EP2625970A2 - Longitudinal conveyor device for rod-shaped articles from the tobacco processing industry - Google Patents

Abstract

The conveyer (1) has lever arms (8) mounted at a rotatory drivable drum (33) in a rotatable movable manner and driven for a rotating movement that is opposite to a rotating movement of the drum at a rotation speed identical to speed of the drum or integral multiples of the rotation speed of the drum. Arms (9) are rotatably mounted at the lever arms, and retainers (10, 11) for rod-shaped products (6, 7) are provided at the arms. The retainers are moved from a crossover point (I) to a transfer point of the products. The lever arms are driven by a swash plate drive.

Description

The invention relates to a longitudinal conveyor for rod-shaped products of the tobacco-processing industry having the features of the preamble of claim 1.

Such longitudinal conveyors are known in the prior art and serve to remove the products continuously fed on one web or on two or more parallel webs and to feed the transverse conveyors conveying the products transversely to the feeding movement, whereby the conveying process can also be reversed.

The longitudinal conveyor is formed of a rotationally driven about a first axis of rotation drum having a plurality of rotationally driven about second axes of rotation lever arms, wherein the second axes of rotation are arranged parallel to the first axis of rotation. The lever arms are driven during the rotational movement of the drum to an opposite to the rotational movement of the drum rotational movement at an identical speed or at an integral multiple of the rotational speed of the drum. The described rotation of the lever arms is the rotational movement which an external viewer would perceive. At the ends of the lever arms projecting arms are provided with a number of tracks corresponding number of receptacles, which are aligned parallel to the tracks and acted upon via a compressed air line in a takeover point and in a transfer point with compressed air. With compressed air according to the invention, both overpressure and negative pressure meant. The arms are moved due to the opposite rotational movement of the lever arms about its longitudinal axis to the drum on an elliptical trajectory and are held during the rotational movements of the drum and the lever arms in a constant, preferably horizontal orientation.

The rod-shaped products are conveyed out of the linear feed at the lower lowest point of the ellipse (first point) and transferred to the transverse conveyor in the subsequent lateral point of the ellipse (second point) farthest from the rotation axis. With a correct adjustment of the sequence of movements of the images they are moved in the first turning point almost parallel to the longitudinal axes of the supplied rod-shaped products and in the second turning point almost transverse to the longitudinal axes of the rod-shaped products.

The rotational movement of the lever arms to the drum is realized via a complex, high-speed transmission, which transmits the rotational movement of the drive means to the lever arms. The transmission is formed by a central sun gear and arranged on the lever arms planetary gears and requires a complex lubrication with a corresponding seal. Overall, the transmission is structurally very expensive and expensive. In addition, the lubrication of the lever arms with oil is relatively often affected by oil leakage, which can lead to contamination of the products and the conveyor in general. Furthermore, a minimum clearance between the gear pairings is required for a trouble-free movement of the operation in each case, which in the addition of the transmission chain of the various gears can lead to a different game of the individual lever arms, so that the lever arms, despite correct installation and adjustment finally during the rotational movement different from each other and are aligned differently from the horizontal orientation.

Such a longitudinal conveyor is for example from the DE 41 29 672 A1 known.

Against this background, the invention has for its object to provide a longitudinal conveyor, in which the disadvantages described above are avoided.

The object is achieved by a longitudinal conveyor with the features of claim 1.

Further preferred developments of the invention can be taken from the subclaims, the figures and the associated description.

According to the basic idea of the invention according to claim 1, it is proposed that the lever arms can be driven by means of a wobble drive. The drive of the lever arms by means of the wobble drive has the advantage that the lever arms are not driven by intermeshing gears, which must be lubricated by an oil sump expensive, but are instead driven by the wobble drive alone by mutually rotatably mounted parts, which much simpler if necessary, can be lubricated with grease. Furthermore, the rotational movement can be transmitted with a correct design of the wobble drive in a very simple kinematic way with a very small number of items. In particular, eliminates the costly to produce and expensive gears, which also need to be individually stored, mounted and adjusted. It is further proposed that the wobble drive comprises a swash plate which drives at least two of the lever arms at the same time.

The advantage of the proposed solution is the fact that the wobble drive integrated particularly easy in the longitudinal conveyor and the tumbling motion can be particularly easily adapted to the rotational movement of the drum and to the rotational movement of the arranged in the drum lever arms. In this case, the swashplate two or more of the lever arms and ideally all lever arms are guided simultaneously and directly, so that the number of parts required for transmitting the rotational movement reduced to the lever arms and ideally to a single part, namely the swash plate, can be reduced. Here, the term "swash plate" is to be understood as including both a disc and a frame to be understood, it is only important that the lever arms in the swash plate or the frame are guided and driven in a fixed spatial relationship to each other. Ideally, the lever arms can thus be driven without play, with only a small bearing clearance is required for a jam-free drive of the lever arms, but for the alignment of the lever arms has no adverse effect. Furthermore, the proposed drive of the lever arms of the assembly and disassembly effort can be significantly reduced, since the previously required complex gear is eliminated, and instead only the swash plate must be mounted or dismantled.

It is also proposed that the swash plate can be driven by means of an eccentric disc driven in opposite directions to the direction of rotation of the drum to a tumbling motion. The advantage of the proposed solution is the fact that to drive the swash plate only a single part, namely the eccentric, is required. The tumbling motion of the swash plate results from a superposition of the rotational movement of the swash plate with the drum and the lever arms and the counter-rotating eccentric disc on which the swash plate is mounted.

The wobbling motion of the swash plate is particularly easily implemented in a rotational movement of the lever arms by the swash plate has receptacles in which engage the lever arms in each case with an eccentric. Since the lever arms rotate with the drum and the swash plate also rotates about the lever arms with the drum, the recordings in the swash plate with a corresponding design of the eccentric perform a rotational movement about the axes of rotation of the lever arms, which by the engagement of the lever arms on the eccentric in a rotational movement of the lever arms relative to the swash plate and the drum is converted.

In this case, it is advantageous for a jam-free movement of the longitudinal conveyor, when the eccentricity of the eccentric disc and the eccentric of the lever arms are identical, wherein the eccentricity is preferably 5 to 40 mm and preferably 20 mm. Furthermore, the proposed eccentricity has been found to be favorable in terms of the lowest possible load on the parts of the wobble drive at the same time as possible a harmonious sequence of movements.

Furthermore, it makes sense for a jam-free and harmonious movement sequence when the eccentrics of the lever arms have an at least nearly identical orientation to the axes of rotation of the lever arms. Thus, the recordings of the swash plate rotate with the eccentrics of the lever arms arranged therein respectively in an identical angular orientation to the axes of rotation of the lever arms.

Basically, the proposed solution enables a play-free drive of the lever arms, so that the lever arms comply with their once preset orientation absolutely and each other much more accurate. In the case of an unwanted or intentional adjustment of the orientation of the lever arms, the lever arms are adjusted together and identically, so that their orientation to each other is not changed substantially.

Basically, the lever arms are driven without play by a mechanically overdetermined system. Thus, the movement in any position inhibits even under unfavorable balance of power itself, it is proposed that the eccentrics of the lever arms are torsionally rigid and pliable. The eccentrics are flexurally but torsionally rigid coupled in itself or in the connection to the lever arms, so that the rotational movement is transmitted as possible without torsion and tension can be compensated by a flexurally soft yielding of the eccentric or the connection between the eccentrics and the lever arms so far that the movement does not jam.

The clamping of the movement sequence can also be prevented by the eccentric of the lever arms in the recordings have a different bearing clearance.

In this case, one of the eccentric with a particularly small bearing clearance in a receptacle and the other eccentric be stored with a larger bearing clearance in the recordings, so that a lever arm during the movement quasi a leadership function is assigned, while the other lever arms perform an identical movement with a small compensation possibility.

The same effect can be achieved by three of the eccentric are stored with a particularly small bearing clearance and the other eccentric with a larger bearing clearance in the recordings. The swash plate is thereby mounted on three of the lever arms in the manner of a three-point bearing, which allows a particularly good guidance of the lever arms relative to the swash plate and vice versa.

Furthermore, a small compensation possibility for an unrestrained movement sequence can be achieved by the eccentrics are mounted by means of elastically mounted in the receptacles bearing rings.

According to a further preferred embodiment of the invention it is proposed that the eccentric disc is drivable via a coupled to the drive means of the drum rotation direction reversing gear. By reversing the direction of rotation, the drum and the eccentric disc can be driven by one and the same drive means, the rotational speed for driving the eccentric disc neither under nor has to be translated, since the eccentric is driven at an identical speed. In addition to the use of a single drive means, this also results in the advantage that the movement of the drum and the eccentric disc are coupled together.

Alternatively, it is proposed that the eccentric disc is controllable via a second drive device, which can be controlled separately from the drive device of the drum. Although the cost of the second drive device increased, but it results in the significant advantage for the present invention that the movements of the drum and the eccentric disc are independently controllable.

It is also proposed that the distances between the axes of rotation of the lever arms to the axis of rotation of the drum and the distances between the axes of rotation of the eccentrics of the lever arms are identical to the center of the eccentric disc rotating about the axis of rotation of the drum. Due to the proposed dimensioning of the distances, a particularly tension-free movement sequence can be achieved.

It is further proposed that the eccentric disc has at least one recess lying opposite the eccentricity of the eccentric disk and / or that a compensating mass arranged opposite the center of the eccentric disk revolving around the axis of rotation of the drum is provided. Due to the proposed recess and / or the balancing mass given by the eccentricity of the swash plate unbalance can be compensated so far that the center of gravity is arranged in total again on the axis of rotation of the drum.

It is further proposed that the swash plate has an adapted to the arrangement and the shape of the receptacles outer contour, whereby the mass of the swash plate can be reduced overall.

It is also proposed that the drive device is oil-lubricated and the wobble drive is not lubricated with oil. By the proposed solution, the longitudinal conveyor can be divided into a total of two constructive assemblies, namely the oil-lubricated drive unit and the not oil-lubricated and maximum greased drum with the swash plate. So that can The drum with the swash plate can be dismantled without having to disassemble an oil-lubricated assembly. The dismantling process is thus clearly facilitated and simplified, since the dismantling does not take place "in the oil".

Fig. 1:

einen Längsförderer mit einer Führungseinrichtung und einem Querförderer;

Fig. 2:

einen Längsförderer mit einer Antriebseinrichtung in Sicht von hinten;

Fig. 3:

einen Längsförderer mit einer Antriebseinrichtung in Schnittdarstellung;

Fig. 4:

einen Längsförderer mit einer Taumelscheibe und einem Koppelring;

Fig. 5:

einen Längsförderer mit einem Drehrichtungsumkehrgetriebe;

Fig. 6:

einen Ausschnitt eines Längsförderers in Schnittdarstellung;

Fig. 7:

einen Längsförderer mit zwei Antriebseinrichtungen in Schnittdarstellung;

Fig. 8:

eine schematische Darstellung zweier elliptischer Bewegungsbahnen der Arme des Längsförderers nach und vor einer Verstellung;

Fig. 9:

eine schematische Darstellung zweier elliptischer Bewegungsbahnen der Arme des Längsförderers nach und vor einer Verstellung mit einer gleichzeitigen Verschiebung des Längsförderers quer zu seiner Drehachse;

Fig.10:

Längsförderer in Sicht von vorne auf die Hebelarme;

Fig.11:

Längsförderer in Sicht auf die Taumelscheibe von vorne ohne Trommel;

Fig.12:

Längsförderer in Sicht auf die Taumelscheibe von hinten.

The invention will be explained below with reference to preferred embodiments with reference to the accompanying figures. Showing:

Fig. 1:

a longitudinal conveyor with a guide means and a cross conveyor;

Fig. 2:

a longitudinal conveyor with a drive device in view from behind;

3:

a longitudinal conveyor with a drive device in a sectional view;

4:

a longitudinal conveyor with a swash plate and a coupling ring;

Fig. 5:

a longitudinal conveyor with a reversing direction gear;

Fig. 6:

a section of a longitudinal conveyor in sectional view;

Fig. 7:

a longitudinal conveyor with two drive means in sectional view;

Fig. 8:

a schematic representation of two elliptical trajectories of the arms of the longitudinal conveyor to and before an adjustment;

Fig. 9:

a schematic representation of two elliptical trajectories of the arms of the longitudinal conveyor after and before an adjustment with a simultaneous displacement of the longitudinal conveyor transversely to its axis of rotation;

Figure 10:

Longitudinal conveyor in view from the front on the lever arms;

Figure 11:

Longitudinal conveyor in view of the swashplate from the front without drum;

Figure 12:

Longitudinal conveyor in view of the swashplate from the rear.

In the FIG. 1 is a conveyor according to the invention for rod-shaped products 6 and 7 of the tobacco-processing industry, such as cigarettes, cigarillos or filter rods single or multiple length with and without filters to recognize with a maximum thickness of 15 mm. The products 6 and 7 are cut in a preceding step by means of a rotating knife carrier of an endless strand in a predetermined length and on a guide means 3 on two parallel guideways 4 and 5 in two parallel strands of cut and juxtaposed products 6 and 7 in the direction of Transfer point I transports.

The guide device 3 is pivotally mounted in a pivot bearing 13 and formed by means of a height adjustment device 12 in the transfer point I for fine adjustment height adjustable.

During the further transport movement, the products 6 and 7 are transported away from a longitudinal conveyor 1 in the takeover point I of the guideways 4 and 5 and transported to a transfer point II. In the transfer point II, the products 6 and 7 are conveyed away transversely by a cross conveyor 2, which has a plurality of mutually arranged pivotable lever arms and fixed or non-pivotable, rotatable lever arms with arranged thereon receptacles, in which the products 6 and 7 means Negative pressure be adopted. The pivotable lever arms of the cross conveyor 2 are preferably guided on a to the later described arms of the longitudinal conveyor 1 without collision trajectory. This can e.g. be realized by the course of the movement path of the receptacles is selected such that the pivotable arms of the cross conveyor 2 radially enter from outside into the envelope of the arms of the longitudinal conveyor 1 and after taking over the products 6 and 7 again radially outward without that the lever arms thereby cut the path of movement of the remote from the longitudinal conveyor 1 recordings. This makes it possible, inter alia, to drive the longitudinal conveyor 1 and the transverse conveyor 2 with separately controllable individual drives, without causing the risk of a collision of the lever arms of the transverse conveyor 2 and the longitudinal conveyor 1.

The longitudinal conveyor 1 has a rotatably drivable drum 33, projecting on the end face of a plurality of rotatably mounted lever arms 8, the centers are equidistant to each other and each equidistant from the axis of rotation X of the drum 33 are arranged (see also FIG. 10 ). At the ends of the lever arms 8 are each provided to the lever arms 8 rotatably mounted arms 9, which in each case one or more parallel to The receiving direction of the products 6 and 7 arranged receptacles 10 and 11 have. The receptacles 10 and 11 protrude laterally from the arms 9 and include a free space open on one side between them, into which the pivotable lever arms of the cross conveyor 2 dive to take over the products 7 remote from the transverse conveyor 2. Due to the later described drive the lever arms 8 and the rotatable mounting of the arms 9, the arms 9 and in particular the receptacles 10 and 11 thereby on a in FIG. 8 shown elliptical trajectory 43 moves.

In the FIG. 2 the longitudinal conveyor 1 with a drive device 24 in the form of an electric motor can be seen from behind. The entire longitudinal conveyor 1 is fixed by means of a holder 18 on a stand 14, to which below the longitudinal conveyor 1 also a positive guide 52 in the form of a fixed arm 15 is arranged with a curved guide slot 17 arranged therein and a pin 16 guided therein. Further, on the stand 14, a device 51 for displacement of the longitudinal conveyor 1 in the transverse direction to its longitudinal axis in the form of an engaging in the holder 18 and held on the stator 14 fixedly held threaded rod is provided. Further, a coupling ring 20 can be seen, which is connected via a respective coupling arm 21 and gears 38 and 39, each with one of the arms 9. The view of the viewer facing the ends of the lever arms 8 are formed as eccentric 50 and stored in receptacles 32 of a swash plate 23, as in the Figures 5 and 6 can be seen.

In the FIG. 3 is the longitudinal conveyor 1 from the FIG. 2 to recognize in section along the cutting direction AA. The drive device 24 drives the drum 33 via a shaft 25 rotationally, whereby the held in the drum 33 Lever arms 8 are taken to a rotary motion. The axes of rotation Y of the lever arms 8 (see FIG. 10 ) run on a in the FIG. 8 with 42 designated circular path to.

On the shaft 25, a gear 26 is fixed (see also FIG. 5 ), which meshes with a mounted in a housing 19 gear 29. The gear 29 meshes simultaneously with a likewise mounted in the housing 19 gear 28, which in turn meshes with a gear 27 which is rotatably connected to an eccentric disc 31. The eccentric disc 31 is reduced by two recesses 35 in the mass and balanced by a balancing mass 34 together with the swash plate 23 to the axis of rotation of the shaft 25.

The gear pairings of the gears 26,29,28 and 27 together form a reversing gear 30, which drives the eccentric disc 31 to an opposite to the direction of rotation of the shaft 25 rotational movement at an identical speed. This is achieved in this direction of rotation reversal gear by the number of teeth of the gears 26 and 27 is identical. The number of teeth of the meshing gears 28 and 29 is preferably not identical and not identical to the numbers of teeth of the gears 26 and 27, so that the wear of the gears 28 and 29 is as uniform as possible.

On the eccentric disk 31, the swash plate 23 is rotatably mounted, which is driven in a rotation of the eccentric disk 31 against the rotational direction of the shaft 25 to a tumbling motion.

Further, a plurality of Justierbohrungen 51 are provided on the housing 19, via which the housing 19 and the longitudinal conveyor 1 in total in predetermined angular positions opposite the holder 18 and the stand 14 can be fixed for example by means of dowel pins or Absteckdornen. The Justierbohrungen 51 are arranged so that the rotation of the housing 19 and fixing on the respective adjustment bore 51 automatically rotation of the in FIG. 8 shown elliptical trajectory 43 by a predetermined angle result. The Justierbohrungen 51 thus facilitate the adjustment of the elliptical trajectory 43 insofar as a costly retiming or test driving the longitudinal conveyor 1 is no longer required. Each adjustment bore 51 stands for a preferred angular position of the elliptical trajectory.

In the FIG. 6 is an enlarged sectional view through the drum 33 of the longitudinal conveyor 1 can be seen. The lever arms 8 each engage with a shaft 22 provided in the drum 33 recess and are taken by the drum 33 during the rotational movement in the circumferential direction. The drum 33 is rotatably connected to the coupling ring 20, so that the coupling arms 21, the rotational movement of the drum 33 also perform with. Further, the ends of the lever arms 8 are each designed as an eccentric 50 and engage in corresponding receptacles 32 of the swash plate 23 a. The swash plate 23 thereby rotates with the drum 33 and is simultaneously driven by the counter-rotating eccentric disc 31 to a tumbling motion. The wobble of the swash plate 23 then passes through the arranged in the receptacles 32 eccentric 50 of the lever arms 8 to an opposite rotational movement of the lever arms 8 with respect to the rotating drum 33 about their own longitudinal axes, or in other words, to a compensation of the rotational movement of the drum 33rd

Due to the superposition of the rotational movement of the drum 33, which perform the lever arms 8 with, and the opposite direction Rotary movement of the lever arms 8 about their longitudinal axes at an identical speed, run the arms 9 and the receptacles 10 and 11 on a in the FIG. 8 shown elliptical trajectory 43 to.

The speed of the arms 9 and the receptacles 10 and 11 on the elliptical trajectory 43 can be divided into a horizontal speed and a vertical speed. The vertical and horizontal speeds of the arms 9 thereby change during the revolution from a transfer point I, in which the arms 9 are moved almost horizontally, to a transfer point II, in which the arms 9 are moved almost vertically. The decisive for the takeover of the products in the transfer point I overspeed is the horizontal speed of the arms 9 and the recordings 10 and 11 at this point.

In the FIG. 7 an alternative embodiment of the invention can be seen, in which for driving the eccentric disc 31, a separately controllable second drive means 40 is also provided in the form of an electric motor. The rotor of the electric motor is non-rotatably connected to a hollow shaft 41, which in turn is non-rotatably connected to the eccentric disc 31. The second drive device 40 also drives the eccentric disk 31 in the opposite direction to the rotational movement of the first drive device 24 and the drum 33, whereby the same above-described movement of the lever arms 8 and the arms 9 arranged thereon is effected.

In the in the Figures 2 . 3 and 5 Shown embodiment, the adjustment of the alignment of the elliptical trajectory 43 is effected in that the longitudinal conveyor 1 via a rotation of the in the FIG. 2 to be recognized threaded rod 52 along the guide on the stand 14 is moved transversely to its longitudinal axis. On the housing 19 of the reversing direction gear 30, a pin 16 is provided, which projects into the curved or curved guide slot 17 and during the displacement movement of the longitudinal conveyor 1 controlled by the course of the guide slot 17 rotation of the longitudinal conveyor 1 forces a total of its longitudinal axis. The longitudinal axis of the longitudinal conveyor 1 corresponds to the longitudinal axis of the drive shaft of the drum 33 and the axis of rotation of the drum 33. Since the elliptical trajectory 43 of the arms 9 in a fixed relation to the drum 33 and the longitudinal conveyor 1, the trajectory 43 is thereby automatically with twisted. Alternatively, by the rotation of the housing 19 and the eccentric disc 31 are rotated by a rotation of the gears 27,28 and 29 relative to the fixed to be considered gear 26 with respect to the in this case also to be regarded as a fixed drum 33, whereby the alignment of the lever arms 8 is also adjusted to the drum 33. The orientation of the lever arms 8 is here adjusted in the same manner as in the drive by the previously described rotating eccentric disc 31, with the difference that the drum 33 does not rotate in this case, ie it is only the relative rotation angle of the eccentric disc 31 to the drum 33 and thus only the orientation of the lever arms 8 adjusted to the drum 33. Alternatively, the elliptical trajectory of the arms 9 can also be adjusted by the drum 33 is rotated while holding the lever arms 9. This relative rotation of the eccentric disc 31 to the drum 33 and the lever arms 8 finally causes the rotation of the elliptical trajectory 43 in the dashed lines shown orientation 44 with a rotation of the main axes 45 and 46 of the ellipse in the position 47 and 48 by the angle A in the same Way how at a rotation of the longitudinal conveyor 1 in total about its longitudinal axis.

Further, it is necessary that the arms 9 be once again realigned after twisting the elliptical trajectory to correspond to the predetermined orientation in the takeover point and in the transfer point.

In the in the FIG. 7 illustrated embodiment, the angular offset between the eccentric disc 31 and the drum 33 is effected by a separate control of the second drive means 40 by the eccentric disc 31 before starting the first drive means 24 with a stationary drum 33 or rotating drum 33 by the second drive means 40 to a relative angle to the drum 33 is rotated. In addition to the simple adjustment of the elliptical trajectory 43 when the longitudinal conveyor 1 is at a standstill, the use of a second drive device 40 which can be controlled separately also permits fine adjustment of the elliptical trajectory 43 during the rotating drum 33. In particular, the alignment of the elliptical trajectory 43 and the first transfer point I can also be achieved as a function of the cutting movement of the products 6 and 7 to a predetermined rod length intersecting knife carrier done so that the positional accuracy of the products 6 and 7 can be improved to the recordings 10 and 11 by a corresponding control loop, resulting in the further transport of the products creates decisive advantages.

In the FIG. 8 the trajectory of the axes of rotation of the lever arms 8 is represented by a circular path 42. The elliptical trajectory of the arms 9 and the receptacles 10 and 11 arranged thereon are shown as dashed ellipse 43 before the adjustment and shown as an ellipse 44 after the adjustment. As can be seen from the illustration, the original takeover point I can be adjusted by adjusting the elliptical trajectory 43 into the transfer point I '. The overspeeding of the receptacles 10 and 11 in the new takeover point I 'is automatically lower since the takeover point I' is now located at a point on the ellipse 44 in which the receptacles 10 and 11 move at a slower rate in the direction of movement of the supplied products be moved without that the speed of the revolving arms 9 must be changed. Further, by the rotation of the ellipse 44 and the transfer point II in the transfer point II 'adjusted. The transfer point II is always in the vicinity of the point where the receptacles 10 and 11 have the greatest distance in the lateral direction to the axis of rotation.

If the transfer point I itself is adjusted, the rotation of the elliptical trajectory 47 by the displacement of the longitudinal conveyor 1 is transverse to its longitudinal axis, as in FIG. 2 represented, particularly advantageous, since thereby the elliptical trajectory 43 automatically also transversely to the axis of rotation of the drum 33, as in the FIG. 9 is shown, moved. Ideally, the height or side shift of the transfer point I and the transfer point II can be compensated so far that the transfer point exclusively horizontally and the transfer point II are moved only vertically.

Furthermore, it makes sense to adjust the compressed air system in the longitudinal conveyor 1 by appropriate design of the control edges so far that the receptacles 10 and 11 of the longitudinal conveyor 1 in the new position to the drum 33 in the new takeover point I 'be subjected to negative pressure or in the new transfer point II' with overpressure.

As a result, with the same longitudinal conveyor 1 with a very low cost different and optimal for the individual rod lengths of the products takeover points I and overspeed can be realized. Due to this adjustment of the takeover point I, the previously required or accepted high overspeed compared to the previous practice can be made smaller, thereby achieving advantages for a process-safe removal of the products.

All proposed solutions for adjusting the elliptical trajectory 43 has in common that the arms 9 and in particular the receptacles 10 and 11 disposed thereon must be adjusted again after the rotation of the elliptical trajectory 43 in the horizontal orientation or orientation in which the recordings 10th and 11 take over products 6 and 7 at takeover point I. For this purpose, the receptacles 10 and 11 of the arms 9 must be slightly rotated relative to the lever arms 8.

The rotation of the arms 9 to the lever arms 8 is made possible in the present embodiments by the coupling ring 20, which is slightly rotated to adjust the arms 9 at a standstill drum 33. The coupling ring 20 also has a number of arms 9 corresponding number of coupling arms 21.

As in the FIGS. 6 and 7 can be seen, the coupling arms 21 are rotatably connected to the ends in each case with a shaft 37, which upon rotation of the coupling ring 20 to their Be twisted longitudinal axis. The rotational movement of the shafts 37 is transmitted via a transmission with two or more gears 38 and 39 and a rotational movement transmitting belt on a rotatably mounted shaft 36 of the arms 9, so that the arms 9 in a rotation of the shafts 37 in the Hebalarmen 8 um the longitudinal axes of their shafts 36 are rotated. Due to the rotation of the arms 9, the alignment of the receptacles 10 and 11 can be adjusted again so far after the adjustment of the elliptical trajectory 43 that they are again aligned horizontally and / or in the direction of the transfer point I supplied products 6 and 7.

Furthermore, in the FIGS. 6 and 7 to provide the provided at the ends of the lever arms 8 eccentric 50, with which the lever arms 8 are rotatably mounted in corresponding receptacles 32 of the swash plate 23. The lever arms 8 comprise in addition to the eccentrics 50 each have a shaft 22 which are penetrated by the shafts 37 respectively. In addition, the lever arms 8 each have a frontally projecting radial arm 53, in whose radially outer portion in each case the shafts 36 of the arms 9 are rotatably mounted. During the rotational movement of the drum 33, the lever arms 8 are driven due to the wobbling movement of the swash plate 33 and the bearing of the lever arms 8 in the receptacles 32 via the eccentric 50 to a relative to the rotational movement of the drum 33 opposite rotational movement of the same speed. Because of this opposing rotational movement of the lever arms 8, the shafts 36 of the arms 9, which are mounted in the outer sections of the radial arms 53, are moved on the elliptical trajectory 43. The movement of the arms 9 is coupled only insofar with the movement of the lever arms 8 that the axes of rotation of the shafts 36 are guided on the elliptical trajectory 43, but on the other hand, a rotational movement about the axes of rotation of the shafts 36 relative to the lever arms 8 execute. The rotational movement of the shafts 36 to the lever arms 8 is enforced by the rotating with the drum 33 shafts 37, which are fixed relative to the drum 33 via the coupling arms 21.

Due to the rotation of the lever arms 8 and the standstill of the shafts 37 relative to the lever arms 8, the gear formed by the gears 38 and 39 and the rotational movement transmitting belt, are forced to rotate about the shafts 37, which then on the shafts 36th the arms 9 is transmitted, so that the arms 9 during the rotation of the drum 33 and the lever arms 8 have a constant orientation. By the coupling ring 20, the adjustment of the drum 33 and the adjustment of the lever arms 8 can be compensated so far that the arms 9 are finally regarded as stationary with a constant predetermined orientation.

In the FIG. 10 is the longitudinal conveyor 1 in view from the front on the lever arms 8 without the arms 9 can be seen. The lever arms 8 engage with their shafts 22 corresponding recesses in the drum 33, which are arranged concentrically to the rotational axis X of the drum 33 and equidistant from each other. The distances L1 of the axes of rotation Y of the shafts 22 of the lever arms 8 to the axis of rotation X of the drum 33 are identical and define the circular path 42 from FIG. 8 , The lengths L2 of the lever arms 8 are also identical and define the extension and compression of the geometry of the elliptical trajectory 43 in the direction of the major axes 45 and 46. On some of the shafts 22, the lever arms 8 have been omitted for better visibility. The shafts 22 each have an air supply bore 55, a pin 56 for alignment and a plurality of mounting holes 57 for the lever arms 8.

In the FIG. 11 the swash plate 23 can be seen in front view by the drum 33 from the FIG. 10 was removed. The swash plate 23 has a plurality of receptacles 32, which are arranged concentrically and equidistant from each other. Furthermore, the rotatably mounted on the shaft 25 eccentric disc 31 can be seen, which is arranged with its center V eccentric to the axis of rotation X of the longitudinal conveyor 1 and the shaft 25. The degree of eccentricity of the eccentric disc 31 is marked with e1. To reduce weight, two recesses 35 are provided on the eccentric disk 31, which are arranged with respect to the center V of the eccentric disk 31 on the side opposite the eccentricity e1 and thereby reduce the imbalance. The shafts 22 of the lever arms 8 are also arranged with their axes of rotation Y eccentric to the centers V of the receptacles 32 and guided with eccentrics 50 in the receptacles 32. The degree of eccentricity is here marked with e2.

The eccentricities e1 and e2 of the shafts 22 of the lever arms 8 and the eccentric disk 31 are identical in both the absolute dimension and the orientation, so that the connecting lines between the axis of rotation X of the shaft 25 and the axes of rotation Y of the shafts 22 and the connecting lines between the center Z of the eccentric disc 31 and the centers of the eccentric 50 are aligned parallel to each other and the distances L1 and L3 are identical.

The shaft 25 drives the unrecognizable drum 33 and the lever arms 8 in the clockwise direction in the arrow directions P, wherein the swash plate 23 is taken. At the same time, the eccentric disk 31 is rotated counterclockwise in the direction of the arrow Q driven. Since the swash plate 23 is mounted on the eccentric disc 31, this is simultaneously driven during the rotational movement in the direction of arrow P to a tumbling motion, during which the receptacles 32 rotate virtually around the shafts 22 in opposite directions and at an identical speed. Each shaft 22 thus rotates once during one revolution of the drum 33 about its axis of rotation Y against the direction of rotation P of the drum 33rd

In the FIG. 12 the longitudinal conveyor 1 can be seen in view of the balancing mass 34 from the rear. The balancing mass 34 rotates with the shaft 22 and is arranged with respect to the axis of rotation X of the shaft 25 on the opposite side of the eccentricity e1, so that the balancing mass 34 balances the imbalance and acts as a counterweight.

Furthermore, the swash plate 23 is provided on its outer contour 58 with a shape adapted to the arrangement and shaping of the receptacles 32, whereby the mass of the swash plate 23 can be reduced. Furthermore, the balancing weights 54 of the lever arms 8, which are held in a rotationally fixed manner on the shafts 22, can be seen, which likewise have an identical orientation to the shafts 22 due to the eccentric 50, which is aligned identically to the shafts 22.

The swash plate 23 forms together with the eccentric disc 31 has a very simple design tumble drive, with all lever arms 8 can be driven simultaneously in a fixed spatial allocation and alignment with each other. Since the lever arms 8 are mounted with the shafts 22 only in the receptacles 32, and the rotational movement of the lever arms 8 is effected only by a rotational movement of the eccentric 50, the wobble drive with a very small number of items and a be realized very simple construction structure. Furthermore, the wobble drive can be lubricated with grease, so that the longitudinal conveyor 1 can be performed in the region of the drum 33 without oil sump. If the drive means of the longitudinal conveyor 1, such as the direction of rotation reversal gear, must be lubricated with an oil sump, it is advisable to seal them separately against oil leakage and to provide after sealing a constructive interface on which the drum 33 with the wobble drive and the lever arms 8 can be dismantled as an assembly or successively. The assembly work can thus be improved and simplified in the conversion of the longitudinal conveyor 1 to a different format length of the products insofar as they no longer have to be made "in oil".

The advantage of the play-free drive of the lever arms 8 results from the overdetermination of the drive system, which can lead to tension and in extreme cases to self-locking of the longitudinal conveyor 1 at too small bearing clearance. For this reason, it may be useful to deliberately introduce into the system certain flexibilities, so that the drive of the lever arms 8 is stuck in any position. This can e.g. by a flexurally soft but torsionally rigid training of the lever arms 8 and in particular the eccentric 50 done. Alternatively, the bearing clearances of the eccentric 50 in the receptacles 32 can also be dimensioned differently or an elastic bearing can be provided between one or more of the eccentrics 50 in the receptacles 32.

Since the movement of the wobble drive due to the over-determination, although running without play, but also subject to the risk of self-locking, it may be advantageous that the swash plate 23, the eccentric disc 31 and other parts of the Taumeltriebs made together or at least in the processing of the tumble drive defining dimensions are processed together on a processing device, wherein the parts are clamped at the same time and are not stretched between the machining operations. This solution has the advantage that an inaccuracy in the processing, for example, the eccentric disc 31 also takes place during the processing of the swash plate 23, so that the dimensions are identical to each other in each case despite the error in position-specific mounting.

The eccentric disk 31 can also be driven by means of a belt drive, in which case care must be taken that the play in the movement drive is neither too great nor too small, so that the wobble drive does not inhibit itself or quickly wears out due to too much play and becomes unsteady ,

Claims (18)

Longitudinal conveyor (1) for rod-shaped products (6,7) of the tobacco-processing industry with: a drum (33) which can be driven rotationally by means of a drive device (24) in a rotational movement about a first axis of rotation, - A plurality of rotationally rotatably about second axes of rotation rotatably driven lever arms (8), wherein the second axes of rotation are arranged parallel to the first axes of rotation, and wherein - The lever arms (8) rotatably mounted on the drum (33) and to a to the rotational movement of the drum (33) in opposite directions with a rotational speed of the drum (33) identical speed or an integral multiple of the rotational speed of the drum (33) are drivable, and - Arms (9) rotatably mounted on the lever arms (8), on each of which at least one receptacle (10, 11) for a rod-shaped product (6, 7) is provided, which moves during the rotational movement of the drum (33) from a takeover point (10). I) are moved to a transfer point (II) of the products (6,7),
characterized in that - The lever arms (8) are driven by means of a wobble drive. Longitudinal conveyor according to claim 1, characterized in that - The wobble drive comprises a swash plate (23) which drives at least two of the lever arms (8) at the same time. Longitudinal conveyor according to claim 2, characterized in that - The swash plate (23) by means of a direction of rotation of the drum (33) in opposite directions driven eccentric disc (31) is drivable to a tumbling motion. Longitudinal conveyor (1) according to claim 2 or 3, characterized in that - The swash plate (23) has receptacles (32), in which engage the lever arms (8) each with an eccentric (50). Longitudinal conveyor (1) according to claim 2 and 3, characterized in that - The eccentricity (e1, e2) of the eccentric disc (31) and the eccentric (50) of the lever arms (8) are identical. Longitudinal conveyor (1) according to one of claims 3 or 4, characterized in that - The eccentricity (e1) of the eccentric (50) of the lever arms (8) 5 to 40 mm, preferably 20 mm. Longitudinal conveyor (1) according to one of claims 3 to 5, characterized in that - The eccentric (50) of the lever arms (8) have an identical orientation to the axes of rotation of the lever arms (8). Longitudinal conveyor (1) according to one of claims 3 to 6, characterized in that - The eccentric (50) of the lever arms (8) and / or the swash plate (23) torsionally rigid and bendable formed are. Longitudinal conveyor (1) according to one of claims 3 to 7, characterized in that - The eccentric (50) of the lever arms (8) in the receptacles (32) have a different bearing clearance. Longitudinal conveyor (1) according to claim 9, characterized in that - One of the eccentric (50) with a particularly small bearing clearance in a receptacle (32) and the other eccentric (50) are mounted with a larger bearing clearance in the receptacles (32). Longitudinal conveyor (1) according to claim 9, characterized in that - Three of the eccentric (50) with a particularly small bearing clearance and the other eccentric (50) are mounted with a larger bearing clearance in the receptacles (32). Longitudinal conveyor (1) according to one of claims 3 to 11, characterized in that - The eccentric (50) are mounted by means of in the receptacles (32) elastically mounted bearing rings. Longitudinal conveyor (1) according to one of the preceding claims, characterized in that - The eccentric disc (31) via a to the drive means (24) of the drum (33) coupled rotational direction reversing gear (30) is drivable. Longitudinal conveyor (1) according to one of claims 1 to 11, characterized in that - The eccentric disc (31) via a second drive means (40) is controllable, which is separately controlled by the drive means (24) of the drum (33). Longitudinal conveyor (1) according to one of the preceding claims, characterized in that - The distances (L1) of the axes of rotation of the lever arms (8) to the axis of rotation (X) of the drum (33) and the distances (L3) of the axes of rotation (V) of the eccentric (50) of the lever arms (8) to the about the axis of rotation (X) of the drum (33) circumferential center (Z) of the eccentric disc (31) are identical. Longitudinal conveyor (1) according to one of the preceding claims, characterized in that - The eccentric disc (31) has at least one with respect to the eccentricity (e1) of the eccentric disc (31) to its center (Z) opposite recess (35) and / or that to the about the axis of rotation (X) of the drum (33 ) circumferential center (Z) of the eccentric disc (31) arranged opposite balancing mass (34) is provided. Longitudinal conveyor (1) according to one of claims 2 to 16, characterized in that - The swash plate (23) has an adapted to the arrangement and the shape of the receptacles (32) outer contour (58). Longitudinal conveyor (1) according to one of the preceding claims, characterized in that - The drive device oil lubricated and the wobble drive are free of oil lubrication.

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