WO1986006668A1

WO1986006668A1 - Special machine for fabricating workpieces requiring a plurality of working paths with discontinuous motion of the product

Info

Publication number: WO1986006668A1
Application number: PCT/HU1986/000027
Authority: WO
Inventors: István Kerényi
Original assignee: Tungsram Részvénytársaság
Priority date: 1985-05-07
Filing date: 1986-05-07
Publication date: 1986-11-20
Also published as: JPS63500087A; GB2187402B; GB8630515D0; DE3690258D2; HU201491B; HUT41318A; GB2187402A

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

SPECIAL MACHINE FOR MANUFACTURING WORK PIECES WITH DISCONTINUOUS MOVEMENT OF THE PRODUCT BEFORE SEVERAL OPERATIONS

The invention relates to a special machine for the manufacture of n several operations claiming who cheeses with discontinuous movement of the product, as well as an associated gear. The special machine according to the invention consists of a masc frame, the elements built on it, which move discontinuously on a bound path and transport the product, as well as the processing units, which are stationary in relation to the machine frame and connect to the products.

A significant percentage of the products manufactured in the industry are used on single-purpose machines, single-purpose production lines, ie on systems that only serve to produce a certain product / product group / e.g. normal Incandescent lamps /, manufactured. Within this, the majority of single-purpose machines are machines that perform several work steps on the product, or the product is assembled from several sub-products, so a product / more precisely, the semi-product / must be used during the manufacturing process with a series of processing machines or Feed units come into contact. In the majority of cases, this connection requires that the processing feed unit / further processing unit / be substantially stationary with the product for the duration of the operation. In view of the fact that continuous production is indispensable and that the means of production must be used, it seems expedient if several products - more precisely, the products in the different production phases - are connected simultaneously to the processing units. From what has been said, it is clear that the single-purpose machine represents the general model, which consists of the series of several processing units which are suitable for carrying out one work step and which differ from one another, from the group of identical product-transporting elements, and from a transport system which is absolutely reliable ensures that all the products come into contact with all processing units or unit types if several identical individual units are used for the same processing function. Accordingly, the establishment of the connection can be broken down into the phases of approximation - the docking of the technological process - of removal. The transport system is given the task of cyclical temp execution divided .

Within the general single-purpose machine model mentioned, the character of the transport system is divided into two known subgroups; Subgroup of 1 / discontinuously progressing and 2 / continuously moving machines.

In the machines working with discontinuous progress, the transport system is essentially formed by a discontinuously moving ring or chain, which forwards the product transporting elements mounted thereon to the stationary processing units. Every transport moment / occasion, parking etc./ takes place in the same phase.

The transport system of the continuously moving machines consists mainly of the system of continuously moving rings, chains, which partly carry the product-transporting elements, partly convey the processing units, whereby the developing relative movement conditions for the connecting elements are the moments of approach, of the idle / Docking / and removal. The machines described here with a "purely" continuous movement are often supplemented with oscillating / oscillating / following frames or with the processing units mounted thereon.

The characteristics of the two groups can be compared as follows:

The product transporting elements of the discontinuous working machines are also moved, in the majority of cases with cam-provided sliding gears / so-called change-path gears /. Such are described, for example, in the book by Lászlό Horváth, titled "Alternating-Path Gear for a Discontinuous Rotary Movement". The speed of the stepper drive is limited by the inertia and the resilience of the gearbox mentioned. The capacity of such a single-purpose machine type is most often and mostly determined by the factors mentioned. The service life of the product-promoting elements is determined by the slowest technological process / if this cannot be interrupted /. It often happens that the entire machine is operated slowly due to a single slow operation, or there is a need for duplicated or triplicated operation. As an example, the so-called duplex machine should be mentioned, in which double elements for product transport and double processing units are used on a product track line. Accordingly, the machines for the products with a claim to an unbalanced operating time require several processing units than would result from the performance of these units, ie that certain units of the means of production are not used.

In the case of machines with continuous movements, there are fewer problems in connection with the load capacity, rather the force-limiting force effects occur in the following oscillating units. This type of single-purpose machine is often chosen as a success in high-performance systems. Making the connection between the However, the workpiece and the processing unit often pose difficulties. In view of the fact that the task does not consist of parking a single transport system in exact divisions, but rather that exact meeting and regular tracking of moving elements can be realized, the kinematic problems of the machine are reported several times. This is especially true when using hot technologies, where thermal expansion increases the positional uncertainty of the elements. In machines with "pure" continuous movement, the continuous running of the product-promoting element and the processing unit can only be achieved by using chain constructions. In a typical case of this embodiment, a continuously moving, long product chain with a race track format track line is used, which is supplemented by the series of similar but shorter machining unit chains. In this case, the running of the individual chain sections is realized, there are no difficulties with regard to the inertial force, the length of the running chain sections can be chosen freely, which means that the longest technological operation in no way determines the entirety of the machine. The uselessness manifests itself partly in the means which move inactive on the return branch of the unit chains, partly in the excess of elements aligned with the semicircular parts of the processing chains and used for product transport. This type of machine is described by Läszlό Horvath in the book under the title "Automatic machines with continuous movement". It is clear from what has been said that the problems associated with the manufacture of numerous high-precision connections cannot in any way be appropriately solved with the aid of a machine with continuous product movement. In these, the machines with duplex or triplex rings already mentioned are advantageously used.

Accordingly, there are difficulties with the known types of machines in terms of utilization and limited performance due to the imperfection of the transport systems.

The aim of the invention is to eliminate or substantially reduce the difficulties mentioned. According to the invention, the set goal can be achieved with the help of the solution described in the following.

The special machine according to the invention differs from the types described above in that the product-demanding elements - although they reach the stationary processing units with a discontinuous movement - do not carry out the movements simultaneously in a rigid mutual connection, but independently and in relation to one another - in general - Execute postponed phase. This means that, on the one hand, the mass forces do not occur at the same time, the forces are not added, even the product-promoting elements can even be moved in such a way that a mutual balance is achieved.On the other hand, the freedom of movement of the product-promoting elements and the flexibility of the transport system used allow that the service life of the product-transporting elements at the individual processing points is different, which means that the processing is almost optimally used units can be realized. / A number of pieces is used from all units, which is proportional to the duration of the operation required there. / In this way, the various tasks assigned to a single-purpose machine can be carried out at a minimal cost.

To summarize the above, the invention relates to a special machine for the production of workpieces which require several working steps, with discontinuous product movement, the machine consisting of a machine frame, of the product transporting elements built on it and moving discontinuously on a bound path, and of those with the Product connecting processing units.

The solution according to the invention can be characterized in that the product-transporting elements are individually, or at least arranged in two groups, movable relative to one another, individually or in groups bound to the bound web, furthermore the product-supplying elements are provided with a connecting element suitable for a cyclic connection, wherein the connecting elements join the towing system belonging to the machine according to a program, and the program is secured by the programmer.

Also to solve the problem, a continuously rotating input shaft containing a discontinuous rotary motion securing gear was developed, the essence of which is that a gear with discontinuous rotary motion, with a continuously rotating input shaft, characterized in that a against an low-gear stationary gear with internal gearing or external gearing is present, furthermore at least one planetary gear in constant rolling connection therewith is provided, the planetary gear being rigidly connected to a crank arm, the crank arm having a link roller mounted thereon, the link roller in a direction toward the axis of the stationary gear lying guide line, and that the link line is in an essentially rigid connection with a disc mounted in the center line of the stationary gear.

The invention is further explained on the basis of advantageous exemplary embodiments, with reisinvreis on the accompanying drawing. In the drawing: Figure 1 shows the general structure of the single-purpose machine according to the invention, Figure 2 shows the movement conditions of the here shown

Embodiment, Figure 3, the function of displacement vs time, Figure 4, the functions acceleration vs time, Figure 5, the displacement function of the product transport elements arranged in three groups, Fig. 7 and 8 an embodiment of the chain-dragged product transport element, the leadership and the towing, connecting and positioning elements, FIG. 9 shows the time / speed function of the drag chain and the product transporting element moved with it, 10 shows an example of the towing connection element, FIGS. 11, 12 and 13 show an example of a product-transporting element following the cycloidal path, which is designed as a combination of a trolling element-connecting link element, FIG. 14 shows a cam-controlled programmer for controlling the product-transporting element a special program, Fig. 15-16 an example of the control with the combination of a cam and a remote control element, Fig. 17-18 the Ge set the drag chain in motion gear, Fig. 19-20 generate a discontinuous rotation of the transmission with a load-balancing arm system. Figure 1 shows the general structure of the special machine according to the invention.

A machine frame 1 is followed rigidly by a bound track 2, which determines the traffic route of product-transporting elements 3, the degree of freedom being restricted to the mobility in the direction of the track. The machine frame 1 is also connected to processing units which are arranged in a regular division. The product transporting element 3 that is connected to them is fixed with a positioning element 8.

The product transporting element 3 is one Further promoted towing system 6, which consists of a motor 12, a transmission 11, a towing element 10, and an element 9 connecting the latter, the motion transmitting element. The towing elements 10 move in such a way that their movement in the direction of the web drops to the position of the stationary positions / generally for one second / to the zero value, so these are capable / at the moment of standstill / with the connecting element of the product-transporting elements 3 in one to make a shock-free connection and convey it further or to transfer the towed product-transporting element 3 to the positioning element 3 without any difficulty. The order of the connections mentioned is determined by the programmer 7, which can be a mechanical, electrical, pneumatic, etc. unit.

FIG. 2 shows schematically a machine with nine processing positions and eight product-transporting elements, the current movements also being shown: the product-transporting element 3.1. starts from the processing position 4.1, at the same time the product transporting element 3.2 moves. at full speed from the processing position 4.2 to the processing position 4.3. In the meantime, the product transporting element 3.3 arrives. from processing position 4.4. The other product-transporting elements are at a standstill, processing is in progress as soon as the product-transporting element 3.1. reaches the maximum speed, the product-transporting element 3.2 arrives. just in the processing position 4.3., at the same time the product transporting element 3.8., and so on. Figure 3 shows the process in terms of the function of the shift over time. FIG. 2 shows the situation at the moment t _o . This function group of movement includes the processes of acceleration in function time presented in FIG. 4, which show the acceleration conditions of five product-transporting elements 3 against the moment t _o / these can each be done with one Sinusoidal period are marked. It can be seen that if we added the functions shown, the result would be zero. This means that insofar as the moving elements have the same masses, the components of the mass forces directed towards the track balance each other within the towing system 6 which ensures the movement. / The movement of the product transporting elements does not cause vibrations. /

The movement functions shown with a discontinuous line in FIG. 3 characterize the movement of the towing elements 10 of the towing system 6.

The intervals shown in Figure 3 are as follows:

T _l - step duration, ie the time during which a product-transporting element stores the path between two adjacent positions, T _p - the period time perceptible in a standstill position, ie the time elapsed between the starting moments of two, for example, successive product-transporting elements, T _t - The period time perceptible on a product-transporting element, that is, the time between the two contacts time elapsed at the following standstill positions.

In the movement function series chosen here as an example, t _p is longer by half a step time than T _t , ie generally by the amount of the phase shift. It is possible to choose T _t longer, but in this case the mutual distance to the distance described here would be less than the division of the stationary positions, so this solution is given less importance in practice due to the space requirement.

It is evident that by choosing eighteen stationary positions and sixteen product transport elements, using the solution described above, a single-purpose machine with a doubled unit number is obtained.

FIG. 5 shows the movement functions of a machine version with fifteen standstill positions and twelve product-transporting elements, in which there is a requirement that each product should come into contact with a processing point with three times the standstill time. For reasons of continuity, this unit claims a triple quantity, which are arranged in the processing positions 4.20, 4.21 and 4.22. The preceding and following two positions are reserved for the classification from simplex into triplex and vice versa, these generally represent unused positions from the processing point of view.

All other positions are full-fledged simplex positions, ie those points in which all product-transporting elements can be found with a simple downtime. In an analogous manner to the solution shown as an example, machine versions with positions with double, triple, even multiple downtimes can be designed.

FIG. 6 illustrates a possible embodiment of the special machine according to the invention, in which, for special reasons / e.g. space requirement / in the position indicated by x, a point with multiple division for each individual product-transporting element / e.g. can be designed for the wide opening of the product-promoting grippers.

FIGS. 7 and 8 each show an exemplary embodiment for the product-transporting element 3.10, the towing element 10.7 and the positioning element 8.7. specified.

The product-transporting 3.10 element is guided on the bound web 2.7 with the aid of two pairs of rollers 19 / the grippers which engage in the product are not shown here /. The towing element 10.7 forms a special chain link of the movement-transmitting element 9.7 and contains a plate pack 13, the elements of which can be displaced in their planes, as a result of which they take on the shape of the connecting element 5.7 which moves them and thus enter into a connection capable of towing. The towing system works with two chains, which move in relation to each other with a phase shift of 180 °, with a sinusoidal speed effect superposed on the middle speed v ₂ . The speed as a function of time is shown in FIG. 9. The continuous line characterizes the movement of the upper chain, the discon continuous line that of the lower chain. The continuous thick line shows the speed of the product-transporting element 3: at the moment t _o it joins the upper chain, at t ₁ it is detached, a steady state is established, at t ₂ the element can be removed from the lower one Dragging the chain, etc. / In FIG. 3, the continuously ascending discontinuous wavy lines represent the function lines of the movement as a function of the time of the chains, with every second line indicating the movement of the lower chain /. The lower edge of the connecting element 5.7. forms the positioning element 8.7, since in its lower position it sits in a positioning nest 20 and thus keeps the product-transporting element 3.10 in a fixed position; at the appropriate moment / eg t ₂ / the element is lifted out by means of a lifting tongue 21; in this way, when the fastening is stopped, the towing connection is established, which is forcibly maintained up to the next position, but there it jumps repeatedly due to the action of a spring 22, unless there is another lifting tongue 21 ready for operation, because in this case that Element is required. The lifting tongue 21 is the programmer 7.7. controlled, which in the case described here is a control path that rotates synchronized with the transmission 11 of the towing system 6, so that only in the moments when motion-transmitting elements 9.7 / the chains / are stationary at zero speed / or. in a short period against the mentioned moments /, another command is issued.

From Figure 9 it can be seen that in Ver Applying the motion functions mentioned at the moment of the connections, both the speed and the acceleration of the zero are the same, as a result of which a "smooth" connection is established even in the case of fast operation.

A connecting element designed as a laminated core 13 is extremely advantageous since neither the expansion nor the thermal dilation of the movement-transmitting element 9.7 / the drag chain / impair the dynamic conditions of the connections. There is only a minimal error in the size of the chain step. The constituent group shown in FIG. 10 - composed of the connecting element 5.10 and the towing element 10.10 - can be used with the same objective. Prism-shaped bodies 54 can be moved in the straight guide. When the towing element 10.10 rises, an exact connection is established despite the position error shown in FIG. A balance beam 23 ensures a secure connection because it does not allow a further displacement of the prismatic body.

The inertial forces occurring in the embodiment described here act on one chain each as if only a feed of 1/8 times the mass were required. The forces occurring on the two chains equalize each other in the common transmission.

11 to 13 illustrate a further possible embodiment of the towing system 6, which is designed with tapered towing elements 18. The conical movement elements 18 move on a tip-shaped cycloid path, since here a movement-transmitting element containing waves 16 9.11 / chain or wreath / travels at a constant speed along the bound path and entrains the shafts 16 mounted therein, at the lower end of which a gear wheel 15 is attached and at the upper end a crank arm 14, the latter being axially displaceable. In the crank arm 14, the tapered towing element 18 is firmly inserted, as a result of which the tapered towing element 18 executes a compound movement on a half diameter corresponding to that of the rolling circle, since the gear wheel 15 carries out a continuous rolling movement on a stationary toothed rack 17; the cycloid track line is a success. The component of the compound movement which is omitted in the direction of the bound path 2.11 represents a uniformly progressing or a sinusoidal oscillating movement superposed on the circular movement, which corresponds to the movement shown in FIG. With regard to the fact that the tapered towing element 18 comes into contact with the link roller 24 - which is guided in the groove which is designed in the product-transporting element 3.11 and runs vertically on the bound track 2.11 - the latter only transmits the movement of the tapered towing element 18 in the direction of the bound path 2.11, that is to say that the product-transporting element 3.11 follows the motion law according to FIG. 9 / it moves as if it were moved by an alternating path with sinusoidal acceleration /. The 180 ° phase shift between the adjacent tapered towing elements 18 can be secured by a suitable choice of the mounting direction of the crank arms 14.

Stationary control tracks 25 serve as programmer here, 26, 27. The group consisting of the control tracks 25, 26 and 27, which runs under the motion-transmitting element 9.11, comprises three positions of a guide roller 28. The guide rollers 28 are mounted on control arms 29 / with a left-hand, middle and right-hand mounting / which transmit the control movement to the crank arms 14. The movement function series according to FIG. 3 can be realized by the corresponding design of the stationary control tracks 25, 26 and 27. In this case, the connecting elements 5 / the tapered towing elements 18 / always leave two positions empty, one position promoting / see one of the discontinuous wavy line in FIG. 3 /.

At the moment of standstill, guide rollers 24 are always located at the point shown above the meshing point of the gear wheel 15 and the toothed rack 17, which results in the tip of the cycloid track line, here the c-shaped positioning element 8.11 can be arranged, which in our example e.g. fixed with a magnetic force the backdrop roller 24.

If it is now intended to deviate from the simplex movement order according to FIG. 3 / as is the case, for example, with the processing position 4.20 in FIG. 5 /, a path-controlled control flat plate 30 is used on this route / see FIG. 14 /. The cycle time of the control tracks functioning around the triplex position is three times the basic period time / 3 t _p /.

15 and 16 give an example of a version similar to the one described above for the control with planetary gear and link rollers.

In this version there is a remote control rendes element 37 / electromagnet, pneumatic cylinder etc. / a control signal from the programmer 7 / each position belongs to a pair of them in the machine /, on the effect of which, for example, the lower performing element would have shifted a guide roller 32 with the shaft forward, whereupon this - following an auxiliary track 33 - after the position according to FIG. 15 had been reached, a moving rail section 35 braked with friction 34 would take it down with it, after which the latter, with the transmission of a central rod 36, the conical towing element 18.16 a correspondingly precise movement and would thus end the movement. The by-pass control route described here is to be regarded as advantageous, since in this way the demands placed on the remote control effect with regard to the guiding provision, the sequence of the movement and the energy content are in no way exaggerated. If - taking the example described - no command for decoupling arrives, the tapered towing element 18.16 would of course also drag the towed product-transported element.

In the recently described versions - which describe a cycloidal orbit - the adjacent towing elements immediately compensate the mass force at a phase shift of 180 °, so that the greatest force occurring - regardless of the number of product-transporting elements used on the machine - is equal to that The inertia of a single product-transporting element is identical, which means that with a 4 kg element, with the feed 8000 steps per hour, with a 110 mm division Peak force of 320 N occurs with each towing element / if T _p = 4.5 T ₁ /. An extremely important property is shown in the fact that the expansion of the movement-transmitting element hardly influences the smooth running of the connections, the accuracy of the positions, since the points of standstill of the tapered drag elements 18 of the rack 17 are connected.

17 and 18 give an example for the execution of the special transmission of the motion transmitting element 9.7 according to FIGS. 7 and 8 / drag chain pair /. The structure and kinematics are similar to those of the version depicting a cycloid orbit.

A continuously rotating block 37 receives the movement from a driving gear 38. The continuously moving link roller 24.17 describes, as a result of the described planetary movement, also a pointed cycloid, the tangential movement component of which is transmitted to an upper sprocket 40 by means of a grooved shell 39. The neighboring planetary elements - thanks to the position difference of 180 ° with the crank arm - transfer a movement with a half-period phase shift to the lower sprocket, as a result of which the adjoining chains realize the previously defined movement conditions. In the interest of increased resilience, several link elements can of course be operated in parallel along the circumference. / Of course, high-precision elements must be used here to ensure even loading. /

It seems appropriate the special machine according to the invention in the first place as a universal basic machine, with the option of subsequently deciding the movement character that adapts to the current task, which can be achieved by the program prescribed for the programmer. The advantages are evident in the high-performance machines that carry out several operations.

Finally, an example of the design of a conventional stepper drive using the inventive concept is given in FIGS. 19 and 20. The main point is that even when using imprecise elements, a complete load compensation can be achieved.

The set rollers 24.19, which are set in motion in a manner consistent with the previously described, are in constant connection with link lines 41, which essentially move with a washer 42, since a connecting eye 45 and a connecting arm 46 with the aid of a guide pin 44 and an end pin 43 are one Allow movement with a degree of freedom for the relative displacement of the guide lines 41. This remaining degree of freedom is eliminated by the connection between a compensation eyelet 47 and a compensation chain 48. More specifically, this is a system with eight degrees of freedom, - also taking into account the rotation of the disk 42, - so the displacement of the link rollers 24.19, which has fewer errors, brings about the clear, preceding, average rotation of the disk 42.

Accordingly, the arm system not only performs the load balancing, but also the accuracy of the Steps increased. The errors partially compensate each other statistically.

From the uninterrupted series of steps of the disk 42, the conical towing element 18.19 transfers in a manner analogous to that described above every second, third, etc. movement periods to a disk 49 which executes discontinuous steps. The positioning element 8.19 is triggered under the pressure of the pressure-transmitting bolt 50 if the progress is started by lifting the conical towing element 18.19. The lifting is carried out by means of a collar 51 which removes the bolt, e.g. with the help of a movement mechanism designed with cams. The transmission ratios of the drive moving the cam determine the temporal relationship between standstill and movement

Compared to the known cam track versions, the load capacity of the stepper drive is much higher, which can be attributed primarily to the structure with the multi-load elements; the installation space is small / low structure /.

The principle of load balancing described can also be used in the chain drive according to FIG. 17 in the same way.

Claims

PATENT CLAIMS

1.Special machine for the production of workpieces that require several work steps with discontinuous movement of the product, consisting of a machine frame / 1 /, of the attached, on a bound track / 2 / discontinuously moving product-transporting elements / 3 / and the opposite of the machine frame / 1 / stationary processing units that connect with the products, characterized in that the product-transporting elements / 3 / on the bound web / 2 / individually or at least in two groups - arranged to be movable relative to one another - guided individually or in groups on the bound web, furthermore the product-transporting elements / 3 / has a connecting element / 5 / suitable for the cyclic connection, the connecting elements / 5 / following the system belonging to the machine / 6 / according to the program and the program by a programmer / 7 / guarantee t will.

2. Special machine according to claim 1, characterized in that the towing system / 6 / consists of a motion-transmitting element / 9 /, a towing element / 10 /, a transmission / 11 / and a motor / 12 /.

3. Special machine according to claim 1, characterized in that opposite the machine frame / 1 / stationary positioning elements / 8 / are provided which fix the product transporting elements / 3 / in the state of standstill.

4. Special machine according to claim 1, characterized in that between the movement transmitting element / 9 / and Towing element / 10 / there is a direct connection.

5. Special machine according to claim 4, characterized in that the bound path / 2 / is a circular path and the movement-transmitting element is a rigid disc or a ring rotating about a shaft.

6. Special machine according to claim 4, characterized in that the bound web / 2 / consists of straight and circular sections and the movement-transmitting element / 9 / is a chain following this track line.

7. Special machine according to claim 3 and 4, characterized in that the movement-transmitting element / 9 / is set in motion by a drive which ensures the momentary, cyclical standstill.

8. Special machine according to claim 7, characterized in that the towing system / 6 / has two movement-transmitting elements /10.7/ which move in the shifted phase.

9. Special machine according to claim 8, characterized in that a special gear / 11 / is provided which moves the two movement-transmitting elements in phase shift.

10. Special machine according to claim 7, characterized in that the towing element /10.7/ consists of a laminated package / 13 / which is slidably mounted in the plane.

11. Special machine according to claim 7, characterized in that the towing element / 10 / is a prism-shaped body / 54 / guided in two guides, which is designed at the end serving for the connection.

12. Special machine according to claim 1, characterized in that the connection between the movement-transmitting element / 9 / and the towing element / 10, 18 / via one in the movement transmitting element rotatably mounted crank arm / 14 / is realized.

13. Special machine according to claim 12, characterized in that the crank arm / 14 / is fixed by a gear / 15 / on a common shaft / 16 / and the rolling radius of the gear / 15 / substantially corresponds to the radius of the crank arm / 14 / .

14. Special machine according to claim 13, characterized in that toothed segment arches and / or racks / 17 / are attached to the machine frame, which are in constant connection with the movement-transmitting element / 9 / mounted gear wheels / 15 /.

15. Special machine according to claim 12, characterized in that the towing element / 10, 18 / mounted in the crank arm / 14 / secured against rotation is conical and is movable in the axial direction.

16. Special machine according to claim 12, characterized in that the connecting element / 5 / is designed with a nest and for receiving the towing element / 10, 13 /, which in the middle of the product-transporting element / 3 / linearly guided slide roller / 24 / is appropriately arranged, net is suitable.

17. Special machine according to claim 16, characterized in that a relative to the machine frame / 1 / stationary positioning element / 8, 8.11 / is provided, which with a to the jacket of the sliding block / 24 / adapting, o-shaped

Nest is designed.

18. special machine according to claim 17, characterized net that the positioning element 8, 8.11 / made of magnetic material and the positioning of the positioning element / 8, 8.11 / adapting jacket of the sliding block / 24 / made of ferromagnetic material.

19. Special machine according to claim 12, characterized in that the movement-transmitting element / 9 / is in a kinematic connection with a transmission / 11 / which ensures the continuous movement.

20. Special machine according to claim 15, characterized in that the towing elements / 10 / with the movement-transmitting element / 9 / displaceable control arms / 29 / and in different, at least in two moving bands mounted guide rollers / 28 / are provided per control arm; that opposite the machine frame / 1 / the guide rollers / 28 / assume a stationary position, the position being determined by the at least two control tracks / 25, 26, 27 / which are at a standstill and adapt to the movement band of the guide rollers / 28 /.

21. Special machine according to claim 20, characterized in that the control tracks which are at a standstill / 25, 26, 27 / are replaced at least for each section with a control flat plate / 30 /, and to move the control flat plates / 30 / vertically with one on their planes capable line and are connected to a programmer / 7 / in a control connection.

22. Special machine according to claim 15, characterized in that the towing element / 10.18 / by means of a flanged roller / 52 / in any of the leading pairs of grooves of the machine frame / 1 / stationary rail / 53 / ge leads.

23. Special machine according to claim 22, characterized in that the rail / 53 / is designed with interruptions and the interruptions of the stationary rail enclose the moving machine lines / 35 / running vertically on the track.

24. Special machine according to claim 23, characterized in that the movement-transmitting element / 9 / carries an auxiliary track / 33 / designed with a control track following its movement.

25. Special machine according to claim 24, characterized in that the moving rail track / 35 / with the warehouse of the shaft-provided control roller / 32 / is in a rigid connection and the control rollers / 32 / are mounted so that they are axially under a control effect are movable.

26. Special machine according to claim 25, characterized in that the control rollers provided with a shaft / 32 / are arranged such that they only come into contact with any control surface of the auxiliary track / 33 / in the state moved under the control effect.

27. Special machine according to claim 26, characterized in that the remote-controlled implementing elements with the programmer / 7 / are in an actuating connection.

28. Special machine according to claim 1, characterized in that the programmer / 7 / is programmed electronically.

29. Transmission with discontinuous rotary movement, with a continuously rotating input shaft, characterized in that a gearwheel which is stationary relative to a drive arm is provided with internal teeth or external teeth. furthermore at least one planetary gear /15.19/ which is in constant rolling connection therewith is provided, the planetary gear /15.19/ being rigidly connected to a crank arm A4.19 /, the crank arm A4.19 / a link roller /24.19/ mounted thereon, the link roller /24.19/ is guided in a link line / 41 / lying in the direction of the axis line of the stationary gear, and that the link line / 41 / is in an essentially rigid connection with a disk / 42 / mounted in the center line of the stationary gear.

30. Gearbox still claim 29, characterized in that the link line / 41 / supporting disc / 42 / has a controllable towing element /18.19/ capable of a cyclically relative positioned connection.

31. Transmission according to claim 30, characterized in that a, discontinuously progressing disc / 49 /, which is mounted in the center line of the stationary gear, is provided and has a connecting element /5.19/ capable of connecting to the towing element /18.19/.

32. Transmission according to claim 31, characterized in that a programmer / 7 / which is in a kinematic connection with the transmission and which is in a control connection with the towing elements /18.19/.

33. Transmission according to claim 30, characterized in that two or more link lines / 41 / are provided and the number of link rollers /24.19/ matches the number of link lines and the link lines / 41 / itself the disc / 42 / individually and to one relative movement capable connect, and the connection method results in a unit with several degrees of freedom, the number of degrees of freedom corresponding to the number of link lines / 41 /.

34. Transmission according to claim 33, characterized in that any link line / 41 / and any washer / 42 / are connected to one another by means of bolts which connect the two subsequent arms capable of twisting.

35. Transmission according to claim 34, characterized in that a with the of the link line / 41 / and the disc / 42 / existing unit moving endless compensation chain / 48 / is included.