DE202016005707U1 - Transfer device for conveying flat elements, preferably folded into stacks Endlospappe, to a further processing machine - Google Patents

Abstract

Transfer device (1) for conveying starting material, preferably web material (11.1, 11.2), which is provided on storage devices (10.1, 10.2) and conveyed to a further processing machine (9), comprising a frame (2) of horizontal (3.1, 3.2) and vertical linkage (4), wherein the horizontal linkage (3.1, 3.2) extending transversely to the feed direction (6) of the web material (11.1, 11.2) and the vertical linkage (4) the support (12) of the frame (2) form, - at least one pair of guide rails (5.1, 5.2), which extend parallel in the feed direction (6) and on a horizontal linkage (3.1, 3.2) arranged releasably, laterally displaceable and thus to the width (14.1, 14.2) the web materials (11.1, 11.2) are adaptable, wherein a pair of guide rails (5.1, 5.2) has an inlet (7) and an outlet (8) for the feeding web material (11.1, 11.2), - at least one guide unit (20.1, 20.2 ) which is arranged on the horizontal linkage (3.1) and is suitable for conveying the web material (11.1, 11.2) along a path (19.1, 19.2), wherein a guide unit (20.1, 20.2) is held in a holding device (33.1, 33.2) on the horizontal linkage (3.1, 3.2) is laterally displaceable and wherein the guide unit (20.1, 20.2) and about a, transversely to the feed direction (6) extending axis (18.1, 18.2) rotates, characterized in that a guide unit (20.1 , 20.2) consists of a two-sided lever arm (21.1, 21.2) which is rotatable about its axis (18.1, 18.2), and which has an elliptical side surface in the side profile (22) or of two circular sections (FIG. 25.1, 25.2), the two chords of the circular sections (25.1, 25.2) forming a common axis of symmetry (24) and the two arc lengths (26.1, 26.2) forming the outer contour (38) of the two sides form nflächen (23.1, 23.2) and the side surfaces (23.1, 23.2) at their free ends in each case by a transverse strut (39.1, 39.2) are parallel spaced, wherein a cross strut (39.1, 39.2) of a web (28.1, 28.2) and a Wing tip (29.1, 29.2) is formed and that the guide unit (20.1, 20.2) is equipped with a drive (40).

Description

The present invention relates generally to the field of processing articles of sheetlike elements, such as paper and / or cardboard, in particular endless corrugated board, for the manufacture of boxes and cartons for the packaging of packaged goods. When processing z. B. endless corrugated cardboard boxes are on the one hand various steps or working procedures and on the other hand, various machines and devices for transport and mechanical processing, by deformation with and without material removal, necessary.

The present invention relates to such a transport device, hereinafter referred to as transfer device, for transporting or transporting starting material in the form of flat objects, wherein flat objects all types of paper and paperboard products is understood. Such sheet-like objects are made available, for example, as web material. As a description example here is a flat object, which is present as a fan-shaped folded, endless web material made of cardboard used. Such a fan-folded endless web material is provided in stacks on stocking facilities. The fan-folded sheet material may preferably consist of endless corrugated cardboard. The storage device is usually. a loaded transport pallet. The transport pallet is a flat construction of a certain size, e.g. B. a standardized Europoolpalette, which is used for storage and transport of flat objects. Such a pallet may be loaded with flat objects, which may preferably consist of zig-zag layer with or without pre-cut longitudinal grooves equipped endless corrugated board. Such transport pallets are moved and loaded with industrial trucks. With such storage facilities, a transfer device can be equipped.

For further processing of the flat objects, it is therefore necessary to remove them from a storage device and to a further processing machine, for. As a cardboard cutting machine to transport or transport. The gap between the provision of web materials on storage facilities and the inclusion of the web materials in a further processing machine, is closed by the subject invention "transfer device", according to the preamble of claim 1.

Such a web guide and such a method for transporting or transporting web material is known in the art EP 1 687 225 B1 disclosed.

The elements of such a transfer device consist of horizontal and vertical linkages which form a frame, the horizontal linkage of the frame extending transversely to the direction of advance of the fan-folded web material and the vertical linkage forming the supports of the frame, wherein at least one pair of guide rails, the extend in parallel in the feed direction, are attached to a horizontal linkage of the frame and provide the sheet material with a guide extending from the inlet to the outlet of a guide rail, the outlet being connectable to a further processing machine. The guide rails of at least one pair of guide rails are laterally slidable on the horizontal linkage and thereby adaptable to the width of the web materials so that the guide rails are suitable for web materials stacked in laterally separate parallel paths of at least two juxtaposed storage devices on which web material is stacked is to lead to the processing machine. The frame of a transfer device can be technically designed in such a way that the transfer device can also be used as a stand-alone device.

Furthermore, at the top horizontal linkage at least one reel, preferably two reels, which are held such that they are arranged laterally displaceable on the horizontal linkage and rotate about a, extending transversely to the feed direction of the web materials axis free. The known from the prior art rotating reel is formed of star-shaped bar elements that form an equilateral triangle. The angular distance between two adjacent vertical bar elements of the reel is 120 degrees. At the ends of the vertical bar elements extend horizontal bars which are connected to the vertical bar elements. The horizontal bars form the corner lines of the equilateral triangle. The distances between the corner lines give the same length sides of the triangle and correspond to the span length between two adjacent vertical bars of the reel. A span length corresponds to a length between the fold lines of a fan-folded sheet material. The known from the prior art web guide has, especially in the reel design disadvantages, which must be avoided.

Based on the aforementioned prior art, it is the object of the present invention to provide a transfer device, which is inexpensive to manufacture, efficient in transporting endless corrugated board from A to the processing machine B, waives the known reel, simply in Construction is, and has an advantageous drive to support the promotion of endless corrugated board.

• – einen Rahmen aus horizontalem und vertikalem Gestänge, wobei das horizontale Gestänge sich quer zur Vorschubrichtung des Bahnmaterials erstreckt und die vertikalen Gestänge die Träger des Rahmens bilden,
• – mindestens ein Paar von Führungsschienen, die sich in der Vorschubrichtung parallel erstrecken und die an einem horizontalen Gestänge lösbar angeordnet sind und seitlich verschiebbar und somit an die Breite der Bahnmaterialien anpassbar sind, wobei jedes Paar von Führungsschienen einen Einlass und einen Auslass für das zuführende Bahnmaterial aufweist,
• – mindestens eine Führungseinheit, die über eine Haltevorrichtung am horizontalen Gestänge angeordnet und dazu geeignet ist, das Bahnmaterial entlang eines Pfades zu befördern, wobei eine Führungseinheit derart gehalten wird, dass sie auf dem horizontalem Gestänge seitlich versetzbar ist und sich um eine, sich quer zur Vorschubrichtung erstreckende Achse dreht.

According to the invention, the solution consists of a transfer device for conveying starting material, preferably web material, which is provided on storage devices and conveyed to a further processing machine which comprises

• A frame of horizontal and vertical linkage, the horizontal linkage extending transversely to the direction of advance of the web material and the vertical linkage forming the supports of the frame,
• At least one pair of guide rails which extend in parallel in the feed direction and which are detachably mounted on a horizontal linkage and are laterally displaceable and thus adaptable to the width of the web materials, each pair of guide rails having an inlet and an outlet for the infeed web material having,
• - At least one guide unit, which is arranged via a holding device on the horizontal linkage and adapted to convey the web material along a path, wherein a guide unit is held such that it is laterally displaceable on the horizontal linkage and a, transverse to Feed direction extending axis rotates.

From the prior art, reels are known as a drive unit and / or guide unit. Reels can be provided with a drive unit or are driven by the unwinding of web material and are technical tools for winding and / or unwinding of elongate materials such as yarns, ropes, wires, tapes, etc. and therefore have a roll, coil or cross-shaped structure which is rotatably mounted about a central axis, on.

However, the central guide unit of a transfer device according to the invention has a different meaning and function than a rotary reel. According to the object, a flat web material, which is present in a zig-zag position as endless corrugated cardboard stacked on a storage device, to remove and supply to a further processed machine.

To solve this technical problem, the central guide unit is advantageously formed of a two-sided, rotatable lever arm which rotates about its central axis. The direction of rotation of a guide unit is, according to the viewing direction of 1 , anti-clockwise, ie counterclockwise. The direction of rotation of a guide unit can also be clockwise, it depends only on the lateral viewing direction. In all cases, a guide unit rotates along the path in the direction of the feed direction. Furthermore, mechanical forces are to be generated and used when conveying web material with the guide unit. The solution of these objects is achieved in a device of the type mentioned by means of the features mentioned in claim 1. Each lever arm of a guide unit acts like a shovel of a waterwheel. That is, each lever arm is suitable for transporting materials. The side profile of a guide unit is made approximately comparable to an ellipse and therefore looks almost like an air screw of an aircraft or as two, arranged 180 degrees opposite blades of a wind turbine from. The lateral shape of a guide unit may therefore consist of two parallel spaced, approximately elliptical side surfaces or the side surfaces may advantageously consist of two symmetrically arranged circular sections, which abut each other with their chord l _s , which forms the axis of symmetry of the two circular sections. The longitudinal axis of symmetry through the ellipse is identical to the longitudinal axis of symmetry of the circular sections. The area of a circle segment is formed by a straight chord l _s and an arc length l _b , which represents a certain length from the circumference. The outer contour of the side surfaces of a guide unit is formed by the arc length l _b . The web material is, after removal from the storage device, guided along this outer contour and supplied to the guide rails.

Between the two, in a plane parallel spaced side surfaces, along the arc length l _{b of} the ellipse or along the arc length l _{b of} the circular sections a wing, similar to the wing of an aircraft, be spanned. Are no wings spanned between the two side surfaces, is advantageously at the tapered, free outer ends of the side surfaces of a cross member. A cross strut is formed by a web and a wing tip, wherein each cross strut spaced the two side surfaces. The length of a transverse strut forms the width of a guide unit. For the different widths of sheet materials are advantageously different width guide units available, which, due to the detachable arrangement of the holding device on the horizontal linkage, can be changed quickly and easily.

Furthermore, the two webs of the guide unit have wing tips. In one revolution of a guide unit about the axis, the wing tips form the diameter of a circle. The diameter of a circle is thus dependent on the length of the side surfaces or the length of the axis of symmetry. The distance of the wing tips in a guide unit is determined on the one hand by the length of the chord l _s , which runs on the axis of symmetry and on the other hand by the angular distance of the two wing tips of 180 degrees. An angular distance of 180 degrees means that the two wing tips are spaced apart. Between the two transverse struts or wing tips is the outer contour of the guide unit, which extends along the feed direction. The outer contour is determined by the arc length l _{b of} the two circular sections. The two circle sections right and left of the symmetry axis are symmetrical to each other. D. h., The arc length l _{b of} a circular section determines the extent of the length of the outer contour in the guide unit. The arc length l _{b of} the guide unit corresponds to l _b = r ² times ¶ times α divided by 360 degrees and forms the measure of the distance between two fold lines of a fan-folded sheet material. Concretely, this means that the arc length l _{b of} the guide unit advantageously on the longitudinal distance between two successive fold lines in the web material, ie z. B. on the zig-zag folding of endless corrugated board, is tuned. The fold lines run in the web material transverse to the feed direction. Advantageously, the transverse struts can be axially displaced along the axis of symmetry between the side surfaces. For this purpose, the side surfaces and the transverse struts have corresponding corresponding means. The displacement of the transverse struts makes it possible to compensate for length tolerances at the distances between two adjacent fold lines in the web material.

Furthermore, the wing tips of the webs can be easily replaced and equipped with different wing tips. On the one hand, they can consist of different materials, such as plastic, rubber or metal, and on the other hand, they have different shapes and radii at the wing tip. With these measures, the sliding friction or the friction value between the wing tip and the web material should be optimally adjusted in a fold line.

Advantageously, with the different wing tips on the surface condition of the web materials are reacted to achieve optimum transport of the web materials and to avoid slippage between the wing tips and a to be transported web material.

The side surfaces may consist of thin-walled stamped sheet to keep the mass of a guide unit low. The same applies to the webs, which extend transversely to the feed direction of Bahnmaterialeien and allow cross-webs to transport the web materials.

The center axis of a guide unit is arranged in a holding device, which is located on the horizontal linkage, so that the guide unit can be moved laterally on the horizontal linkage and can rotate freely about an axis mounted transversely to the feed direction. In principle, the advance of the web material takes place through the cardboard loading in a further processing machine. The carton puller pulls the web material provided in the guide rails of the transfer device into the further processing machine. The advance of the cardboard is not continuous, but in equidistant intervals. It is fed a certain predetermined length of the web material, then stops the Kartonageneinzug and further processing of the retracted cardboard in the machine begins. When further processing is complete, the cardboard feeder pulls in the next length of corrugated board. When retracting the web material, the feeder is substantially supported by the guide unit, which is arranged along the path and the guide rails in the transfer device. The support consists on the one hand of the guide rails, which selectively feed the web material of the further processing machine and on the other hand from the rotatably mounted guide units which receive the web material from the storage facilities, along a path on the guide units and feed the guide rails. The wing tips of the guide unit engage in the fold lines of the web material and pick up on the storage device in zig-zag stacked web material. From the first engagement of a wing tip in the fold line of a web material to the delivery of this fold line of the web material in a guide rail, rotate the wing tips of a guide unit about its axis. To convey the web material is of the two-sided lever of the guide unit always, similar to the pedal of a bicycle, a lever arm in use, uzw. when a wing tip is engaged with a fold line of the web material, whereby a torque is generated.

Simplified shown is the torque M depending on the tensile force F from the moving in the feed direction web material and the acting lever a, from which M = F · a follows. In other words, the force system with the single force F acting at the tip of the wing, which now acts in M. The force F on the lever arm (the guide tip) thus always causes a rotation of the guide unit and a change in the lever a. When conveying a web material along a path by means of the guide unit according to the invention, which engages with its wingtip in a fold line, the lever changes a and thus also the torque changes M. The change of the lever a occurs due to the rotation of the impeller. Is this located? Impeller in the horizontal position, the lever a is the largest. In the assumed view of a left-handed guide unit while the radius r remains constant, but the lever a to the pivot point is lower because the impeller rotates from the horizontal to the vertical position, the wing tip is then vertical. In the vertical position, the lever a is the smallest. Upon further rotation of the impeller, the lever a increases again, up to the point where the wing tip leaves the fold line in the web material. The web material is then at the inlet of a guide rail.

Various drives are available for driving the guide unit. For example, the drive of a belt drive, a chain drive, a toothed belt drive or gear drive consist. The toothed belt drive, the chain drive and the gear drive have over the normal belt drive the advantage that a slip on the belt sheath can not be done. The toothed belt drive has a drive belt on which is provided with a toothing, wherein the toothing engages positively in toothed pulleys. The toothed belt drive combines the properties of a flat belt and a chain. Chain drives are traction mechanism. They transmit turning forces with a fixed or changeable gear ratio via a chain and sprockets. An arrangement of drive and driven gear with a revolving chain is referred to as a chain drive. The inventive guide unit is advantageously equipped with a supporting vibration damping gear drive. The vibration damping gear drive affects the torque M and the vibration that occurs at the wing tip of a guide unit, while conveying web material along the path. The supporting vibration damping gear drive is integrated in the holding device of the guide unit. The vibration damping gear drive consists of three successively meshing gears, a one-sided lever arm, which is arranged on a gear and one, hinged to the lever arm cylindrical tension spring. Two of these gears make a simple reduction, according to i = ^Z output divided by ^Z drive. The reduction ratio is 1: 2. The third gear is only the change of direction and the attachment of a one-sided lever. Therefore, there is a gear ratio of i = 1: 1 between the second and the third gear. The drive gear I is seated, depending on the embodiment of the guide unit, whether it is located on an axle or shaft, on the side surface or on the shaft of the guide unit and is thus operatively connected to the guide unit. In any case, the guide unit is coupled to the drive element, which is designed here as a gear which executes the same speed as the guide unit. The drive gear transmits its speed to the meshing second driven gear. The second gear has half the number of teeth of the drive wheel, which corresponds to a reduction ratio of i = 1: 2. The second gear transmits its speed to the meshing third driven gear. The third gear has the same number of teeth as the second gear, whereby the overall reduction ratio remains the same. That is, once the guide unit rotates about its axis, the last driven gear has rotated twice in the same direction of rotation of the guide unit. At the last driven gear a unilateral lever arm is arranged. The lever arm rotates with the gear, whereby the lever arm also covers two revolutions, compared to one revolution of the guide unit. The length of the lever arm is tuned such that a machine element attached thereto, in the form of a technical spring, is elastically deformed by a calculated length, or can be pulled long. A spring is usually a metallic technical component that behaves sufficiently elastically in practical use. In the present case, a gas spring or a coil spring can be used. The gas spring is a pneumatic spring that uses high pressure gas to provide the spring force. The helical tension spring is a helically wound wire. All applications of the listed springs are based on their ability to store and release potential energy. Both types of springs can be used in the present subject of the invention. Preferably, a Schraubenzug- or gas spring in the 2a . 2 B shown and used in the further description, without limiting the types of springs in the invention. The path of deformation of the spring is thus dependent on the length of the lever arm to which the Schraubenzug- or gas spring is mounted. The helical tension spring is a cylindrical tension spring. Due to their shape changes, tension springs can store and release forces. The resulting spring force and the spring travel of the tension spring are adapted to the required torque in the guide unit via the wire diameter, the winding diameter, the number of spring windings and the length of the unloaded tension spring. The tension spring is loaded by pulling the ends apart. The force is applied via an eyelet at the spring end. The eyelet is articulated on the lever arm, wherein the lever arm pulls the tension spring apart. As a result, the mainspring absorbs energy and stores it until delivery. The other spring end is attached to the holding device. The stored energy is largely released when contracting the tension spring.

The operation of this inventive guide unit in the embodiment with vibration damping gear drive will now be explained with reference to sub-steps.

Step a) represents the initial situation. The transfer device is equipped with a unwound web material, starting from a storage device until the entry of a further processing machine. If the feeder of the processing machine is now operated, the web material will move in the feed direction. The displacement of the web material is in principle not along a plane, but over two large radii, which extend in opposite directions in the feed direction of the paths and the tracks. The web material practically overcomes a wave crest first and then passes through a wave trough. The wave crest is formed by the first radius r _{1 of} a guide unit which extends above the web material to be received by the stock means, while the wave crest is formed by the second radius r _{2 of} the guide rails. The guide rails adjoin the side facing away from the guide unit. The web material is thus first directed upwards to the facing side of the guide unit and then guided over the radius r ₁ formed by the guide unit, the web material abutting the bow length l _{b of} the guide unit. Following the formed by the guide unit radius r _1, the web material along the radius r ₁ is guided to the opposite running radius r ₂ of the curved guide rails.

So that the fold line of a web material just taken up also presses firmly against the clockwise rotating wing tip I and does not slip, a certain force F is required, which occurs through the web material applied over the radius r ₁ . The force F is taken from the weight and the rigidity, as well as the feed rate of the endless web material, whereby the guide unit has a certain torque. At the same time, the wing tip I of the guide unit engaging in engagement with the fold line is braked. The braking of the rotating guide unit and thus the guided over it web material, via the, connected to the guide unit vibration damping gear drive. The vibration-damping gear drive has access to the, moving in the feed direction web material on the engaging in the web material wing tip I. When receiving the web material on the guide unit, the tension spring of the gear drive is relaxed, since the two end points of the tension spring take the smallest possible distance from each other. The lever arm points vertically in the direction of the tension spring. The tension spring is in bottom dead center, in the relaxed state and contains no stored energy. With the tension spring released, a wing tip I of the two-sided lever arm is in the clockwise position between 6:00 and 3:00 pm, approximately at 4:30 pm. Between 15:00 and 16:30 is the receiving area of the web material, in which the wing tip I engages the fold line of a web material.

The 180 degrees opposite wing tip II, is at a relaxed tension spring at the same time in the bottom dead center of the mainspring clockwise between 12:00 and 09:00 clock, approximately at 10:30 clock. The web material generates in the region of the fold line a certain force F on the, the web material donating wing tip II and also generates a torque.

In step b), the guide unit rotates further to the left (counterclockwise). Accordingly, the lever arm of the gear drive has also rotated further to the left (counterclockwise). The elastic tension spring gradually deforms and spins as the lever arm rotates, thus absorbing energy which is dissipated upon transmission of the force F of the web material to the guide unit. Nevertheless, the torque M at the wing tip I remains relatively constant for the following reason. On the way of the wingtip I, which moves to the left and receives the web material, in the transport area from 4.30 pm to 1.30 pm, the distance between the wingtip and the central axis is extended, and then it shortens again, thus increasing the torque of the guide unit and then off again, although the web material moves at a constant radius r ₁ . The increase in the torque of the guide unit occurs when the wing tip I rotates 45 degrees and is in the range of the time between 16:30 and 15:00 clock, the receiving area of the web material. In this area, the tension spring is already tensioned continuously and absorbs energy from the guide unit. The decrease in the torque of the guide unit occurs when the wing tip I rotates another 45 degrees and is in the range of the time between 15:00 and 13:30 clock. Nevertheless, in this area, the mainspring continues to be continuously tensioned until it reaches its top dead center at 13:30. D. h., The wing tip I has in the range between 16:30 and 13:30 clock, 90 degrees on the radius r _{1 of} the guide unit through, while the lever arm of the gear drive in the same time zone already 180 degrees from bottom dead center to the top Dead center has covered.

The torque decrease of the guide unit in the clock range between 15:00 and 13:30 clock is the power in the exciting Tension spring in the gear drive against. If the wingtip I picking up the web material has made a 90 degree clockwise turn between 16:30 and 13:30, the wing tip I is at about 1:30 pm. The lever arm of the gear drive has, due to the reduction ratio, now made a 180 degree turn and now points perpendicular in the opposite direction of the tension spring. The tension spring is now at top dead center and in the maximum tensioned state, whereby the force F generated via the gear drive is now greatest in the tension spring. In the clock area at 13.30 the displacement distance a of the wing tip I to the central axis of the guide unit has now decreased and thus the torque of the guide unit has also reduced, although the web material has remained the same on the radius r _{1 of} the guide unit.

The wingtip II, which lies opposite the sheet material receiving wing tip I, is located in the delivery area of the web material and the lever arm of the gear drive is at top dead center of the mainspring and thus clockwise between 09:00 and 06:00, approximately 07:30. The web material generates a certain force F in the region of the fold line, which produces a torque in effect with the lever a. The torque is very low in the delivery of the web material to a guide rail by the decreasing lever a.

In step c) takes the, the web material receiving wing tip I, a further rotation by 90 degrees and is then in the clock area between 12:00 and 09:00 clock, approximately at 10:30 clock. Accordingly, the opposing wing tip II of the donor sheet has also rotated 90 degrees and is now in the clock area between 18:00 and 15:00, approximately at 16:30, in the receiving area of the web material. The lever arm of the gear drive has now, in the further 90 degrees of rotation of the wing tip I, again made a rotation of 180 degrees, whereby this is again in the bottom dead center of the mainspring. This means that when passing through the wing tip I in the clock area 13:30 to 12:00 (45 degrees), the torque of the guide unit decreases and goes to zero at about 12:00, because the displacement distance a goes to zero. From 12:00, the displacement distance a of the wing tip I increases again and thus the torque, while the, stored in the mainspring force F, is returned to the guide unit. The wing tip II is located in the receiving area of the web material.

In step d) takes the, the web material receiving wing tip I, a further rotation by 90 degrees and is then in the clock area between 09:00 and 06:00 clock, so in the delivery area of the web material, approximately at 07:30 clock. Accordingly, the opposing wing tip II of the donating web material has also rotated 90 degrees and is now clockwise between 15:00 and 12:00, that is in the transport area of the web material, approximately at 13:30. The lever arm of the gear drive has now again made a rotation of 180 degrees in the further 90 degrees rotation of the wing tip I, whereby this is again in the top dead center of the tension spring. The wing tip I turns from 07:30 to 16:30 clock, it goes through the idle area, because it does not convey any web material in this time range, while the wing tip II passes through the clock range from 13:30 to 10:30 and transported web material. In the same time range from 07:30 to 16:30 (angular range of 90 degrees) relaxes the tension spring and gives the stored force or restoring force to the gear on which the lever arm is attached and thus to the guide unit again and is about 16:30 in the bottom dead center. The lever arm points at 16:30 clock again perpendicular to the tension spring. The wing tips I and II have now completed a rotation of 360 degrees about the central axis of the guide unit and the process previously described under step a) to d) begins again.

Preferred embodiments and further developments emerge from the subclaims. The advantages and features will become apparent from the general description of the invention and the description of the embodiments and from the accompanying drawings.

The invention is therefore based on the idea to provide a cost-effective transfer device for conveying flat objects that are available, for example, as a web material available. It is flat sheet material, which is present as a fan-shaped folded endless corrugated board. Furthermore, an inventive guide unit is to be provided as an advantageous conveyor for flat web material, which can be integrated into the transfer device. A further advantageous embodiment of the invention is that the guide unit is equipped with a vibration-damping gear drive. The vibration-damping gear drive makes it possible to selectively extract energy from the guide unit and to redeploy it in a defined manner in order to optimize the transport of sheet material from provided storage devices to a further processing machine. For this purpose, a tension spring is available as having energy storage.

The invention is not limited to the illustrated and described embodiments, but also includes all, in the sense of Invention equally effective designs and means. Furthermore, the invention has hitherto not been limited to the feature combination defined in the independent claim, but may also be defined by any other combination of specific features of all the individual features disclosed overall. This means that in principle virtually every single feature of the independent claim can be omitted or replaced by at least one individual feature disclosed elsewhere in the application.

A concrete embodiment of the invention is shown in the drawings 1 , and 2 shown purely schematically and will be described in more detail below. Further details and embodiments of the invention can be taken from the following description and the drawings. It shows:

1 an inventive transfer device in perspective view with preferred side view right, and

2a a guide unit according to the invention in a perspective view with a preferred side view right, and

2 B a guide unit according to the invention in a perspective view with preferred gear drive.

The 1 shows a concrete embodiment of an inventive transfer device 1 in a perspective view with a preferred side view from the right. In principle, it is the transfer device 1 to a conveyor for flat, fan-shaped folded endless web materials 11.1 . 11.2 , The web materials 11.1 . 11.2 are preferably made of endless corrugated cardboard. The transfer device 1 includes a frame 2 , consisting of horizontal linkage 3.1 . 3.2 and vertical side panels 4 where the horizontal linkage 3.1 . 3.2 transverse to the feed direction 6 of the web material 11.1 . 11.2 extends and the vertical side panels 4 the carriers 12 of the frame 2 form. The horizontal linkage 3.1 . 3.2 are further carriers of at least one pair of guide rails 5.1 . 5.2 that are in the feed direction 6 extend parallel, wherein the pairs of guide rails 5.1 . 5.2 the web material 11.1 . 11.2 a guide 13 pretend. The guide rail pairs 5.1 . 5.2 are on the horizontal linkage 3.1 . 3.2 arranged laterally displaceable. Not just a pair of guide rails 5.1 . 5.2 can be moved sideways, but also the individual guide rails 5.11 . 5.12 the guide rail pairs 5.1 . 5.2 , Due to the lateral displacement of the individual guide rails 5.11 . 5.12 , is an adaptation to the width 14.1 . 14.2 of railway materials 11.1 . 11.2 possible. This can all widths 14.1 . 14.2 from, to storage facilities 10.1 . 10.2 provided web materials 11.1 . 11.2 along the tracks 15.1 . 15.2 be guided. Each pair of guide rails 5.1 . 5.2 has an inlet 7 and an outlet 8th for the feeding web material 11.1 . 11.2 on. The inlet 7 the guide rail pairs 5.1 . 5.2 takes that from a leadership unit 20.1 . 20.2 upcoming railway material 11.1 . 11.2 on and gives this at the outlet 8th to a processing machine 9 from.

The of the storage facilities 10.1 . 10.2 provided web materials 11.1 . 11.2 , before they get into the guide rail pairs 5.1 . 5.2 can be introduced via a leadership unit 20.1 . 20.2 be directed. Every leadership unit 20.1 . 20.2 is in a holding device 33.1 . 33.2 arranged. The holding device 33.1 . 33.2 turn is on the horizontal linkage 3.1 arranged. The leadership units 20.1 . 20.2 lead the web material 11.1 . 11.2 from the provided storage facilities 10.1 . 10.2 along a path 19.1 . 19.2 , to the inlet 7 the guide rail pairs 5.1 . 5.2 , wherein a guide unit 20.1 . 20.2 from a holding device 33.1 . 33.2 held so that they are on the horizontal linkage 3.1 is laterally displaceable. Both fixtures 33.1 . 33.2 with the integrated guide units 20.1 . 20.2 can thus be moved laterally. Due to the lateral displacement, the individual guide units 20.1 . 20.2 to the width 14.1 . 14.2 the railway materials 11.1 . 11.2 and at the distance 17 between two juxtaposed storage facilities 10.1 . 10.2 , customizable. The leadership units 20.1 . 20.2 can thus always be centered in the feed direction 6 to be transported web materials 11.1 . 11.2 be set. Due to the lateral adjustment of the holding devices 33.1 . 33.2 with the integrated guide units 20.1 . 20.2 , can all widths 14.1 . 14.2 from, to storage facilities 10.1 . 10.2 provided web materials 11.1 . 11.2 along the paths 19.1 . 19.2 be guided.

The in a holding device 33.1 . 33.2 arranged guide units 20.1 . 20.2 have a central axis 18.1 . 18.2 on, which is transverse to the feed direction 6 the railway materials 11.1 . 11.2 extends and around which a leadership unit 20.1 . 20.2 rotates. Such a rotatable guide unit 20.1 . 20.2 becomes as follows from the 2a . 2 B seen from a two-sided lever arm 21 that's about its axis 18.1 . 18.2 is rotatable, formed. A two-sided lever arm 21 consists of the individual lever arms a 21.1 and b 21.2 and can in the page profile 22 have an elliptical side surface. In the present embodiment of 1 and 2 becomes a side surface 23.1 . 23.2 from two, with its chord l _s adjoining circle sections 25.1 . 25.2 , educated.

The chord l _s of the circuit portions 25.1 . 25.2 a side surface thus formed 23.1 . 23.2 form a common axis of symmetry 24 and the two arc lengths l _b 26.1 . 26.2 the circle sections 25.1 . 25.2 form the outer contour 38 the two side surfaces 23.1 . 23.2 and thus the side profile 22 a two-sided lever arm 21 the leadership unit 20.1 . 20.2 , The side surfaces 23.1 . 23.2 are at their free pointed ends in each case by a cross strut 39.1 . 39.2 spaced apart in parallel, with a transverse strut 39.1 . 39.2 from a jetty 28.1 . 28.2 and a wing tip 29.1 . 29.2 is formed, as from the following 2 seen.

In the 2a is, in perspective view, a guide unit according to the invention 20.1 with holding device 33.1 from the 1 , with preferred side view right, shown. The in the 1 indicated reference numerals are taken here analogously. The following description of the guide unit 20.1 can also for the leadership unit 20.2 identical, because the leadership unit 20.2 , like in the 1 shown in the embodiment of the guide unit 20.1 equivalent.

The leadership unit 20.1 , consisting of a two-sided lever arm 21 that made two side profiles 22.1 . 22.2 , the two cross struts 39.1 . 39.2 and their axis 18.1 is formed in the fixture 33.1 stored. The side profiles 22.1 . 22.2 again consist of two side surfaces 23.1 . 23.2 , each side surface 23.1 . 23.2 from two circle sections 25.1 . 25.2 , each having an arc length l _b 26.1 . 26.2 have, is formed. The circle sections 25.1 . 25.2 with its arc length l _b 26.1 . 26.2 form the outer contour 38 the two-sided lever arm 21 , The outer contour 38 a leadership unit 20.1 . 20.2 , can between the parallel spaced side surfaces 23.1 . 23.2 be closed and thus a wing 27 form. Furthermore, the leadership unit 20.1 with a vibration-damping drive 40 fitted. The drive 40 can for the first and second leadership unit 20.1 . 20.2 from a gear drive I, II 40.1 . 40.2 consist. The gear drive I, II 40.1 . 40.2 acts on the first and second guide unit 20.1 . 20.2 , depending on the position of the Schraubenzug- or gas spring 45 , on the one hand, as a drive 34 and on the other hand as a brake 34 one. Acts the gear drive I, II 40.1 . 40.2 as a drive 34 , please refer 2 B , the web material becomes 11.1 . 11.2 in the feed direction 6 , in addition to being pulled in by the machine 9 , accelerated. Acts the gear drive I, II 40.1 . 40.2 as a brake 34 , the web material becomes 11.1 . 11.2 in the feed direction 6 braked. Both, the first leadership unit 20.1 and the first gear drive I 40.1 , are in the first fixture 33.1 arranged.

Now to the crossbar 39.1 . 39.2 a leadership unit 20.1 coming from a footbridge 28.1 . 28.2 and a wing tip 29.1 . 29.2 is formed, in each case a transverse strut 39.1 . 39.2 the two side surfaces 23.1 . 23.2 spaced. The length of a crossbar 39.1 . 39.2 makes the width 31 the leadership unit 20.1 , Every crossbar 39.1 . 39.2 between the side surfaces 23.1 . 23.2 is in the axial direction of the axis of symmetry 24 adjustable, because the side surfaces 23.1 . 23.2 and the footbridges 28.1 . 28.2 corresponding corresponding means 37 exhibit. Furthermore, the in the jetty 28.1 . 28.2 arranged wing tip 29.1 . 29.2 replaceable as wear element. The two wing tips 29.1 . 29.2 form at one revolution of the guide unit 20.1 . 20.2 or with one revolution of the two-sided lever arm 21 the diameter 30 a circle with a given radius r. The diameter 30 a circle is thus dependent on the length 32 the side surfaces or the length of the axis of symmetry 24 , The distance of the wing tips 29.1 . 29.2 in a leadership unit 20.1 is on the one hand by the length 32 the chord l _s determines which one on the symmetry axis 24 runs and on the other hand by the angular distance of the two wing tips 29.1 . 29.2 of 180 degrees.

The length of a normal embodiment of a wing tip 29.1 . 29.2 corresponds to the width 31 a leadership unit 20.1 , as shown here. In another embodiment, the length of the embodiment may be a wing tip 29.1 . 29.2 across the width 31 a leadership unit 20.1 go out to the leadership unit 20.1 a wider web material 11.1 . 11.2 adapt.

The cross struts 39.1 . 39.2 a leadership unit 20.1 are spaced by an angular distance of 180 degrees and the intermediate outer contour 38 , which are along the feed direction 6 extends is determined by the arc length l _b 26.1 . 26.2 a circle section 25.1 . 25.2 certainly. The arc length l _b 26.1 . 26.2 a leadership unit 20.1 corresponds to the length distance 35 two adjacent fold lines 36.1 . 36.2 in a web material 11.1 . 11.2 , please refer 1 ,

According to the 2 B is a perspective view, an inventive drive 40 a leadership unit 20.1 with holding device 33.1 from the 1 , in a preferred side view right, shown. The in the 1 and 2a indicated reference numerals are taken here analogously. The following description of the drive 40 for a first guide unit 20.1 , also for the drive 40 the second guide unit 20.2 identical, because the second Guide unit 20.2 , like in the 1 shown, the execution of the first guide unit 20.1 equivalent.

Every leadership unit 20.1 . 20.2 is with a vibration-damping gear drive 40.1 . 40.2 fitted. A gearwheel drive 40.1 consists of three successively meshing gears I, II, III 41 . 42 . 43 , a one-sided lever arm 44 and a Schraubenzug- or gas spring 45 ,

One of the three gears 41 . 42 . 43 located on the shaft (central axis 18.1 ) of the leadership unit 20.1 , This is the guide unit 20.1 coupled with the drive element, here as the drive gear I 41 is formed and the same speed as the guide unit 20.1 having. The drive gear I 41 transmits its speed to the meshing second driven gear II 42 , The second gear II 42 forms a reduction gear II 42 because the second gear II 42 only half the number of teeth of the drive wheel I 41 having. The reduction gear II 42 transmits its double speed to the meshing third driven gear III 43 , The third gear III 43 forms a driven gear 43 and has the same number of teeth as the second reduction gear II 42 , The output gear III 43 on the one hand serves the direction of rotation and on the other hand is on the output gear III 43 a one-sided lever arm 44 arranged. The one-sided lever arm 44 turns with the output gear III 43 , whereby the one-sided lever arm 44 also two revolutions with respect to one revolution of the first guide unit 20.1 performs. The direction of rotation change is necessary, so that the one-sided lever arm 44 the same direction of rotation as the first guide unit 20.1 performs. On the lever arm 44 is a machine element, preferably a Schraubenzug- or gas spring 45 arranged. The one end 46 the screw tension or gas spring 45 is rotatably mounted. The other end 47 the screw tension or gas spring 45 is on the fixture 33.1 attached. The operation of the gearwheel drive 40.1 and the coil tension or gas spring 45 has already been shown in the previous description. Depending on the position of the lever arm 44 and thus the Schraubenzug- or gas spring 45 this acts as a drive or as a brake on the gear drive 40.1 one.

When carrying a web material 11.1 . 11.2 along a path 19.1 . 19.2 with the aid of the guide unit according to the invention 20.1 . 20.2 with her wing tip 29.1 . 29.2 in a fold line 36.1 . 36.2 engages, the acting lever changes a 49 and thus also the torque M changes. The change of the acting lever a 49 occurs due to left-handed rotation 51 the impeller 50 or the two-sided lever arm 21 on. Is the impeller 50 in the horizontal position, the acting lever is a 49 the biggest. In the assumed view of a levorotatory impeller 50 Although the radius r remains constant, but the lever acting a 49 to the fulcrum becomes lower, because the impeller 50 turns from the horizontal to the vertical position, with the wing tip 29.1 . 29.2 then it is vertical. In the vertical position the acting lever is a 49 the smallest. Upon further rotation of the impeller 50 the acting lever takes a 49 back up to the point where the wing tip 29.1 . 29.2 the fold line 36.1 . 36.2 in the web material 11.1 leaves. The, at the wingtip 29.1 . 29.2 the lever arm a 21.1 and on the lever arm b 21.2 attacking force F 48 always causes a twist of the impeller 50 and a path change of the acting lever a 49 ,

LIST OF REFERENCE NUMBERS

1

Transfer device

2

frame

3.1

horizontal linkage

3.2

horizontal linkage

4

Vertical side panels

5.1

Pair of guide rails

5.11

Guide rail (v. 5.1 )

5.12

Guide rail (v. 5.1 )

5.2

Pair of guide rails

6

feed direction

7

Inlet (v. 5.1 . 5.2 )

8th

Outlet (v. 5.1 . 5.2 )

9

machine

10.1

stocker

10.2

stocker

11.1

Web material (v. 10.1 )

11.2

Web material (v. 10.2 )

12

Carrier (v. 2 )

13

guide

14.1

Width (v. 11.1 )

14.2

Width (v. 11.2 )

15.1

Railway I (v. 11.1 )

15.2

Railway II (v. 11.2 )

16.1

Longitudinal edge (v. 11.1 )

16.2

Longitudinal edge (v. 11.2 )

17

Distance (between 10.1 u. 10.2 )

18.1

Axis (v. 20 )

18.2

Axis (v. 20 )

19.1

Path (v. 11.1 )

19.2

Path (v. 11.2 )

20.1

Guide unit

20.2

Guide unit

21

two-sided lever arm

21.1

Lever arm a

21.2

Lever arm b

22.1

side profile

22.2

side profile

23.1

side surface

23.2

side surface

24

Symmetry axis (= l _s )

25.1

circular section

25.2

circular section

26.1

Arc length l _b

26.2

Arc length l _b

27

wing

28.1

web

28.2

web

29.1

pinion

29.2

pinion

30

diameter

31

Width (v. 20 )

32

Length (v. 21 )

33.1

holder

33.2

holder

34

Drive / brake

35

Distance (between 36.1 u. 36.2 )

36.1

Fold line (v. 11.1 )

36.2

Fold line (v. 11.1 )

37

medium

38

outer contour

39.1

crossmember

39.2

crossmember

40

drive

40.1

Gear drive I (v. 20.1 )

40.2

Gear drive II (v. 20.2 )

41

Drive gear I

42

Reduction gear II

43

Output gear III

44

one-sided lever arm

45

Schraubenzug- / gas spring

46

End (v. 45 )

47

End (v. 45 )

48

Tensile force F

49

acting lever a

50

impeller

51

left-handed rotation

l _s

tendon

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 1687225 B1 [0004]

Claims (11)

Transfer device ( 1 ) for conveying starting material, preferably web material ( 11.1 . 11.2 ), which is based on storage facilities ( 10.1 . 10.2 ) and to a further processing machine ( 9 ), includes: - a framework ( 2 ) of horizontal ( 3.1 . 3.2 ) and vertical linkage ( 4 ), the horizontal linkages ( 3.1 . 3.2 ) transversely to the feed direction ( 6 ) of the web material ( 11.1 . 11.2 ) and the vertical linkages ( 4 ) the carriers ( 12 ) of the frame ( 2 ), - at least one pair of guide rails ( 5.1 . 5.2 ), which are in the feed direction ( 6 ) extend in parallel and that on a horizontal linkage ( 3.1 . 3.2 ) releasably arranged, laterally displaceable and thus to the width ( 14.1 . 14.2 ) of the web materials ( 11.1 . 11.2 ) are adaptable, whereby a pair of guide rails ( 5.1 . 5.2 ) an inlet ( 7 ) and an outlet ( 8th ) for the feeding web material ( 11.1 . 11.2 ), - at least one guide unit ( 20.1 . 20.2 ) mounted on the horizontal linkage ( 3.1 ) is arranged and suitable, the web material ( 11.1 . 11.2 ) along a path ( 19.1 . 19.2 ), whereby a management unit ( 20.1 . 20.2 ) in a holding device ( 33.1 . 33.2 ) mounted on the horizontal linkage ( 3.1 . 3.2 ) is laterally displaceable and wherein the guide unit ( 20.1 . 20.2 ) and around one, transversely to the feed direction ( 6 ) extending axis ( 18.1 . 18.2 ), characterized in that a guide unit ( 20.1 . 20.2 ) from a two-sided lever arm ( 21.1 . 21.2 ) around its axis ( 18.1 . 18.2 ) is rotatable, is formed and in the side profile ( 22 ) has an elliptical side surface or of two, with their chord l _s adjoining circular sections ( 25.1 . 25.2 ) formed side surface ( 23.1 . 23.2 ), whereby the two tendons of the circular sections ( 25.1 . 25.2 ) has a common axis of symmetry ( 24 ) and the two arc lengths ( 26.1 . 26.2 ) the outer contour ( 38 ) of the two side surfaces ( 23.1 . 23.2 ) and the side surfaces ( 23.1 . 23.2 ) at their free ends in each case by a transverse strut ( 39.1 . 39.2 ) are spaced parallel, with a transverse strut ( 39.1 . 39.2 ) from a footbridge ( 28.1 . 28.2 ) and a wing tip ( 29.1 . 29.2 ) and that the management unit ( 20.1 . 20.2 ) with a drive ( 40 ) Is provided. Transfer device ( 1 ) according to claim 1, characterized in that each transverse strut ( 39.1 . 39.2 ) between the side surfaces ( 23.1 . 23.2 ) in the axial direction of the axis of symmetry ( 24 ) is adjustable because the side surfaces ( 23.1 . 23.2 ) and the webs ( 28.1 . 28.2 ) corresponding means ( 37 ) and that each web ( 28.1 . 28.2 ) one wing tip each ( 29.1 . 29.2 ) contains. Transfer device ( 1 ) according to one of claims 1 to 2, characterized in that the transverse struts ( 39.1 . 39.2 ) a management unit ( 20 ) are spaced by an angular distance of 180 degrees and that the intermediate outer contour ( 38 ), which along the feed direction ( 6 ), through the arc length ( 26.1 . 26.2 ) of a circle section ( 25.1 . 25.2 ) is determined. Transfer device ( 1 ) According to claim 1, characterized in that the arc length ( 26.1 . 26.2 ) a management unit ( 20 ) the longitudinal distance between two adjacent fold lines ( 36.1 . 36.2 ) in a web material ( 11.1 . 11.2 ) corresponds. Transfer device ( 1 ) according to one of claims 1 to 5, characterized in that the guide unit ( 20 ) with a vibration-damping drive ( 40 ) is trained. Transfer device ( 1 ) according to claim 5, characterized in that the vibration-damped drive ( 40 ) from a gear drive ( 40 ) is formed, which consists of three successively meshing gears ( 41 . 42 . 43 ), a one-sided lever arm ( 44 ) attached to one of the gears ( 43 ) and one, on the lever arm ( 44 ) hinged spring ( 45 ), consists. Transfer device ( 1 ) according to claim 6, characterized in that the spring ( 45 ) consists of a cylindrical helical spring or a gas spring. Transfer device ( 1 ) according to claim 6, characterized in that the gear drive ( 40.1 . 40.2 ) depending on the position of the tension spring ( 45 ) as a drive unit ( 34 ) or as a brake ( 34 ) acts. Transfer device ( 1 ) according to one of claims 5 to 8, characterized in that the gear drive ( 40.1 . 40.2 ) and the tension spring ( 45 ) on the holder device ( 33.1 . 33.2 ) are arranged. Transfer device ( 1 ) according to one of claims 6 to 9, characterized in that the one end ( 46 ) of the tension spring ( 45 ) with the lever arm ( 44 ) around the gear III ( 43 ) turns. Transfer device ( 1 ) According to one of claims 6 to 10, characterized in that the tension spring ( 45 ) in the relaxed state with the, perpendicular to the mainspring ( 45 ) pointing lever arm ( 44 ), has a bottom dead center and the tension spring ( 45 ) in the tensioned state with the, perpendicular to the tension spring ( 45 ) opposite pointing lever arm ( 44 ), has a top dead center.

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