EP2258522B1 - 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 having the features of the preamble of claim 1. 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.

Such 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, the endless strand of tobacco, filter material or the like, separated by means of the cutting device. 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 of Strand are separated and then in a subsequent order cigarettes of a second length, which deviates from the first length. As already mentioned, it is an essential condition for an optimal cut that the positions of the cutting device and the counter bearing are matched to the respective cutting length and matched to one another. In other words, an adjustment of the cutter and the abutment for each article length is required. The adjustment of the cutting length can be achieved, inter alia, by changing the diameter of the running circle L. However, this causes the distance between the cutter and the conveyor to change.

In known devices, 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 coordination of the required adjustments can be made only by trained specialist personnel, since only with many years of experience, an optimal setting and optimal tuning can be achieved. Complex is also a resulting from the change of the track height adjustment, which must be performed manually.

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 an easily adjustable stranding machine.

This object is achieved on the one hand by a device having the features mentioned in that the counter bearing is a Tubenrad, the Tubenrad an actuator is assigned for height adjustment. By means of the actuator for height adjustment, any change in the diameter of the circuit, for example, by replacing the Tubenrades during operation of the device automatically be compensated, without the elaborate parking work by an operator are necessary.

Preferably, the actuator is connected to the controller. With this embodiment, the entire adjustment can be optimally coordinated.

In an advantageous development of the invention, the counter bearing is assigned an addition gear as a device for superposition of an adjusting 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 anvil during operation of the device, so that downtime of the device for purposes of adjustment can be reduced or even avoided altogether. 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 5. The advantages achieved thereby have already been described above, so that reference is made to avoid repetition of the statements regarding the device itself.

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 device for cutting with a cutting device, an abutment, a common drive for the aforementioned components and a controller for linking the components,

Fig. 3

a schematic representation of another embodiment of the device for cutting with a cutting device, an abutment, a common drive for the aforementioned 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 according to FIG. 10 on average.

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, the basis of the FIG. 1 First, a known as a stranding machine 10 device is shown, which is used for the production of rod-shaped articles, such as cigarettes, filters or the like. 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, stranding machines 10 for other products, such as filters, constructed in a corresponding 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 articles, which can also be operated as a single, separate unit, will be described in detail first with reference to FIGS FIG. 2 explained in more detail. The device 16 essentially comprises a cutting device 18 and an abutment 19. The abutment 19 is directly associated with a drive means 20, the drive means 20 being in operative connection with the abutment 19 by means of a toothed belt 21 or a comparable means. 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 via a hinge element 25, preferably one Cardan joint, connected to the cutter 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 in FIG. 3 shown. 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 drive means 20 and the cutting device 18 is a separate drive means 31 associated with the abutment 19. 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 will be given below on the basis of FIG. 5 explained in more detail. 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 one with respect to the Cutting wheel 32 radially extending axis formed rotatable or pivotable. 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 function picture 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 in such a way that they run perpendicular to the strand 17 at the point of intersection S with 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 or the cutting wheel 32 is associated with the knife table 36 of 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 always perpendicular to the strand 17 regardless of the angle β at the intersection point S.

The counter-bearing 19 is in a first embodiment according to the FIGS. 2 to 4 formed as a tube drive and includes an eccentric 42. The eccentric 42 is associated with a connecting rod 43, a holding element 44 and a guide member 45 for 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 44 is 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 FIG. 4 in that both drives 20, 31 are coordinated with one another in such a way that they are at 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 for complete 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 48 assigned a device 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 shaft 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 gear 51, 52 have a ring gear 54 and 55, a set of planetary gears 56 and 57 and a sun gear 58 and 59. Each set planetary gears 56, 57 comprises one or more planetary gears, wherein in the illustrated embodiment, two planetary gears 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 adjusting 53rd and 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.

In the FIG. 6 shown eccentric 42 is a first embodiment of the first embodiment. The eccentric unit 42 according to FIG. 6 has a first disc 67, a second disc 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 the FIG. 7 refer to. 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 re-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 and according to FIG. 7 rejects the However, the eccentric 42 on two tooth rails, namely the toothed rail 72 which carries the pin 73, and a toothed rail 74 which carries a balance 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 tooth rails 72, 74 result from the FIGS. 8a to d.

In the FIGS. 9a and b a further embodiment of the first embodiment is shown. The eccentric unit 42 according to FIG. 9 corresponds essentially to the eccentric unit 42, which is based on the FIGS. 7 and 8th has been described, so that a renewed description is omitted. 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 can according to a second embodiment, for example, a Tubenrad according to the Figures 10 and 11 can be used 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 retainer 83 is pivotally mounted on the conveyor 82 so that format holders 86 associated with each retainer 83 and, in the illustrated embodiment, by way of example, hold two parallel transported strands 17, preferably in any position, but especially at the time of counter-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, which are arranged offset from each other in parallel. 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 holding elements 83 arranged on the hinge elements 92 are always in the same position with respect to the alignment with the strands 17, despite the rotation of the discs 87, 88. 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 adjusting elements 94 each have a pin 96 or pin or the like, wherein the pins 96 are guided in a control or adjusting cam 97. The control curve 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 can eg in the arrangement according to FIG. 4 be integrated, 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. By an 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.

• Der Strang 17 wird in der Strangmaschine 10 insbesondere mit den Mitteln 14 hergestellt. Vom endlosen Strang 17, der kontinuierlich gefördert wird, schneidet die Vorrichtung 16 nun einzelne Artikel, die Stöcke 34 ab. Das geneigte Schneidrad 32 mit den Messern 33 rotiert. Beim Auftreffen eines der Messer 33 auf den Strang 17, also im Schnittpunkt S, steht das Messer 33 senkrecht zum Strang 17. Der Strang 17 ist in dem Halteelement 44, der Tube, gehalten bzw. geführt. Dadurch wird verhindert, dass der Strang 17 dem Messer 33 beim Schnitt ausweicht. Das Halteelement 44 wirkt somit als Widerlager. Um ein vollständiges Durchschneiden des Strangs 17 zu erreichen, tritt das Messer 33 auf der gegenüberliegenden Seite des Strangs 17 wieder aus, wobei das Messer 33 in diesem Augenblick in den Schneidspalt 46 eintaucht. Während der gesamten Schnittbewegung bzw. Schnittausführung bewegen sich Strang 17, Messer 33 und Halteelement 44 mit gleicher Geschwindigkeit in Transportrichtung T, da sowohl das Messer 33 als auch das Halteelement 44 im Schnittpunkt S eine axiale Geschwindigkeitskomponente aufweisen. Für das Messer 33 wird diese durch den Neigungswinkel β des Schneidrades 32 zum Strang 17 bestimmt. Für das Halteelement 44 wird sie durch den Hub bzw. die Exzentrizität des Pleuels 43 definiert. Bestimmender Parameter für die Schnittlänge ist jedoch bevorzugt der Neigungswinkel β. In Abhängigkeit der Größe des Neigungswinkels β muß sich auch die Drehzahl des Schneidrades 32 ändern, um die notwendige Bedingung für einen optimalen Schnitt "axiale Geschwindigkeitskomponente des Messers entspricht Fördergeschwindigkeit des Strangs" einzuhalten, da der Strang 17 stets mit konstanter Geschwindigkeit gefördert wird. Bedingt durch die Drehzahl bzw. Umfangsgeschwindigkeit des Schneidrades 32 ergibt sich eine bestimmte Schnittlänge der Stöcke 34. Verkleinert man z.B. den Neigungswinkel β, muß auch die Drehzahl reduziert werden. Mit der reduzierten Drehzahl verlängert sich die Zeit zwischen zwei Schnitten, so dass es im Ergebnis zu längeren Stöcken 34 führt. Jeder Länge des Stocks 34 ist damit ein Datensatz zugeordnet, der die wesentlichen Parameter Stranggeschwindigkeit, Neigungswinkel, Drehzahl des Scheidrades für die jeweilige Vorrichtung 16 beinhaltet.

In the following, the method principle for changing the cutting length of the article is exemplified first with reference to a single strand 17 of tobacco, in particular on the basis of FIGS. 4 and 6 described in more detail:

• 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 when 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 comply with the necessary condition for an optimum cut "axial velocity component of the blade corresponds to the conveying speed of the strand", since the strand 17 is always conveyed at a constant speed. Due to the rotational speed or circumferential speed of the cutting wheel 32, a certain cutting length of the poles 34 results. If, for example, the inclination angle β is reduced, the rotational speed must also be reduced. With the reduced speed, the time between two cuts increases, resulting in longer sticks 34 as a result. Each length of the stick 34 is thus associated with a data set that includes the essential parameters strand speed, inclination angle, speed of the separating wheel for each device 16.

The change in length of the sticks 34 is now introduced according to the invention so that an operator inputs a changed stock length, for example, via a control panel and thus informs the controller 28. 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 26 and the drive 20 and provides for an adaptation of the holding elements 44 to the new positioning / adjustment of the knife 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 through 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 or hollow shaft 64 is generated so that the disc 67 is driven at a speed which differs from the drive speed of the disc 68. As a result, the stroke or the eccentricity of the pin 69 and thus of the connecting rod 43 are 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 procedure is 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 / adjustment of the holding elements 44 in Dependence of the input changed inclination angle β. 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.

• Die Längenveränderung der Stöcke 34 wird nun erfindungsgemäß so eingeleitet, dass ein Bediener eine veränderte Stocklänge beispielsweise über ein Bedienpult eingibt und damit der Steuerung 28 mitteilt. Die Steuerung 28 sucht zu der vorgegebenen Stocklänge den entsprechenden Neigungswinkel β, löst eine Verstellung des Messertisches 36 mittels des Stellantriebs 27 aus und passt die Drehzahl des Schneidrades 32 über den Antrieb 31 an den veränderten Neigungswinkel β an. Nahezu synchron leitet die Steuerung 28 die veränderten Daten an den Stellantrieb 104 sowie den Antrieb 100 weiter und sorgt für eine Anpassung der Haltelemente 83 an die neue Positionierung/Einstellung des Messers 33. Mit anderen Worten wird die Position der Halteelemente 83 nachgeführt, so dass diese trotzt der veränderten Schnittlänge im Schnittpunkt S wieder diametral dem Messer 33 gegenüberliegt. Alle Schritte erfolgen automatisch und sind somit bedienerunabhängig und können während des Betriebs der Vorrichtung 16 bzw. der Strangmaschine 10 erfolgen. Genauer passiert folgendes: Nach der bzw. durch die Verstellung des Neigungswinkels β und der dadurch ausgelösten Veränderung der Drehzahl des Schneidrades 32 wird der Stellantrieb 104 aktiviert und treibt das Additionsgetriebe 103 an. Durch das Additionsgetriebe 103 wird eine der Rotationsbewegung überlagerte Rotationsbewegung auf die Scheiben 98, 99 ausgeübt, was zu einer Verdrehung der Stellkurven 97 führt. Durch die Stellkurven 97 werden die Stifte 96 radial nach außen oder innen bewegt, je nach Drehrichtung der Scheiben 98, 99, was durch die Verstellung der Stellelemente 94 zu einer Veränderung des Durchmessers des Laufkreises L führ. Wird der Durchmesser des Laufkreises L bei gleichbleibender Anzahl Halteelemente 83 größer, wird die Schnittlänge ebenfalls größer, weil die Intervalle, in denen ein Halteelement 83 den Schnittpunkt S durchläuft, größer werden. Durch Reduzierung des Durchmessers wird eine Verkürzung der Schnittlänge erreicht.

The cutting of several strands 17 at the same time, with variable length, is based on the FIGS. 4 and 11 explained in more detail:

• The change in length of the sticks 34 is now introduced according to the invention so that an operator inputs a changed stock length, for example, via a control panel and thus informs the controller 28. 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 adjusts 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 104 and the drive 100 and ensures an adaptation of the holding elements 83 to the new positioning / adjustment of the blade 33. In other words, the position of the holding elements 83 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. 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 is one of Rotational movement superimposed rotational movement on the discs 98, 99 exercised, resulting in a rotation of the control curves 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 (6)

1. Apparatus for cutting at least one continuously conveyed rod (17) into rod-shaped articles of variable length, in particular cigarettes, filters or the like, including a cutting device (18) formed from a cutting wheel (32) which is rotatable by means of a drive means (31), which is arranged at an angle to the rod (17) to form an axial speed component in the direction of the rod (17) and is displaceable to vary the angle of inclination β, and at least one blade (33) arranged on the cutting wheel (32), wherein the cutting device (18) for varying the angle of inclination β includes a blade carrier (35) for receiving the cutting wheel (32), a blade table (36) for receiving the blade carrier (35), and the adjusting drive (27) for pivoting the blade table (36) and the blade carrier (35) arranged thereon about a pivot axis (37) which runs vertically to the rod (17), a counter-support (19), wherein the counter-support (19) is assigned a drive means (100) for driving the counter-support (19), as well as a control means (28) for controlling the drive means (31, 100) and the adjusting drive (27), characterized in that the counter-support (19) is a tube wheel, wherein the tube wheel is assigned an adjusting drive (109) for adaptation of height.
2. Apparatus according to claim 1, characterized in that the adjusting drive (109) is connected to the control system (28).
3. Apparatus according to claim 1 or 2, characterized in that the counter-support (19) is assigned an addition gear mechanism as a device (102) for superimposing a displacing movement in addition to the actual driving movement.
4. Apparatus according to claim 3, characterized in that the tube wheel is assigned an adjusting drive (104) which is in functional connection with the device (102) and is connected to the control system (28).
5. Apparatus according to any one of claims 1 to 4, characterized in that the tube wheel includes a rotatable element (82) with at least one holding element (83) comprising a cutting gap (84), the or each holding element (83) being radially displaceable for adjustment of the running circle L formed by the holding elements (83).
6. Continuous rod-making machine for the manufacture of rod-shaped articles, in particular cigarettes, filters or the like, essentially including a storage container (11) for the material to be processed, means (14) for forming at least one continuously conveyed rod (17), a rod conveyor (15) and an apparatus (16) for cutting the continuously conveyed rod (17), characterized in that the apparatus (16) for cutting is designed according to any one of claims 1 to 5.

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