the press die is movable transversely to its axis of rotation in order to release the positive locking position.

[0006] In the solutions known from the prior art, the press dies are displaced along their axis of rotation to release the form-locking position, in order to then be able to bring another press trough into working position, in particular due to the rotational displacement capability of the press die that is then released.

[0007] The proposed solution involves a radial movement of the press die relative to the axis of rotation to release the positive locking position. This results in more convenient handling. The movement transverse to the axis of rotation to release the positive locking position can be accompanied by a rotational displacement of the press die to adjust the press cavity. The transverse displacement can be derived from the rotational displacement. The rotational displacement can force a transverse displacement of the press die.

[0008] To allow the press die to be moved laterally, a bolt or similar component that receives the axis of rotation and supports the press die can be guided in a slotted hole.

[0009] A pressing trough of the press die is preferably formed by tooth-like projections, which flank the pressing trough in the circumferential direction of the press die. Each projection can have an engagement surface on its outer side that can be brought into engagement with a positive locking element in a working position of the pressing trough. Viewed radially to an axis of rotation, the engagement surface with the positive locking surface forms an acute angle with respect to a straight line passing through or parallel to the axes of rotation of the opposing press dies. This acute angle can be, for example, 5 to 45 degrees, or, for example, 15 to 30 degrees.

[0010] The contact surface of the tooth-like projection preferably interacts with a correspondingly interlocking surface of the interlocking element that extends at the same acute angle. In the interlocking position, the interlocking surface and the contact surface can be in contact with each other, in particular, they can be in a flat, flush position.

[0011] The positive locking element with the positive locking surface is preferably fixed and therefore cannot be displaced on the press jaw associated with the press die.

[0012] The contact surface of a press trough that is engaged can belong to a press trough opposite the axis of rotation of the press die, which is in its working position. In this way, a quasi-rear positive locking support of the press die can be achieved in the area of ​​the positive locking elements.

[0013] In a press die that can be rotated for adjustment, several differently shaped press recesses are provided around the circumference, which are spaced apart from each other in the circumferential direction by tooth-like projections.

[0014] With respect to the aforementioned straight line, two opposing bearing surfaces can be provided. These bearing surfaces are preferably formed on the projections that circumferentially delimit the press trough, and the bearing surfaces can be arranged to repel each other with respect to the straight line.

[0015] In the case of the formation of two opposing impact surfaces, two positive locking surfaces cooperating with these impact surfaces are preferably also provided.

[0016] The acute angles of both impact surfaces and / or both positive locking surfaces can also be the same.

[0017] As a result of a preferential rotational action on the press die, the contact surface, which advances in the direction of rotation of the press die, slides on the associated positive locking surface of the positive locking element. This leads to a displacement of the press die in a direction transverse to its axis of rotation until the contact surface leaves the positive locking surface and the positive locking engagement is thereby at least temporarily released.

[0018] The form-fit surface on which the die-side bearing surface can slide can form a sliding surface, for example, in the form of a guide ramp, allowing the die to be brought into a stop-limited rotational end or form-fit position when rotated about its axis of rotation. Particularly in conjunction with a spring force acting on the die in its home position, this prevents any unintentional retention in the dead center position. Instead, the die projection slides down the sliding surface, which rises or falls relative to a top view, after which, particularly due to spring force, an automatic rotational shift into the form-fit position is achieved.

[0019] The sliding surface can have a curved edge profile when viewed from a top view. The curve is calculated from the friction parameters of the press die and the interlocking surfaces of the form-fitting element, thus preventing self-locking due to this friction pairing. The interacting surfaces of the press die and sliding surfaces meet at an angle (relative to a top view) that is preferably greater than 4 degrees.

[0020] Preferably, two opposing guide slopes are provided, which, with reference to a top view of the matrices and positive locking means, in which the matrix rotation axes are represented as points, form a roof-like course of the positive locking surface.

[0021] In particular, if both contact surfaces and positive locking surfaces have the same angles, the effect described above can be achieved in both directions of rotation of the press die. By changing the acute angle of one of the two contact surfaces and / or one of the two positive locking surfaces, especially towards a more acute angle, further down to a parallel alignment with the straight line, an adjustment direction of rotation for the press die can be specified.

[0022] A press die can only be moved out of its form-lock position against spring force. At least this spring force must be overcome to adjust the press die.

[0023] The spring force preferably acts transversely to the orientation of the axis of rotation of the press die on the press die or a bolt or the like guiding the press die. The spring acts in such a way that the press die is loaded directly or indirectly into the positive locking position.

[0024] The spring force and / or the acute angle in the area of ​​the impact surface and / or the form-fitting surface can be selected in such a way that direct manual adjustment of a press die is possible, i.e. in particular a translation-free rotational displacement of the press die by manual action on the press die or an adjusting element directly connected to the press die.

[0025] The spring force and / or the acute angle can also be selected such that only one gear adjustment is possible. With such a gear adjustment, a transmission is preferably provided so that even larger spring forces and / or frictional forces between the impact surface and the positive-locking surface can be overcome with normal hand force.

[0026] The problem mentioned at the outset is further solved in the subject matter of claim 6, wherein it is based on the fact that each press die is adjustable via an adjusting wheel coupled to it by means of a gear mechanism, wherein the adjusting wheel and the press die have different axes of rotation.

[0027] Each press die can be adjusted via an adjustment wheel coupled to it via a gear mechanism, whereby the adjustment wheel and the press die have different axes of rotation.

[0028] Each press die is adjustable via an associated adjustment wheel to reposition the press trough into the working position. This allows the user to operate the press die at a distance, particularly by hand. The adjustment wheel is geared to the press die. This may involve direct action of the adjustment wheel on the press die, or a reduction or gear ratio may be incorporated.

[0029] The adjusting wheel may have numerals, in particular numbers, to mark the press trough in its working position. The axes of rotation of the adjusting wheel and the press die preferably run parallel to each other, or in particular, parallel and offset from each other.

[0030] Each press jaw extends longitudinally from the hinge point where it connects to the associated handle to the free end corresponding to the press die. The axes of rotation of the press die and the adjusting wheel of a press jaw can be offset from each other in this longitudinal direction.

[0031] The adjusting wheel can act directly on the press die, for example, by designing the adjusting wheel and the press die, or by designing sections of them as friction wheels or gears. A gear-like coupling via a friction belt is also possible.

[0032] Preferably, the adjusting wheel acts on the press die via a gear wheel. The gear wheel is interposed in a gearbox-like manner. A reduction or reduction gear can also be achieved via this mechanism.

[0033] Furthermore, the press die can be rotatable about a fixed axis of rotation, i.e., in particular one that cannot be displaced transversely to the geometric transverse axis.

[0034] The problem mentioned at the outset is further solved in the subject matter of claim 10, wherein it is based on the fact that signs (45), in particular numbers, are provided which identify the different press troughs (27, 28) and that the signs (45) are placed on a part (33, 47) separate from the press die (23, 24), which is not subjected to any pressing force during pressing and consists of a material different from a material of the press die (23, 24).

[0035] The markings typically refer to the nominal diameters of the associated press dies. It is known to engrave these markings directly into the press dies, for example, in the area of ​​tooth-like projections flanking the press dies.

[0036] The conventional method of engraving characters into the heavy-duty press dies proves to be time-consuming. Often, these characters are engraved by hand. Arranging the characters on a separate part, independent of the die and not subjected to the pressing force during the pressing process, offers advantages, particularly in the choice of part material and the method of applying the characters. The part material can be of a lower grade than the press die. For example, the part can be made of standard steel, but also of materials such as aluminum, plastic, cardboard, or paper.

[0037] The symbols can be printed onto the separate part in the simplest way. Alternatively, the symbols can be applied, for example, as self-adhesive film.

[0038] The separate part can be permanently attached to the press die. For example, the separate part can be glued or screwed to the press die.

[0039] In one embodiment, the separate part can be arranged coaxially to the press die, for example in the case of a disc-like design of the separate part.

[0040] The separate part, bearing the markings associated with the press trough in its working position, may protrude visibly beyond a free edge of the corresponding press jaw. A window-like opening may also be provided, particularly in the area of ​​the press jaw, through which the marking is visible.

[0041] Furthermore, the separate part can be arranged around another axis of rotation, separate from the axis of rotation of the press die, and be connected to the press die via a gear mechanism. For example, the separate part can also be a handwheel for adjusting the press die.

[0042] When a permanent gear-like coupling is formed between the press dies (see also below), only one separate part with markings can be provided. Since the press dies are rotated synchronously into the working position, and thus the corresponding press troughs are always aligned with each other in the working position, only one marking indicator is necessary.

[0043] In addition to printing the markings onto the separate part, integral forming of the markings with the separate part is also possible, for example, by stamping them into a separate part made of a metal material or by manufacturing the separate part using a plastic injection molding process. In a preferred design of the separate part as a zinc die-cast part, the markings can be incorporated directly during the casting process.

[0044] The press die can also be secured in a pressing position by a positive-locking interaction with a spring. The determined or set press die position is therefore preferably secured by a positive lock. For this purpose, a spring can be provided which interacts indirectly or, preferably, directly with the press die. The projections extending radially to the axis of rotation of the press die form contact surfaces on their circumference, against which, in a preferred embodiment, the spring engages to create the positive-locking interaction. Rotation of the press die from the pressing position is only possible by overcoming the spring force. By overcoming the spring force, the spring, or a spring leg of the spring, is deflected, in particular by a projection of the press die.

[0045] The spring can be a wire spring, in particular a torsion spring. A leaf spring is preferred in this regard, which, in the pressing position, bears with a broad side against one or more projecting bearing surfaces of the press die.

[0046] In a further embodiment, the leaf spring can be supported on the axle of a gear wheel. The leaf spring can also be bent around this axle of the gear wheel to apply the spring force. This bending section of the leaf spring is located at least approximately in the middle of a longitudinal extension of the leaf spring. One free end of the leaf spring acts against the press die. The other free end of the leaf spring is preferably held in the area of ​​the associated press jaw.

[0047] In a crimping tool of the type described above, a gauge section may also be provided which is adapted to an outer contour of the crimping die in the area of ​​a crimping recess and allows the crimping tool to close only if the crimping die is arranged in the crimping tool with a crimping recess orientation suitable for crimping.

[0048] Due to a possible operating error when adjusting the press die to use a different press trough, the press die may not reach its final, possibly locking, position, but rather a slightly rotated position relative to it. This can lead to damage to the press die during subsequent pressing. The proposed solution counteracts such operating errors.

[0049] The gauge section is adapted to the outer contour of the press die(s) in the area of ​​interaction with the die(s), preferably outside the press recesses. If the press die is not correctly aligned, a circumferentially extending projection between two press recesses engages against a flank of the gauge section during the closing movement of the pliers, acting as a barrier and / or guide.

[0050] Thus, if the press die is not correctly aligned, a flank of the gauge section can obstruct the pivot path of a press die projection, preventing the pressing position from being reached in that press die position.

[0051] The flank of the gauge section can also be aligned in such a way that a forced control of the press die is achieved as the die projection runs along the flank, in order to at least shift a press trough adjacent to the projection into a working position.

[0052] The jig section can be designed as a plate section. Furthermore, the jig section can be triangular in a plan view in which the geometric axes of rotation of the press jaws are represented as points, with one apex of the triangle preferably contour-adapted to the outer contour facing the projections that one-sidedly delimit the press troughs of both press dies.

[0053] The material thickness viewed perpendicular to the surface area of ​​the plate part can correspond to the material thickness of a press die viewed in the same direction.

[0054] Furthermore, the teaching section preferably extends into a plane that simultaneously accommodates both press matrices.

[0055] Furthermore, the gauge section can be mounted on the pivot axes of the press jaws. The gauge section can thus be traversed by corresponding pivot pins. If the gauge section has a triangular plan view, these axes or pivot pins are preferably each assigned to a corner area.

[0056] It may be provided that the press die is constantly coupled by a gear, regardless of the pivoting position of the press jaws.

[0057] Due to the geared coupling of the press dies, the rotational adjustment of one press die to move a desired press trough into the working position automatically results in a corresponding adjustment of the other press die. The adjustment of both press dies is synchronous. The coupling mechanism is preferably designed such that when one press die is adjusted, the corresponding press troughs of both press dies always move into their respective working positions.

[0058] The gear-like coupling of the press dies is preferably always maintained, regardless of the pivot position of the press jaws; that is, preferably both in the maximum open position of the press jaws and in the closed position, and preferably also in any intermediate position between the open and closed positions. The coupling of the press dies is thus not lost during pivoting movements of the press jaws. The assignment of press troughs to the intended pressing operation, preferably maintained via the coupling, is always preserved, preferably until a deliberate change occurs due to a rotational displacement of a press die.

[0059] The gear coupling can be used to achieve an over- or under-reduction ratio.

[0060] A die can be moved transversely to the axis of rotation by means of a gear wheel. This transverse movement can disable the positive locking mechanism of the press die in the working position. Furthermore, a radial displacement of the press die relative to the axis of rotation can be combined with a rotational movement of the press die to align a different press trough into the working position.

[0061] It can also be provided that a press die can be moved from a first pressing position secured by positive locking to a second pressing position secured by positive locking by means of a gear wheel.

[0062] A press die can be adjusted by means of a gear mechanism to move another press trough into a working position against a force that forces the press die into a positive-locking working position, during a movement transverse to its axis of rotation. The force that forces the press die into the positive-locking working position can result from a spring acting directly or indirectly on the press die. This can be a conventional cylindrical spring, such as a compression or tension spring; alternatively, for example, a torsion spring. Furthermore, the force can also result from a resilient element in the form of an elastically restoring plastic or similar material.

[0063] The gear-like coupling can be achieved via continuously meshed gears. By preferably arranging such gears coaxially to the pivot axes of the press jaws, a constant coupling of the gears is achieved, independent of the press jaw pivot position.

[0064] A permanent gear-like coupling can also be provided by direct or indirect connection of the press dies via a transmission belt, and in particular via at least one elastic belt.

[0065] It may further be provided that one or both press dies are adjustable via an adjusting wheel, possibly with an intermediate gear wheel, and that a gear wheel and / or the adjusting wheel is designed to be fully or partially elastically deflectable.

[0066] This design prevents damage to the crimping jaw, particularly to one or both crimping dies and / or related components in the working position, in the event of a possible misalignment of the crimping dies relative to each other during a crimping jaw closing movement. Due to the deflection of the gear wheel and / or the adjusting wheel, the forces acting on the crimping dies and / or the gear(s) or the adjusting wheel do not damage the adjusting and / or crimping components. Under corresponding force, the gear wheel and / or adjusting wheel deflect completely or partially in the direction of the force, resulting from a misalignment of the crimping dies. Gears can thus also be moved into a disengaged or overrun position.Due to the preferred elasticity, a self-return of the gear wheel and / or adjusting wheel to the original functional position is achieved when the force is removed.

[0067] Elastic deflection can be achieved, for example, by a support for the gear wheel and / or adjusting wheel that is essentially spring-loaded in the direction of force application, or, for example, by the axle body of such a wheel. The gear wheel and / or adjusting wheel can also be made of an elastically compliant material, such as rubber.

[0068] Furthermore, the gear wheel and / or the adjusting wheel can have toothed teeth, whereby the gear wheel and / or adjusting wheel acts in the form of a gear, wherein one or more groups of two or more toothed teeth are formed, wherein the toothed teeth of a group are formed on a common retaining part and the retaining part is connected to a radially inner area of ​​the gear wheel or adjusting wheel via a single springable branch.

[0069] It may further be provided that the crimping tool has a determining part for determining the diameter of an electrical conductor onto which it is to be crimped, and that the determining part has a plurality of passage openings, each with a narrowest cross-section corresponding to a nominal diameter of an electrical conductor.

[0070] This allows for the classification of the conductor to be crimped according to its size and the selection of the corresponding crimping die size. A gauge-like identification element can be provided for this purpose. This element can be made of a hard plastic or, alternatively, a metal material. The opening, which corresponds to the conductor diameter, indicates to the user which crimping die size to select. The identification element can therefore have markings corresponding to the openings, for example, in the form of diameter designations or crimping die sizes.

[0071] The determining element on the crimping tool must always be freely accessible for use. A fold-out arrangement of the determining element on the crimping tool is preferred, so that when not in use, the determining element can be pivoted from a working position to a non-working position. The non-working position can be a concealed position.

[0072] A pivot axis of the determining part in this respect can be aligned parallel to the axes of rotation of the press dies.

[0073] The determining element can also be arranged in overlapping position with a jaw plate of a press jaw. From this overlapping position, the determining element can be moved into the operating position by pivoting.

[0074] Preferably, two jaw plates are arranged overlapping each other, with the determining part being able to be arranged between the jaw plates, particularly in the non-use position.

[0075] If one press jaw is equipped with an adjustment wheel for synchronous adjustment of the press dies, the other press jaw may be equipped with the swiveling determining part.

[0076] The openings of a determining part can be designed for inch-based cable sizes or for those that are metric-based.

[0077] A gear with toothed teeth can be provided, wherein one or more groups of two or more toothed teeth are formed, wherein the toothed teeth of a group are further formed on a common retaining part and the retaining part is connected to a radially inner area of ​​the gear via a single springable branch.

[0078] Gears of the type in question are known. Reference is made, for example, to DE 397 646. The branch comprising the group of gear teeth is able to deflect circumferentially under appropriate force.

[0079] It is preferred that the branch is connected to the mounting part off-center in the circumferential direction. Due to this off-center arrangement, in addition to resilient deflection in the circumferential direction, resilient deflection in the radial direction (relative to the axis of rotation of the gear) is also achievable, even with central loading, and particularly with strictly radial loading of the mounting part.

[0080] The open-edged slots flanking each springable branch extend over a radially greater length than the circumferential tooth gap between two interlocking teeth.

[0081] Such a gear can be manufactured using laser cutting technology. The spring-loaded connection of a group of teeth to the radially inner area allows for elastic deflection of this group of teeth under appropriate force. The connecting branch acts like a spring arm.

[0082] Preferably, the branch is designed to extend in a circular segment shape when viewed from above, thus approximating a leaf spring shape. The branch can also be attached to the mounting part off-center in the circumferential direction, particularly with respect to the extent of the mounting part in the circumferential direction of the gear.

[0083] Preferably, the mounting part has three, four, or more teeth. More preferably, the gear has several groups of four teeth each, and even more preferably eight groups.

[0084] In the relaxed position of the arms supporting the mounting parts, the teeth of all groups of a gear produce a uniform circumferential tooth pattern along a circular line.

[0085] The ranges or value ranges or multiple ranges specified above and below also include all intermediate values ​​with regard to the disclosure, particularly in 1 / 10 increments of the respective dimension, and possibly even dimensionless values. For example, the specification "5 to 45 degrees" also includes the disclosure of 5.1 to 45 degrees, 5 to 44.9 degrees, 5.1 to 44.9 degrees, 6.8 to 37.2 degrees, etc. This disclosure can serve, on the one hand, to delimit a specified range boundary from below and / or above, or alternatively or additionally, to disclose one or more singular values ​​from a given specified range.

[0086] The invention is explained below with reference to the accompanying drawings, which, however, only represent exemplary embodiments. A part that is explained only in relation to one of the exemplary embodiments and is not replaced by another part in a further exemplary embodiment due to the special feature highlighted therein, is thus also described for this further exemplary embodiment as a possible existing part. The drawing shows: Fig. 1: In view a manually operated crimping tool in a first embodiment, relating to a crimping jaw closing position; Fig. 2: the side view here; Fig. 3: the cut according to line III-III in Fig. 2; Fig. 4: the enlargement of area IV in Fig. 3; Fig. 5: one of the Fig. 3 corresponding representation, however concerning the opening of the press jaws; Fig. 6: one of the Fig. 5 corresponding representation, with a dashed line depiction of interlocking gears; Fig. 7: one of the Fig. 6 corresponding representation, concerning an intermediate position in the course of adjusting the press dies; Fig. 8: in view a crimping tool in a second embodiment; Fig. 9: one essentially of the Fig. 3 corresponding representation, concerning a third embodiment; Fig. 10: another essentially the Fig. 3 corresponding illustration, concerning a fourth embodiment of the crimping tool as a motor-driven crimping tool; Fig. 11: one of the Fig. 3 corresponding illustration, concerning a further embodiment; Fig. 12: In exploded view, an embodiment of a press die with a coaxially associated separate part, Fig. 13: one of the Fig. 5 corresponding illustration, relating to a further embodiment of a crimping tool; Fig. 14: a further embodiment in a representation according to Fig. 13; Fig. 15: the crimping tool according to Fig. 14 in press position; Fig. 16: one of the Fig. 5 corresponding illustration, but concerning an alternative embodiment with regard to the press dies; Fig. 17: another embodiment of a crimping tool according to the illustration in Fig. 5; Fig. 18: the crimping tool according to Fig. 17 in press position; Fig. 19: one of the Fig. 17 essentially corresponding description, concerning a misalignment of the press dies; Fig. 20: one of the Fig. 17 corresponding representation, concerning an alternative embodiment; Fig. 21: a positive locking device in top view, relating to a further embodiment; Fig. 22: one of the Fig. 6 substantially corresponding representation, concerning a further alternative embodiment; Fig. 23: the cut according to line XXIII-XXIII in Fig. 22; Fig. 24: another one of the Fig. 3 substantially corresponding top view of a crimping tool, relating to a further embodiment; Fig. 25: a gear wheel of the crimping tool according to Fig. 23 in individual top view; Fig. 26: the enlargement of area XXV in Fig. 24; Fig. 27: in schematic representation a gear wheel in arrangement position, relating to a further embodiment; Fig. 28: one of the Fig. 26 corresponding illustration, concerning a further embodiment; Fig. 29: in perspective representation a didactic-like definitional section; Fig. 30: the top view of the determining part; Fig. 31: the cut according to line XXX-XXX in Fig. 29.

[0087] The presentation and description initially refers to Fig. 1 A hand-operated crimping tool 1 in a top view showing a working position, i.e., a crimping position. The crimping tool 1 is essentially symmetrical about an axis xx and has two crimping jaws 2, 3 and two handles 4, 5 designed as angled levers. The latter are connected to each other at their angled ends by a pivot pin 6 arranged on the axis of symmetry xx.

[0088] On both sides of the pivot pin 6, the press jaws 2, 3 are hinged with their free end areas to the handles 4, 5, wherein the press jaws 2, 3 and the handles 4, 5 are provided with bolts 7, 8 which pass through the press jaws 2, 3 and the handles 4, 5 and which are secured with spring washers 9, 10.

[0089] The press jaws 2, 3, which are essentially identical in shape with respect to axis xx, each consist initially of two jaw plates 11, 12 and 13, 14 spaced apart from each other in the axial direction of the bolts 7, 8 and also of the pivot pin 6. The bolt-side end regions of the handles 4, 5 engage in the space between the jaw plates 11, 12 and 13, 14.

[0090] The press jaws 2, 3 are connected on both the top and bottom sides, corresponding to the outwardly facing flat side of the jaw plates, by tabs 15, 16, which in turn are connected to each other by axle bolts 17, 18 passing through the press jaws 2, 3.

[0091] The geometric axes of the bolts 7, 8, the pivot pin 6 and the axle bolts 17, 18 are aligned transversely to the axis xx and perpendicular to a plane extension of the press jaws 2, 3 with respect to their broad sides.

[0092] The pivot axes of the press jaws 2, 3 are formed by the axle bolts 17, 18, whereby the press jaws 2, 3 are divided into short front lever arms 19, 20 and longer rear lever arms 21, 22 facing the pivot bolts 7, 8.

[0093] In the short, front lever arms 19, 20 of the press jaws 2, 3, a press die 23, 24 is rotatably mounted on an axis 25, 26. The axes 25, 26 each pass through both jaw plates of the press jaws 2, 3 and are secured on both sides, e.g., by screws. The geometric axis of rotation of the press dies is denoted by y.

[0094] The press dies 23, 24 have the plan shape of an even-numbered polygon. In the illustrated embodiment, the press dies 23, 24 are designed as regular hexagons in plan view.

[0095] The generally disc-shaped press dies 23, 24 have press recesses 27, 28 with different opening cross-sections on their circumference, each assigned to a side surface of the preferred hexagon.

[0096] In a top view, for example, according to the Fig. Figure 3 shows that the press troughs 27, 28 have the shape of half an equilateral hexagon. In working position, i.e., in pressing position according to the Fig. 1 to 4 each form two press recesses 27, 28 with the same opening cross-section together a regular hexagon for pressing cable lugs, connectors or the like onto electrical conductors etc.

[0097] For the proper crimping of a cable lug or the like, crimping troughs 27, 28 of the same size and adapted to the crimping process must be moved into the working position. This is done by rotating the crimping dies 23, 24 about the axes 25, 26.

[0098] The rotational movement of the press dies 23, 24 is synchronized. This is achieved by a constant gear-like coupling of the press dies 23, 24, which coupling is independent of the pivoting position of the press jaws 2, 3.

[0099] For the gear-like coupling, in a first embodiment according to the Fig. 1 to 7 on each press jaw 2, a gear wheel 29, 30 in the form of a gear is rotatably arranged. The diameters of the gear wheels 29, 30 are the same.

[0100] Like the press dies 23, 24, the gear wheels 29, 30 extend in the remaining space between the jaw plates of the press jaws 2, 3.

[0101] The gear wheels 29, 30 are rotatably mounted on the axle bolts 17, 18, with the gear-shaped gear wheels 29, 30 meshing with each other. The selected arrangement of the gear wheels 29, 30 on the axle bolts 17, 18 ensures meshing in every pivot position of the press jaws 2, 3.

[0102] The outer diameter of each gear wheel 29, 30 corresponds essentially to the diameter of a circle connecting the radial tips of the press dies 23, 24.

[0103] On the axes 25, 26, output gears 31, 32 are provided, which are non-rotatably connected to the respective press die 23, 24. In the first embodiment, the output gears 31, 32 are gears which mesh with the respective associated gear wheel 29, 39.

[0104] The diameter of the output gear 31, 32 is reduced compared to the diameter of the gear 29, 30. Thus, an output gear 31 has an outer diameter that is approximately 0.4 to 0.5 times the outer diameter of a gear 29, 30.

[0105] Furthermore, the diameter of a driven wheel 31, 32 is chosen such that, with reference to a projection along the axis of rotation y, it does not protrude into the press recesses 27 or 28 of the associated press die 23, 24.

[0106] Furthermore, a separate part 33 in the form of an adjusting wheel 68 is provided on a press jaw 3. This is rotatably mounted in the area of ​​the rear, longer lever arm 22 about an axle bolt 34 with a pivot axis z that passes through the associated jaw plates 13, 14. The separate part 33 is designed in the shape of a circular disk with a circular disk surface that extends parallel to the broad surfaces of the gear wheels 29, 30 and the press dies 23, 24, offset in plane.

[0107] Associated with a disk surface of the separate part 33, a drive wheel 35 in the form of a gear is arranged on this part in a rotationally fixed and coaxial manner. This gear meshes with the external teeth of the associated gear wheel 30 of the press jaw 3.

[0108] The arrangement of the axle bolt 34 is preferably chosen such that the separate part 33 projects freely outwards, i.e., away from the opposite press jaw 2, with a partial section extending beyond the plan contour of the press jaw 3, for manual operation of the drive wheel 35. Thus, the drive wheel 35 can be operated, for example, by thumb, with the thumb surface rotating the separate part 33 over its circumferential edge.

[0109] A rotary displacement of the separate part 33 leads via the transmission, consisting of drive wheel 35, gear wheels 29, 30 and output wheels 31, 32, to a synchronous rotary displacement of the press dies 23, 24, so that by displacing only one part (separate part 33) identical press troughs 27, 28 can always be brought into the working position opposite each other.

[0110] As an alternative to the gear-gear arrangement, the gear-like coupling according to the embodiment can be in Fig. 11. This can also be achieved by means of transmission belts.

[0111] In this case, the circular disc-shaped separate part 33 and the press dies 23, 24 have cylindrical sections 36 to 38 arranged in a rotationally fixed and coaxial manner to them, the outer surfaces of which may be roughened, for example, by microstructuring.

[0112] Such cylinder sections 39, 40 are also freely rotatable on the axle bolts 17, 18.

[0113] Each axle-bolt-side cylinder section 39, 40 is connected via an output belt 41, 42 to the cylinder section 36, 37 of the associated press die 23, 24.

[0114] A drive belt 43, which may be laid crosswise, connects the cylinder section 40 on the axle bolt side with the cylinder section 38 of the separate part 33.

[0115] The two cylinder sections 39 and 40 on the axle bolt side are connected to each other via a transmission belt 44, which is preferably arranged crosswise.

[0116] On the separate part 33, symbols 45 in the form of numbers are applied to its circular disc surface, corresponding to the nominal diameters of the press troughs 27 and 28. The symbols 45 are arranged on a circle around the geometric axis of the axle bolt 34, such that the nominal diameter relating to the press troughs 27, 28 in the working position is recognizable to the user either on the section of the separate part 33 projecting beyond the plan view of the press jaw 3 (cf. Fig. 1 or Fig. 3) or by a window 46 punched out in the jaw plate 13 of the press jaw 3 covering the numeral side of the separate part 33 (cf. e.g. Fig. 8).

[0117] It can also be, as in Fig. Figure 12 shows by way of example a separate part 47 with applied, e.g. printed or integrally formed with the separate part, markings 45, which part 47 is arranged coaxially to a press die 23, 24 and is further formed, e.g. contour adapted with the press die 23, 24.

[0118] Part 47 is non-rotatably connected to the press die 23, 24, e.g. by a non-circular design of the bore and the section of the axis passing through it, through which the axis passes through.

[0119] Regardless of the design and arrangement of the separate part bearing the characters 45, this part is not subjected to any pressing force during pressing. Preferably, a different material is selected for the separate part compared to the press dies 23, 24, e.g., zinc die-casting, which facilitates the application of the characters 45, e.g., by printing or by embedding the characters 45 during the casting process.

[0120] The respective working position of the press dies 23, 24 is secured by a positive locking mechanism. For this purpose, each press die 23, 24 is assigned a bracket-like positive locking element 48, 49. The positive locking elements 48, 49 extend in the space between the assigned jaw plates of the press jaws 2, 3 and are held in the jaw plates by means of pin-like projections 50, 51.

[0121] The positive locking means 48, 49 are arranged facing away from the press trough 27, 28 in the working position.

[0122] Viewed in the circumferential direction of each press die 23, 24, a tooth-like projection 52, 53 extends between two adjacent press troughs 27, 28, which is essentially radially oriented with respect to the geometric axis of rotation y of the press die 23, 24.

[0123] Each projection 52, 53 has two bearing surfaces 54, 55 and 56, 57 respectively, which form an obtuse angle to each other in plan view. The bearing surfaces result in a roof-shaped pointed end of each projection 52, 53.

[0124] The impact areas 54, 55 and 56, 57 extend further in relation to a floor plan according to Fig. 3 on a line connecting the tips of the projections 52, 53 of a preferred hexagonal contour.

[0125] The bearing surfaces 54, 55 and 56, 57 of the projections 52, 53, which define the press trough 27, 28 opposite the press trough in the working position, interact with adapted positive locking surfaces 58 to 60 and 61 to 63 of the positive locking means 48, 49.

[0126] Preferably, the bearing surfaces of the projections 52, 53 lie fully against the associated positive locking surfaces of the positive locking means 48, 49 in the positive locking position.

[0127] With reference to a straight line A connecting the geometric axes of the axle bolts 17, 18, the positive locking surfaces 59, 62 extend in the pressing position of the press jaws 2, 3 as shown in the illustration in Fig. 4 in a transverse direction to the line A. The bearing surfaces 55, 57 of the press dies 23, 24, which are directly adjacent to the press trough 27, 28 facing the positive locking means 48, 49 in the circumferential direction, are supported in the positive locking position on these positive locking surfaces 59, 62 which are oriented transversely to the line A.

[0128] In the positive locking position, the further bearing surfaces 54, 56 extend at an acute angle α of approximately 30 degrees to the line A (with reference to the pressing position according to Fig. 4).

[0129] The corresponding interlocking surfaces 58, 60 and 61, 63 extend from the interlocking surfaces 59, 62 at a corresponding acute angle, for the preferred full-surface contact of the corresponding bearing surfaces.

[0130] The press dies 23, 24 are in the form-closing position as shown in the illustration. Fig. 3 rotationally secured. To rotate the press dies 23, 24, the positive locking must first be released. This is done in conjunction with the rotational action on the press die 23, 24, in particular by the gear-translated action via the separate part 33 by hand.

[0131] The axes 25, 26 of the press dies 23, 24 are guided in elongated holes 64, 65 of the press jaws 2, 3, which are aligned with respect to a plan view transversely to the orientation of the positive locking surfaces 59, 62. This allows the press dies 23, 24 to be displaced transversely to the positive locking means 48, 49 to release the positive locking mechanism.

[0132] Such a displacement occurs against the force of a spring 66. This can be a cylindrical compression spring, such as in Fig. 1 shown, which is seated in a radial bore of the axis 25, 26 and is supported against a boundary wall of the associated elongated hole 64, 65.

[0133] The spring can also be used according to the illustration in Fig. 9 a torsion spring which is held in the area of ​​the axle bolts 17, 18 and with its free ends acts on the axes 25, 26 of the press die 23, 24 in the direction of the positive locking means 48, 49.

[0134] The spring force always acts in the direction of the positive locking position, regardless of the pivot position of the press jaws 2, 3.

[0135] To adjust the press dies 23, 24, the disc-shaped separate part 33 is used as shown in the illustration. Fig. 6 preferably rotated in the direction of arrow a – with reference to the illustration in a clockwise direction. This results in a counter-rotation of the two gear wheels 29, 30 in the directions of arrows b, c.

[0136] The output gears 31, 32 and, accordingly, the press dies 23, 24 are rotated in the opposite direction d, e via the gear wheels 29, 30. This results in a forced lateral displacement of the press dies 23, 24, caused by the sliding of the bearing surfaces 54 and 56 on the associated positive locking surfaces 60, 63. This lateral displacement is superimposed on the rotational displacement of the press die 23, 24.

[0137] If the subsequent projection 52, 53 in the direction of rotation exceeds a dead center position (shown in Fig. 7), the spring force acting on the axes 25, 26 of the press dies 23, 24 causes the press dies 23, 24 to be moved backwards in the direction of the positive locking position with the positive locking means 48, 49.

[0138] As in the exemplary embodiment of the Fig. As shown in Figure 21, the corresponding positive locking surface 59 or 62 can be provided with two sliding surfaces 77 oriented towards each other in a roof-like manner. The positive locking surface 59, 62 is preferably tapered at the level of a line connecting the die rotation axes y in the direction of the die 23, 24. The sliding surfaces 77 are designed to conform to a curved section with respect to a top view, such that, starting from one end, the positive locking surface 59, 62 first has an ascending and then a descending surface.

[0139] The press die 23, 24 thereby experiences an angular momentum towards the next form-locking position upon exceeding or reaching the dead center position, due to the spring force acting upon it. Conversely, before reaching the dead center position (when the angular force acting on the die ceases), it experiences a reverse angular momentum towards the previous form-locking position. This prevents the press die 23, 24 from unintentionally remaining in the dead center position and thus prevents self-locking.

[0140] The press trough 27, 28, now in working position, can be read with regard to its nominal width on the separate part 33.

[0141] If the bearing surfaces 54, 56 and the associated positive locking surfaces 58, 60 and 61, 63 have the same acute angles to the line A, then a change of the press troughs 27, 28 can be achieved by rotating the separate part 33 in one direction or the other, in the direction of arrow a or opposite.

[0142] It is also possible for only one direction of rotation to be specified, by having one of the previously described angles of the bearing surfaces and positive locking surfaces have a comparatively small acute angle and thus form a non-overrunnable stop.

[0143] The press dies 23, 24 can also be adjusted with the press jaws 2, 3 open by directly engaging one of the press dies 23 or 24 (possibly omitting the separate disc-shaped part 33). The movement of one press die 23 leads, via the provided gearing, to the synchronous movement of the other press die.

[0144] In Fig. Figure 10 shows an electrically operated crimping tool 1, in which the crimping jaws 2, 3 are moved into the crimping position and back again by means of an electrically actuated plunger. The crimping process is triggered by a finger-operated lever 67.

[0145] The crimping tool as shown in Fig. 10 features a previously described gear mechanism for coupling the press dies 23, 24, as well as a separate disc-shaped part 33 for manual adjustment of the press dies. Numbers 45 are printed on or embedded in the separate part 33 to indicate the set nominal diameter of the press troughs 27, 28.

[0146] The mode of operation with regard to the adjustment of the press dies 23, 24 is the same as that of the hand-operated press pliers 1.

[0147] In Fig. Figure 13 shows a further embodiment of a crimping tool 1, in which an adjusting wheel 68, 69 is arranged on each crimping jaw 2, 3. Here too, the axis of rotation z of each adjusting wheel 68, 69 extends parallel to and offset in the longitudinal direction of the crimping jaw 2, 3 from the axis of rotation y of the associated crimping die 23, 24.

[0148] The adjusting wheels 68, 69 are geared to the associated press die 23, 24 via gear wheels 29, 30.

[0149] In this embodiment, the gear wheels 29, 30 are arranged such that their tooth rings do not mesh with each other in any pivoting position of the press jaws 2, 3.

[0150] In this embodiment, the adjustment of a modified press jaw is carried out by individually adjusting both press dies 23, 24 via the respective adjusting wheel 68, 69.

[0151] The adjustment of the press dies 23, 24 is also carried out here by acting in an area spaced apart from the press dies 23, 24, in particular by rotational displacement of the associated adjusting wheel 68, 69.

[0152] This also offers the advantageous possibility of placing the Pressmaul numbers 45 on the adjustment wheels 68, 69.

[0153] The Fig. 14 and Fig. Figure 15 shows an embodiment with a synchronous adjustment of the press dies 23, 24, e.g. according to the first embodiment.

[0154] One of the press jaws, here press jaw 2, carries a pawl 70 which is rotatably mounted on a pawl parallel to the pivot axis of press jaw 2. This pawl is held in a home position by a tension spring 71 which is also held at the other end of press jaw 2. Fig. 14 loaded.

[0155] The locking pawl 70 has a pawl lug 72. This has, in its basic orientation, according to Fig. 14 in the direction of the pivot point of the handle 4 on the press jaw, which is penetrated by the bolt 7.

[0156] Furthermore, a radial extension is molded onto the locking pawl 70. This nose 73, pointing laterally towards the other press jaw 3, serves as an emergency release.

[0157] In the area of ​​the pivot point of the handle 4, which is penetrated by the bolt 7, a gear segment 74 is formed coaxially to the bolt 7 or to its bolt axis, for interaction with the latch nose 72.

[0158] The locking pawl 70 is arranged lying between the jaw plates 11, 12 of the press jaw 2 and engages in an open position of the press jaw 1 according to Fig. 14 into a non-geared area of ​​the pivot point.

[0159] By pivoting the handles 4 and 5 to close the crimping jaws 1, the latch nose 72 engages in the gear segment 74 in a locking manner, so that from this position only a further displacement of the handle 4 towards the other handle 5 is possible.

[0160] Such a forced locking mechanism ensures that full pressing pressure must always be applied when creating a press connection.

[0161] Upon reaching the pressing position, the latching nose 72 has overrun the gear segment 74 and is then back in its extended starting position (cf. Fig. 15), so that the handles 4, 5 or the crimping jaw 1 can be opened with a ratchet-like overrun.

[0162] In an emergency, the locking pawl 70 can be moved into a non-engagement position by the user via the nose 73, so that the crimping tool 1 can be opened even without completion of a crimping operation.

[0163] Fig. Figure 16 shows an alternative embodiment with press matrices 23, 24, each of which, with reference to the plan view, draws a regular pentagon with respect to its outer contour.

[0164] Accordingly, five press recesses 27, 28 are provided around the circumference, centrally located at the longitudinal edge edges. Projections 52, 53 extend between these recesses in the circumferential direction.

[0165] The projection 52, 53, which is diametrically opposite the press trough 27, 28 in the working position, serves in conjunction with the positive locking means 48, 49 to lock the press die 23, 24 in the working position.

[0166] For this purpose, the projection 52, 53 with its tip area having the contact surfaces 54 and 56 dips into a notch-like recess of the form-locking means 48, 49, which notch-like recess forms the corresponding form-locking surfaces 58, 60 and 61, 63 respectively.

[0167] The form-fitting surfaces 58, 60 and 61, 63 extend with reference to the floor plan according to Fig. 16 beyond the press trough 27, 28 adjacent to the captured projection 52, 53. Furthermore, preferably, the bearing surfaces of the projection 52, 53, which precedes or trails in the direction of rotation of the press die 23, 24, are also supported.

[0168] In the embodiment according to the Fig. 17 to 19 is based on a crimping tool according to the illustrations in the Fig. 1 to 6, a teaching part 75 is provided. This is preferably a plate part with a substantially triangular ground plan as shown in Fig. 17.

[0169] The gauge section 75 preferably extends between the jaw plates, and thus preferably in the plane of the press dies 23 and 24. The gauge section 75 can have a thickness, considered in the axial direction of the press dies 23 and 24, that corresponds to that of the press dies 23, 24.

[0170] Furthermore, in the illustrated embodiment, the teaching part 75 is penetrated and thus held in place by the axle bolts 17 and 18 in the area of ​​two triangular points.

[0171] This results in a triangular tip 76 of the teaching part 75, which tip projects into the mouth of the press jaw 1, into which mouth the press troughs 27, 28 in working position also project when the press dies 23 and 24 are properly aligned.

[0172] The flanks of the tips 76 are adapted to the outer contour of the projections 52 and 53, in particular adapted to the impact surfaces 55 and 57.

[0173] The bearing surfaces 55, 57, two projections 52, 53 facing each other in working position, close in the pressing position according to Fig. 18 an obtuse angle of, for example, 120 degrees, which corresponds to the included angle of the acute flanks of the teaching part 75.

[0174] With correct and locked alignment of the press dies 23 and 24 according to the illustration in Fig. 17. The press jaws 2 and 3 can be closed. The essentially opposing bearing surfaces 55, 57 of the projections 52 and 53, which are abutting each other in the press position, may be supported by the pointed flanks of the gauge part 75.

[0175] If, however, the press dies 23 and 24 are not completely displaced into their final and preferably locking position (cf. Fig. 19) During the closing movement of the jaws, at least one of the projections 52, 53 strikes the facing flank of the tip of the gauge section 76. This can lead to a blockage of the closing movement of the jaws, due to jamming.

[0176] The flanks of the gauge section 75 adjoining the tip area are preferably concave when viewed from the outside of the gauge section 75. This provides controlled guidance of the projection 53, 53, which impacts the press die during the closing movement if the press die is not correctly adjusted, preferably in the direction of the usual rotational displacement of the press die 23, 24 until the working position is reached.

[0177] Fig. Figure 20 shows an embodiment with a gauge part 75 of the type described above, in which the press dies 23 and 24 of the press jaw 1 can be adjusted individually and directly by hand.

[0178] The Fig. 22 and Fig. Figure 23 shows a further embodiment of a crimping tool 1 with crimping dies 23 and 24 that are synchronously adjustable via gear wheels 29 and 30 and preferably an adjusting wheel 68.

[0179] In this embodiment, the press dies 23 and 24 are rotatably mounted about fixed axes 25 and 26, which preferably cannot be displaced transversely to the axis y.

[0180] A pressing position of the press dies 23, 24, found in particular via the adjusting wheel 68 and the gear wheels 29, 30, is also secured in this embodiment.

[0181] Each press die 23, 24 is associated with a leaf spring 78. The spring 78 is fixed at one end to a mounting pin 79, which mounting pin 79 is held on the associated press jaw 2, 3, in particular between the associated jaw plates. The spring 78 extends from the mounting pin 79 towards the associated press die 23, 24, partially surrounding the pivot pin 17, 18 under resilient bending of the associated gear wheel 29, 30, thus providing appropriate support for the spring 78 with one of its broad sides against the pivot pin.

[0182] The end of the spring 78 facing away from the end of the holder extends after the support area on the axle bolt 17, 18 in a direction away from the press recess 27, 28 in the pressing position.

[0183] The spring 78, with its free section tensioned via the axle bolts 17, 18, is supported against the facing bearing surfaces 55 and 57 of two successive projections 52, 53 in the direction of rotation of the press die 23, 24. The spring force acting on the projections 52, 53 creates a positive locking interaction to secure the press die 23, 24 in the established pressing position. Rotation of the press die 23, 24 inevitably occurs against the (in relation to the illustration in Fig. 22) counterclockwise force of spring 78. By rotating the press die 23, 24, the free spring leg is deflected further.

[0184] The width of the leaf spring considered in the direction of the axis of rotation y of the press die 23, 24 preferably corresponds to the height of the bearing surfaces cooperating with the spring 78 considered in the same direction and thus further preferably to the material thickness of the press die 23, 24 in the area of ​​the projections 52, 53 considered further in the axial direction.

[0185] Fig. Figure 24 shows another embodiment of the crimping tool 1. In this embodiment, the crimping dies 23, 24 are also adjustable together and synchronously via gear wheels 29, 30, for which purpose an adjusting wheel 68 acting on a gear wheel is further provided.

[0186] Gear wheels 29 and 30 are identical in design.

[0187] Furthermore, the gear wheels 29, 30 are designed to be elastically deflectable. For this purpose, the toothed teeth 80 of each gear wheel 29, 30 are divided into groups 81 of four consecutive toothed teeth 80 in the circumferential direction.

[0188] The gear teeth 80 of a group 81 are formed on a mounting part 82. From this, a spring-loaded branch 83 extends in a single piece and is connected to a radially inner, also single-piece and uniformly formed area 84 of the gear wheel 29, 30.

[0189] The gear wheel 29, 30 or gear 86 has eight groups of four teeth 80 evenly distributed around its circumference, which eight groups 81 are connected to the inner area 84 via a branch 83.

[0190] The branches 83 are connected off-center to the mounting part 82 with respect to a radial r (relative to the geometric axis of rotation of the gear wheel 29, 30 or the gear 86), which radial r passes centrally through the mounting part 82 in its circumferential extent. Preferably, the connection of the branch 83 in the circumferential direction is formed at the end of the mounting part 82.

[0191] Each tooth 80 can form the end region of the retaining part 82. The radial r can run centrally through a gap formed between the middle teeth 80.

[0192] Starting from the connection to the mounting part 82, each branch 83 extends with reference to a top view according to Fig. 24 curved segment, moving away from the mounting part 82 in the circumferential direction and engaging radially inside the circumferentially adjacent group 81 or of the mounting part 82.

[0193] The connection of the branch 83 to the radially inner area 84 can be chosen such that a radial passing through this connection area in the middle intersects at least approximately the branch connection area at the same time on the support part 82 of the circumferentially adjacent group 81.

[0194] Due to the aforementioned design of the gear wheel 29, 30 or gear 86, a resilient deflection of an engaged group 81 of gear teeth 80 is given, even under central, in particular strictly radial, loading, whereby a resilient effect can be achieved in both radial and circumferential directions.

[0195] Alternatively, a spring effect can also be achieved by making the gear 86, e.g., the gear wheel 29, 30, from a compliant material, or, for example, by making it from a rubber material. A springable displacement can also be achieved, as shown schematically and exemplified in Fig. 27. The axle bolt 17, 18 can be guided in an elongated hole of a jaw plate and loaded into a central working position by compression springs 88.

[0196] Alternatively, the gear 86, such as the gear wheel 29, 30, and also the adjusting wheel 68, 69, can be formed by a circumferential tooth ring 89, which is connected to the inner area 84 via elastically springable spring arms 90 that extend in a circular segment shape in plan view (cf. Fig. 28).

[0197] To classify the conductor to be crimped with regard to the crimping trough size, a gauge-like determining element 91 can be provided. This is plate-shaped, e.g., made of a hard plastic, or alternatively of a metal material.

[0198] The determining part 91 can be pivotably arranged on the crimping jaw 1, in particular between the jaw plates 11, 12.

[0199] The defining part 91 can have integrally formed pivot pins 92 which engage in corresponding bores or recesses in the jaw plates 11, 12. The resulting geometric axis of rotation runs parallel to the axes y of the press dies 23, 24.

[0200] The determining part 91 is thus moved from a non-use position, in which it is arranged between the overlapping jaw plates 11, 12, into a position in Fig. 24. Usage position shown in dash-dots can be folded out.

[0201] To grasp the determining part 91, a gripping section 93 is formed which also projects freely beyond the facing edge edges of the jaw plates 11, 12 in the non-use position.

[0202] Furthermore, friction projections 94 can be provided on both broad surfaces of the determining part 91 near the pivot pins 92, which hold the determining part 91 in the non-use position by means of frictional engagement with the facing surfaces of the jaw plates 11, 12.

[0203] Furthermore, the defining element 91 has several passage openings 95 penetrating its broad side surfaces. Preferably, the number of passage openings 95 is adapted to the number of press troughs 27, 28 of the press dies 23, 24.

[0204] Each passage opening 95 has a narrowest cross-section, in particular in the area of ​​a ring-collar-like extension in the area of ​​a broad side surface of the defining part 91, which narrowest cross-section corresponds to a nominal diameter of an electrical conductor.

[0205] Associated with the through-openings 95, information on the crimping recesses 27, 28 can be provided across the broad side of the defining part 91, corresponding to the setting specifications on the adjusting wheel 68 or directly on the crimping dies 23, 24. This allows for a clear classification of the electrical conductor and thus of the cable lug or the like to be crimped, as well as of the crimping recesses 27, 28 to be set.

[0206] To facilitate the insertion of the electrical conductor into the opening 95, the opening has at least one funnel-shaped section 96. This is preferably formed on the broad side of the defining part 91 opposite the ring collar.

Claims

[1] Crimping tool (1) in particular for crimping cable lugs or the like onto electrical conductors, with two crimping jaws (2, 3) pivoting relative to each other, wherein in each crimping jaw (2, 3) a crimping die (23, 24) rotatably mounted having several different crimping recesses (27, 28) extending over a circumference with respect to an axis of rotation (y), characterized by , that a position corresponding to a working position of a press trough (27, 28) is secured by positive locking and that the press die (23, 24) can be moved transversely to its axis of rotation (y) to release the positive locking position. [2] Crimping tool according to claim 1, characterized by, that a press recess (27, 28) of the press die (23, 24) is formed by tooth-like projections (52, 53) which on an outside of the press recess (27, 28) has a contact surface (54 to 57) which can be brought into engagement with a positive locking means (48, 49) in a working position of the press recess (27, 28), wherein, viewed in the direction radial to the axis of rotation (y), a contact surface (54 to 57) which is brought into engagement with a positive locking surface (59, 62) encloses an acute angle (α) with respect to a straight line (A) passing through the axes of rotation of the opposing press dies (23, 24) or parallel thereto. [3] Crimping tool according to claim 2, characterized by, that the form-fitting surface (59, 62) forms a sliding surface (77) that rises and / or falls in a top view, whereby the press die (23, 24) can be brought into a stop-limited rotational end position about its axis of rotation (y), and / or, preferably, that the engaging actuation surface (54 to 57) of a press trough (27, 28) belongs to a press trough (27, 28) opposite the axis of rotation (y) of the press die (23, 24), which is in working position. [4] Crimping tool according to one of claims 2 or 3, characterized by , that with respect to the straight line (A) two opposing impact surfaces (54 to 57) are provided, and / or, preferably, that the acute angles (α) of both impact surfaces (54 to 57) are equal. [5] Crimping tool according to any one of claims 1 to 4, characterized by, that a press die (23, 24) can only be moved out of the positive locking position against spring force and / or, preferably, that the spring force and / or the acute angle (α) are selected such that manual adjustment of a press die (23, 24) is possible, and / or, preferably, that the spring force and / or the acute angle (α) are selected such that only gear adjustment is possible. [6] Crimping tool (1) according to the features of the preamble of claim 1 or according to one of the preceding claims, characterized by , that each press die (23, 24) is adjustable via an adjusting wheel (68, 69) coupled to it by means of a gear mechanism, wherein the adjusting wheel (68, 69) and the press die (23, 24) have different axes of rotation (y, z). [7] Crimping tool according to claim 6, characterized by, that the axes of rotation (y, z) run parallel to each other, and / or, preferably, that a press jaw (2, 3) has a longitudinal direction from a hinge on the handle side to a free end, and that the axes of rotation (y, z) are offset from each other in the longitudinal direction. [8] Crimping tool according to one of claims 6 or 7, characterized by , that the adjusting wheel (68, 69) acts on the press die (23, 24) via a gear wheel (29, 30). [9] Crimping tool according to one of claims 6 to 8, characterized by , that the press die (23, 24) is rotatable about a fixed axis (25, 26), and / or, preferably, that the press die (23, 24) is secured in a pressing position by a positive locking interaction with a spring (78), and / or that the spring (78) is a leaf spring, and / or that the spring (78) is supported on the axis (17, 18) of a gear wheel. [10] Crimping tool according to the features of the preamble of claim 1 or according to one of the preceding claims, characterized by , that symbols (45), in particular numbers, are provided which identify the different press recesses (27, 28) and that the symbols (45) are applied to a part (33, 47) separate from the press die (23, 24), which is not subjected to any pressing force during pressing and is made of a material different from a material of the press die (23, 24). [11] Crimping tool according to claim 10, characterized by , that the separate part (47) is firmly connected to the press die (23, 24) and / or, preferably, that the separate part (47) is arranged coaxially to the press die (23, 24), and / or preferably, that the separate part (33) is arranged about a further axis of rotation and is gear-connected to the press die (23, 24). [12] Crimping tool according to one of claims 10 or 11, characterized by, that the characters (45) are printed on the separate part (33, 47) and / or, preferably, that the characters (45) are integrally formed with the separate part (33, 47). [13] Crimping tool according to one of the preceding claims, characterized by , that a gauge part (75) is provided which is adapted to an outer contour of the press die (23, 24) in the area of ​​a press recess (27, 28) and allows the press jaw (1) to close only when the press die (23, 24) is arranged with a press recess (27, 28) of the press jaw (1) in an orientation suitable for pressing. [14] Crimping tool according to claim 13, characterized by , that the gauge part (75) is designed as a plate part, and / or, preferably, that the gauge part (75) is mounted on the pivot axes of the press jaws (2, 3). [15] Crimping tool according to one of the preceding claims, characterized by, that the crimping tool (1) has a defining part (91) to be crimped onto the conductor for determining the diameter of an electrical conductor and that the defining part (91) has a plurality of passage openings (95) each with a narrowest cross-section corresponding to a nominal diameter of an electrical conductor. [16] Crimping tool according to claim 15, characterized by , that the determining part (91) is provided to be foldable on the pressing jaw (1), and / or, preferably, that the determining part (91) can be arranged in overlap with a jaw plate (11 to 14) of a pressing jaw (2, 3), and / or, preferably, that two jaw plates (11 to 14) are arranged in overlap with each other and that the determining part (91) can be arranged between the jaw plates (11 to 14).

Images