HU201491B - Single-purpose machine for producing workpieces required several operations with intermittent product moving and drive of intermittent rotary motion - Google Patents

Abstract

The disclosed machine comprises a frame (1) on which are mounted the product transport elements (3) which discontinuously move on a path (2) and the stationary machining units facing the frame and coming in contact with the product. The elements (3) for transporting the product on the path (2) are movably arranged facing each other either individually or in two groups, and are guided on the bound path separately or as a group. Furthermore, the product transport elements (3) have a connection element (5) enabling a cyclic connection, which connection elements are connected according to the program to the trading system inherent to the machine, the execution of the program being provided for by the program transmitter (7).

Description

BACKGROUND OF THE INVENTION The present invention relates to a target machine for the production of multi-tasking workpieces by means of a batch movement, which consists of a machine rack, a built-in, productive lifting device for moving batch paths and machining units relative to the machine rack.

In addition to the above-mentioned target machine, the present invention also relates to another invention, which relates to a batch rotary actuator with a continuously rotating drive shaft and a batch rotating output shaft.

Its essence, kinematic basis is the same as described for the target machine.

A significant percentage of products manufactured by the industry are made on target machines, on a series of target machines, ie on 15 machines that are used only to produce a particular product (group of products) (eg standard filament lamp). Within this, the majority of target machines perform more operations on the product or it is made up of several sub-products, so a single product (more precisely a semi-finished product) has to come into contact with a series of machining units and metering units in the manufacturing process. In most cases, this relationship requires that the machining unit (hereinafter referred to as the machining unit) be substantially stationary with respect to the product for the duration of the operation.

Since production must be continuous, the means of production must be used, and it is advisable to have several products (or more precisely a semi-finished product in different stages of production) associated with the processing units at the same time.

The general model of the target machines follows, consisting of a series of different machining units to perform one operation, a set of product transport elements containing the same items, and a conveying system that ensures that all products are in contact with all with a machining unit, or with a unit capability if multiple identical entities are used for the same machining function. So the necessary connection: approach - docking - technology operation - moving away can be divided into moments. This must be made possible by the conveyor system 45 cycles.

Within the above general purpose machine model, two known subgroups can be distinguished according to the nature of the transport system:

1) incrementally stepped 50

2) a group of continuously moving machines.

In the case of staggered machines, the conveying system is a substantially intermittent moving wreath or chain that conveys the mounted product transport elements 55 to the stationary machining units. All transporting moments (start, stop, etc.) occur in the same phase.

The conveying system of continuously moving machines consists mainly of a system of continuously moving wreaths and chains, on which the product transport elements, partly the machining units travel, and the relative movement conditions of the contacting elements ensure the approach, co-operation (docking), moving away. 65

The "clean" continuous-motion machines described here often are supplemented by swinging (swinging) scaffolds and rigs. equipped with machining units.

The characteristics of the two groups are compared as follows:

The product conveying elements of the articulated machines are moved together, most often with camshaft gear units (so-called shifting gears). These are described e.g. László Horváth's book entitled "Intermittent Gears for Intermittent Rotary Movement". The speed of stepping is limited by the inertia force here and the load capacity of these gears. This is the most common and crucial determinant of the performance of this type of target machine. The downtime of product supply elements is determined by the slowest technological operation (if it cannot be interrupted). Often a single operation requires the whole machine to be run slowly or somehow duplicated or tripled. An example of this is the so-called. a duplex machine that uses twin conveyor elements and twin machining units in a product line. Machines for products with such unequal operating time thus require more machining units than would be the result of the performance of these units, i.e. certain units of the manufacturing tool are not utilized.

For machines with continuous motion, there are fewer mass force load problems and only power-limiting forces appear on the swing following units. Therefore, this type of target machine is often chosen for high performance machines. However, the connection between the workpiece machining unit is a major problem. Because it is not the task of stopping a single conveyor system on precise divisions, but the exact meeting and regular movement of moving parts, the kinematic problems of the machine are manifold. This is especially true in the case of the use of hot technologies, where thermal expansion increases the position uncertainty of the elements. My "clean" continuous-motion machines can only be solved by the use of chain structures for a more durable co-operation of the product conveyor unit. A typical case in point is the use of a continuous-motion, long racing track supply chain and a series of similar but shorter machining unit chains. Here the straight chain sections run together, there are no weight problems, the length of the interconnected chain sections is optional, so the longest technological operation here is not decisive for the machine as a whole. The underutilization is partly embodied in idle traveling devices in the downstream part of the machining unit chains and partly in the overhead of the product transporting elements in line with the semicircular parts of the machining chains. This type of machine is described by László Horváth in his book "continuous motion automata".

Consequently, it is not advisable to solve the problem of the target machine, which requires a lot of high-precision connection, with a machine with continuous product movement. For these, the above mentioned duplex, triplex wreath machine-2HU 201491 Β two is used.

Thus, the machine types currently in use have problems of utilization and performance limitations due to imperfections in the conveyor systems used. It is an object of the present invention to eliminate or substantially reduce these problems. This object has been achieved by the present invention, which is solved by the invention described below.

The target machine according to the invention differs from the above-described types in that the product conveying elements reach the stationary machining units by intermittent movement, but they do not do this in rigid connection with one another, but independently, usually in an offset phase. Thus, on the one hand, their mass forces do not appear at the same time, they do not add up, in fact, the moving elements of the transporting elements can be arranged in such a way that they compensate each other. On the other hand, the freedom of movement of the product transport elements and the flexibility of the transport system used allow the product transport elements to have different downtime in machining locations, so that near-optimal utilization of the machining units can be achieved. (We use a number of units proportional to the time required to operate each unit.) This can solve various target machine tasks at minimal cost.

In summary, one object of the present invention is a target machine for the production of multi-tasking workpieces by means of a batch movement consisting of a machine rack, a built-in, batch-moving product conveyor, and a machining unit that is stationary relative to the machine rack. The target machine according to the invention is characterized in that the product conveying elements are individually or at least two groups arranged individually or in groups on the fixed track, movable relative to one another, and the product transport elements have a coupling element suitable for cyclic engagement. They are attached to a machine towing system by program, which is provided by a program transmitting structure.

Another invention is an intermittent rotary drive with a rotary drive shaft which comprises a gear which is stationary relative to the gear housing. It has a planetary gear, crank arm, and a backstage roller. The latter is guided in a stripline in the direction of the axis of the stationary gear.

The invention will now be described in more detail and, in order to facilitate this, a drawing appended thereto, comprising the following figures:

Figure 1: Outline of the general structure of the target machine

Fig. 2 is a diagram showing the motion relations of an exemplary embodiment,

Figure 3 is a graph of the displacement-time function of Figure 2,

Figure 4: acceleration-time functions for Figure 3,

Figure 5: The displacement function of the product transport elements grouped into three groups,

Figure 6: Product transport element showing movement version,

Figure 7 is a cross-sectional view of an exemplary embodiment and guide of the chain-driven product conveyor;

Figure 8 is a sectional view, A-A, of the machine portion of Figure 7;

Figure 9: Speed-time curve of the drag chain and the product conveyor it moves,

Figure 10 illustrates an exemplary drag coupler

Figure 11 is a cross-sectional view of an exemplary embodiment of a product transport element combination of a slider coupling element following a cyclic path and the associated conductor element,

Figure 12 is a side view of the machine portion of Figure 11,

Figure 13 is a top view of the machine portion of Figure 11,

Figure 14: Cam-operated program transmitter for controlling a specific product transport element,

Figure 15 is a side view of an exemplary embodiment of a cam remote control element combination;

Figure 16 is a sectional view of the machine portion of Figure 15,

Figure 17 is a sectional view of a towing chain moving gear,

Figure 18 is a top view of the machine portion of Figure 17,

Fig. 19 is a sectional view of the load balancing lever system and switch mechanism of an intermittent pivoting actuator;

Figure 20 is a top view of the arm system of Figure 19.

Figure 1 illustrates the general construction of a target machine according to the invention, which is described below.

A fixed track 2 is rigidly connected to the rack 1, which defines the path of the product transport elements 3, limiting its degree of freedom to trajectory direction. Machining units 4 are also connected to a rack 1 and are arranged in regular divisions. The product transport element 3 which is in contact with them is secured by a positioning element 8. The product conveying element 3 is conveyed by a towing system 6 consisting of a motor 12, a gear 11, a towing element 10 and a motion transmitting element 9 connecting the latter. The movement of the towing member 10 is such that its orbital motion at the stationary position is reduced to zero (usually for a moment) so that it is here (at the moment of stopping) to contact and remove the coupling member of the product transport elements 3 or transfer the product transport element smoothly to the 8 positioning elements.

The order of these connections is determined by the programmer 7 (mechanical, electrical, pneumatic, etc.).

Figure 2 is a schematic view of nine machining position machines with eight product transport elements, showing the instantaneous motions: from the 4th machining position, 3.1 product transport elements

4.2 from machining position to 4.3 machining position, the product transport element 3.3 has arrived

From 4.3 machining positions 4.4 machining positions

-3EN 201491 Β doba. The other 3.4-3.8 product conveyor elements reach maximum speed, the product conveyor element 3.2 arrives at machining position 4.3, and at the same time 3.8 product conveyor elements start, and so on. 5

The process is plotted versus time in Figure 3. Figure 2 shows the instantaneous position t _o . This group of motion functions includes the acceleration-time functions shown in Fig. 4, which show the acceleration ratios of five product transport elements 3 to the moment (these are characterized by one sine function period). It can be seen that summing up the functions shown would result in zero. This means that if the movable elements are of the same mass, the trajectory components of the masses 15 compensate for each other within the traction system 6 providing the movement (the movement of the transport elements 3 does not cause vibrations). In Fig. 3, the dashed motion functions illustrate the movement of the pulling members 20 10 of the towing system 6.

the time intervals indicated in Figure 3 are as follows:

Ti = step time, that is, the time taken for the product transport element to travel between two adjacent positions; 25

T p = periodic time perceptible in a stationary position, ie. the time elapsed between the starting moment of two consecutive product transport elements;

T, = period of time perceptible on a product transport element 3, e.g. the time elapsed between touching two consecutive standing positions.

In the example motion series selected here, tp is one-half step longer than Tt, i.e., generally, the amount of phase shift. It would be possible for T to be longer, but in this case the distance between the moving elements would be smaller than the division of the standing positions, thus this solution has less practical significance for the sake of reservation.

Obviously, using 18 stationary posters and 16 product transport elements 40, we obtain an analogous double unit target machine, etc.

Figure 5 is an example! It depicts the motion functions of 15 machine models with 12 stationary transport elements, with the requirement that each product touch a three-time machine. For reasons of continuity, this unit should be tripled. This is where the machining positions 4.20,4.21, 4.22 are located. The preceding and following 2-2 positions are reserved from simplex to triplex and vice versa. These are usually unused places for machining purposes. All other positions are full simplex positions, that is, 55 points on which each product transport item is located in a single standstill.

Machine version 60 can be edited analogously to the exemplary solution, or employing positions with more than three downtime.

It demonstrates Figure 6. destination machines according to the invention the possibility that a specific (ie. Space requirements) end, denoted by x, positions indicated by arrows multiple scale divisions space formed 65 ⁶ out for each product conveyor element (eg. The product conveyor clamps wide opening for the purpose).

Figures 7 and 8 show the product conveying element 3.10,>

10.7 dragging element and 8.7 positioning element by example! .

The 2.7 knit track guides 3.10 product transport elements through two pairs of 19 castors (product-related grippers not shown). The drag element 10.7 is the spe- cially moving element 9.7.

It has a discrete chain member 13, the elements of which are displaceable in their planes, thereby adopting the shape of the switching member 7.5 which displaces them and thus engages in a pulling action. The towing system operates with 2 chains moving with a 180 ° phase shift superimposed on a s2 velocity superimposed on a mean velocity v ₂ . Their speed-time function is shown in Figure 9. The solid line represents the upper and the dashed line the lower chain. The continuous thick line is the velocity flow of the product conveying element 3: at that moment it is connected to the upper chain, at t it is disconnected, it stands, at t _{2 it} drags itself with the lower chain, and so on. (The dashed wavy lines of Fig. 3 are the moving-time function lines of these chains, with every second being the movement of the lower chain). The lower edge of the 5.7 switching element is a 8.7 positioning element, because the lower position of sitting 20 locating the nest and thus recorded 3.10 would supplier elements from the 21-accent language, push the appropriate moment (eg. T _2), thus also eliminating the capture of a pulling link is also created, which is forced to stay until the next position, but jumps there with 22 springs. If you just don't wait for a 21 highlighting language, then there will be forwarding. The highlighting tongue 21 is controlled by the program transducer 7.7, which in this case is a track which rotates in harmony with the gear 11 of the coupling system 6, so that only the motion transmitting elements (chains) 9.7 give additional moments at zero speed (around this time). instructions. It can be seen in Fig. 9 that the velocity and the acceleration at the moment of switching are also zero at the moment of switching applied, which makes it possible to make a "smooth" connection even during fast operation.

The belt assembly coupling element 13 is advantageous because the elongation or thermal expansion of the motion conveying element 9.7 does not impair the dynamic conditions of the coupling. There is only a minimal error in the size of the chain step \. For similar purposes, it is applicable;

The coupling element 5.10 -10.10 of the coupling member 5.10 shown in FIG. The column bodies 54 can be moved in a straight line.

As the towing member 10.10 rises, despite the position error in Fig. 10, an exact connection is established between the two. 23 balance arms make the connection more secure by preventing any further movement of the 54 columnar bodies.

The mass forces appearing in the embodiments shown on each chain appear as if only 17-8 times the mass had to be moved. The forces in the two chains balance each other in the common gear.

Figures 11, 12 and 13 show another embodiment of the towing system 6. Here, 18-cone towing-trolley-4HU 201491 Β are moving on a peak cyclic path. Here is the

9.11 The motion transducer (chain or wreath) moves at a constant speed along the fixed track and carries the axles 16 bearing in it, the lower end of which has a gear wheel 15 and the upper end 14 has a crank arm. The latter is axially displaceable. The crank arm 14 is tightly fitted with a conical towing element 18 at the same radius as the gear wheel 15. Thus, the conical towing element 18 performs a complex movement as the gear 15 is continuously rolling on the stationary rack 17. The result is the cyclois trail. This complex motion has a

The component of 2.11 in the direction of a fixed orbit is a smoothly moving or superimposed sinusoidal oscillating motion, similar to the motion shown in Figure 9. Since 18 conical towing elements a

The product conveyor 3.11 engages with a slider roller 24 formed in a groove perpendicular to the fixed path 2.11, so that the latter conveys only the 2.11 motion of the conical towing element 18 so that the product conveyor 3.11 follows the motion law of Figure 9. so-called sinusoidal shifting path). By changing the mounting direction of the 14 crank arms, a 180 ° phase shift between adjacent towing elements (18 conical towing elements) can be ensured.

As a program structure, 25,26,27 control tracks are used. There are three types of control roller positions 28 arranged on the control track group 25.26,27, which pass beneath the motion transmitting element 9.11. The guide rollers 28 are mounted on the control arms 29 (with left, center and right mounting) which transmit the control movement to the crank arms 14. With the appropriate design of the stationary control paths 25,26,27, the motion function of Fig. 3 can be implemented. 5 coupling elements (18 conical towing elements) here always carry two positions empty, carrying one (see one of the dashed wavy lines in Figure 3).

the scooter rollers are always at the position shown at the moment of stopping -15 gears -17 above the junction of the rack. This is the peak of the cycloid path, where the c-shaped positioning element 8.11 can be placed. fixes 24 kuhsa rollers with magnetic force.

If you want to deviate somewhere from the simplex movement order shown in Figure 3 (such as machining position 4.20 in Figure 5), you use the path-guided control address sheet 30 in that section (see Figure 14). The control time of the control tracks running around the triplex position is three times the base period time (3.t _p ).

Figures 15 and 16 show an example of control for a planetary wheel with a backstage roller similar to the previous one.

remote control actuator (electromagnetic, air cylinder, etc.) receives control signal from 7 program transducers (one per unit is included in the machine). the lower actuator pushed the control roller 32 forward and coupled to the auxiliary track 33, following the position shown in Fig. 15, would lower the friction-braked movable rail section 35, which would move the cone pulling member 18.16 through the central rod with a sufficiently precise motion. to complete the move. The control bypass shown here is advantageous because it provides a solid response to the remote control effect in terms of timing, movement, energy content. If, in the example shown, no disconnection instruction is received, the dragged product transport element would of course be carried

18.16 Tapered towing bracket.

In the latter described cyclic path variants, adjacent drags directly compensate for each other's mass force at 180 ° phase shift. Thus, the machine employs any product transport element, the maximum force applied being the inertia of a single product transport element. Namely, a 4 kg element, 800 steps / hour, at 110 m pitch, 320 N peak force is applied to each drag element (if T _p = 4.5 Ti). It is a very important property that the elongation of the motion transducer element has no influence on the smoothness of the couplings and the accuracy of the positions, since the stopping points of the conical towing elements 18 are connected to the rack 17.

A17. and Figures 18 and 18 show an exemplary variation of a special actuator for moving the motion transducer element (pulling chain pair) shown in Figures 7 and 8. Construction, kinematics, similar to Figures 11-13. 1 to 4 illustrating the cycloid path of FIGS.

the continuously rotating block receives movement from the drive gear 38. Constantly moving

As a result of the planetary motion described above, the roller 24.17 also describes a tapered cyclone whose tangential movement component is carried by the groove cup 39 on the upper sprocket 40. The adjacent planetary elements, by virtue of their 180 ° C crankshaft position difference, transmit half-period offset phase motion to the lower sprocket 40. Thus, the chains associated with them fulfill the previously defined motion relations. Of course, for the sake of load, several sliding elements can be operated in parallel along the circumferences. (Of course, high-precision batteries are needed here for even load

The target machines of the present invention are primarily intended to be manufactured as universal base machines, with the option of a selectable, post-adjustable motion character, which is achieved through a suitable program for the programmer. Its advantages are high performance multi-action machines.

Finally, an ordinary stepping motor operating using the ideas described above is an example! 19 and 20. The point is that even with inaccurate batteries, it provides perfect load balancing.

Similarly to the foregoing, the skid rollers 24.19 are in constant contact with the skid lines 41, which move substantially together with the dial 42, since through the connecting pins 45 and the connecting pins 46, the pins 43 and guide pins allow a degree of freedom of relative movement of the skids. This is mara5

-5GB 201491 Β the degree of freedom is terminated by the connection of 47 balancing eyes and 48 balancing chains. Specifically, this also takes into account the rotation of the 42 discs of the eight degrees of freedom, so moving the eight scooter rollers with more or less errors results in a clear rotation of the 42 discs averaging the former.

Thus, the arm system not only performs load balancing but also significantly improves the accuracy of the step. Errors statistically partially compensate for each other.

from the continuous step sequence of the pulley, similarly to the above, the conical towing element 18.19 carries every second, third, etc. movement period on the 49-step disc. The positioning element 8.19 is triggered by the pressure of the force transfer pin 50 when the stepping process begins by raising the conical towing element 18.19. The latter is provided by the pin-lifting crown 51, for example, by a cam actuating mechanism. The gear ratios of the latter control gear determine the ratio of time to position and movement.

This stepping gear has a much higher load capacity than the known cam tracks, mainly due to the multiple load bearing elements. Small installation space required (low construction).

The load balancing principle shown can also be applied to a chain actuator of FIG.

Claims (34)

PATENT CLAIMS A special purpose machine for the production of multi-tasking workpieces by means of a batch movement, consisting of a machine rack, a built-in productive transport element moving batchwise and a machining unit stationary in relation to the machine rack, characterized in that the product transport elements (3) track (2) individually or in at least two groups, arranged removably relative to each other, connected to the fixed track (2) individually and in groups, and the product conveying elements (3) having a coupling element (5) suitable for cyclic engagement, the coupling elements (5) they are connected to the machine pulling system (6) according to a program, and the target machine has a program transmitting structure (7) associated with the coupling elements (5). Target machine according to claim 1, characterized in that the towing system (6) consists of a motion transmitting element (9), a pulling element (10), a gear unit (11) and an engine. Target machine according to claim 1, characterized in that it has positioning elements (8) standing relative to the machine rack (1), which secure the product transporting elements (3) in their upright position. Target machine according to claim 1, characterized in that the motion transmitting element (9) is in direct contact with the pulling element (10). Target machine according to claim 4, characterized in that the fixed track (2) is a circular path and the motion transmitting element (9) is a rigid disc or ring rotating about an axis. Target machine according to Claim 4, characterized in that the knit track (2) consists of straight and circular sections, the motion transmitting element (9) being a chain following this path. Target machine according to claim 3 or 4, characterized in that the motion transmitting element (9) is permanently connected to the output gear (11) capable of instantaneous cyclic stops. The target machine according to claim 7, characterized in that its towing system (6) and its gear unit (11) are doubled. The target machine according to claim 7, characterized in that its drag element (10.7) consists of a plate (13) which is displaceable in its plane. Target machine according to claim 7, characterized in that the towing element (10) is a two-wire-shaped block body (54) which has a stepped configuration at the end thereof. The target machine according to claim 1, characterized in that the connection between the motion transmitting element (9) and the pulling element (10.18) is effected via a crank arm (14) pivotally mounted on the motion transmitting element (9). The target machine according to claim 11, characterized in that the crank arm (14) is mounted on a common shaft (16) with a gear wheel (15) and that the radius of the gear wheel (15) is substantially equal to the radius of the crank arm (14). Target machine according to Claim 12, characterized in that the toothed rails and / or racks (17) are fixed to the machine rack (1), which are sewn in constant contact with the gear wheels (15) mounted in the movement element (9). The target machine according to claim 11, characterized in that the pulling element (10,18), which is guided against the pivot in the crank arm (14), is conical and can be displaced axially. Target machine according to Claim 11, characterized in that the coupling element (5) is adapted to receive a matching pulling element (10,18) in the center of the skid roller (24) which is straightened in the product transport element (3). The target machine according to claim 15, characterized in that it has a positioning element (8,8,11) formed by a c-shaped nest which fits with the periphery of the skid roller (24) and fixed to the machine rack (1). The target machine according to claim 16, characterized in that the positioning element (8,8.11) is magnetic, the periphery of the skid roller (24) fitting to the positioning element (8, 8.11) has ferromagnetic properties. The target machine according to claim 11, characterized in that the motion transmitting element (9) is kinematically connected to a continuous motion actuator (11). Target machine according to claim 14, characterized in that its pulling elements (10) are provided with different control levers (28) mounted on at least two movement tracks, which are movably guided relative to the motion transmitting element (9), and the guide rollers (28) being positioned relative to the body of the machine (1) and defined by at least two stationary guide tracks (25,26,27) aligned with the track of the guide rollers (28). 20. A target machine according to claim 19, characterized in that the stationary control tracks (25,26,27) are replaced at least in intervals by a control plane (30), the control planes (30) having a wire capable of moving perpendicular to their plane. equipped with and controlled by a program transmitting device (7). The target machine according to claim 14, characterized in that its pulling element (10,18) is guided by a flanged roller (52) in one of the guide groove pairs of a stationary rail (53) which is stationary with respect to the machine rack (1). 22. The target machine according to claim 21, characterized in that the stationary rail (53) is formed by interruptions, which intervene to extend the rail sections (35) perpendicular to the path. The target machine according to claim 22, characterized in that the motion transmitting element (9) carries an auxiliary path (33) formed with a guiding track moving therewith. The target machine according to claim 23, characterized in that the movable rail section (35) is rigidly connected to the bearing housing of the axial guide roller (32) and these axial guide rollers (32) are displaceably embedded in their axial direction. 25. The target machine according to claim 24, characterized in that the axial guide rollers (32) are disposed so that they are in a position rubbed by one of the guide surfaces of the auxiliary track (33) only when moved under control action. The target machine according to claim 25, characterized in that the remote control actuating elements are operatively connected to the program transmitting device (7). The target machine according to claim 1, characterized in that the program transmitting structure (7) is electronically programmable. 28. An articulated rotary gear having a continuously rotating drive shaft, an intermittently rotating output shaft, characterized in that it has an external or internal gear gear which is stationary relative to the gear housing and having a gear crank fixed at least one planet (15.19). (14.19) and a mounted roller roller (24.19) therein, and the roller roller (24.19) is guided in staggered wires (41) which are perpendicular to the axis of the stationary gear and connected to a pulley (52) . The gear unit according to claim 28, characterized in that the disc (42) carrying the stripline (41) comprises a controllable drag element (18.19) capable of relative relative positioning. Gear according to Claim 29, characterized in that it comprises an intermittent stepped disc (49) mounted in the axis of the stationary gear and having a coupling element (5.19) which can be connected to the steering element (18.19). The gear unit according to claim 30, characterized in that the gear unit has a program transmitter structure (7) in kinematic relationship with the control element (18.19). Gear according to Claim 29, characterized in that it has two or more skewer rollers (41) and an equal number of skewer rollers (24.19), and that the skewer rollers (41) are connected to the roller (42) individually in relative movement. 42), and by virtue of their mode of engagement, the stripline wires (41) and the dial (42) form a multi-degree unit having the same degree of freedom as the stripline wires (41). Gear according to claim 32, characterized in that each of the skid lines (41) and the disc (42) are connected to each of them by means of a carp pair connected by pins. The gear unit according to claim 33, characterized in that there is an endless leveling chain (48) movable with the unit of the skid lines (41) and the disc (42).