JPS60217014A - Shearing tool for cutting continuous rod shaped body - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] The present invention has two shearing forces, at least one of which is configured in the shape of a disk, and revolves around an intangible rotating shaft provided in a direction transverse to the plane of the disk. is supported axially and radially in an annular guide member concentric therewith and rotatably supported against the other shear force, with the result that both of these shear forces can be closed or completely closed. A cutting machine, especially manually, for cutting a continuous rod, such that each cutting edge forming an aperture that can be directly approached or guided through said intangible axis of rotation. Regarding the formula cable cutter.

In conventional technology cable cutters and similar shear shears, especially manual lever shears that must cut with very smooth and clean cuts, the shear forces push them axially apart from each other at the beginning of the cut. It is especially commendable to not be. Such hazards arise when both shearing forces are usually configured as double lever levers to effect the cut at their respective forward ends and their respective rearward ends pivoted about a central axis of rotation. It's especially big because it looks like this. In order to prevent the free ends of the helical recruits from being forced apart, a bracket has been previously provided at the shear force on one side to enclose the shear force on the other side. Efforts have been made to provide an effect that counteracts the spread. In another known construction, each shear force is retained in each annular guide member at a portion of its outer circumference on both sides of its shear aperture, which each carry a variable axial force of about 90 It is adapted to be received by a large surface that covers an angle of .degree. (German Patent Application No. 2,516,754).

In this case, however, the bearings known from the various conventional helicoids are bolted, although in this case each blade of the helix is additionally radially supported on its outer periphery in a respective annular guide member. is provided in the axis of rotation, thereby requiring that a perforation opening defined by the shear edges of both shear forces be provided at a radial distance from the axis of rotation. The effective length of the lever arm in the cutting thereby significantly increases the strength and first of all the drive force to be applied or the rotational moment required, and with it the dimensions of the shearing head as well as the drive power to be used. and the size of the force transmission gear, which ultimately determines its manufacturing cost.

According to German Patent No. 8711056, two devices are provided, each of which has a cutting aperture open towards the edge, which are rotatably guided relative to each other and which are connected to an operating lever arm. Manual lever shear recruits with disc-shaped shear forces are known. In this case, each shearing aperture has a narrowed inner end for noiselessly cutting steel wire and an outwardly widening part for cutting wire rope. have. The cutting blades are guided closely together in their outer parts, but have an intermediate spacing in their inner converging parts which project into their common axis of rotation. Therefore, here relatively thick external parts need to be cut externally using a larger lever arm length.
The relatively small parts are not cut smoothly, but are crushed internally to reduce noise. Both require an undesirable waste of force, which also makes the recruits relatively heavy and expensive.

Problems to be Solved by the Invention The purpose of the present invention is to provide a cutting machine of the type mentioned at the beginning of the text, which is compact and lightweight, with a given cutting performance, and which is slightly smaller than those of known construction. It is configured so that it can be operated by force.

Means for solving the problem In order to achieve this object, according to the invention an actuating device is provided for at least one shear force) and an actuating device is provided for this shear force by this. The present invention is constructed and equipped so that the acting force applied thereto is directed toward approximately the center of the object to be cut which is confined within the opening.

According to another proposal of the invention, the shearing head enclosing both shearing forces is fastened in a holder provided with an actuating device so as to be exchangeable with different shearing heads of other construction and/or size. to be done. In principle, therefore, only one holder can be used and then, if required, various shearing heads for different materials can be attached to it.

According to another proposal of the invention, the second shearing force provided inside the first shearing force is formed as an arcuate portion having a maximum width matching the opening width of the first shearing aperture. It has a protrusion extending from its guide. In principle, such a protrusion could be made to remain firmly connected to the internal shear force after it has been fitted, e.g. by gluing, brazing or otherwise, but advantageously, however, this does not require removal. It is preferable that the shear be removably attached so that the shearing force can be removed and the shear can be replaced.

This projection is preferably designed as a holder plate with a flange overlying the second shear force, which is preferably mounted between the cutting blade and the connecting flange of the holder. .

Action: At least at the end of the shearing process, all the objects to be cut are increasingly moved toward the axis of rotation, and the acting force of the shearing force on the driven side is
It is aimed directly at the object to be cut which is confined within the aperture. In this case, the base of the cutting opening is provided with a slight distance from the rotating shaft, and the tightening allowance is adjusted accordingly.
It may also be advantageous to leave some core behind to ensure that peeling is prevented.

The larger the width of the aperture is selected, the larger the arm rotation angle required, which results in a uniform and extremely smooth sheared surface even when the material cross-sectional area is large. Depending on the type of material to be cut, the shear edge can correspondingly be formed as follows, i.e. pressed over a relatively small length at the beginning of the cut, where the greatest possible rotational moment is to be exerted. A crushing cut is made, or a pulling cut is made with a large protection length, which is only then directed towards the core - C so that it gradually transitions to the crushing cutting mode. be able to.

As a result, the final stage of the shearing process is crushed and the gap is not enlarged, and the gap can be formed softly and without impact. Moreover, here the frictional forces between the two shear force contact surfaces, especially on their outer circumferential surfaces, are virtually canceled out. The applied driving force is converted almost optimally with high efficiency, which in addition to the relatively small primary work
It also enables the fabrication of extremely lightweight shearing materials with correspondingly large shearing performance. The radial support of the annular guide means for at least one of the shear forces is arranged obliquely to its axis of rotation such that the shear forces are pressed against each other by a shear reaction force, inter alia in a trapezoidal manner. It would be particularly advantageous to form. In this way, possible play tolerances caused by manufacturing inaccuracies K can be avoided, and the shearing force disks can be counteracted by being pushed apart from each other. The post-polishing process is achieved by a constant mutual pressing action on this radial cutting surface, and this pressing force is very proportional to the cutting resistance, i.e. when opening the cutting surface. It disappears significantly.

According to one preferred embodiment of the invention, the movable shearing force has an annular flange formed on either side of the shearing force disk, into which the actuating device engages from the outside, and which engages from the inside. The annular flange has a guide for a fixed shear force maintained from the open side. This arrangement, with a fixed shear force held on one side, allows the opposite side of the movable shear force to remain completely free, so that it can cut close to various obstacles on the sides, or This provides the advantage that different actuation means can be connected to the movable shear force. Here, whether the fixed shear force is on the inside or the movable shear force is on the inside, the inner groove, which serves as a guiding member, is always limited by the removable arch-shaped foundation annulus. I can do that. By removing such a protruding annular member, which may be divided into several parts, the shear forces inside it can be freely extracted in the axial direction.

A gear cutter 9 is provided on the outer periphery of the movable shearing force so that a sequential engagement means that can be moved directly or indirectly toward the holder lever by rotating the pivot lever engages with this gear. can do. In order to widen this rotational stroke, the actuating device may have a pinion connected upstream of the movable shearing force, into which the operating and launching pawl engages.

The present invention further has two shearing forces, at least one of which can be rotated toward the other shearing force by a latch type operating device having a latch claw and an operating claw. Shear recruits whose pawls engage in said movable shear force-subject gear cutters and are supported on support members, among others rotatable levers, movable in opposite directions. related. In this case, a particularly simple and inexpensive control mechanism is obtained by a single tensioning spring K, which is provided between the two latch claws and acts in the engagement direction on this and its support member.

That is, this single spring has three functions and is, for example, formed in the form of a flexible compression spring, supported on its latches on different sides of its respective axis of rotation, in the event of the action of forces in opposite directions. Rotational pressure in the same direction can be obtained.

Finally, the invention still further provides at least one rotatably mounted movable shear force on which a releasable actuating device and a return spring act.
A shear recruiter for cutting a continuous rod-shaped object in the horizontal direction,
Among other things, it also concerns manual recruits. Conventionally, in the case of such a new recruit, the pullback was always performed in the opening direction.

However, if a movable shear force is provided which can be rotated through more than 180°, as is the case with this shear recruit according to the invention, the return spring has a line of action that can move beyond its axis of rotation. It is advantageous to bias the movable shearing force in one direction of rotation or another depending on the position of the object. If a rotation angle of approximately 180' is used for the cutting process, one or three further control steps push the movable shearing force beyond its dead center so that it now acts in the forward direction. It would be simple to release the return spring, which no longer exerts a force, so that this spring also pulls back the shear force in the first part of its travel range, opposite to its direction of rotation.

The return spring is advantageously a flexible tension spring connected on one side of the movable shear force so that it cantilevered from the opposite side. In this case, it is not a problem that the tension spring bends slightly to the side when it comes into contact with the sheared material near the end of the shearing process.

BRIEF DESCRIPTION OF THE DRAWINGS The accompanying drawings illustrate, by way of example, various embodiments of the invention.

The main part of the cable cutter shown in Figs. 1 to 5 is the holder lever 1, and the shearing head 2
is fixed, and rotatably supports a rotary lever 4 by means of a joint bolt 3. Lever 1
The lever 4 is made of a metal plate bent into a U-shape.

The essential part of the shearing head 20 is a movable shearing force 5, which is in the form of a flat cylindrical shearing force disk 6, with an annular flange 7 formed on one side of its periphery; is formed in the shape of a gear with a gear cutter 8 on the outside, and an annular groove 9 is formed on its inner surface, which is defined by a low protruding annular portion 11.

A shearing opening 12 is formed in this movable shearing force and opens outward in the radial direction, and the base 1 of this opening
3 has a semicircular shape 9, and a shear edge 14 and a support edge 15 extend parallel to each other from both sides thereof. This shear edge 14 rests on the shear surface 17 inside the shear blade disc 6, as best shown in FIG. The outer sliding surface 16 is also partially shown in FIG.

The fixed shear force 18 has the shape of an approximately semi-cylindrical disc, the outer peripheral edge 19 of which is guided in the annular groove 9. The shearing edge 21 with a fixed shearing force is shown in FIGS. 1 and 5. In the shearing opening position, the supporting edge 15
and extends along the aperture base 13 , where it is surrounded by the sliding surface 22 . Then, the shear edge 21 transitions to an end face 23 rising perpendicularly to the shear force plane (Fig. 4.5).

The dimensions of the fixed shear force 18 are chosen such that it can be guided as a whole through the shear opening 12 of the movable shear force and into the annular groove 9 of this.

However, due to the limited size of this shear opening 12, its circumferential angle is often insufficient for proper guidance, and the fixation of its fixed shear force also poses various difficulties. To improve this guidance and retention, a separate holder plate 24 is used, the thicker part 25 of which rests against the end face 23 of this in the plane of the fixed shear force, and the projection 26 The protrusion has the same thickness as the fixed shear force 18 and is fitted tightly into the annular groove 9.

A seven-rank section 27 protrudes from the thicker guide section of this, which overlies the fixed shear force 18 on the outside.

An upwardly projecting connecting flange 28 of the holder lever 1 is used to hold the fixed shear force 18 and the holder plate 24 together. Four holes 29 are provided in this connecting flange for screws 31 designed as socket head screws. In addition, two screw holes 32 are provided on the right side in FIG.
5 , two holes 33 are formed in their connecting flanges 21 , which are above the threaded holes 34 of this fixed shear force 18 . The fixed shear force is therefore applied in this part to the connecting flange 28 via the screw 31 and the intermediately arranged holder plate 24.
Fixed. This connection is complemented by a screw fixation in the guide section 250 section.

Moreover, the protrusion 26 enlarges the outer circumferential length of the peripheral guide of the movable shear force 5 to about 370°, so that the radial and axial direction on the outer circumference of the guide unit constituted by the fixed shear force and the holder plate 24 is Accurate and reliable guidance of the moving shear force is provided.

Among them, as can be seen from FIG. 1 and FIGS.
Similarly, this movable shear force extends through the solid axis of rotation 36 and tangent to the fixed shear force, at which point the lever arm length is zero and therefore, for a given rotational moment, the effective cutting The force approaches an infinite value, a convention further explained below with reference to FIGS. 6-9.

In order to drive the movable shearing force 5, an operating claw 3T supported by a shaft 30 is used at the rotating arm 4, and this holds the joint bolt 3 by fitting it into its play hole 38. , and its operating projection 39 cooperates with the movable shear gear tooth 8.

Into this same toothing 8 engages the free end of a latch pawl 41, which is fixedly seated on an axle 42 rotatably supported in the holder lever 1. This shaft projects outwardly at one end and is also rotatably mounted with an operating lever 43 which has an outwardly bent actuating plate 44 and an inwardly bent actuating plate 44 at its free end. It has a stop plate 46 which projects into the arcuate slit 45 in this direction. Therefore, the latch pawl 41 can be directly moved from the outside using the operating lever 43.

A spring 47, which is configured as a helical compression spring, is fitted at its ends into the boreholes of the winter melons 37 and 41, respectively, as follows: the claws are turned and moved counterclockwise. The movable shear force toothing 9 is fitted and held in part 8 and furthermore the holder lever 1
A force acting in the direction of rotation and removal is applied between the rotation lever 4 and the rotation lever 4. The recruit can therefore operate levers 1 and 4 with one hand simply by periodically pressing them together. In this case, the shaft 3
0 is the joint bolt 3 on the arcuate trajectory in the clockwise direction.
0 revolution, it moves in the shi direction, and pushes the operating protrusion 39 held in the gear cutter 8 by the spring 4T toward the upper right in FIG. 5, thus circulating the movable shearing force 5 around the operating path. make it move. In this case, the latch pawl 41 is unlatched in a short time from the six blades against the force of the spring 47, and then relatched by the force of this spring (thereby), e.g. Even if it is rotated outward again by the spring 47, the movable shearing force is prevented from rotating in the return direction.

The gear cutter 8 does not extend over the entire circumference of the movable shear force. At each end uncoved arches 48 and 49 are left, which are not necessary for sequential engagement as described above, but which facilitate adjustment to the starting and ending positions. do.

The actuating projection 39 thus engages the rear second tooth of the arcuate portion 49 in the fully closed starting position shown. In this position, when the rotary lever 4 is sequentially engaged as described above, the shear edge 1
4 and 21 approach each other in the first rotation angle of 30° in FIG. 7, the deformation still takes place relatively far outwards and there is therefore an embossing that imposes an even greater rotational moment. However, as the shearing process progresses further, the effective length of the cutting lever arm from the rotating shaft 36 always decreases, i.e. the rotational moment to be applied becomes always smaller, or for a given driving rotational moment. In this case, the leverage becomes even greater. Thus, as shown in FIG. 9, the length of the lever arm effective in the shearing process becomes approximately zero just before the final closed position.

It can be seen from FIGS. 7-9 that each effective shear edge still has a distance from its axis of rotation 36 before reaching final closure. In principle, the shearing edges 14 and 21 can be designed to have a stronger helical shape near the axis of rotation, i.e. a greater curvature, so that, at least initially, a greater proportion of the shearing edges 14 and 21 are applied to the cutting mechanism 9. , that is, relatively small rotational moments are required at the beginning of shearing, and a large operating angle can be utilized. In this case, the remaining cut surface will be closer to the axis of rotation 36 at the end of the shearing process.

After the end of the shearing process, the movable shearing force 5 can be rotated further in the cutting direction of the first one, in which case both claws 3
1 and 41 are slid over the toothings and also on the toothless arches 48 and 49 without any particular resistance.

However, especially when it is not necessary to complete the shearing process to the end, it is sufficient to simply rotate the operating lever 43 in the clockwise direction in FIG.
As shown in the figure, the latch pawl 41 is first directly rotated out of its engagement by the shaft 42, which in turn abuts the operating pawl 37, causing it to rotate together with it and similarly removed from its engagement.

The movable shearing force 5 can then also be turned back into the operating direction from the shearing process.

One of the particular advantages of this construction according to the invention is that a completely different variety of shearing heads 2 can be connected to the connecting flange 28. This includes differences not only in the material of the shear forces, but also in the shape of the shear edges of the two shear forces and their diameters, the limits of which depend on the length and strength of the levers 1 and 4 and the connecting flange 28. only it is noticed.

The embodiment shown in FIGS. 10 to 13 differs from the above-described embodiment in that the operating pinion 52 meshes with the gear cutter 8 of the movable shearing force 5. In this way, an additional operating path corresponding to the angle between the two pawls 37 and 410 is obtained. Although the arcuate sections 148 and 149 are also kept free from the gear cutter, their outer diameter corresponds to the root diameter of this gear cutter, so that in this section the movable shear forces are It can be rotated on and along a pinion 52 , which is supported on a bolt 53 in a pivot arm 104 . In the shearing head 2 there are only two further apart mounting pins 50 which allow the holder plate 24 to be precisely aligned with the fixed shearing force 18 and complement its connection.

Since the operating pinion 52 is rotated in a direction opposite to the movable shear force 5, the operating pawl 37 and the latch pawl 41 are connected to the operating pinion on the left side in FIG. 10 on the opposite side. The spring 147 fitted between the two pawls is therefore placed above the bearing pin 130 on the operating pawl and above the bearing pin 130 on the latch pawl 141.
They are engaged below 42.

A seven-piece arm 54 is provided at the rotation arm 104, and the bent end plate 55 of this arm is inserted into the cutout portion 56 of the latch pawl 141 to reach the rotation end position shown in FIG. The stopper surface 5 of this
It comes close to 1. As a result, the latch pawl 141 is rotated in a counterclockwise direction, and the operating small gear 52 is removed.

Similarly, just before this terminal position, the operating claw 1
37 comes into contact with the stopper plate 58 of the rotating lever 104, and the operating pawl is removed from the operating small gear 52, thereby allowing the movable shear force to freely rotate in the manner described above.

Here, this rotation is further brought about by a return spring 59 configured as a tension spring, which is connected to the holder lever 101 by its one hook end 61 in the part of the bearing pin 1420, while its other hook end 61 The end 62 is hooked radially spaced from the axis of rotation 36 at the movable shear force 5 . Furthermore, this connection position should be chosen such that the line of action of the average force of the spring is approximately the same rotation between the hook ends in the shear end position shown in FIG. It extends through the axis. starting position,
That is, the open position is also about 1 to this shear end position.
Since they are opposed at an angle of 80 DEG, the movable shearing force is rotated back in one direction or the other to the starting position for the next new shearing process after the two claws have been disengaged. There is no danger of any malfunction during the forward rotation, since the shearing opening is already closed at the start of the shearing process, and the ψ-n ,,u ,-5//This is because there is no jealousy. The return spring 59 also extends inside the bulge 63 of the holder lever 101 and is thereby protected against the outside.

In all drive or actuating devices, the drive-actuating force applied from the outside to its movable shear force passes through at least approximately the center of the object to be sheared, i.e. the shear between FIGS. 7 and 8. It is designed to act in a position of force. In this way, the frictional forces between the two shear forces are largely eliminated. This results in very high efficiencies, ie with relatively low driving forces and correspondingly low tool weights, extremely high shearing efficiencies can be achieved.

The quality of the cut is further improved if the movable shear force 105 is supported by a molded contact surface 60 on the outer edge of the fixed shear force 181 through its annular groove 109, as shown in FIG.

In this case, the cutting reaction force acting mainly in the radial direction between the two shear forces causes the m-directed pressing force component to deflect to a smaller size within the radial cutting plane, resulting in manufacturing inaccuracies. Based on this, any play that may exist in some cases is compensated for. This has the opposite effect, such that the helicoids are spread apart from each other, and a continuous post-polishing effect is obtained. When the shear resistance disappears, this pressing force is also removed, especially when releasing this shear recruit.

One of the special advantages of the construction according to the invention is also that the function of the actual catch can be controlled from the part of the holder lever 1 and the pivoting lever 4, i.e. it can be manually operated in the tip part of the recruit. This means that you don't have to rely on what you do. This makes it easy to use the tool completely apart, and allows for practical one-handed handling. For example, with a shear recruit according to the invention weighing only 500.9, substantially greater shear capacity is obtained with improved shear quality than with a conventional shear recruit weighing 1.3 Kf. was completed.

The embodiments shown above can be further modified in various ways. In other words, different springs can be used for the return, in particular different leaf springs. It has already proven advantageous to support the fixed shear by means of an internal groove of the movable shear, however, for example if the movable shear is mounted on some special bearing means or if the internal It is also possible to provide other bearing means, such as bearing in fixed shear forces.

It is likewise possible for one shearing section to be held by a removable arcuate ring which is axially removable from the guide above the other shearing section. In this way, for example, the circumferential connection of the fixed shearing section with the holder plate 24 is omitted, and the arcuate section used for guidance is integrated. Each shear edge also has a rotation axis 36
It is not necessary to pass exactly through the axis of rotation; it is only necessary that the two interlocking edge portions have a gradually decreasing distance from this axis of rotation towards the end of the shearing process. In this way it is ensured that shearing can be carried out reliably at large leverages. The resulting cut surface is also smooth and clean, because the relative feed is carried out over a large circumferential length, and each shear section is always held in contact with the other in the section of the cut surface. This is because they will be mutually eliminated again. In addition, the shear resistance then present is not very large despite the large joint surface, since these forces can be easily overcome by its large leverage, and the actual joint pressure is This is because it is affected by the shear resistance of

As described above, even though the magnitude of these shearing parts is small, even a relatively thick and hard object to be sheared can be sheared with a small amount of force consumption between the two shearing parts that are in close contact with each other. can.

[Brief explanation of the drawing]

FIG. 1 is a front view of a first specific example of a couple cutter according to the present invention, and FIGS. 2 and 3 are respectively shown in FIG. 1.
A side view including a partial cross-sectional view along line ■ and line ■-■, Figure 4 is a cross-sectional view along line ■-■ in Figure 1, and Figure 5 is a cross-sectional view along line v-v in Figure 3. , FIGS. 6 to 9 are a series of illustrations illustrating the shearing process at different positions of the shearing force; FIG. 1O shows a second embodiment of the cable cutter according to the invention along x-xm of FIG. Shown in cross-sectional view, the first
1 is a sectional view taken along line MM in FIG. 12, FIG. 12 is a front view of this second specific example, and FIG. 13 is a front sectional view of a third specific example of the cable cutter according to the present invention. FIG. 14 shows an improved version of the shear force guide in cross section. 1.101... Holder lever, 2... Shearing head 3... Joint bolt 4.104... Rotating lever 5.105... Movable shearing arm 6... Shearing blade disc T... - Annular flange 8... Gear cutter 9 part 9.109... Annular groove 11... Projecting annular part 12... Opening for hole 14.21... Shear edge 16.22... Slide surface 1B , 181... Fixed shear force 24... Holder plate 21... Flange portion 28... Connection flange 30.42... Shaft rod 36... Rotating shaft 37.137... Operating claw 38... ... Playing hole 39 ... Operation protrusion 41.141 ... Latch claw 43 ... Operation lever 45 ... Arcuate slit 47.147 ... Tension spring 50 ... Installation is done by Bi1 52 ...・Operating small gear 59...Return spring 63...Extrusion section agent Masao Miyake and one other person Fl [3,7゜Procedural amendment (method) August 'X, 1980 Commissioner of the Patent Office Shiga Number of characters: 1, Indication of the case 1982 Patent No. 1 No. 70153 2, Title of the invention: Scaffolder for cutting continuous rod-shaped bodies 3, Person making the amendment: Relationship of the case: Patent applicant address: Name (name) Exshield Bolter 4, Deputy
People〒100

Claims (13)

[Claims] (1) An annular guide having two shearing force plates, at least one of which is configured in the shape of a disk, and is concentric with the rotation axis of an intangible rotating shaft provided in a direction transverse to the plane of the disk. axially and radially supported in the member so as to be rotatable relative to the other shear force, forming an aperture for both shear forces that can be closed or completely closed; In a cable cutter, especially a manual cable cutter, for cutting continuous rods, one side Shear force of (
5, 105), said actuating device is arranged in such a way that the acting force imparted to this shearing force is directed approximately towards the center of the material to be cut, which is enclosed within said opening (12). characterized by being formed and arranged,
New recruit. (2) At least one shear force (105, 181)
The radial support of the reward guide means (109) for (60) is formed,
A recruit according to claim 1. (3) the holder (1) provided with said actuating device so that the shearing head (2) containing both shearing forces (5, 18) can be exchanged for various shearing heads of other shapes and/or sizes; ), the recruit according to claim 1 or 2, wherein the recruit is fixed to: (4) The movable shear force (5) is applied to the shear blade disk (6)
) with an annular flange (7) formed laterally into which the actuating device engages from the outside, and which has a fixed shear internally retained from the open side of said annular flange (7). Claim 1. having a guide (9) for the force (18). The new product mentioned in paragraph 2 or 3. (5) The opening according to claim 1 or 4, wherein the annular groove (9) serving as a guide is axially delimited by a removable projecting annular part (11). (6) The maximum width at which the second shear force (18) guided inside the first shear force (5) matches the opening width of the opening (12) of the first shear force (5). 6. A seat according to claim 1, wherein the seat is formed as an arcuate section with a removable projection (24) forming the length of the guide thereof. New products that are not listed on the website. (7) The holder 7 has a flange portion (26) in which the protruding portion covers the second shearing force (18).
6. A shearing holder according to claim 6, characterized in that it is formed as 4) and is mounted between the shearing force (18) and the connecting flange (28) of the holder plate. (8) A gear cutter (8) is provided on the outer periphery of the movable shearing force (5). The invention according to any one of claims 1 to 4 and 6, in which the successive engagement means (37), which can be moved directly or indirectly, engage. (9) The actuating device has a pinion (52) connected in front of the movable shearing force (5), to which an operating pawl and a latch pawl (
137, 141) are interlocked, as claimed in claim 8. (10) It has two shearing forces, and the movable shearing force of at least one of them is rotatable with respect to the other by a hook-type operating device having a latch claw and an operating claw. , in a shearing mechanism in which these pawl members mesh into gear cutting portions provided on the movable shearing force and are supported by mutually movable support members, in particular rotatable levers, both the pawls Among the members (37, 41), these and their supporting members (1, 4) may be described in any one of item 9. (11) Tension spring configured as a flexible compression spring (
47) connects each claw member (37, 41) with their rotation axis (3
0, 42) supported on mutually different sides of claim 10 (12) Cutting a continuous bar having at least one rotatably supported movable shearing force on which a removable actuating device and a return spring act. In hand-operated models, especially manual models, the return spring (59) has a line of action that can move beyond the axis of rotation (36) and is rotated beyond its 180'' as a so-called "over-center spring". According to any one of claims 1 to 11, the movable shearing force (5) is biased in one direction of rotation or in the opposite direction depending on its position. Not new. (13) A flexible tension spring as a return spring (59) is connected to the side of the movable shear force (5), and this is cantilevered from the opposite side, the patent The invention as set forth in claim 12.