EP1035965B1 - V-belt drive - Google Patents

Abstract

The aim of the object is a v-belt drive for diverting a vertical pressure force comprising a driver (1), a slider (2) and a slider accommodator (3), characterised in that the driver (1) has a prismatic guide (13), the travel path Y of the slider (2) on the driver (1) is smaller than the travel path X of the slider (2) on the slider accommodator (3) and the angle α between Y and X is 45-70°.

Description

The invention relates to a wedge drive for deflecting a vertical pressing force with a driver 1, a slider 2 and a slide holder 3.

Wedge drives are used in metalworking to deflect a vertical pressing force in any other one Direction used.

Metalworking of body parts and other parts today takes place in industrial continuous process. This means, that these metal parts in a continuous workflow manufactured, shaped, punched and processed become. These are often a variety of different Presses used. In these presses come specially for this Body parts made tools in which the wedge drives are installed, for use. The wedge drives in the Tools are needed to a machining of the body parts to allow at any point of the metal part. This processing is permanently significant Forces on the wedge drives used. Usual presses work with pressures from 100 t to over 2000 t. At a Continuous machining process these forces permanently on the wedge drives used. The wedge drives need therefore be designed for such use, that they such forces over the longest possible lifetimes without Wear and tear can endure and continue one enable reproducible, precisely fitting machining of the metal parts.

Wedge drives are known from the prior art.

For example, DE 26 40 318 A1 describes a wedge drive for redirecting a vertical pressing force in a for the forming process for this angle acting force. This Wedge drive consists of a drive wedge, on which a vertical Force of a corresponding work press acts and one Slide wedge, which transmits the force to the horizontal. Of the Driver wedge and the slide wedge run either over one rounded cooperating area or in another Embodiment over a roll.

Usually there are above hanging wedge drives in the Body industry used, from a driver, a Pusher and slider pusher (see, e.g., US-A-5,101,705). On the top the slide holder acts a vertical force that the Slider holder presses down. The driver is in the tool firmly anchored, so that when pressure on the slider recording the slider anchored in the slide in a any direction outside the vertical working direction is pressed.

Frequently, overhead wedge drives are used. At this Design, the slide depends in his leadership movable in the Slider receiving. The driver sits rigidly in the lower part and specifies the working direction of the slider. On the downhill In the press, the spring-loaded slider sets the driver on and is from the further pressed down slide recording pushed over the driver surface in working direction.

However, the wedge drives known from the prior art have Significant disadvantages, so that the slide used Of the prior art often have only short lives and due to their structural design high wear are exposed. They must therefore often already after short maturities are replaced because they wear and tear show, so that an exact deflection of the vertical Press forces is no longer possible, resulting in metalworking leads to unacceptable tolerances.

A disadvantage of such slide is, for example, that the Running accuracy of the slide only from the leadership of the slider is ensured in the slide holder. The slider has opposite the driver no guidance and is only on the flat surface of the driver, without that here is a guide available. This has the consequence that a very precise fit must be set, only with large technical effort can be produced and therefore very expensive is. Furthermore, the on the slider recording exercised forces in a directional manner only by the leadership recorded on the slide recording, but over the Driver passed on undirected. This leads to a premature Wear of such wedge drives.

Another disadvantage of the wedge drives of the prior art it is that the guides of the slider in the slide holder often be kept too short, which leads to that despite extremely accurate tolerances no good running properties the slider can be realized. Furthermore, the running accuracy the slider is reduced by too fast wear, because the entire force is directed to relatively short guides is.

Another disadvantage is that the behavior of the driver angles, ie the angle between the sliding surface of the slider on the driver and the sliding surface of the slider on the Slider recording is designed so that the slider recording accelerates the slider. This results in a frequent Overuse of the sliding elements and thus an increased Wear.

Another disadvantage is that the sliding plates on which Move slider and driver or slide holder and slider, not ideally stacked. This increases in turn, the wear due to an unfavorable development of forces on the sliding plates and continues to increase the effect of small tolerance inaccuracies in such a Arrangement to significantly larger positional inaccuracies of the Guide the punching unit.

Another disadvantage is that the withdrawal forces in conventional slides are often too small. This causes, if it is due to wear to a Sliding change in the slide comes, the spring the slider can not push back.

Furthermore, often the forced return are designed too small. Due to insufficient retraction forces, it may happen that the slide is stuck. This can occur, for example, when the spring to push back the slide breaks or due to wear a lower spring force exercises. In order to avoid in such a case that demolish the punching units, the forced return must the Pull back the slide. If the forced return device, however too weak, he tears off. This will also the Punching unit damaged because the slide only in its advanced Location lingers and can not be pushed back can. This break not only sets the entire slider function overrides, but sets a complete readjustment the entire new punching units ahead and thus can lead to significant damage to the tool.

Another disadvantage is that the slide stops frequently are arranged too small or unfavorable. One too small Slider stop can be due to a permanent use in the Tool to be demolished. This means that the slider slips out of his leadership in the slide holder and easy falls on the driver. The slider recording would then in another downhill on this uncontrolled in the Tool lying foreign matter and considerable damage cause the tool. An unfavorably mounted stop also leads to an increased effort in the Installation and removal, because the appropriate screws to Einund Removal often accessible only by special tools.

Thus, it was the technical object of the invention, a Wedge drive to provide the above described Does not have disadvantages and in a continuously industrial Manufacturing process can be produced if possible long service life and cost-effective use.

This object is achieved according to the invention by a wedge drive, characterized in that the driver 1 a Prism guide 13 has that the travel path Y of the slider 2 on the driver 1 is smaller than the travel X of the Slider 2 on the slide holder 3 and wherein the angle α between Y and X is 45 to 70 °.

With these measures, the above-mentioned disadvantages of the prior art overcome. The use of a prism guide 13 significantly increases the running accuracy of the slider at the power stroke, because not only a guide of the slider takes place in the slide holder 3, but also in the driver 1. As a result, on the one hand, the wear of the slider guide reduced in the slide holder 3 and on the other hand increases the accuracy of the slider run.

In a further embodiment, the prism guide 13 designed so that the prism falls off to the outside Slanted. This measure ensures that Bluff bodies, such as screws, metal parts and the like, the could dissolve during production and on the driver 1 fall down, not on the sliding surface between driver and Sliders can remain, but slide down from this. This is a trouble-free run of the slider on the driver 1 guaranteed.

With the further measure, namely that the travel Y of the Slider 2 on the driver 1 is smaller than the travel path X of the slider 2 on the slide holder 3 is reached, that the guide surfaces seen from the vertical between slide holder / slider and slider / driver almost completely cover what an ideal pressure pickup of the Press guaranteed. Furthermore, the guides of the Slide holder 3 to the mounting surface so far to the rear pulled down, that they cover almost all, what a ideal pressure deflection on the mounting surfaces means.

In a preferred embodiment, the ratio of Travel path Y to travel X at least 1: 1.5. The longer ones Sliding surfaces are thus between slider and slide holder attached to there for the slide retraction enough circulation to provide. The ideal power diversion required larger stroke allows a more accurate Guide the slider in the slide holder. The shorter ones Sliding surfaces are located between driver and slider, so as to achieve an ideal and accurate deflection of the forces.

The angle α between travel Y and travel X is 45 to 70 °, more preferably 55 to 60 °. With This measure is achieved, that the slide holder 3 the Slider 2 is not accelerated during the working stroke, i. that the Arbeitsweg can not be longer than that to the bustle of the Slider required stroke of the press. This ratio is Decisive for the service life and power development of the Slide 2. Since the travel between slide recording and Sliders are preferred at least 1.5 times longer than the Travel between driver and slider, these are thus also able to realize a larger stroke, necessarily is required to the above ratio of Traversing each other to achieve. The slider runs with it slower without acceleration and therefore gentler on material.

In a further preferred embodiment, the forced return clamp 16 on both sides by means of a shoulder 15 in one Groove enclosed in the slide 2. By the two-sided bordering in a groove in the slide increases the stability of the Forced return in the direction significantly. This can do with it be reduced in size without his Function loses or danger of breakage exists. Furthermore the forced return is shunted in the slide, so that his Tensile forces can not act on the mounting screws. Due to the lateral border of the forced return is mounting is particularly easy and no adjustment required. The position of the forced return is determined so that the Slider first has to go back to complete with his clip to be able to drive out of the driver. Attaching the Forced return bracket 16 allows only two grooves in the Driver 1 milling. This also reduces the cost the production of the wedge drive according to the invention.

In a further preferred embodiment, for the Guide of the slide in the slide holder Angle strips 10 used. These consist in a preferred embodiment made of bronze and fitted with an angle bar Sliding elements made of graphite. Such parts are commercially available Available parts that are maintenance-free and therefore cost-effective Enable production. Furthermore, a light one Adhering to the tolerances guaranteed to the exact Run the slide 2 may be needed.

In a preferred embodiment, the slider receptacle 3 Shoulders on which the angle strips 10 einschuleten are arranged. The one shoulder of the angle strips in the Slider mount allows the sliding play without aligning only to ensure the manufacturing tolerances. This also leads to a cost savings in the production and assembly of the wedge drive according to the invention.

In a further preferred embodiment is in the Slider recording 3 arranged a spring 9 through which the Holding screw 6 is guided. The screw secures the slider 2 against falling out. The steel spring is used for retrieval of the slider 2 after the operation. In a preferred Embodiment is the spring force of the spring 9 so Measure that they are at least 5 times the pusher weight of the slider 2 is. This is required for the Retraction force is always so great that the slide completely is moved back before he lifts off the driver 1. This Return forces must be high enough for forced return must be used only when breaking the spring. The forced return is therefore only an emergency backup to ensure should, that even if the retreat of the Spring 9 no damage to the screwed punching elements is to be feared.

Furthermore, the use of a retaining screw 6, the automatically via the slider biases the spring, the slide very easy to install and remove. This saves costs especially in the training phase of the slide and the Changing the slide in the tool shop.

In a particularly preferred embodiment, the retaining screw 6 at its tip with a custom-made approach 20, which makes it possible, the retaining screw 6 in the Thread blind hole 21 of the slide holder 3 to block too Screw. This eliminates any costly Hubeinstellen and allows a repeatability of the spool stroke to be realized under exclusion of assembly errors. Furthermore, this method is considerably cheaper than the usual Hubeinstellungsverfahren.

The retaining screw 6 is in a further preferred embodiment on the screw head with a metal disk 7 and a Damping disc 8 equipped. The damping disk exists preferably of a damping material such as a thermoplastic Plastic or rubber and dampens the returning Slider on the upward stroke of the press, so that a hard Striking against the retaining screw is avoided. Also This contributes to a longer shelf life of the invention Wedge drive at.

The dimension of the retaining screw is preferably dimensioned so large that they are at least 100 times the slider weight is. This is to be excluded that the holding element during the mission ever breaks off and thus to break of the slider 2 leads.

In a further preferred embodiment is in the lower Part of the driver 1 and in the upper part of the slide holder 3 a keyway 22 is arranged, which allows the slider Always align exactly in the tool. The exact training and adjustment of the wedge drive is therefore minimized in the tool.

It is further preferred that the driver 1 and at the Slider recording 3 each arranged at least one paragraph 23 is that after aligning the slider 2 in the tool as a stop surface for a wedge, which is transverse to the working direction runs, serves. This will be possible thrust forces intercepted.

The structural design of the wedge drive according to the invention allows it, the screwing of all parts of the wedge drive so to make sure that all screws without disassembling any Parts are accessible from above or below. Thus, the Use of the wedge drive according to the invention, even in tight spaces Space conditions are realized in tools.

In a further preferred embodiment is on the Prism surface of the prism guide 13 of the slider 2 a Sliding plate 12 is arranged. In a further preferred embodiment is on the path of the slide holder 3 a flat bar 11 is arranged. In a preferred embodiment consist of the angle bar 10, the flat bar 11 and the Sliding plate 12 made of bronze, with this in a preferred manner Sliding elements made of graphite are arranged. Because of the engagement Such maintenance-free sliding is a low-friction Running the slider in the slide holder 3 and in the Driver 1 achieved.

It is also particularly preferred for the slide return to use a gas spring. This has the advantage that realizes such a greater return force with the same size can be and continues to be the life of a gas spring higher than the commonly used steel springs.

Fig. 1

zeigt einen Querschnitt auf Mitte des erfindungsgemäßen Keiltriebs entlang der Achse X in Figur 2 oder 3.

Fig. 2

zeigt eine Vorderansicht des erfindungsgemäßen Keiltriebs in Achse X in Figur 1.

Fig. 3

zeigt eine Ansicht des erfindungsgemäßen Keiltriebs von hinten entlang der Achse Z in Figur 1.

Fig. 4

zeigt eine Vorderansicht des erfindungsgemäßen Keiltriebs.

Fig. 5

zeigt eine Seitenansicht des erfindungsgemäßen Keiltriebs.

Fig. 6

zeigt eine Rückansicht des erfindungsgemäßen Keiltriebs.

Fig. 7

zeigt eine Skizze, in der die Verfahrwege Y des Schiebers 2 auf der Schieberaufnahme 3 und die Verfahrwege X des Schiebers 2 auf dem Treiber 1 angegeben sind sowie auch der Winkel des Treibers 1 zur Schieberaufnahme 3.

Fig. 8

zeigt einen Querschnitt auf Mitte des erfindungsgemäßen Keiltriebs, wobei die Schieberrückholung über eine Gasdruckfeder 26 erfolgt.

Fig. 9

zeigt eine Ansicht des erfindungsgemäßen Keiltriebs gemäß Figur 8 entlang der Achse Z in Figur 8.

The following figures are intended to explain the invention in more detail.

Fig. 1

shows a cross section on the center of the wedge drive according to the invention along the axis X in Figure 2 or 3.

Fig. 2

shows a front view of the wedge drive according to the invention in axis X in Figure 1.

Fig. 3

shows a view of the wedge drive according to the invention from behind along the axis Z in Figure 1.

Fig. 4

shows a front view of the wedge drive according to the invention.

Fig. 5

shows a side view of the wedge drive according to the invention.

Fig. 6

shows a rear view of the wedge drive according to the invention.

Fig. 7

shows a sketch in which the travels Y of the slider 2 on the slider holder 3 and the travel paths X of the slider 2 are indicated on the driver 1 and also the angle of the driver 1 to the slide holder. 3

Fig. 8

shows a cross section of the center of the wedge drive according to the invention, wherein the slide return takes place via a gas spring 26.

Fig. 9

shows a view of the wedge drive according to the invention according to Figure 8 along the axis Z in Figure 8.

Figure 1 shows a cross section of the wedge drive according to the invention along the axis X of Figure 2 or 3. The on the Slide holder 3 acting force of a corresponding press is indicated by an arrow. Moved by the action of the force the slide holder in the direction of the Z-axis after down to the pushed back by the spring 9 slider. 2 on the driver 1 touches down. In another downstroke the Press is now over the two driving surfaces in X and Y axis the slide advanced in Y axis. In this case, the spring 9 squeezed to the slider in the following Upward stroke of the press only to push back again before he lifts off the driver 1. The numeral 6 denotes the retaining screw with the slider 2 fixed to the slide holder 3 is so that he can not fall out. The numeral 7 shows the steel disc, number 8 the damping disc, with which is achieved that when relaxing the wedge drive of reduces impact acting on the head of the retaining screw becomes. The numeral 9 shows the spring, which is a return of the Slider 2 after the punching process allows. The number 14 shows the two-sided enclosure of the forced return bracket 16 in the slider 2. The numeral 15 denotes the shoulder in Slide, which is achieved by the tensile forces of the slider do not act on the fixing screws. The numeral 17 denotes the mounting surface, on the example Punching units or other metalworking tools be attached. The numeral 19 designates the sliding surfaces the slide holder 3, which preferably consist of bronze and are provided with sliding elements made of graphite. This ensure a maintenance-free and friction-reduced gliding of the slider on the slide holder 3. The numeral 20 denotes the approach for the retaining screw 6. The numeral 21 denotes the threaded blind hole for the slide holder 3. The numeral 22 denotes a keyway in the upper part of Schieberaufnahme 3 and in the lower part of the driver 1 for more accurate Adjustment in the tool. The numeral 23 denotes one Paragraph in driver 1 and slider receptacle 3, the after aligning the slider 2 in the tool as a stop surface for a wedge that runs across the working direction, serves.

FIG. 2 shows a front view of the invention Wedge drive along the axis Y in Figure 1. The numeral 12 denotes the sliding plates attached to the slider 2 and put on the driver 1 while redirecting the force. These sliding plates are preferably made of bronze and continue to have sliding elements made of graphite. The numeral 13 denotes the prism guide, the one outward has sloping slope. This will ensure that metal parts, screws or shavings used in metalworking arise and on the sliding surface of the driver. 1 meet, do not lie there, but fall down sideways and thus the function of the wedge drive according to the invention do not bother. The numeral 4 denotes the bracket 1, the numeral 5 the bracket 2. These are used to secure the forced return 16 in case of breakage of the spring 9, to a return to grant the slide at spring break and tearing out to avoid the screwed punching elements. The Paragraph 23 indicates the paragraph already mentioned above on the driver 1, the numeral 22 denotes the keyway in the bottom Part of the driver 1.

FIG. 3 shows a cross-sectional view of the invention Wedge drive along the axis Z in Figure 1. The numeral 6 denotes the retaining screw, with the slider 2 in the Slider holder 3 is secured. Number 9 describes the above-mentioned spring and the numbers 10 and 11, the angle bar or the flat bar on the slide 2 is opposite the slide holder 3 moves. As already mentioned above mentioned, both the angle bar and the flat bar exist in a preferred embodiment of bronze. These bars furthermore preferably contain sliding elements made of graphite, to allow for better gliding. The numeral 18 denotes the shoulder of the angle bar 10 in the slide holder 3. This allows that it is ensured that the sliding play only on the Manufacturing tolerances needs to be aligned.

Figures 4, 5 and 6 show external views of the invention Cotter key.

FIG. 4 shows a front view of the wedge drive according to the invention. The numeral 1 denotes the driver, the numeral 2 the Slider and the number 3, the overlying slide holder. The number 17 shows the relatively large mounting surface of the Wedge drive according to the invention, which is about 40% higher than at comparable wedge drives with similar external dimensions. in the In the present case, this mounting surface has dimensions of 75 x 105 mm. The numeral 13 denotes the prism guide with the arranged thereon sliding plates 12, in a preferred manner made of bronze and containing sliding elements made of graphite. When a vertical force on the upper part of the slider receptacle 3 is directed, the spring 9 is first compressed, to the well visible in the figure 4 paragraph the slider holder 3 impinges on the slider 2. From this Time is then the slider 2 via the driver 1 in the desired direction pushed.

FIG. 5 shows a side view of the wedge drive according to the invention. The numeral 16 here is the forced return bracket designated. It consists of a single bracket each each side, namely the bracket 4 and the bracket 5. With This compulsory return ensures that at break the spring 9 of the slide 2 can still be moved back. Also clearly visible is the shoulder 15 in the slider as well paragraph 23 in the slide holder 3. The numeral 18 shows the shoulder on the slide holder 3, at which the angle strips 10 are attached.

FIG. 6 shows a rear view of the wedge drive according to the invention. The number 1 indicates the driver with the prism guide 13. The numeral 12 indicates the sliding plates, the Numeral 10, the angle strips for the slide guide 2 and the Paragraph 19, the sliding surfaces of the slide holder 3. Continue well recognizable is the forced return bracket 16 and the shoulder in the slider 2, in which the forced return bracket 16 is arranged is.

Figure 7 shows a sketch in which for the inventive Wedge drive important laws regarding the relationship the travels X and Y and the angle of the travel paths X and Y are shown. X denotes the travel path X of the slider 2 on the slide holder 3, Y denotes related to the travel of the slider 2 on the driver 1 on the length. The angle α denotes the angle between the travel path Y and the travel X, it is 45 to 70 °, preferably 55 to 60 °.

FIG. 8 shows a particularly preferred embodiment of the invention Wedge drive according to the invention, in which the slide return by means of a gas spring. The use of a gas spring instead of the usual steel springs has the advantage that by means of the gas spring a significantly greater return force can be realized with the same size. The Gas spring is designated by the numeral 26.

As a holding element for the movable slide 2 is a Guide sleeve 25 is inserted, which in a bore, the was drilled by the slide 2 itself, is plugged. This guide sleeve 25 has a shoulder at the lower end, on which a damping disk 28 has been placed. In the slide 2 is further incorporated a reduction in the lower area, which are executed according to the stroke of different depths can. Between this reduction and the approach of the guide sleeve 25 can now be the slider, if he after the operation driving back to its final position, his Run required hub. The reduction beats it the damping disk 28, which the slider 2 against falling out guaranteed. With such a construction, only one works axial force on the retaining element, so that the life of the Retaining element is considerably increased. Another advantage This embodiment is that maintenance work faster and can be carried out more easily if, for example, the Slide elements of the slide return can be replaced have to. Replacing a gas spring 26 in built Condition is by means of a mounting plate 27 in the rear part Slider 2 easy and fast to complete. This mounting plate 27 only has to be dismantled, the gas spring can then just back from the guide sleeve 25th be pulled out.

Another advantage of using a gas spring is the non-positive connection of the holding element in the Schieberaufnahme 3. Since the holding element at each stroke of Press a punch in the form of the slider weight and the associated It is advisable to intercept this in dynamics a particularly preferred embodiment does not have a to realize screwable solution. Screwable connections namely, tend to solve themselves, so that not It can be guaranteed that the slide 2 during use can always be kept. A breakage of the retaining elements would inevitably entail that the slide 2 from his Pickup slips out and on the tool base falls, so that the rejoining tool on the underlying slider 2 ascends and so the entire tool can destroy. The frictional connection of the holding element is therefore of enormous importance. The holder of Slide stop sleeve 25 via a removable Corner. It takes place in the preferred embodiment Help an angle 24, which in a screwed groove on the holding element is inserted. The angle is open at the top, so that you simply insert it into the groove of the sleeve 25 can, while you put the sleeve through the receiving hole stuck in the slide holder. The angle itself has on its folded thighs a mounting hole, with he can be screwed to the slide holder.

The disassembly of the slide under the press can also done in a simple manner. Since the slider is assembled in Condition is a rather heavy component, which also during the familiarization phase of the often installed and expanded It is recommended that the installation be as easy as possible possible. For disassembly must in the preferred Embodiment of the wedge drive only the fastening screw the angle 24, which locks the retaining element removed so that by pulling this angle 24 Pull out the slider 2 with the retaining element to the rear can. This screw is in the rebounded state of the slider 2 easily accessible and thus is in this location Slide change without disassembly of the entire body possible. This can save considerable costs.

FIG. 9 shows a cross-sectional view of the invention Slider with gas spring along the axis Z in Figure 8. With the numeral 26, the gas spring is designated, the against Slipping out by means of the mounting plate 27 is secured. The number 3 indicates the slide holder, the number 2 the slider, the number 29 the flat bar and the number 30 the angle bar.

With the wedge drive according to the invention, it is the first time succeeded to provide a tool with which permanently and despite the action of high forces, accurate metalworking possible at any point of a body part is. The wedge drive according to the invention has a long service life, can be produced inexpensively and is largely maintenance-free.

references

1

driver

2

pusher

3

spool location

4

Bracket 1

5

Bracket 2

6

retention screw

7

metal disc

8th

damping plate

9

feather

10

angle bar

11

flat bar

12

sliding plate

13

V guide

14

double-sided surround

15

Shoulder in the slide

16

Zwangsrückholklammer

17

bolting

18

Shoulder angle strips

19

Sliding surfaces Slider intake

20

Approach retaining screw

21

Thread blind hole slide holder

22

Keyway driver, slider holder

23

Paragraph driver, slider holder

24

corner

25

guide sleeve

26

Gas spring

27

plate

28

damping plate

29

flat bar

30

angle bar

Y

Traverse of the slide 2 on slide holder 3

X

Travel of slider 2 to driver 1

Z

axis

α

Angle between X and Y

Claims (16)

1. A cotter key for the deflection of a vertical pressing force with a driver (1), a cam (2) and a cam bed (3), wherein

   the driver (1) has a V-guide block (13),

   the travel path Y of the cam (2) relative to the driver (1) is shorter than the travel path X of the cam (2) relative to the cam bed (3) and the ratio of travel path Y to travel path X is at least 1:1.5,

   the angle α between travel path Y and travel path X being 55 to 70°.
2. The cotter key according to claim 1, characterized in that the V-block of the V-guide block (13) has an inclined face sloping downwardly in outward direction.
3. The cotter key according to claim 1 or 2, characterized in that a positive return (16) is constrained on both sides by a shoulder (15) in a keyway in the cam (2).
4. The cotter key according to claims 1 to 3, characterized in that the cam bed (3) has shoulders on which guide angles (10) are positioned in a shouldered arrangement.
5. The cotter key according to any of claims 1 to 4, characterized in that a spring (9) through which a retaining screw (6) is inserted is arranged in the cam bed (3).
6. The cotter key according to claim 5, characterized in that the spring loading of the spring (9) is at least the 5-fold of the cam's weight.
7. The cotter key according to claim 5 or 6, characterized in that the retaining screw (6) is provided at its tip with a precision-turned shoulder (20) which makes it possible to screw the retaining screw (6) in the blind threaded hole (21) of the cam bed (3) in an on-block fashion.
8. The cotter key according to any of claims 5 to 7, characterized in that the retaining screw (6) is equipped at the screw head with a metal washer (7) and a shock absorber ring (8).
9. The cotter key according to any of claims 1 to 8, characterized in that the underside of the driver (1) and the upper side of the cam bed (3) each have a keyway (22) arranged thereon for easier alignment of the cam in the tool.
10. The cotter key according to any of claims 1 to 9, characterized in that the driver (1) and the cam bed (3) each have at least one step (23) arranged thereon which, after alignment of the cam (2) in the tool, serves as a stop face for a key running at right angles to the working direction.
11. The cotter key according to any of claims 1 to 10, characterized in that wear plates (12) are arranged on the V-block surface of the cam (2).
12. The cotter key according to any of claims 1 to 11, characterized in that a slide plate (11) is arranged on the guiding face of the cam bed (3).
13. The cotter key according to any of claims 4 to 12, characterized in that the guide angle (10), the slide plate (11) and the wear plate (12) are made of bronze.
14. The cotter key according to any of claims 4 to 12, characterized in that the guide angle (10), the slide plate (11) and the wear plate (12) contain sliding elements made of graphite.
15. The cotter key according to claims 1 to 4 and 9 to 14, characterized in that a gas spring (26) is arranged in the cam bed (3).
16. The cotter key according to claims 1 to 4 and 9 to 15, characterized in that the bushing (25) for the cam stop is held with a detachable angle (24).

Images