TW201531386A - Crimping pliers - Google Patents

Abstract

The present invention relates to crimping pliers in particular used for forming at least three recesses at a contact element housing an electrical conductor. The inventive crimping pliers (1) comprise a toggle lever drive (6). The toggle lever drive (6) is built with an elastic pressure lever (18). The pressure lever (18) is preferably built with an offset or cranking (33) so that with the application of a longitudinal force the pressure lever (18) is biased by a bending. The flexible design of the pressure lever (18) provides a variable crimping stroke (in particular also in connection with a forced locking mechanism (28)) for different dimensions of the contact elements to be crimped.

Description

Pressure clamp

The present invention relates to a squeeze jaw that is used to squeeze a workpiece. For example, the squeezing tongs are used to deform the periphery of the workpiece or the periphery of the contact element, in particular a plurality of grooves and/or extruded core sleeves, contact bushings or cable joints to the periphery. The conductor is equal.

EP 0 732 779 B1 discloses a squeeze tong for pressing a core sleeve with a stripped electrical conductor. The squeeze tong has a clamp head. The jaws are formed with a base. The base is securely coupled to a fixed handle. A swinging ring is rotatable about the die axis relative to the base body. The oscillating ring has a radial indentation in the region of its inner surface, thereby forming a splined shaft section. The six extrusion punches are evenly arranged to distribute around the die axis. The squeezing punches are rotatably supported on the oscillating pin shaft held by the base body, respectively. In the end region facing away from the die, the pressing punch respectively finds a receiving portion in a notch in the splined shaft notch of the oscillating ring. The rotation of the oscillating ring causes a common oscillation of these squeezing punches. The radially inner die faces of the extrusion punches form a die that is closed to the greatest extent in the circumferential direction, the cross-sectional area of the die being reduced as the swinging ring rotates and the resulting rotation of the punching punches is reduced. Thereby, the core sleeve is pressed. The operation of the jaws in the form of a relative rotation of the oscillating ring relative to the base body is carried out by means of a drive pin or a oscillating pin hinged to the oscillating ring. The drive pin or the swing pin is oscillating The component part of the support, an end region of the movable handle, is hinged to the pivot ring by means of it. By means of a further pivot bearing, a pressure bar is articulated on the movable handle slightly spaced apart from the previously mentioned pivot bearing, wherein the pivot bearing forms an elbow joint. The pressure bar is hinged to the fixed handle in the end region facing away from the elbow joint. For this purpose, the pressure bar forms a support ball and the receiving portion is situated in a support half-shell formed by a fixed handle. A return spring acting in the opening direction of the squeezing tongs is directly hinged to the oscillating ring at a spring foot point, while the other spring foot of the return spring is hinged to the fixed handle. Leaving the connection area between the elbow joint and the support ball, the pressure bar has a partial periphery provided with a tooth portion, the periphery of which interacts with a stop element. The stop element is rotatably mounted on the movable handle and is loaded into a balanced position by a spring acting between the stop element and the movable handle. The use of the toothed portion of the pressure bar and the stop element forms a positive stop, by means of which it is ensured that the one-timed compression stage of the pressure tong is also reduced in the case of a reduced actuating force applied to the handle It is guaranteed without the opening movement of the jaws. In particular, the opening movement is possible when the pressure lever completely ends the predetermined total stroke.

EP 0 732 779 B1 describes the problem in which a final state, in advance of the predetermined final size of the die, is predetermined by the positive stop in a squeeze tong with a positive stop. interdependent. If the squeezing tongs are used to extrude workpieces of different sizes (for example due to tolerances in the manufacture of the workpiece or the use of different types of workpieces), it must always be pressed up to the mentioned final dimensions of the dies. Regardless of the size of the workpiece, the total extrusion stroke is thus always the same, and the active pressing force is related to the workpiece size. This affects the uniformity and quality of the extrusion results in some cases. It is also possible that the components of the squeezing tongs will be damaged due to their overload until they break.

In this context, EP 0 732 779 B1 proposes a ball bolt that non-rigidly supports the pressure bar. In particular, according to EP 0 732 779 B1, the fastening handle is configured elastically in the region of the connection between the base body and the bearing half-shell. Thereby, the support half-shell can be compressed depending on the magnitude of the applied pressing force. The movement of the handles together can achieve this compression of the support half-shell without the further reduction of the cross-sectional area of the punch by the rotation of the swing ring relative to the base. Thus, for a larger workpiece, the final state of the forced stop can be achieved in accordance with EP 0 732 779 B1, in that the extrusion punch is first moved together in one stroke during a squeeze stroke. This extent is less than the extent of the motion of the extrusion punches that are combined with each other for smaller workpieces. The further movement of the handles together is then not caused by further movement of the pressing punches together, but rather to the elastic deformation of the fixed handle. It is also possible to superimpose the movement of the extrusion punch and the deformation of the fixed handle.

In order to ensure sufficient elasticity of the support of the support half-shell, the fastening handle is constructed with two handle parts which are connected to one another in a V-shaped manner in one end region. In the other end region, one handle part constitutes the support half-shell, while the end region of the other handle part is firmly connected to the base body of the jaws or constitutes the base body. Both handle components are constructed elastically. For this purpose, the handle part which forms the bearing half-shell is designed to be narrowed toward the bearing half-shell, while the other handle part has a certain degree of contraction so that it can be elastically deformed with the active hand force. The rigid connection area of the two V-shaped handle parts must be designed in such a way that the squeeze jaws can be manipulated by the user's hand in this connection area. According to EP 0 732 779 B1, the connection of the two handle parts via a form-locking connection takes place via a transverse pin and a longitudinally pressed projection. The effect of the elastic support in the region of the support half-shell by means of the pressure bar is also referred to as "force-stroke balance" in EP 0 732 779 B1.

A further prior art in the case of a clamping head having more than two pressing punches by means of a rotary oscillating ring, wherein the prior art of the nipper has been disclosed in the patent document DE 101 40 270 B4 and DE 10 2005 003 615 B3 In this case, the extrusion punches are not rotatably held on the base body, but are guided in a radially inwardly movable manner relative to the base body, and wherein different drives for actuating the jaws are used here. Kinematics device.

It is also proposed according to EP 0 158 611 B1 to elastically support the hinge point of the pressure bar on the fixed handle. Here, this is done by arranging the support pin carried by the pressure bar in the elongated hole of the fixed handle, wherein the support pin can be moved along the elongated hole under the loading of the helical spring.

DE 31 09 289 C2 likewise proposes to elastically support a pressure bar, here for a squeezing tong having a scissor squeeze jaw. In this case, the elastic support of the pressure bar is ensured in that the handle has a narrowing in the form of a slit in the region of the pivot point for the pressure bar, which narrowing leads to the branching of the fixed handle, accompanied by The reduction in the cross-section of the fixed handle material in this branching region. The reduction in the cross section of the material results in an elastic deformation of the fixed handle in the case of the acting pressing force.

SUMMARY OF THE INVENTION The object of the invention is to propose a pressure tong having an alternative or widening possibility for forming the squeezing force-extrusion stroke characteristic and/or having a force-stroke for squeezing workpieces of different sizes Balanced offering.

The object of the invention is solved according to the invention by the features of the independent patent claims. Further preferred embodiments according to the invention are obtained from the dependent patent claims.

The squeeze jaw according to the invention has a jaw. Clamp head forming with substrate and manipulation body. In order to generate a squeezing motion of the squeezing punch, the manipulating body can be moved relative to the base body. The fixed handle is firmly connected to the base. A movable handle (directly or indirectly) is hinged to the manipulating body. The movable handle is pivotably connected to a pressure bar via an elbow joint, which is in turn pivotably hinged to the fixed handle.

The invention proposes that, unlike the prior art explained at the outset, the retractability of the drive kinematics of the squeezing tongs is ensured in such a way that the hinge point of the pressure bar on the fixed handle is resiliently retractably constructed. (See EP 0 732 779 B1, EP 0 158 611 B1 and DE 31 09 289 C2), but rather the plunger itself is constructed to be retractable. This design can be simplified with respect to embodiments known from the prior art, since it is not mandatory: - the handle must be constructed with two handle parts which must be connected to each other in a V-shape and must be separately Elastically configured and must be equipped with a constriction, as is the case with EP 0 732 779 B1, the guiding of the oscillating bearing for the strut in an elongated hole must be carried out under the loading of the helical spring, like In the case of the case of EP 0 158 611 B1, the fixed handle must be equipped with a branch through the slit and a purposeful weakening, as is the case with DE 31 09 289.

Rather, the design of the fixed handle does not require special requirements in terms of the stiffness of the fixed handle. Retractability and force-stroke balance can be achieved according to the invention (at least also by selection - the length of the pressure bar; - the material of the pressure bar and its rigidity; - the cross section of the pressure bar and its cross section; and / or - the geometry of the pressure bar.

It is predetermined in structure. In this case it can be considered that the pressure bars with different retractability can be used for different squeeze jaws, while the other components of the squeeze jaws, in particular the fixed handle, do not have to be changed. In this way, it is possible in the scope of the invention to also provide a press tong for different purposes of use by replacing the pressure bar alone.

In principle, it is possible to use the jaws of the clamping jaws and to manipulate any structure of the kinematic device. It is also entirely feasible that there are only two extrusion punches in the jaws, in which case there are also two die halves under certain conditions, which remain in the base and the manipulator or in the base and The manipulator is integrally constructed. For a particular application of the measure according to the invention, the squeeze jaws have at least three squeeze punches which are supported relative to the base of the jaws in such a way that they can move radially inwards. The movement can be a pivoting of the pivoting support which is fixed to the base body (see EP 0 732 779 B1) or a radial movement (see DE 10 2005 003 615 B3, DE 10 2011 052 967 B4 and DE 101 40 270 B4). ). In this case, the actuating body is embodied as a pivoting ring that is rotatable relative to the base body. The oscillating ring has grooves or raised surfaces through which the squeezing punches can move radially inwards as the oscillating ring rotates.

The mechanical load of the pressure bar can be arbitrary as long as the mechanical load causes the pressure bar to be repellent. For example, it is conceivable that the pressure bar is elastically configured in its longitudinal direction such that when the pressure bar is loaded, the pressure bar changes its length due to the active positive stress. In a particular embodiment of the invention, the pressure bar is constructed with a curved handle. The curved shank construction of the pressure bar results in: acting on the hinge point of the pressure bar on the two handles The force force not only results in a pure load of the pressure bar with a positive stress, which acts in the direction of a longitudinal axis which connects the aforementioned joint points to one another. Specifically, the curved shank construction of the pressing rod causes the pressing rod to undergo bending, wherein the bending load is related to the degree of bending of the pressing rod. The retractability of the pressure bar can be specified in a structurally targeted manner by selecting the cross section of the pressure bar, the elastic modulus of the pressure bar, the course of the pressure bar and the bending shank and the inertia area moment. It is also possible to set the retractability by the structural setting of the buckling behavior, under certain conditions until a non-linear repellent behavior is set, which is caused by the bending load and the superposition of the load with the longitudinal force. The handle is obtained. It is also entirely feasible that the retractability of the pressure bar according to the invention is obtained by a superposition of different mechanical load types.

In principle, it is also possible to prevent automatic resetting of the squeezing tongs from the closed state that has been reached, so that the reset must be caused manually. If an automatic reset in the opening direction is desired, this automatic reset can be performed by a return spring that loads the handle directly or indirectly in the opening direction. In principle, the repositioning spring can be arranged in any position on the kinematic device and between any component. For a particular embodiment of the invention, a spring foot of the return spring is supported in the region of the elbow joint on the movable handle, preferably on the elbow joint itself. In contrast, the other spring foot of the return spring is supported on the fixed handle.

It is possible that the squeezing tongs are not configured with a positive stop, such that the manipulation of the squeezing tongs raises the need for increased use of compactness and the user observes the resulting squeezing stroke and/or Estimate the hand force to terminate the extrusion process. However, for an advantageous embodiment, the squeezing tongs according to the invention are equipped with a positive stop device, thereby ensuring a careful execution of the squeezing process up to a defined final state. In this case, it is preferred according to the invention The final state is related not only to the relative movement of the manipulator relative to the base, ie to the total squeezing stroke of the ram, but also to the elastic bounce distance of the retractable ram, wherein There may be a structurally predetermined correlation between the mentioned influence parameters.

According to another aspect of the invention, a rod extends through the return spring, which can be used to guide the return spring and, for example, to prevent buckling of the return spring. In the context of the invention, the lever can be embodied in a multi-functional manner in that the lever is equipped with a toothing, with which the positive stop can then be formed. This results in a particularly compact design and/or a reduction in the required mounting elements under certain conditions.

It is entirely feasible that the pressure bar extends between the two handles for all possible operating states of the handle. In a further embodiment of the invention, a particularly compact design and a widening of the possibility of the pressure lever bending and the configuration of the kinematic device of the toggle transmission are obtained, according to which the movable handle has a A notch that is open in the direction of the fixed handle. The plunger can enter the open notch as the handle is closed (completely or only partially). In order to mention only one non-limiting example, the handle can be formed in the region of the pressure bar with two plates with a spacing between the two plates, the gap being formed between the two plates, the pressure bar entering with the handle closed In the gap. It is also possible for the fastening handle to form a U-shaped cross section in the region of the pressure bar, wherein the gap is then formed between the two parallel legs of the U, into which the pressure bar can enter.

In principle, there are various possibilities for the course of the central axis of the pressure bar. In order to mention only some non-limiting examples, the pressure bar may have a central axis consisting of straight segments that are inclined relative to each other or have a curved course (with or without at least one turn point). For an aspect of the invention, the plunger bending handle increases from the elbow joint toward the fixed handle, preferably with no transition points and with a continuous increase. Engaging the pressure bar in the In the region of the oscillating support on the fixed handle, the central axis forms an angle a of at least 90 with the longitudinal axis of the fixed handle.

It is also possible for the bending central axis of the pressure bar to be connected to the longitudinal axis of the pressure bar (the longitudinal axis connecting the elbow joint to a pivoting support by means of which the handle is articulated The handle has a maximum spacing of at least 1.5 cm, preferably at least 2 cm or at least 2.5 cm. In this case, the load of the pressing bar with the bending moment increases with the increased maximum spacing because the lever arm of the force acting on the hinge point of the pressing bar becomes larger as the pitch becomes larger.

In another refinement of the invention, a connecting axis between the die axis of the die and the oscillating support in which the movable handle is hinged on the oscillating ring and the die and the The angle formed between the connection axes between the midpoints of the free ends of the fixed handles is greater than 50°, in particular greater than 55°, 60° or 65°.

It is entirely possible that a die formed by a plurality of extrusion punches is arranged substantially centrally between the extensions of the two handles in the region of the jaws. However, for a particular aspect of the invention, the die formed by the plurality of extrusion punches is eccentric, i.e., disposed in the extension of the fixed handle. This makes it possible to increase the distance between the articulation point of the movable handle on the actuating body, in particular the oscillating ring, and the die, whereby the force transmitted by the articulation point has an enlarged lever arm, so that It can eventually cause an increase in the pressing force and/or can provide a very compact jaw.

In a further refinement of the invention, the spacing between the pivoting support of the movable handle that is articulated on the oscillating ring and the longitudinal axis of the die is 30 mm. A spacing between the oscillating support and the elbow joint that articulates the movable handle on the oscillating ring is 14.5 mm. The elbow joint and the swinging branch for articulating the pressure bar on the fixed handle The spacing between the parts is 80mm. However, it is also possible for at least one of the distances to differ from the described distance by a maximum of 20%, in particular by a maximum of 10% or 5% (wherein the deviation of the individual distances can be the same or different).

For another aspect of the invention, for an open handle, the two handles have a pitch of 118 mm at 30 mm from their free ends. For a closed handle, the two handles have a 41 mm spacing at 30 mm from their free ends. However, it is also entirely possible that at least one of the spacings differs from the stated spacing by a maximum of 20%, in particular by a maximum of 10% or 5%. For this design, good hand maneuverability is achieved for different hand sizes of users of different hand sizes.

Advantageous developments of the invention are obtained from the patent claims, the description and the figures. The advantages mentioned in the description of the features and the combination of the features are merely exemplary and can alternatively or cumulatively function without necessarily having to obtain advantages by embodiments according to the invention. Without departing from the subject matter of the appended patent claims, the prior application file and the disclosure of this patent apply as follows: from the drawings (particularly from the illustrated geometrical and relative geometrical dimensions of the plurality of components) And other features are derived from their relative arrangement and interaction. Combinations of features of different embodiments of the invention or combinations of features of different patent claims may likewise be different from the selected references of the patent claims and are thus inferred. This also relates to features which are shown in a plurality of separate figures or mentioned in their description. These features can also be combined with features of different patent claims. The listed features may also be removed in the patent claims for other embodiments of the invention.

The features mentioned in the claims and the description are to be understood in terms of their number such that there are only a large number of these numbers or more than the mentioned number, without the need The explicit use of the adverb "at least". When, for example, a return spring is mentioned, this can be understood by the fact that there is exactly one return spring, two return springs or more. The features may be supplemented by additional features or they are the only features from which the corresponding finished product is produced.

The reference signs included in the claims are not intended to be limited by the scope of the claimed subject matter. They are only used for the purpose of making the claims easier to understand.

1‧‧‧Squeezing forceps

2‧‧‧ clamp head

3‧‧‧handle

4‧‧‧handle

5‧‧‧Manipulation of kinematics

6‧‧‧Toggle lever transmission

7‧‧‧ base

8‧‧‧Manipulator

9‧‧‧ Die axis

10‧‧‧ gap

11‧‧‧ slot

12‧‧‧Swing pin

13‧‧‧Extrusion punch

14‧‧‧ die face

15‧‧‧ die

16‧‧‧Swing support

17‧‧‧Swing support

18‧‧‧Press

19‧‧‧Swing support

20‧‧‧Toggles

21‧‧‧Toggles

22‧‧‧Return spring

23‧‧‧Spring foot

24‧‧ ‧ spring foot

25‧‧‧ elbow joint

26‧‧‧ pole

27‧‧‧ teeth

28‧‧‧Forced stop device

29‧‧‧ Spring

30‧‧‧stop claws

31‧‧‧ longitudinal axis

32‧‧‧ center axis

33‧‧‧Cut handle

34‧‧‧Swing ring

35‧‧‧ Sections

36‧‧‧ gap

37‧‧‧ longitudinal axis

38‧‧‧ spacing

39‧‧‧connection axis

40‧‧‧ spacing

41‧‧‧ spacing

42‧‧‧ spacing

43‧‧‧connection axis

The invention is further illustrated and described below in accordance with the preferred embodiments illustrated in the drawings.

Figure 1 shows a schematic sketch of a squeeze jaw according to the invention in an open state; Figure 2 shows the squeeze jaw according to Figure 1 in a closed state; Figure 3 shows the opening A front view of a structural design of the squeezing tongs in the state; Figure 4 shows the squeezing tongs according to Figure 3 in a closed state.

The squeezing tongs 1 according to the invention are shown schematically in FIGS. 1 and 2, wherein the imaginary, invisible edge slanting lines are shown here. It is possible that the squeezing tongs 1 are manufactured in a plate structure.

The squeeze jaw 1 has a clamp head 2. The actuation of the squeezing tongs is carried out by means of a manual actuating of the handles 3 , 4 , wherein an actuating kinematic device 5 is connected between the handles 3 , 4 and the caliper 2 , which is embodied as a toggle drive 6 .

For the illustrated embodiment, the jaw 2 is formed with a base body 7 and a manipulating body 8, The base body and the actuating body are each configured in a plate shape. For the embodiment shown, the operating body 8 is constructed as a oscillating ring 34. The base body 7 is rigidly connected to the handle 3, which is therefore also referred to as a "fixed handle". For the embodiment shown, the base body 7 and the handle 3 are formed in one piece in the form of a plate, in particular as a stamping. With respect to the base body 7, the manipulating body 8 is rotatable about the die axis 9 in the plane of the drawing, the die axis being oriented perpendicular to the plane of the drawing. The manipulating body 8 has a continuous indentation 10 having a circular profile with grooves 11 extending radially outwardly and evenly distributed over the periphery, thereby forming a splined shaft section. For the embodiment shown, the manipulating body 8 has six such slots 11. Here, the six pivot pins 12 are likewise distributed evenly on the periphery of the die axis 9, their longitudinal axes being oriented perpendicular to the plane of the drawing of FIG. 1 and they are carried by the base body 7. In the plane of the drawing, six extrusion punches 13 are mounted in a pivotable manner in the plane of the drawing. The extrusion punch 13 constitutes a die face 14 by means of a beveled end face which is built in the radial direction. The die faces 14 of the extrusion punch 13 collectively form a die 15 which substantially circumferentially surrounds the die axis 9, the cross section of which corresponds in the present case to having the same side length Hexagonal. The cross-sectional area of the die 15 decreases as the squeeze punch 13 swings clockwise. In the region of the end opposite the die face 14, the pressing punches 13 are each situated in the receiving portion in the associated groove 11. These grooves 11 form a type of carrier for squeezing the punch 13, so that the rotation of the manipulating body 8 causes the pressing punches 13 by the contact of the mentioned end regions of the punching punch 13 with the grooves 11. Co-swing at the same swing angle. As a result, the extrusion of the workpiece arranged in the die 15 can be carried out as a result of the reduction of the cross-sectional area of the die 15 with the rotation of the manipulating body 8 relative to the base body 7.

The design of the previously described and illustrated in the figures of the clamping head 2 is only exemplarily selected, wherein an additional design of the clamping head 2 can also be used in the context of the invention. The scheme, for example, is based on the prior art cited at the outset; - the steering projection having the replacement groove 11; - the freedom of movement of the extrusion punch 13 capable of swinging guidance, and the like.

It is also entirely possible for the clamping head 2 to be configured for a different extrusion process, for example a different number of extrusion punches, wherein only two extrusion punches or die halves can be present and also A stamping halves can be formed by the base body 7 and a stamping halves can be formed by the actuating body 8 , which in this case do not rotate relative to each other, but can move relative to one another in the direction of the extrusion stroke.

The generation of the relative movement of the operating body 8 relative to the basic body 7 takes place via the toggle transmission 6. For this purpose, the handle 4 is hinged to the pivot bearing 16 on the actuating body 8 in the region of the end facing the clamping head 2 . The handle 4 is also referred to as a "movable handle" for this reason. Slightly spaced from the oscillating support member 16, a pressure bar 18 is hinged to the oscillating support member 17 on the handle 4. The other end region of the pressure bar 18 is hinged in the oscillating support 19 on the handle 3. The oscillating bearing 17 in this case forms an elbow joint 25 for the toggle 20 which is formed by the handle 4 in the region between the oscillating supports 16 , 17 and which is used for the toggle 21, the toggle lever is composed of a pressure bar 18. The two toggle levers 20, 21 form an obtuse angle in the open state according to Fig. 1, the obtuse angle having, for example, an angle in the range of 130°, 140° or 150° ± 10%, and the two toggle levers are shown in the figure. 2 Approaching as the handles 3, 4 of the extended position are closed.

Alternatively, the squeeze jaw 1 can be loaded in the opening direction by a return spring 22, whereby an automatic induction of the opening movement can be achieved at the end of the total stroke of the squeeze jaw 1. For the illustrated embodiment, the return spring 22 acts between these handles 3, 4. Here, the spring feet The point 23 is supported on the elbow joint 25, while the other spring foot 24 of the return spring 22 is supported on the handle 3, preferably directly adjacent to the jaw 2 or the manipulating body 8. Preferably, the return spring 22 is oriented substantially perpendicular to the longitudinal axis 37 of the handle 3.

For the embodiment shown, the lever 26 , which is likewise articulated in the elbow joint 25 , extends through the interior of the return spring 22 , which is embodied here as a helical spring. The rod 26 has a toothing 27 on its underside. The positive stop 28 is formed by the toothing 27 of the rod 26. The forced stop device 28 has a stop pawl 30 that is pivotably supported relative to the handle 3 and is loaded by a spring 29. As the handle is closed, the pawl 30 slides pawlly along the tooth portion 27 of the rod. If the hand force applied to the handles 3, 4 is temporarily reduced, the pawl 30 secures the position of the rod 26 in the forced stop 28 by being inserted into the toothing 27 of the rod 26, thereby also The state of the handles 3, 4 is insured and the closed state of the die 15 is maintained. This makes it possible to insure the extrusion level reached at one time. With the predetermined final state of the lever 26 in the forced stop 28, the stop action of the positive stop 28 is released by the proper configuration of the tooth 27 and the pawl 30, thereby enabling the squeeze The opening movement is achieved at the end of the pressing process. However, it will be apparent to those skilled in the art that the basic principles of the present invention are not mandatory to use with the use of a forced stop, a repositioning spring, and/or the use of the rod 26.

It is assumed that the handles 3, 4 and the pressure bar 18 (for the pressure bar 18, this assumption is different from the configuration according to the invention) is rigid, the closing movement of the handles 3, 4 causes the toggle gear 6 to move towards the extended position This causes the handle 4 to exert a force on the manipulating body 8 by means of the oscillating bearing 16 which has at least one component which is circumferentially opposed to the die axis 9 and thereby causes the die 15 to close. For the mentioned assumptions of the rigid part, the closed state of the squeezing tongs interacts with the fixed predetermined final cross section of the ram 15 , which can lead to the problems explained at the outset. In order to correct this, it is proposed according to the invention that the pressure bar 18 is constructed to be retractable. This is understood to be any repellent which results in the deformation of the pressure bar 18 in the manner in which the usual hand force is applied to the handles 3, 4, i.e. the distance between the elbow joint 25 and the oscillating support 19 is due to this deformation. And change to a significant extent. To suggest only a few non-limiting examples, the spacing of the elbow joint 25 from the swing support 19 can vary by at least 0.5 mm, at least 1 mm, or at least 1.5 mm. The provision of the retractable pressure bar 18 according to the invention has the following differences to the extrusion process depending on the design of the workpiece arranged in the die 15 (especially depending on the cross-section and/or rigidity of the workpiece) influences:

- For a sufficiently small and/or soft workpiece, the closing of the die 15 can take place over the entire circumference without significant deformation of the pressure bar 18. Correspondingly, the pawl movement of the toothing 27 of the lever 26 relative to the pawl 30 is caused by the closing movement of the die 15.

- At the other extreme consideration, it should be assumed that in the open state according to Fig. 1, the die 15 is completely filled with a workpiece of a desired rigidity. In this case, regardless of the magnitude of the force generated by the toggle transmission 6 and transmitted to the operating body 8, the relative rotation of the operating body 8 relative to the basic body 7 is not performed and the closing of the die 15 is not performed. Specifically, the sequential increase in the pressing force applied to the handles 3, 4 only results in elastic deformation of the pressure bar 18. As the spacing between the elbow joint 25 and the oscillating bearing 19 is reduced, the toggle gear 6 is also close to the extended position and the handles 3, 4 can be moved together relative to one another. This also causes a pawl-like relative movement of the toothing 27 of the rod 26 relative to the pawl 30. For a sufficiently large actuating force applied to the handles 3, 4, a complete squeezing stroke can be reached and the final state predetermined by the positive detent 28 can be reached without changing the cross section of the ram 15. As the final state is reached, an opening movement can then be performed.

- for a practical situation in the case of using the present invention, according to arrangement in the die 15 The difference in the size of the workpiece and the resistance of the workpiece relative to the deformation not only causes relative rotation of the manipulating body 8 relative to the base body but also deformation of the pressing bar 18. Thus, in this case, not only the relative rotation of the manipulating body 8 with respect to the base body 7 but also the relative movement of the tooth portion 27 of the lever 26 with respect to the pawl 30 is obtained in connection with the deformation of the pressing bar 18. The relationship of the different contributions for this relative movement is related to the workpiece size and the rigidity of the workpiece: the larger the workpiece and the more rigid the workpiece, the deformation of the compression rod 18 on the relative movement of the tooth portion 27 of the rod 26 relative to the pawl 30 The bigger the share.

In the case of the illustrated embodiment, the pressure bar is formed with a thickening in the end regions, in the region of the thickening, a plurality of supports are formed in order to form the elbow joint 25 and the pivot bearing 19 . eye. The longitudinal axis 31 is used to indicate the line of connection between the elbow joint 25 and the oscillating support 19. In contrast, the central axis 32 represents the axis that is curved here following the contour of the plunger 18. For example, the central axis 32 represents the cross-sectional center axis of the axis or geometry referred to as the "neutral phase" in the mechanical device that is subjected to bending.

The pressure bar 18 has a curved handle 33. Starting from the toggle lever 25, the compression lever 18 is first constructed approximately linearly or with a small curvature. This bending continuously increases in the direction of the oscillating support 19 with an increasing degree of reinforcement. For the illustrated embodiment, the pressure bar 18 is approximately configured in the form of a "hockey stick" in which the elbow joint 25 is arranged in the region of the "handle" and the pivot bearing 19 is arranged at the end of the "hitting surface" In the area. Due to the curved shank 33, the force acting along the longitudinal axis 31 causes the pressure bar 18 to undergo bending which is applied by the handles 3, 4 to the pressure bar 18. In addition to the thickened portion mentioned, the cross section of the pressure bar continuously increases from the elbow joint 25 toward the swing support 19 .

It can be seen in FIG. 2 that for the closed handles 3 , 4 a partial section 35 of the pressure bar is arranged superposed relative to the handle 4 . For example, a handle 4 having two parallel, spaced apart plates can be formed, wherein a notch 36 is formed between the two plates, the portion of the handle 18 Section 35 can enter the gap as the handles 3, 4 are closed. However, it is also entirely possible for the handle 36 to be embodied in a C-shape or a U-shape in cross section, wherein the recess 36 is formed between parallel legs of C or U, the recess being oriented such that the partial section 35 It can enter the gap 36 with a closing motion. As can be seen in Figure 2, the partial section 35 into the gap 36 can be more than half of the plunger 18.

For the illustrated embodiment, the bending of the central axis 32 is such that, at least in the open state shown in Figure 1, the angle of the central axis in the oscillating bearing 19 relative to the longitudinal axis 37 of the fixed handle 3 is More than 90°. The course of the pressure bar 18, in particular the bending of the central axis 32, is such that a maximum distance 38 is obtained between the central axis 32 and the longitudinal axis 31, for example at least 1.5 cm, preferably at least 2 cm or at least 2.5cm.

The connecting axis 39 between the die axis 9 and the oscillating bearing member 16 forms an angle ß with a connecting axis 43 which connects the free end of the fixed handle 3 or its midpoint to the die axis 9. The angle ß is preferably greater than 50°, in particular greater than 55°, 60° or 65°.

The preferred geometric relationship on the nippers is shown in Figures 3 and 4. In this case, the covered edges in Figures 3 and 4 are likewise shown. The die 15 is arranged substantially in an extension of the longitudinal axis 37 of the handle 3. In particular, the distance 40 between the die axis 9 and the longitudinal axis 37 is at most less than 8 mm, in particular less than 5 mm or 3 mm.

In the open state of the handles 3, 4 according to Fig. 3, the handles have a spacing 41 of 118 mm spaced 30 mm from their free ends. In contrast, the corresponding spacing 42 according to Figure 4 is only 41 mm. However, it is entirely feasible that one of the mentioned spacings 41, 42 is at most 20%, in particular at most 10% or 5%, deviating from the stated dimension setting.

Furthermore, it can be recognized that the metallity according to the embodiment shown in FIGS. 3 and 4 The handles 3, 4 are each received in a receiving area made of plastic in the area loaded by the user's hand, which are adapted to the contact of the user's hand in terms of contour and elasticity. It is clear from FIG. 4 that for this design, the partial section 35 also enters the notch 36 of the handle 4 (and the receiving body made of plastic) as the handle is closed.

In order to ensure a good conversion of the hand force in the squeeze tongs 1, the angle between the connecting axis of the oscillating supports 16, 19 and the connecting axis 39 should be at least approximately close to the closed state of the handles 3, 4. It is 90°, wherein the angle can also be offset by 90° by ±5°, for example ±3°.

The oscillating support 19 is arranged in the lower half of the handle which is measured from the caliper 2. For example, the swing support 19 is spaced from the free end of the handle 3 by less than 7 cm, such as less than 6 cm or less than 5 cm.

Preferably, the movement of the oscillating support 16 during the closing movement of the handle (without significant deformation of the plunger 18) is approximately 5.5 mm. In this case, a hand distance of 30 mm from the end of the handles 3, 4 should pass through a stroke of approximately 80 mm. For the two requirements mentioned, that is, the stroke of the oscillating support member 16 and the stroke of the hand distance are obtained under certain conditions: the pitch of the oscillating support members 16, 17 is approximately 14.5 mm, and the oscillating support The spacing of the pieces 17, 19 is preferably 80 mm, wherein it is also possible to deviate from these size settings by ±20%, for example ±10% or ±5%.

1‧‧‧Squeezing forceps

2‧‧‧ clamp head

3‧‧‧handle

4‧‧‧handle

5‧‧‧Manipulation of kinematics

6‧‧‧Toggle lever transmission

7‧‧‧ base

8‧‧‧Manipulator

9‧‧‧ Die axis

10‧‧‧ gap

11‧‧‧ slot

12‧‧‧Swing pin

14‧‧‧ die face

15‧‧‧ die

16‧‧‧Swing support

17‧‧‧Swing support

19‧‧‧Swing support

20‧‧‧Toggles

24‧‧ ‧ spring foot

25‧‧‧ elbow joint

28‧‧‧Forced stop device

29‧‧‧ Spring

30‧‧‧stop claws

32‧‧‧ center axis

33‧‧‧Cut handle

34‧‧‧Swing ring

37‧‧‧ longitudinal axis

38‧‧‧ spacing

43‧‧‧connection axis

Claims (22)

a squeezing tong (1) having: a) a nipper (2) having a base body (7) and a manipulator body (8), said manipulator body being capable of being said to produce a squeezing motion a base (7) movement; and b) a fixed handle (3) and a movable handle (4), the fixed handle being securely coupled to the base body (7), the movable handle being hinged to the On the operating body (8); and c) wherein the movable handle (4) is swingably connected to a pressing rod (18) via an elbow joint (25), the pressing rod can be pivotally hinged The fixed handle (3) is described, and d) the pressure bar (18) is configured to be retractable. The pressing tong (1) according to the first aspect of the patent application, characterized in that the pressing rod (18) is constructed with a curved shank (33). The pressing tong (1) according to the first aspect of the patent application, characterized in that a) at least three pressing punches (13) are movable radially inward relative to the base body (7), b The manipulating body (8) is configured as a oscillating ring (34) rotatable relative to the base body (7), the oscillating ring having grooves (11) or raised surfaces through which the grooves or raised surfaces follow The rotation of the oscillating ring (34), the extrusion ram (13) can move together radially inward. A squeezing tong (1) according to any one of claims 1 to 3, characterized in that a reset spring (22) loads the handles (3, 4) in the opening direction. The squeeze tong (1) according to the fourth aspect of the patent application, characterized in that a) a spring foot point (23) of the return spring (22) is supported in the region of the elbow joint (25) On the movable handle (4), and b) the other spring foot point (24) of the return spring (22) is supported on the fixed handle (3) Upper. A squeezing tong (1) according to any one of claims 1 to 3, characterized in that there is a forced stop device (28). The squeeze tong (1) according to the fifth aspect of the patent application is characterized in that a forced stop device (28) is present. A squeezing tong (1) according to claim 7 of the invention, characterized in that the rod (26) extends through the return spring (22), wherein the rod (26) is provided with a tooth (27) The forced stop device (28) is formed by the tooth portion. The squeeze tong (1) according to any one of the preceding claims, wherein the movable handle (4) has a gap open toward the fixed handle (3) (36), the pressing rod (18) partially enters the notch as the handle (3, 4) is closed. The pressing tong (1) according to any one of the preceding claims, wherein the pressing rod (18) has a partial section (35) for closing The handle (3, 4) is oriented parallel to the longitudinal axis of the movable handle (4) or arranged to overlap the movable handle (4). The pressing tong (1) according to claim 9 is characterized in that the pressing rod (18) has a partial section (35) for the closed handle (3, 4) The orientation is parallel to the longitudinal axis of the movable handle (4) or is arranged to overlap the movable handle (4). The pressing tong (1) according to the second aspect of the patent application, characterized in that the bending shank (33) of the pressing rod (18) is from the elbow joint (25) toward the swinging support member (19). Increase direction Big. The pressing tong (1) according to claim 12, characterized in that the pressing rod (18) has a curved central axis (32), the curved central axis a) is at the pressure a rod (18) hinged in the region of the oscillating support (19) on the fixed handle (4) to form an angle a of at least 90 with the longitudinal axis (37) of the fixed handle (3), and / or b) having a maximum spacing (38) of at least 1.5 cm, preferably at least 2 cm or at least 2.5 cm with respect to the longitudinal axis (31) of the pressure bar (18), the longitudinal axis causing the elbow joint (25) The oscillating bearing (19) is connected, and the ram (18) is hinged to the fixed handle (3) by means of the oscillating bearing. A squeezing tong (1) according to claim 1, 2, 3, 12 or 13 of the patent application, characterized in that, in a) the die axis (9) and the movable handle (4) are a connecting axis (39) between the swinging support members (16) hinged on the operating body (8) and b) a midpoint of the free end of the fixed handle and the die axis (9) The angle ß formed between the connecting axes (40) is greater than 50°, in particular greater than 55°, 60° or 65°. The pressing tong (1) according to claim 1, 2, 3, 12 or 13 of the patent application, characterized in that the dies (15) are arranged in an extension of the fixed handle (3). The pressing tong (1) according to the invention of claim 14, characterized in that the dies (15) are arranged in an extension of the fixed handle (3). Squeeze tongs (1) according to the scope of claim 1, 2, 3, 12 or 13 of the patent application, characterized Wherein a) the movable handle (4) is hinged to the swing ring (34) by the swing support (16), the spacing between the swing support and the die axis (9) 30 mm, b) the movable handle (4) is hinged to the swing ring (34) by the swing support (16), between the swing support and the elbow joint (25) a spacing of 14.5 mm, and c) a distance between the elbow joint (25) and the oscillating support (19) that articulates the pressure bar (18) on the fixed handle (3), Or at least one of the spacings differs from the stated spacing by at most 20%, in particular by a maximum of 10% or 5%. A squeeze tong (1) according to the fifteenth aspect of the patent application, characterized in that a) the movable handle (4) is hinged to the swing ring (34) by the swing support (16) Above, the spacing between the oscillating support and the die axis (9) is 30 mm, b) the movable handle (4) is hinged to the oscillating ring (34) by the oscillating support (16) The distance between the oscillating support and the elbow joint (25) is 14.5 mm, and c) the elbow joint (25) and the pressure rod (18) are hinged to the fixed handle ( 3) The spacing between the upper oscillating supports (19) is 80 mm, or at least one of these spacings is offset by a maximum of 20%, in particular by a maximum of 10% or 5%, from the stated spacing. A squeeze tong (1) according to claim 16 of the invention, characterized in that a) the movable handle (4) is hinged at the swing by the oscillating support (16) a ring (34), a spacing between the oscillating support and the die axis (9) is 30 mm, b) the movable handle (4) is hinged by the oscillating support (16) On the oscillating ring (34), the spacing between the oscillating support and the elbow joint (25) is 14.5 mm, and c) the elbow joint (25) is hinged to the pressure rod (18) The spacing between the pivoting supports (19) on the fixed handle (3) is 80 mm, or at least one of these spacings is offset by a maximum of 20%, in particular by a maximum of 10% or 5%, from the described spacing. A squeeze tong (1) according to claim 1, 2, 3, 12 or 13 of the patent application, characterized in that a) for the open handle, the two handles (3, 4) are at a distance from them The free end 30mm has a pitch of 41mm (41), b) and for a closed handle, the handles have a 41mm spacing (42) 30mm from their free end, or in these spacings At least one of the spacings differs from the stated spacing by a maximum of 20%, in particular by a maximum of 10% or 5%. The squeezing tongs (1) according to the fifteenth aspect of the patent application, characterized in that a) for the open handle, the two handles (3, 4) have 118 mm at 30 mm from their free ends The spacing (41), b) and for the closed handle, the two handles have a 41 mm spacing (42) 30 mm from their free ends, or at least one of these spacings is the most spaced 20% deviation, especially the most More deviations of 10% or 5%. The squeezing tongs (1) according to claim 18, wherein a) for the open handle, the two handles (3, 4) have 118 mm at 30 mm from their free ends The spacing (41), b) and for the closed handle, the two handles have a 41 mm spacing (42) 30 mm from their free ends, or at least one of these spacings is the most spaced The deviation is 20%, especially the maximum deviation is 10% or 5%.