CN103286372B - Ratchet cutter - Google Patents

Abstract

The invention relates to a manually operated ratchet cutter (1), in particular a cable cutter, with movable and fixed handle parts (2, 3), wherein the fixed handle part (2) forms a first fixed blade (4), and on the upper end region of the fixed blade (4), a movable blade (5) is hinged, which is used to cooperate with the fixed blade (4) scissors, and the movable blade (5) is parallel to The first knife body (4) moves on the plane, and has a ratchet mechanism with a brake claw (7) and a feed claw (8), and the ratchet mechanism is arranged on the outer circumference of the movable blade body (5). The meshing teeth are engaged, wherein the brake pawl (7) can also be moved to the release position, and the return spring acts between the fixed and movable handle parts (2, 3), characterized in that the The return spring (15) acts both on the movable handle part (3) and on the brake pawl (7).

Description

Ratchet Nippers

technical field

The invention relates to a manually operated ratchet cutter, in particular a cable cutter, having a movable and a fixed handle part, wherein the fixed handle part forms a first fixed blade and is articulated on the upper end region of the first blade A second movable blade for cooperating scissor-like with the first blade, the second blade moves in a plane parallel to the first blade and includes a ratchet mechanism having a detent pawl and a feed pawl, the ratchet mechanism being in contact with the first blade body Engaging teeth provided in the outer circumference of the second blade engage, wherein the locking pawl can be moved into the release position.

Background technique

Ratchet cutters of this type have been known in various forms. See for example EP 0 468 196 A1.

In the disclosed ratchet cutter, a return spring is provided between the fixed handle part and the movable handle part. Furthermore, the detent pawl is acted upon by means of a spring into a meshing position with the meshing teeth of the movable blade.

Contents of the invention

Based on the described prior art, the technical problem to be solved by the present invention is to provide an advantageously designed ratchet cutter.

A possible solution to the technical problem is solved according to the first inventive concept in a ratchet nipper, in which the restoring spring acts both on the movable tong arm and on the locking pawl. Thus, on the one hand a spring can be dispensed with. On the other hand, it is also possible to influence the spring force acting on the locking pawl as a function of the open position of the handle part. The force can be higher in the case of a smaller open position. When operating ratchet cutters, such as cable cutters, but also in general, the lower open position usually corresponds to the highest feed force, wherein during unclamping, depending on the object to be severed, there is often The highest force is also applied in the return direction.

Another possible solution to the technical problem is solved in a ratchet cutter in which the feed pawl is provided with five or more teeth for simultaneous engagement with the meshing teeth of the movable blade. This design shows that in the case of five or more teeth, especially if six teeth can be engaged at the same time, the ratchet drive mechanism is significantly reduced against foreign debris (Verschmutzung). sensitivity. Despite the certain presence of foreign matter, it still carries out the actual meshing of the teeth with a high degree of probability.

Another possible solution to the technical problem is solved in a ratchet cutter, wherein the feed pawl has an active section for cooperating with the detent pawl, depending on the open position of the handle part, so that the detent Jaw disengagement movement. The feed pawl is mounted rotatably within the movable handle part, preferably within a certain angular range, so that it can simultaneously be used to act on the detent pawl for a disengagement movement of the detent pawl. This also depends on the open position of the handle part. In the larger open position, which can only be reached, for example, by special movements, such as gripping with both hands, the opening movement of the handle part can only cause a disengagement movement of the locking pawl.

Another possible solution to the technical problem is solved in a ratchet clipper, wherein the locking pawl has two engagement segments, that is to say two or more teeth, wherein the two The teeth preferably protrude from the tooth roots in the meshing direction, such that the front teeth in the meshing direction are set back or set back to a certain extent compared to the rear teeth in the meshing direction. It can thus be achieved that the teeth of the brake pawl (despite having two or more teeth) can still move despite the circular movement of the brake pawl within a certain range during the disengagement movement and/or the meshing movement. In or out of the teeth of the second blade engaging teeth, a virtually simultaneous engaging or disengaging movement takes place.

Teeth of the same design can also be further provided with an optional design on the feed jaw, which can also combine one or more of the above-mentioned design, especially in combination with the previously described design of the feed jaw. combination. This also makes it possible that during the disengagement movement and/or the meshing movement of the feed jaws with the toothing of the movable blade, in any case two or more teeth engage in meshing virtually simultaneously. In this case, too, the front teeth can likewise be offset or moved forward (vorversesetzen) as in the ratchet pawl. It is important to match the tooth shape of the meshing tooth to which the second blade belongs. There are different protrusion heights at the root of the tooth, and it can only be placed on the root of the tooth with the smallest protrusion. This is because it is not the actual projecting height of such teeth that protrude freely, but the actual ratio of the tooth tips to one another and the actual ratio of the tooth meshing areas to one another that is important.

Further features of the invention are described or illustrated below, also in the description of the drawings and in the drawings, generally in terms of their preferred allocation to the aspects already referred to above. However, these features are also significant in relation to the assignment of only one or more of the features described or illustrated here, independently of one another or in other overall schemes.

In this way it is firstly preferred that the tooth height of the movable blade toothing is relatively small. The tooth height is preferably between 0.5 and 1.3 mm, more preferably 0.9 mm. All intermediate values, 0.6 mm etc., especially a pitch of 0.1 mm, are therefore also included in the disclosure.

The feed jaws preferably have the same tooth height.

It is also preferred that the restoring spring for the return movement of the movable handle part relative to the fixed handle part is a helical torsion spring, wherein further preferably the longitudinal axis of the coils of the helical torsion spring extends perpendicularly to the plane along which the blades move relative to each other. In addition, preferably, the helical torsion spring is superimposed on the fixed pliers arm, wherein the first action arm of the helical torsion spring acts on the movable pliers arm, and does not depend on the open position superimposed on the fixed pliers arm, and is located in the movable pliers arm .

The other arm of the helical torsion spring preferably also cooperates with the brake pawl in the region of overlap with the arm of the stationary caliper.

It is also preferred that the fixed tong arm has a support plate in the region of the support of the movable tong arm, wherein the support plate has a stepped recess in which the active flange of the engaging pawl and the active play of the brake pawl lie. . The recess is preferably designed to open towards an end remote from the handle end of the ratchet cutter.

It is also preferred that the movable blade has one or more through-openings on its blade. Further preferably, the stationary blade has one or more recesses extending in the shearing direction in its interaction region with the movable blade plane.

Description of drawings

The invention is explained in greater detail below with the aid of the drawing, which shows only one exemplary embodiment. in:

Figure 1 shows a first view of the ratchet cutter with the handle arms in the open position;

Fig. 2 shows the view according to the situation of the handle arm shown in Fig. 1 being tightened up the closest;

Fig. 3 shows according to Fig. 1 and Fig. 2, wherein the handle arms are farthest apart and reach the release position with respect to the second blade;

Figure 4 shows an enlarged view of the area of the brake pawl and the feed pawl at the engagement position of the feed pawl;

Figure 5 shows a view in the released position according to Figure 4;

Figure 6 shows an exploded view of the ratchet cutter in the area of the feed and brake pawls;

Figure 7 shows a top view of the view of Figure 5;

Figure 8 shows a separate schematic view of the brake pawl;

Figure 9 shows a separate schematic view of the feed jaw; and

FIG. 10 shows a partially enlarged view of FIG. 7 .

detailed description

First, a ratchet cutter 1 designed here as a cable cutter is shown and explained with reference to FIGS. 1 to 3 .

The ratchet cutter 1 has a fixed handle part 2 and a movable handle part 3 .

The fixed handle part 2 is connected with the fixed first blade body 4 . In addition, a movable second blade 5 is also provided. The second blade body 5 is hinged 8 with the first blade body 4 in the upper hinge part 6 . The second blade body 5 and the first blade body 4 act together in a scissors manner.

1 to 5 and 7 each show a view looking towards the fixed first blade 4 . That is, the fixed blade 4 faces the observer. In contrast, in the illustration of FIG. 6 , the viewing direction is towards the handle parts 2 , 3 , and the fixed blade 4 lying underneath is viewed in perspective.

The second blade 5 moves in a plane parallel to the plane of extension of the first blade 4 .

A detent pawl 7 is provided to prevent the second knife body 5 from returning. Furthermore, a feed jaw 8 is provided, by means of which the second blade body 5 is moved relative to the first blade body 4 in the shearing direction.

On the outer circumference of the second blade 5 there is provided a toothing 9 , with which the feed jaw 8 engages for the forward movement by means of a toothing 10 . The locking pawl 7 , which can be overridden during the forward movement, but which can be locked in the case of a return movement tendency, is likewise offset laterally to the feed pawl 8 and meshes with the toothing 9 . In this exemplary embodiment it can be seen that six teeth 10 are provided on the feed jaw 8 . The overlapping region 40 associated with the tooth 10 is assigned to the fixed blade 5 or the plate-shaped part 22 and, in the meshed state, the movable blade 5 is provided with a toothing. Not only does this result in an advantageous guidance, but the movement of the feed jaw 8 also has an effect on possible foreign matter contamination of the movable blade.

For the return movement of the second blade 5, the pawl 7 can be moved into the release position, see FIGS. 5 and 7 .

This release position is achieved in the exemplary embodiment by a larger open position between the handle parts 2 and 3 , see FIG. 3 .

In this larger open position, the movable handle part 3 moves the locking pawl 7 out of engagement by means of the feed pawl 8 .

The movable handle part 3 is rotatably mounted in the plate-shaped part 22 via the rotary shaft 21 , see FIG. 6 . In addition, one side of the rotary shaft 21 is provided with a receiving opening 23 in the handle part 3 , in which receiving opening is accommodated the biasing spring 14 for the feed jaw 8 , which will be described further below.

For a longitudinal axis A extending through the axis of rotation 21 , for example parallel to the fixed handle part 2 , the receiving opening 23 is arranged on the side of the longitudinal axis A facing away from the fixed handle part 2 .

In addition, a bearing hole 35 is provided in the movable handle part 3 on the blade side on the axis of rotation 21, but this bearing hole is not closed on a part of its circumference. The journal 13 , which is preferably formed in one piece with the feed jaw 8 , is accommodated in the bearing bore 35 .

As shown in Figure 2, the receiving hole 23 is located on its extension line, approximately on the central axis of the receiving hole 23, at the position where the handle parts 2 and 3 are closest to each other, at the point where the blade 4, 5 splits to the longitudinal axis A direction.

Furthermore, a locking lever 19 is articulated on the movable handle part 3 so as to be rotatably movable about an axis 24 . The stop lever 19 has an actuating flange 25 in the interior space between the handle parts 2 , 3 . In the closed position of the handle parts 2 and 3, the stop rod 19 can use its tip to engage with the positioning groove 39, see FIG. 2 . The positioning groove 39 is provided on the plate-shaped member 20 , and the other surface of the plate-shaped member forms an outer surface and is arranged on the plate-shaped member 22 .

In a further detail, the cantilever 11 of the feed jaw 8 , preferably depending on the position of the handle parts 2 , 3 relative to each other, overlaps the detent jaw 7 , as will be described in more detail below. As shown in FIG. 7 , the superimposition is on the side of the hinge 12 of the brake pawl 7 facing the feed pawl.

When the movable handle part 3 was moved to the open position shown in FIGS. Movement in the direction of disengagement. This movement is opposed to the force of the loading spring 14 which tries to press the feed dog 8 into the toothing 9 . Compressed at the latest by loading spring 14 , the force (momentary) applied to the pawl 7 by the cantilever 11 is so great that the pawl 7 also disengages against the force of the return spring 15, as shown in FIG. 7 .

In a further detail, a form-fitting groove 26 is provided on the feed jaw 8 , into which groove the tip 27 of the boom 11 engages. This engagement occurs in the open position of the handle parts 2 , 3 shown in FIG. 1 and in particular in the extended position of the handle parts 2 , 3 shown in FIG. 3 in the release position. However, the closest position of the handle members 2, 3 as shown in FIG. 2 is not preferred.

Furthermore, in the position shown in FIG. 3 , there is a pressing in relation to the loading spring 14 and/or the rear area 28 of the feed jaw 8 comes into contact with the end face 29 of the movable handle part 3 . The end face 29 surrounds the opening of the receiving opening 23 in this region or around the movable handle part 3 .

The compression of the charging spring 14 means that the coils of the helical torsion spring rest directly against one another, thus acting as a rigid part in the direction of compression of the charging spring 14 .

Thus, during the opening movement described in FIG. 3 , a lever-like transmission is transmitted from the movable handle part 3 via the feed pawl 8 to the detent pawl 7 . The cantilever 11 , or preferably in particular the tip of the cantilever 11 , presses against the tip region 30 of the locking pawl 7 and thus pivots it around the joint 12 in the direction of the fixed handle part 2 .

For this purpose, a stop 31 is preferably provided in the tip region 30 of the locking pawl 7 , with which the boom 11 or preferably the tip 27 of the boom 11 comes into contact.

It can be seen that the form-fitting grooves 26 are preferably provided between the stop 31 and the engagement section 18 in the deep plate-shaped region 32 of the above-mentioned locking pawl 7 .

The back-moving spring 15 both acts on the movable handle part 3 and also acts on the brake pawl 7 .

The return spring 15 has two spring arms 16 , 17 which are prestressed and connected to the movable handle part 3 and the locking pawl 7 in a position spread apart from one another. For this purpose, the spring arms 16 , 17 are bent at right angles at their ends and engage in corresponding bores of the pawl 7 and the handle part 3 . It can be seen that the ends shown are bent opposite each other.

Corresponding receiving openings in the pawl 7 are provided between the articulation part 12 and the engagement section 18 of the pawl 7 . Almost and preferably on the connecting line between the geometric axis of the joint 12 and the tip of the scarf. In this case, it is further preferred not in the center, but offset to the scarf section 18 .

For example, in the working position shown in FIG. 4 , the brake pawl 7 is embedded in the engaging tooth 9 by means of the engagement section 18, and the movable handle part 3 moves from the intermediate position of FIG. 4 to the position of FIG. Maximum feed position. It can be seen that the return spring 15 moves the movable handle part 3 back from the maximum feed position in FIG. 2 to the starting position in FIG. 4 or FIG. 1 when manual loading is released.

In a further detail, the return spring 15 is formed in one piece as a coil spring. The center axis M of the coil 33 of the return spring 15 runs perpendicular to the plane of the plate-shaped part 22 on which it extends.

The plate 22, as shown in particular in FIG. 6, has planar regions 22a and 22b of different depths thereon. The planar area 22a is a recess in the planar area 22b, and the planar area 22b continues up to the tip of the fixed blade.

In this depth, the deeper flat region 22 a opens into the lateral end face 34 of the fixed first blade 4 .

In particular, the return spring 15 and the feed jaw 8 are arranged in the deeper flat region 22a. They are preferably on the surface of the planar region 22a.

It is also important that the movable blade 5 has one or more through-holes 36 . As can be seen, such a through-opening 36 preferably extends longitudinally in the direction of extension of the movable blade.

As an alternative or in combination thereto, the stationary blade 4 preferably also has a plurality of recesses 37 facing the movable blade 5 , see in particular FIG. 6 . The recesses 37 extend longitudinally and follow one another in the direction of extension, but are preferably each closed in the form of islands. Overall this advantageously reduces the friction between the blades 4 , 5 .

The through-opening 36 is preferably arranged in the widest region of the movable blade 4 . In relation to the circumferential angle of the movable blade 4 , looking towards the hinge 6 , the through hole 36 is preferably in the angular range a of 15°-90°, more preferably in the angular range a of 15°-45°.

In further detail, the feed jaw 8 has six teeth 10 , such as shown in FIG. 6 . These six teeth 10 mesh simultaneously with the toothing 9 in the feed direction, see FIG. 4 .

Furthermore, on the ratchet cutter 1 , a stop lever 19 is rotatably hinged to the movable handle part 3 . According to FIG. 2 , in the closed position, which in this form can also be used as a transport position, the securing position can be reached by means of the locking rod 19 , which can enter, as described, into the positioning groove 39 of the plate 20 .

The embodiment is further described with reference to FIG. 10 , especially on the feed pawl 8 in the longitudinal direction of the brake pawl 7, a plurality of scarfing segments 18 are sequentially provided, and these scarfing segments have different heights h ₁ and h ₂ , starting from the tooth root 38 stands out. In FIG. 10 this different height is shown exaggerated for better illustration. It can be seen that the front engagement section 18 in the advance direction is raised lower than the rear engagement section 18 in the advance direction. The teeth 10 of the feed jaw 8 can also have a corresponding design.

All features disclosed are (per se) essential to the invention. Therefore, the disclosure content of the present application also includes the disclosure content of the associated and/or attached priority documents (copies of the pre-application), for the purpose of simultaneously incorporating the features of these documents into the claims of the present application. Dependent claims indicate in their optional parallel text independent inventive improvements to the prior art, in particular in order to base a divisional application on the basis of these claims.

List of reference signs

1 Ratchet Nippers

2 handle pieces (fixed)

3 handle pieces (movable)

4 (first) blade

5 (second) blade

6 hinges

7 pawl

8 Feed claws

9 teeth

10 teeth

11 cantilever

12 hinges

13 Journal

14 spring loaded

15 return spring

16 spring arm

17 spring arm

18 scarf

19 stop lever

20 plates

21 axis of rotation

22 plates

22a plane area

22b plane area

23 receiving hole

24 axes

25 Operating flange

26 form fit groove

27 tip

28 rear area

29 end faces

30 tip area

31 stop

32 plates

33 spring coil

34 pins

35 Bearing hole

36 through hole

37 recess

38 root

39 positioning slot

40 lap area

a Alpha

A Bearing shaft

M axis

h ₁ height

h ₂ height

Claims (5)

1. A manually operated ratchet cutter (1) having fixed and movable handle parts (2, 3), wherein said fixed handle part (2) constitutes a first fixed blade body (4), and On the upper end region of the first fixed blade (4), a movable blade (5) is hinged, which is used to cooperate with the first fixed blade (4) scissors, and the movable blade (5) is parallel to the The ratchet scissors (1) also have a ratchet mechanism comprising a brake pawl (7) and a feed pawl (8), and the ratchet mechanism is connected to the movable blade body The meshing teeth on the outer circumference of (5) engage, wherein the pawl (7) can also be moved to the release position, and a return spring acts between the fixed and movable handle parts (2, 3) , characterized in that the return spring (15) acts on both the movable handle member (3) and the brake pawl (7). 2. Ratchet cutter according to claim 1, characterized in that the feed pawl (8) is provided with five or more teeth for simultaneous engagement with the meshing teeth of the movable blade (5). 3. The ratchet cutter according to claim 1 or 2, characterized in that the feed pawl (8) has an active section for depending on the fixed handle part (2) and the movable handle part ( The open position of 3) cooperates with the detent pawl (7) to cause a disengaging movement of the detent pawl (7) when the fixed and movable handle members (2, 3) are opened. 4. The ratchet cutter according to claim 1 or 2, characterized in that the brake pawl (7) is provided with two or more engagement segments (18), wherein the engagement segments (18 ) is provided with such a length in the meshing direction or with such a protrusion height (h ₁ , h ₂ ) protruding from the dedendum (30) that the front gear in the meshing direction is more than the rear gear in the meshing direction Connect segment (18) to a certain extent after wrong or indentation. 5. Ratchet cutter according to claim 1, characterized in that the ratchet cutter is a cable cutter.