EP1640125A1 - Process and apparatus for cutting a continuously guided rod in rod-shaped articles of variable length - Google Patents

Abstract

The cutting device (18) has associated adjusting devices which are coupled to a counter bearing (19) to produce one active connection. A servo drive (27) is associated with the cutting device and a servo drive (26) is associated with the counter bearing, with the servo drives being connected to one another by a control (28). Independent claim describes extruding machine producing lines of cigarettes, filters etc and having cutting machine as above. Independent claim describes method for cutting line of material where the length of the section can be adjusted by selectively moving the cutter or the counter bearing.

Description

The invention relates to a device for cutting at least one continuously conveyed strand into strand-like articles of variable length, in particular cigarettes, filters or the like, comprising a cutting device, an abutment and adjusting devices for the cutting device and the abutment for changing the cutting length of the article. Furthermore, the invention relates to a stranding machine for producing strand-like articles, in particular cigarettes, filters or the like, essentially comprising a storage container for the material to be processed, means for forming at least one continuously conveyed strand, a strand conveyor and a device for cutting the continuously conveyed strand. Furthermore, the invention relates to a method for cutting at least one continuously conveyed strand into strand-shaped articles of variable length, in particular cigarettes, filters or the like comprising the steps: feeding the strand into the region of a device for cutting in particular according to one of claims 1 to 21, with a cutter, an abutment and adjusting means for the cutter and the anvil, cutting at least one article of a first length from the strand, adjusting the cutter and the anvil to a changed article length, and cutting at least one article having a second length from the first length differs.

Such methods and devices are used in particular in the tobacco processing industry. Usually, the generic devices are part of a stranding machine for the production of cigarettes, filters or the like. The devices can also be used as a single machine. In the production of individual sections, the so-called sticks of the continuous strand of tobacco, filter material or the like, separated by means of the device for cutting. These cuts must be made exactly to produce a high and consistent quality. The device for cutting is preferably arranged above or below a strand or several strands. At the intersection of cutter and strand the abutment of the cutter must be opposite to prevent dodging of the strand and at the same time to ensure the leadership of the strand. Only then is an exact and reproducible cut quality achieved.

Depending on the order to be processed with the device or with the stranding machine, it may be necessary to change the cutting length of the articles. This means, for example, that in a first order cigarettes of a first length are to be separated from the strand and subsequently in a subsequent application cigarettes of a second length deviating from the first length. As already mentioned, it is an essential condition for an optimal cut, that the positions of cutting device and counter-bearing adapted to one of the respective cutting length and matched to each other on the other hand. In other words, an adjustment of the cutter and the abutment for each article length is required.

In known devices and methods, the change in the cutting length is associated with considerable effort. Thus, first various fasteners, such as e.g. Unions, the separate units cutting device and thrust bearing are released to successively adjust the cutter and the anvil and tune each other. This is very time consuming and can only be done with machine downtime, which in turn leads to a loss of production. Furthermore, the adjustment and adjustment of the required adjustments can only be made by trained personnel, since only with many years of experience, an optimal setting and optimal tuning can be achieved.

It is therefore an object of the present invention to provide a device which allows a simplified adjustment for cutting articles of variable length. Furthermore, it is an object of the invention to provide a simple to be set stranding machine create. Another object is to propose a simple and easy to handle method for cutting articles of variable length.

This object is achieved on the one hand by a device having the features mentioned in the fact that the adjusting devices for the cutting device and the counter-bearing for producing an operative connection are coupled together. As a result, a change in the length of the articles to be cut is ensured in a surprisingly simple and particularly effective manner. The length-adjustable device according to the invention ensures that the adjustment of one component by means of the operative connection leads to an automatic co-adjustment of the other component. In other words, the adjustment results in e.g. the cutter inevitably to a corresponding adjustment of the thrust bearing. Furthermore, the operative connection creates an automatic and inevitable adjustment of the adjustment of the cutting device on the one hand and the adjustment of the abutment on the other hand, without any intervention of an operator. Advantageously, u.a. a quick and safe adjustment of the entire device, the adjustment requiring no special expertise or experience. Due to the active compound of said components, the release and fixation effort is furthermore considerably reduced, since the actual adjustment is only to be made on a single component.

Preferably, an actuator is associated with both the counter bearing and the cutting device, wherein the actuators are connected to each other via a controller for producing the operative connection. As a result, the simple adjustment of the cutting device and the thrust bearing is supported particularly effective.

In an advantageous development of the invention, the abutment is assigned a device for superimposing an adjustment movement in addition to the actual drive movement. The device allows for a particularly simple and accurate adjustment of the anvil depending on the selected article length. On the other hand, the device also ensures an adjustment or adjustment of the position of the abutment during operation of the device, so that Downtime of the device for purposes of adjustment can be reduced or even avoided altogether.

Particularly preferred is the design of the device as an addition gear. The addition gear is particularly well suited to implement the coordinated Vertellung / settings.

On the other hand, the object is achieved by a stranding machine with the features mentioned in the fact that the device is designed for cutting according to one of claims 1 to 21. The advantages achieved thereby have already been described above, so that reference is made to avoid repetition on the statements regarding the device itself.

Furthermore, the object is achieved by a method with the steps mentioned above, that for changing the length of the strand to be cut articles only one component, namely either the cutting device or the anvil, is adjusted and the other component in dependence of the displaced component inevitably with misguided. As a result, the adjustment effort is significantly reduced. Furthermore, the coordination of the individual components is operator-independent, since an automatic adaptation results from the forced adjustment of the respective other component on the basis of the displaced component.

Preferably, the adjustment can also be done while the machine is running, so that dispensed with a machine downtime and a loss of production can be avoided.

Fig. 1

eine perspektivische Ansicht einer Strangmaschine mit einer Vorrichtung zum Schneiden eines kontinuierlich geförderten Strangs in strangförmige Artikel,

Fig. 2

eine schematische Darstellung einer ersten Ausführungsform der Vorrichtung zum Schneiden mit einer Schneideinrichtung, einem Gegenlager, einem gemeinsamen Antrieb für vorgenannten Komponenten sowie einer Steuerung zum Verknüpfen der Komponenten,

Fig.

3 eine schematische Darstellung einer weiteren Ausführungsform der Vorrichtung zum Schneiden mit einer Schneideinrichtung, einem Gegenlager, einem gemeinsamen Antrieb für die vorgenannten Komponenten sowie einer Steuerung zum Verknüpfen der Komponenten,

Fig. 4

eine schematische Darstellung einer weiteren Ausführungsform der Vorrichtung zum Schneiden mit einer Schneideinrichtung, einem Gegenlager, separaten Antrieben für die vorgenannten Komponenten sowie einer Steuerung zum Verknüpfen der Komponenten,

Fig. 5

eine Funktionsdarstellung der mit dem Strang in Eingriff befindlichen Schneideinrichtung,

Fig. 6

eine Seitenansicht einer ersten Ausführungsform des Gegenlagers mit einer als Doppelexzenter ausgebildeten Exzentereinheit im Schnitt,

Fig. 7

eine Seitenansicht einer weiteren Ausführungsform des Gegenlagers mit einer als Zahnschienensystem ausgebildeten Exzentereinheit im Schnitt,

Fig. 8a bis d

Detailansichten des Zahnschienensystems gemäß Figur 7,

Fig. 9a und b

Detailansichten einer weiteren Ausführungsform des Zahnschienensystems,

Fig. 10

eine Vorderansicht einer weiteren Ausführungsform des Gegenlagers als Tubenrad, und

Fig. 11

eine Seitenansicht der Ausführungsform gemäß Figur 10 im Schnitt.

Further advantageous and preferred features, embodiments or method steps will become apparent from the dependent claims and the description. Particularly preferred embodiments and the method will be explained in more detail with reference to the accompanying drawings. In the drawing shows:

Fig. 1

a perspective view of a stranding machine with a device for cutting a continuously conveyed strand in strand-like articles,

Fig. 2

a schematic representation of a first embodiment of the apparatus for cutting with a cutting device, an abutment, a common drive for the aforementioned components and a controller for linking the components,

FIG.

3 shows a schematic representation of a further embodiment of the device for cutting with a cutting device, an abutment, a common drive for the abovementioned components and a controller for linking the components,

Fig. 4

a schematic representation of another embodiment of the device for cutting with a cutting device, an abutment, separate drives for the aforementioned components and a controller for linking the components,

Fig. 5

a functional representation of the cutter engaged with the strand,

Fig. 6

a side view of a first embodiment of the thrust bearing with an eccentric formed as a double eccentric in section,

Fig. 7

a side view of another embodiment of the abutment with a trained as a rack rail system eccentric in section,

Fig. 8a to d

Detailed views of the rack rail system according to FIG. 7,

Fig. 9a and b

Detail views of another embodiment of the rack rail system,

Fig. 10

a front view of another embodiment of the abutment as Tubenrad, and

Fig. 11

a side view of the embodiment of Figure 10 in section.

The apparatus and method are for cutting articles from one or more parallel strands of tobacco, filter material or the like having a length adjustment of the variable length article cutting device.

For the sake of clarity, FIG. 1 shows, first, a device known as a stranding machine 10, which is used to produce rod-shaped articles, such as e.g. Cigarettes, filters or the like is used. The stranding machine 10, shown in the figure by way of example a cigarette rod machine, comprises substantially next to a storage container 11 for the material to be processed or a conveyor 12 for transporting the material from the storage container 11 to a storage shaft 13, means 14 for forming a Strands or more parallel strands, a strand conveyor 15 and a device 16 for cutting the continuously conveyed strand or several continuously funded strands. The stranding machine 10 may be formed as a single, double or multiple strand machine. In principle, strand machines 10 are for other products, such as e.g. Filter, constructed in a similar manner. In particular, each stranding machine 10 comprises a device 16 for cutting the continuously conveyed strand.

The principle of a first embodiment of this device 16 for cutting, for example, a single continuously conveyed strand 17 into rod-shaped or rod-shaped articles, which can also be operated as a single, separate unit, will be explained in detail initially with reference to FIG. The device 16 essentially comprises a cutting device 18 and an abutment 19. The abutment 19, a drive means 20 is assigned directly, wherein the drive means 20 by means of a toothed belt 21 or a comparable means in operative connection with the Counter bearing 19 is. However, the drive means 20 also serves to drive the cutting device 18. For this purpose, a mechanical coupling 22 is provided. The mechanical coupling 22 is designed as a bevel gear set 23. Other conventional couplings 22 are also used. The bevel gear set 23 is in operative connection with the drive means 20 via a toothed belt 24 or a comparable means. The coupling 22 is connected via a joint element 25, preferably a universal joint, with the cutting device 18 to the drive. Both the counter bearing 19 and the cutting device 18, an actuator 26 and 27 is assigned. The actuators 26, 27 in turn are connected to each other via a controller 28 for producing the operative connection.

Another embodiment of the invention is shown in FIG. The device 16 is in principle similar to the device 16 described above, so that the same reference numerals are used for the same parts. To produce the operative connection between the drive means 20 and the coupling 22, an adjusting mechanism 29 is provided which is associated with the mechanical coupling 22. The adjusting 29 serves to compensate for the phase shift of the drive means 20, which is triggered by an adjustment of the thrust bearing 19. The adjusting 29 is manually adjustable. Preferably, however, an adjusting drive 30 is assigned to the adjusting mechanism 29. The actuator 30 is in turn connected to the controller 28, which is also connected to the actuators 26, 27 of the cutting device 18 and the thrust bearing 19.

In the embodiment according to FIG. 4, which again has the essential components of the embodiments described above, the abutment 19 is assigned the drive means 20 and the cutting device 18 a separate drive means 31. The drive means 20, 31 are connected to each other via a control for producing the operative connection. Preferably, the controller is the controller 28, which already connects the actuators 26, 27 with each other. In other words, both the cutting device 18 and the abutment 19 is assigned its own main drive 31 and 20 and its own actuator 27 and 26, respectively.

The essential components of the cutting device 18 are a cutting wheel 32, which can be driven in rotation by means of the drive means 31, and at least one blade 33. The cutting wheel 32 is inclined with respect to the strand 17. Details on this will be explained in more detail below with reference to FIG. Preferably, a plurality of blades 33 are distributed on the circumference of the cutting wheel 32 with the Schneidraddurchmesser D _s and arranged at the same distance from each other. Each of the knives 33 is movable on the cutting wheel 32, namely preferably rotatable or pivotable about an axis extending radially relative to the cutting wheel 32. To change the inclination angle β between cutting wheel 32 or knife 33 and strand 17, the cutting wheel 32 is adjustable, namely formed in particular pivotable.

From the functional diagram according to FIG. 5, it can be seen that the or each strand 17 is conveyed continuously in the transport direction T. The axis of rotation R _{s of} the cutting wheel 32 extends at an angle to the strand 17. As a result, the central axis M _{s of} the cutting wheel 32 also runs obliquely or inclined at an angle, the so-called helix angle or inclination angle β, to the strand 17. The angle β is preferably between 60 ° and <90 °. The knives 33 are arranged on the cutting wheel 32 so that they run at the intersection S with the strand 17 perpendicular to the strand 17. Due to the inclination below said angle β and the rotation of the cutting wheel 32, there is a horizontal, preferably axial velocity component of the cutting wheel 32 or the respective knife 33 engaged in the direction of the strand 17 or in the transport direction T. The transport speed T of the strand 17 as well as the axial velocity component of the cutting wheel 32 and the knife 33 at the intersection S are almost identical. The inclination angle β is variable. However, in order to satisfy the condition "equality of the strand velocity and the axial velocity component" with the angle β changed, the rotational speed of the cutting wheel 32 is to be changed, which in turn leads to shortened or elongated articles, namely the sticks 34.

To illustrate a particularly preferred embodiment, the cutting device 18 additionally comprises a knife carrier 35 and a knife table 36. The knife carrier 35 serves to mount the cutting wheel 32 and is arranged on the knife table 36. The drive 31 for the cutting wheel 32 is assigned to the blade carrier 35. The knife table 36 itself is movable, namely formed in particular pivotable. For this purpose, the knife table 36 is pivotable about a pivot axis 37. The pivot axis 37 extends in the embodiment shown perpendicular to the strand 17. A pivoting about this pivot axis 37 leads to the change of the angle β. For automated pivoting of the knife table 36 and thus of the knife carrier 35 and the cutting wheel 32 is the knife table 36 associated with the actuator 27. The knife table 36 itself is mounted on a base 38, which in turn is arranged fixed to the frame. At or on the base 38, a carrier 39 for a support member 40 of the cutting wheel 32 is arranged. The stationary and rigid support member 40 is connected via a hinge 41 with the cutting wheel 32 and serves to guide the knife 33, which are arranged on the circumference of the cutting wheel 32 and (not shown) have radially inwardly directed guide elements. This ensures that the blades 33 are independent of the angle β in the intersection S always perpendicular to the strand 17.

The counter bearing 19 is formed in a first embodiment according to Figures 2 to 4 as a tube drive and comprises an eccentric 42. The eccentric 42 is a connecting rod 43, a holding element 44 and a guide member 45 assigned to the connecting rod 43. By the eccentric unit 42 and by the eccentric unit 42 associated components is also an axial velocity component of the holding element 44, which has a cutting gap 46, in the direction of the strand 17 and its transport direction T guaranteed. The holding element 44, that is the so-called tube, is arranged at a free end of the connecting rod 24. With the other end of the connecting rod 24 is attached to the eccentric 42. The guide element 45 is formed in the embodiment shown as a leaf spring 47. The leaf spring 47 is fixed at one end to the connecting rod 43 and at the other end frame or frame side. Instead of the leaf spring 47, however, other common guide elements 45 can be used. Due to the described design of the thrust bearing 19, the axial velocity component of the holding element 44th reached, which must correspond to the axial velocity component of the blade 33 at the intersection S.

The speed ratios of cutter 18 and thrust bearing 19 correspond. This means for the embodiment according to Figure 4, that both drives 20, 31 are coordinated with each other so that they are in the same speed ratio to each other. At the intersection S of knife 33 and strand 17, the knife 33 and the holding member 44 are diametrically opposed to the cutting gap 46, such that the strand 17 is guided within the holding element 44, namely in the tube, and the knife 33 to the full Passage through the strand 17 in the cutting gap 46 of the holding element 44 occurs. Both the knife 33 and the holding member 44 run with the strand 17 in the axial direction in the transport direction T, so that during the cut no relative movement between strand 17, knife 33 and retaining element 44 exists.

To adjust the eccentricity, ie to change the stroke of the eccentric 42, the abutment 19 or more precisely the eccentric 42 itself is assigned a device 48 for superimposing a rotational movement in addition to the rotational movement of the eccentric 42, wherein the rotational movement by a drive shaft 20 operatively connected to the drive 49 is generated. The device 48 is preferably designed as an addition gear 50. Other mechanical solutions for superimposing an additional movement on the eccentric unit 42 can also be used. The addition gear 50 essentially comprises two planetary gears 51, 52, which are connected in parallel with each other. Furthermore, an adjusting shaft 53 is part of the device 48. The two planetary gear 51, 52 are arranged as a link between the actuator 26 and the adjusting shaft 53. Both planetary gears 51, 52 have a ring gear 54 and 55, a set planetary gears 56 and 57 and a sun gear 58 and 59, respectively. Each set of planetary gears 56, 57 comprises one or more planetary gears, wherein in the embodiment shown two planet gears are provided are. All or individual drives 20, 31 or actuators 26, 27 are preferably designed as electric motors.

The actuator 26 is in operative connection with the ring gear 54, for example via a toothed belt 60 or the like. The ring gear 54 is on the one hand centered directly on the adjusting shaft 53 and centered on the other via the set planet gears 56 and the sun gear 58 indirectly on the adjusting shaft 53. The ring gear 55 is fixedly arranged on the frame 61 and positioned centrally relative to the drive shaft 49 of the eccentric unit 42. The sun gear 59 is fixedly connected to the drive shaft 49. The planetary gears of both sets 56, 57 are associated with each other in pairs, wherein each planetary gear of the set 56 are arranged with a planetary gear of the set 57 on a common axis 62 and 63, respectively. The adjusting shaft 53 is disposed within the formed as a hollow shaft 64 drive shaft 49, wherein the adjusting shaft 53 and the hollow shaft 64 are mounted against each other. The adjusting shaft 53 projects out of the hollow shaft 64 on the side facing the eccentric unit 42. At the protruding from the hollow shaft 64 end of the adjusting shaft 53, a gear 65 is arranged. The gear 65 is preferably formed integrally with the adjusting shaft 53 and in operative connection with the eccentric 42. Usually, adjusting shaft 53 and hollow shaft 64 rotate synchronously at the same speed or speed. By operating the actuator 26 in addition to the operation of the drive 20, a speed difference between the adjusting shaft 53 and hollow shaft 64 can be generated, so that a superimposed movement on the eccentric unit 42 can be exercised, which leads to the adjustment of the eccentricity. The hollow shaft 64 is in turn for example via a toothed belt 66 or the like with the drive 20 in operative connection.

The eccentric unit 42 shown in Figure 6 is a first embodiment of the first embodiment. The eccentric unit 42 according to FIG. 6 has a first disk 67, a second disk 68 and a pin 69 to form a double eccentric. The first disk 67 is associated with the drive shaft 49 of the eccentric unit 42 and mounted rotationally fixed on this symmetrically to the axis of rotation 70 of the adjusting shaft 53 or hollow shaft 64. The first disc 67 is thus driven to rotate directly by the drive shaft 49. The second disc 68 is arranged eccentrically to the first disc 67 and stored relative to the latter. The second disk 68 is in operative connection with the gear 65 of the adjusting shaft 53. On the second disc 68, the pin 69 is arranged, and eccentric to the central axis 71 of the Disc 68. The pin 69 is preferably an integral part of the disc 68, namely integrally connected thereto and serves to receive the connecting rod 43rd

An alternative embodiment of the first embodiment is shown in FIG. The eccentric unit 42 shown therein is formed of a rack rail system. The addition gear 50 is provided and formed in the same manner as described above, so that a further description is omitted. The eccentric unit 42 may be formed from a toothed rail 72 and a pin 73. The pin 73 is arranged on the toothed rail 72. In other words, the toothed rail 72 carries the pin 73, which is arranged eccentrically to the adjusting shaft 53 for the toothed rail 72. Preferably, however, according to FIG. 7, the eccentric unit 42 has two toothed rails, namely the dental splint 72, which carries the spigot 73, and a dental splint 74, which carries a balancing weight 75. The toothed rails 72, 74 are provided with a toothing 76 and 77, respectively, to form a linear guide. The two toothed or flat rails 72, 74 are by means of the toothing 76, 77 with the gear 65 of the adjusting 53 in engagement and thus in operative connection. By rotation of the gear 65, the toothed rails 72, 74 are linearly movable in opposite directions. The toothed rails 72, 74 are arranged on a plate 78, which is fixed, so rotationally fixed to the hollow shaft 64 is arranged. The guide member 45 in this embodiment is formed of a plurality of guides, preferably two side guides 79, 80 and a center guide 81. The details of the embodiment according to FIG. 7, in particular the design and arrangement of the toothed rails 72, 74, are shown in FIGS. 8a to d.

FIGS. 9a and b show a further embodiment of the first embodiment variant. The eccentric unit 42 according to FIG. 9 essentially corresponds to the eccentric unit 42 which has been described with reference to FIGS. 7 and 8, so that a renewed description is dispensed with. In contrast to the previously described embodiment of the rack rail system, the toothed rails 72, 74, however, are curved. Upon actuation of the adjusting shaft 53, which is in engagement with the teeth 76, 77, the toothed rails 72, 74 quasi rest on one another. The curvature may be circular, arcuate or otherwise shaped.

In another embodiment, not shown, an unbalance shaft may be additionally provided. The imbalance shaft serves to compensate for the radial stroke of the eccentric 42 and is driven by the drive 20, which also serves to drive the hollow shaft 64. At the imbalance shaft a Verstellgewicht is arranged, which is radially positionable in linear guides.

The trained as a so-called tube drive thrust bearing 19 is described only as an example. Alternatively, other well-known elements can be used as an abutment 19 with a corresponding holding element or holding elements.

Instead of the tube drive, according to a second embodiment, e.g. Also, a Tubenrad be used according to Figures 10 and 11 as an abutment 19. The tube wheel essentially comprises a rotationally drivable element 82, which serves as a conveying means and has at least one, but preferably a plurality of holding elements 83. The holding elements 83 serve to hold and guide the strand 17 or the strands 17 in particular at the time of cutting the strand 17 or the strands 17. Each holding element 83 has a cutting gap 84, which is designed to dip the knife 33. The element 82 is rotatably driven about an axis 85. Several, preferably twelve holding elements 83 are distributed uniformly over the circumference of the element / conveyor 82. Each support member 83 is pivotally mounted on the conveyor 82 so that format holders 86 associated with each support member 83 and in the illustrated embodiment are exemplified for holding two parallel conveyed strands 17, preferably in any position, but particularly at the time of counteracting during cutting of the strand 17 or the strands 17 parallel to the strand 17 and the strands 17 run. This is usually the horizontal position. To change the radius of the conveying means 82 or, more precisely, of the running circle L formed by the rotating holding elements 83, the holding elements 83 are designed to be radially adjustable. The adjustment can be done manually or automatically.

The conveyor 82 has two discs 87 and 88 which are mounted on the common axis 85. The preferably one-piece axis 85 is parallel angled or offset, that is, that it has two sections 85.1 and 85.2, the are arranged offset parallel to each other. The sections 85.1 and 85.2 or the central axes 89 and 90 of the sections 85.1 and 85.2 are parallel to each other. The outer disc 87, which is disposed at the free end 91 of the axis 85, is associated with the portion 85.1 and rotates about the central axis 89. The inner disc 88 is associated with the portion 85.2 and rotates about the central axis 90. Accordingly, the discs 87, 88 arranged parallel and axially offset from one another. Both discs 87, 88 are coupled together via hinge members 92 and thereby operatively connected so as to rotate about the central axes 89, 90 at the same speed. The holding elements 83 are associated with the front disc 87. More precisely, the retaining elements 83 are non-rotatably arranged at free ends 93 of the joint elements 92 which protrude beyond the disk 87.

The discs 87, 88 have the same diameter in the embodiment shown. However, the diameters can also be different. Each disc 87, 88 has adjusting elements 94. The adjusting elements 94 are arranged in the region of the circumference of the respective disc 87 or 88. The number of actuators 94 per disc 87, 88 corresponds to the number of holding elements 83. The actuators 94 are segmented, i. that each actuator 94 is formed separately from the adjacent actuator 94. Each retaining element 83 is associated with a pair of control elements. The pair of control elements is formed from an actuator 94 of the disc 87 and a corresponding actuator 94 of the disc 88. The adjusting elements 94 of a pair of adjusting elements are arranged one behind the other in front view. The connection between the discs 87, 88 and between the adjusting elements 94 of each pair of adjusting elements is made by the hinge elements 92, which are formed as well as the axis 85 parallel offset. The hinge elements 92 are mounted in the adjusting elements 94, so that the arranged on the hinge elements 92 retaining elements 83 are despite rotation of the discs 87, 88 always in the same position with respect to the alignment to the strands 17. The adjusting elements 94 are arranged in recesses 95 of the discs 87, 88.

The adjusting elements 94 may have different embodiments. Shown is an embodiment in which the actuating elements 94 each have a pin 96 or pin or the like, wherein the pins 96 guided in a control or actuating cam 97 are. The control cam 97 or a plurality of actuating curves 97 run radially outwards starting from the axis 85, so that a change in the position of the control curves 97, in particular a rotation of the disks 97 and 99 having the control curves 97, inevitably results in a radial adjustment of the control curves 97 Pins 96 and thus the actuators 94 has per se result. In other embodiments, the adjusting elements 94 spindles assigned by means of which the adjusting elements 94 are radially movable. For this purpose, the spindles are radially aligned and extend transversely to the axis 85. Other conventional adjustment mechanisms are also used.

The discs 87, 88 are driven in rotation by means of a drive 100. The drive 100 is connected via a toothed belt 101 or other transmission elements in operative connection with the disc 88. By the hinge elements 92, the rotation of the disc 88 on the disc 87 is transferable. Both discs 87, 88 basically rotate at the same speed. To change the diameter of the conveying means 82 or of the running circle L described by the holding elements 83, an additional movement can be superimposed on the rotational movement of the discs 87, 88. For this purpose, the disks 87, 88 are preceded by a device 102 which corresponds to the device 48. The device 102 is likewise designed as an addition gear 103. The addition gear 103, the components of which have already been described above in connection with the other embodiments, can be driven by means of an actuator 104, which is in operative connection with the gear 103 by means of a toothed belt 105 or an equivalent transmission element. Other mechanical solutions for superimposing an additional movement can also be used. The adjusting elements 94 of a pair of adjusting elements are operatively connected to one another by a coupling 106, in particular a Schmidt coupling. Other types of couplings, such as an Oldham coupling or drive shafts or other conventional coupling elements are also used.

The Tubenrad may be integrated, for example, in the arrangement of Figure 4, so that then the drive 100 and the actuator 104 are connected to the controller 28. The entire unit of conveyor 82, gear 103 and clutch (s) 106 is disposed on a frame 107 and guided on or in linear guides 108. Through a Actuator 109, the entire unit is designed height adjustable. The height adjustment serves to compensate for the change in diameter of the conveyor 82 or to compensate for the radial displacement of the holding elements 83. The actuator 109 may also be connected to the controller 28.

As an alternative to the above-described connections of the cutting device 18 with the abutment 19, which are formed from a combined mechanical and electrical coupling, the connection can also be formed purely electrically or purely mechanically.

In the following, the method principle for changing the cut length of the article will be described in more detail by way of example initially with reference to a single strand 17 made of tobacco, in particular with reference to FIGS. 4 and 6:
The strand 17 is produced in the stranding machine 10, in particular by the means 14. From the endless strand 17, which is continuously conveyed, the device 16 now cuts off individual articles, the sticks 34. The inclined cutting wheel 32 rotates with the blades 33. Upon impact of one of the knives 33 on the strand 17, ie at the intersection S, the knife 33 is perpendicular to the strand 17. The strand 17 is held or guided in the holding element 44, the tube. This prevents the strand 17 from escaping the knife 33 during cutting. The holding element 44 thus acts as an abutment. In order to achieve a complete cutting of the strand 17, the knife 33 exits on the opposite side of the strand 17 again, the knife 33 is immersed in the cutting gap 46 at this moment. During the entire cutting movement or cut execution, strand 17, knife 33 and holding element 44 move at the same speed in the transport direction T, since both the knife 33 and the holding element 44 have an axial velocity component at the point of intersection S. For the knife 33 this is determined by the inclination angle β of the cutting wheel 32 to the strand 17. For the retaining element 44, it is defined by the stroke or the eccentricity of the connecting rod 43. However, the determining parameter for the cut length is preferably the inclination angle β. Depending on the size of the inclination angle β, the rotational speed of the cutting wheel 32 must also change in order to fulfill the necessary condition for an optimum cutting "axial speed component of the blade corresponding to the conveying speed Due to the rotational speed or peripheral speed of the cutting wheel 32 results in a certain cutting length of the sticks 34. If, for example, reduces the angle of inclination β, and the speed must be reduced the reduced speed increases the time between two cuts so that, as a result, it leads to longer sticks 34. Each length of stick 34 is thus associated with a data set which contains the essential parameters strand speed, inclination angle, speed of the separating wheel for the respective device 16 ,

The change in length of the poles 34 is now introduced according to the invention so that an operator enters an altered pole length, for example via a control panel and thus the controller 28 notifies. The controller 28 searches for the predetermined pole length the corresponding inclination angle β, triggers an adjustment of the knife table 36 by means of the actuator 27 and adapts the rotational speed of the cutting wheel 32 via the drive 31 to the changed inclination angle β. Almost synchronously, the controller 28 passes on the changed data to the actuator 26 and the drive 20 and provides an adjustment of the holding elements 44 to the new positioning / adjustment of the blade 33. In other words, the position of the holding elements 44 is tracked so that they defies the changed cutting length at the intersection S again diametrically opposed to the knife 33. All steps take place automatically and are therefore operator-independent and can take place during the operation of the device 16 or the stranding machine 10. More precisely, the following happens: After or by the adjustment of the inclination angle β and the thereby triggered change in the rotational speed of the cutting wheel 32, the actuator 26 is activated and drives the addition gear 50 at. By the addition gear 50, a speed difference between the adjusting shaft 53 and the drive shaft 49 and hollow shaft 64 is generated so that the disc 67 is driven at a speed which differs from the driving speed of the disc 68. As a result, the stroke or the eccentricity of the pin 69 and thus of the connecting rod 43 is adjusted. This leads to the adjustment of the position / adjustment of the holding elements 44 as a function of the angle of inclination β changed at the outset, as well as to adapt the rotational speeds or the speed ratio of the drives 20 and 31st

With reference to the embodiment according to FIGS. 7 to 9, the method runs essentially the same. The method differs in that the plate 78 is driven at the drive speed of the hollow shaft 64, while the speed difference between the adjusting shaft 53 and hollow shaft 64 causes the adjusting shaft 53 causes a displacement of the toothed rails 72, 74, whereby the eccentricity of the pin 73 and thus the connecting rod 43 changed. This in turn leads to the adjustment of the position / setting of the holding elements 44 as a function of the angle of inclination β changed at the beginning. In the case of the use of linear toothed rails 72, 74 or the double eccentric compensation adjustment is necessary. With the adjustment of the eccentricity or of the stroke, the drive shaft of the drive 20 also twists. This phase shift must then be compensated by means of the actuator 30. This compensation setting is eliminated when using curved toothed rails 72, 74, since no phase shift occurs due to the curvature of the toothed rails 72, 74.

Of course, the procedures described also apply to several strands of tobacco, filter material or other materials to be cut at the same time. The adjustment of the inclination angle β can also be done manually on the cutting wheel 20. The other settings / adjustments then necessarily result from the coupling of cutting device 18 and abutment 19.

The cutting of several strands 17 at the same time, with variable length, will be explained in more detail with reference to FIGS. 4 and 11:
The change in length of the poles 34 is now introduced according to the invention so that an operator enters an altered pole length, for example via a control panel and thus the controller 28 notifies. The controller 28 searches for the predetermined pole length the corresponding inclination angle β, triggers an adjustment of the knife table 36 by means of the actuator 27 and adapts the rotational speed of the cutting wheel 32 via the drive 31 to the changed inclination angle β. Almost synchronously, the controller 28 forwards the changed data to the actuator 104 and the drive 100 and ensures that the holding elements 83 are adapted to the new one Positioning / adjustment of the knife 33. In other words, the position of the holding elements 83 is tracked, so that it defies the changed cutting length at the intersection S again diametrically opposite the knife 33. All steps take place automatically and are therefore operator-independent and can take place during the operation of the device 16 or the stranding machine 10. Specifically, the following happens: After or through the adjustment of the inclination angle β and the thereby triggered change in the rotational speed of the cutting wheel 32, the actuator 104 is activated and drives the addition gear 103 at. By the addition gear 103, a rotational movement superimposed on the discs 98, 99 is exercised, which leads to a rotation of the adjusting cam 97. By adjusting curves 97, the pins 96 are moved radially outward or inward, depending on the direction of rotation of the discs 98, 99, which leads to a change in the diameter of the running circle L by the adjustment of the adjusting elements 94. If the diameter of the running circle L increases with the number of holding elements 83 remaining the same, the cutting length also becomes greater because the intervals at which a holding element 83 passes through the point of intersection S become larger. By reducing the diameter, a shortening of the cutting length is achieved.

Since the strand 17 and the strands 17 are always conveyed in the same plane, a height adjustment of the conveyor 82 is necessary with a change in the diameter of the running circle, so that the holding elements 83 in the intersection point S are always in the line level. For height adjustment of the actuator 109 is activated, which moves the entire unit including the conveyor 82 up or down.

Claims (28)

Device for cutting at least one continuously conveyed strand (17) into strand-shaped articles of variable length, in particular cigarettes, filters or the like, comprising a cutting device (18), an abutment (19) and adjusting devices for the cutting device (18) and the abutment (19) for changing the cutting length of the articles, characterized in that the adjusting devices for the cutting device (18) and the abutment (19) are coupled together to produce an operative connection. Apparatus according to claim 1, characterized in that both the counter bearing (19) an actuator (26, 104) and the cutting device (18) is associated with an actuator (27), wherein the actuators (26, 27, 104) via a controller (28) are interconnected to produce the active compound. Apparatus according to claim 1 or 2, characterized in that at least one drive (20, 100) for driving the cutting device (18) and the counter-bearing (19) is provided. Apparatus according to claim 3, characterized in that the drive (20, 100) as a main drive for driving the thrust bearing (19) is formed and a mechanical coupling (22) for driving the cutting device (18). Apparatus according to claim 4, characterized in that the mechanical coupling (22) is associated with an adjusting mechanism (29). Apparatus according to claim 5, characterized in that associated with the Verstellgetnebe (29) is an actuator (30), wherein the actuator (30) to the controller (28) is connected. Device according to one of Claims 1 to 6, characterized in that a main drive (31) is associated with both the counter bearing (19), a main drive (20, 100) and the cutting device (18), the main drives (20, 31, 100 ) are connected to each other via a controller (28) for producing the operative connection. Device according to one of claims 1 to 7, characterized in that the cutting device (18) of a rotationally driven cutting wheel (32) arranged to form an axial velocity component in the direction of the strand (17) inclined thereto and for changing the inclination angle β is formed adjustable, and at least one on the cutting wheel (32) arranged knife (33) is formed. Apparatus according to claim 8, characterized in that the cutting device (18) for changing the inclination angle β a knife carrier (35) for receiving the cutting wheel (32), a knife table (36) for receiving the knife carrier (35) and the actuator (27). for pivoting the knife table (36) and the knife carrier (35) arranged thereon about a pivot axis (37) which runs vertically to the strand (17). Device according to one of claims 3 to 9, characterized in that the counter bearing (19) is associated with a device (48, 102) for superimposing an adjusting movement in addition to the actual drive movement. Device according to Claim 10, characterized in that the device (48, 102) is an addition gear (50, 103). Apparatus according to claim 10 or 11, characterized in that the actuator (26, 104) of the abutment (19) with the means (48, 102) is in operative connection. Device according to one of claims 1 to 12, characterized in that the abutment (19) is formed from a tube drive. Apparatus according to claim 13, characterized in that the tube drive comprises an eccentric unit (42). Apparatus according to claim 14, characterized in that the eccentric unit (42) has a connecting rod (43), a holding element (44) which has a cutting gap (46) at the free end of the connecting rod (43) and a connecting element (45) for the connecting rod (43) is assigned to form an axial velocity component of the cutting gap (46) in the transport direction T of the strand (17). Apparatus according to claim 14 or 15, characterized in that the eccentric unit (42) for forming a double eccentric a first rotatably driven disc (67) which is centrally positioned on an adjusting shaft (53) of the eccentric unit (42), a second disc (68 ) disposed eccentrically to the first disc (67) and a pin (69) disposed eccentrically to the second disc (68) and the adjusting shaft (53). Apparatus according to claim 14 or 15, characterized in that the eccentric unit (42) comprises a toothed rail (72) and a pin (73), wherein the toothed rail (72) eccentrically to an adjusting shaft (53) of the toothed rail (72) arranged pin (73) bears. Apparatus according to claim 17, characterized in that a second toothed rail (74) is provided which carries a balance weight (75). Apparatus according to claim 17 or 18, that the or each toothed rail (72, 74) is curved. Device according to one of claims 1 to 12, characterized in that the abutment (19) is formed from a tube wheel. Apparatus according to claim 20, characterized in that the tube wheel comprises a rotatably drivable element (82) having at least one holding element (83) having a cutting gap (84), wherein the or each holding element (83) for adjusting by the holding elements (83) formed running circle L is radially adjustable. A stranding machine for producing strand-like articles, in particular cigarettes, filters or the like, essentially comprising a storage container (11) for the material to be processed, means (14) for forming at least one continuously conveyed strand (17), a strand conveyor (15) and a device (16) for cutting the continuously conveyed strand (16), characterized in that the cutting device (16) according to any one of claims 1 to 21 is formed. Method for cutting at least one continuously conveyed strand (17) into strand-shaped articles of variable length, in particular cigarettes, filters or the like, comprising the steps: - Feeding the strand (17) in the region of a device (16) for cutting in particular according to one of claims 1 to 21, with a cutting device (18), an abutment (19) and adjusting devices for the cutting device (18) and the abutment ( 19) Cutting at least one article of a first length from the strand (17), - Adjusting the cutting device (18) and the anvil (19) to a changed article length, and Cutting at least one article having a second length that deviates from the first length,
characterized in that for varying the length of the strand (17) to be cut articles only one component, namely either the cutting device (18) or the anvil (19), is adjusted and the other component in dependence of the displaced component inevitably adjusted , A method according to claim 23, characterized in that the cutting device (18) is adjusted and this adjustment inevitably leads to a coordinated adjustment of the counter bearing (19). A method according to claim 23 or 24, characterized in that the adjustment is coordinated by means of a controller (28). Method according to Claim 25, characterized in that the controller (28) additionally controls or regulates the drives (20, 31, 100) for the cutting device (18) and the abutment (19). Method according to one of claims 23 to 26, characterized in that the adjustment can take place while the machine is running. Method according to one of Claims 25 to 27, characterized in that the device (16) for cutting is informed exclusively of a desired article length, on the basis of which the controller (28) executes the entire adjustment of the device (16) fully automatically.

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